EP0085279B1 - Directional control valve to obtain in a hydraulic appliance the alternative motion of a piston operating to charge and fire a tool, specially suitable for hydraulic hammers - Google Patents
Directional control valve to obtain in a hydraulic appliance the alternative motion of a piston operating to charge and fire a tool, specially suitable for hydraulic hammers Download PDFInfo
- Publication number
- EP0085279B1 EP0085279B1 EP82830014A EP82830014A EP0085279B1 EP 0085279 B1 EP0085279 B1 EP 0085279B1 EP 82830014 A EP82830014 A EP 82830014A EP 82830014 A EP82830014 A EP 82830014A EP 0085279 B1 EP0085279 B1 EP 0085279B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- sleeve
- control valve
- fluid
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000012530 fluid Substances 0.000 claims abstract description 42
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 10
- 239000007789 gas Substances 0.000 claims description 5
- 229910052757 nitrogen Inorganic materials 0.000 claims description 5
- 238000012423 maintenance Methods 0.000 abstract description 2
- 238000004519 manufacturing process Methods 0.000 abstract 1
- 238000009527 percussion Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/14—Control devices for the reciprocating piston
- B25D9/16—Valve arrangements therefor
- B25D9/20—Valve arrangements therefor involving a tubular-type slide valve
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/14—Control devices for the reciprocating piston
- B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D2209/002—Pressure accumulators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D2209/005—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously having a tubular-slide valve, which is coaxial with the piston
Definitions
- the invention relates to a directional control valve, that is a device making use of a sleeve valve to supply or return incompressible fluid from a cylinder, e.g. of a hydraulic hammer, in which a piston operating to charge and fire a tool has to be effected to an alternate motion.
- a directional control valve that is a device making use of a sleeve valve to supply or return incompressible fluid from a cylinder, e.g. of a hydraulic hammer, in which a piston operating to charge and fire a tool has to be effected to an alternate motion.
- a cylindrical control valve i.e. a sleeve coaxial to the cylinder in which the piston moves.
- control valves as well as being subjected to continuous and strong stresses, need complex circuits for oil discharge, little working tolerances and frontal fluid tight joints that may fail owing to abnormal wear caused by repeated impacts.
- the mobile member that is the sleeve is really struck by the same piston which acts as a shoulder, and elastic devices, as spring cushions, don't minimize the stresses the control valve is subjected to.
- a directional control valve of a hydraulically operated percussion device in which a sleeve-like shaped valve member responsive to the movements of the piston is contained in a pressure chamber for alternately connecting said chamber to a channel system including a high pressure and low pressure branch for conducting hydraulic pressure fluid to and from said pressure chamber.
- the invention solves the problem of how to design a double acting directional control valve for hydraulically operated percussion devices, in which the stresses transmitted to the piston by the tool in operation subjected to an alternate motion, are not taken by the valve device, thereby averting any risk of damage to the mobile distributing valve element in the form of a sleeve-shaped slide element.
- the invention solves also the problem relative to cutting the maintenance costs of the hydraulically operated percussion devices with a control system less complex, and therefore manufactured at a lower cost because of its simplicity.
- control valve includes a cylindrical sleeve-shaped distribution valve member 5, positioned in same cylindrical chamber 1 in which the piston moves.
- the sleeve-shaped element (1) has an outwardly directed flange means 6 forming an annular rim 5a that strikes against face 1b of annular groove 1a forming an annular chamber in the wall of the cylindrical chamber 1, limiting the stroke of the sleeve element 5.
- This cylindrical chamber 1 having a diameter D 1 is coaxially connected to the cylindrical chamber 2A having a diameter D 4 inferior to D 1 , through annular groove 3 having a diameter D 3 greater than D 1 , but smaller than the diameter D 2 of the above groove 1a in order to form a second circular shoulder 4 for limiting the stroke of the sleeve 5 itself in the other direction and submit to a greater thrust the rim 5a having an area higher than the area of the opposite rim 5b of the sleeve-shaped element 5.
- the sleeve-shaped element works so that it can permit the moving up of piston 7 which has two different diameters D 7 (A) and (C) D 8 , where D 7 is greater than D 8 , to compress a gas (e.g. nitrogen) contained in a hermetic compression chamber 11.
- a gas e.g. nitrogen
- Piston upstroke and downstroke speed are respectively related with pump delivery capacity and with expansion speed of gas compressed in the chamber 11.
- the sleeve-shaped element 5 surrounds the section A of piston 7 that enters in the chamber 1 forming a fluid tight fit.
- the piston sleeve shaped element 5 surrounds the head B of piston 7 that enters in the high-pressure chamber 1 instead of the section A.
- the inlet ports of high-pressure channel 8 are opened while the outlet ports of low-pressure channel 9 are closed by the sleeve-shaped element 5.
- the piston moves down although high-pressure hydraulic fluid via channel 12 acts at the same time on the rim 7a of piston; infact, area A1 of rim 7a is smaller than area 7b of piston.
- section B of the piston allows the flow of high-pressure fluid to the annular chamber 3 so that the fluid itself can press on circular surface 5a of the sleeve which, being larger than the circular surface 5b, causes a resultant thrust which moves up the sleeve until to close the ports of high-pressure channel 8 and to open the outlet ports to low-pressure channel 9. This causes the upward movement of piston 7 only because of the thrust of the hydraulic fluid on the annular surface 7a of the piston (Fig. 7).
- Sleeve 5 moves down again to open the inlet ports of high-pressure channel 8 and to permit the repeating of a new cycle.
- the sleeve 5 moves down to open the inlet ports of the fluid, the sleeve forces the fluid which is in the annular space formed under the surface 5a into little duct 15 and then via the annular recess formed by section 7d of piston 7, in the low-pressure duct 16.
- the appliance is equipped with a pneumatic accumulator 11 a of nitrogen with a diaphragm 18 and with a sequence and velocity controlling valve 17, which exploiting the pressure decrease taking place on the beginning of recharging stroke for the higher hydraulic flow required by the recharge of accumulator 11a, at first closes and after throttles the outlet port of the low-pressure duct 10, in order to reduce the moving up velocity of the piston.
- the piston impact is damped by the compressed fluid in the upper part of chamber 1 and being part A of piston diametrically greater than the B one to make as a shoulder, by rim 13 formed in the cylindrical chamber 2A and by the fluid contained in the same cylindrical chamber 2A.
- the fluid-tight of inlet and outlet ports is, infact, made by the lateral outside surfaces 5e of the sleeve and 6b of flange 6 of the same sleeve.
- the sleeve element 5 acts as a cylinder for piston 7, moving coaxially to it in the opposite direction, thus avoiding frontal impacts against piston 7 and consequently stresses in the sleeve element.
- the fluid-tight seal of the inlet and outlet ports is made only by the sleeve like element5 and is independent from the piston wear.
Landscapes
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Valve Device For Special Equipments (AREA)
- Percussive Tools And Related Accessories (AREA)
- Fluid-Driven Valves (AREA)
Abstract
Description
- The invention relates to a directional control valve, that is a device making use of a sleeve valve to supply or return incompressible fluid from a cylinder, e.g. of a hydraulic hammer, in which a piston operating to charge and fire a tool has to be effected to an alternate motion. There is a large number of directional control valves for hydraulic appliances, using a cylindrical control valve, i.e. a sleeve coaxial to the cylinder in which the piston moves.
- This, actuated by the hydraulic fluid alternately, opens and closes the supply and return ports for the hydraulic fluid, so that the fluid can be alternately forced on the upper or lower face of the same piston to fire it or to force it back (recharge).
- These control valves, as well as being subjected to continuous and strong stresses, need complex circuits for oil discharge, little working tolerances and frontal fluid tight joints that may fail owing to abnormal wear caused by repeated impacts.
- In some directional control valves, the mobile member that is the sleeve, is really struck by the same piston which acts as a shoulder, and elastic devices, as spring cushions, don't minimize the stresses the control valve is subjected to.
- From US-A-4022108 a directional control valve of a hydraulically operated percussion device is known in which a sleeve-like shaped valve member responsive to the movements of the piston is contained in a pressure chamber for alternately connecting said chamber to a channel system including a high pressure and low pressure branch for conducting hydraulic pressure fluid to and from said pressure chamber.
- The invention here claimed is intended to remedy these drawbacks.
- The invention solves the problem of how to design a double acting directional control valve for hydraulically operated percussion devices, in which the stresses transmitted to the piston by the tool in operation subjected to an alternate motion, are not taken by the valve device, thereby averting any risk of damage to the mobile distributing valve element in the form of a sleeve-shaped slide element.
- The invention solves also the problem relative to cutting the maintenance costs of the hydraulically operated percussion devices with a control system less complex, and therefore manufactured at a lower cost because of its simplicity. Two ways to carry out the invention are described in detail below with reference to the drawings in which:
- Fig. 1a, is a detailed longitudinal section of a first embodiment the central valve with the sleeve-shaped distribution member closing the exhaust ports.
- Fig. 1, shows the device applied to hammers with piston actuated by impact energy of free nitrogen compressed by the same piston during the recharging stroke, with piston in recharging stroke;
- Fig. 2 shows the device in the same recharging stroke of the piston, moving down to close the hydraulic fluid supply port and to open the exhaust port;
- Fig. 3 shows the device with piston on top dead center, closing the hydraulic fluid supply port;
- Fig. 4 shows the device closing the supply port and piston in striking phase;
- Fig. 5 shows a second embodiment of the device applied to a hydraulic hammer with piston actuated directly by the fluid under pressure and accumulator of nitrogen to balance pressure variations, with piston in striking phase;
- Fig. 6 shows the operation of the control valve to close the supply ports of fluid under pressure;
- Fig. 7 shows the device while the piston is in recharging stroke, i.e. sleeve valve member opening the exhaust ports;
- Fig. 8 the device with the piston making a fluid tight seal with sleeve valve member of control valve to cause the opening of the supply port of the hydraulic fluid under pressure.
- Referring to Fig. 1 a, the control valve includes a cylindrical sleeve-shaped
distribution valve member 5, positioned in samecylindrical chamber 1 in which the piston moves. - Along one edge, the sleeve-shaped element (1) has an outwardly directed flange means 6 forming an
annular rim 5a that strikes againstface 1b of annular groove 1a forming an annular chamber in the wall of thecylindrical chamber 1, limiting the stroke of thesleeve element 5. Thiscylindrical chamber 1 having a diameter D1, is coaxially connected to thecylindrical chamber 2A having a diameter D4 inferior to D1, throughannular groove 3 having a diameter D3 greater than D1, but smaller than the diameter D2 of the above groove 1a in order to form a secondcircular shoulder 4 for limiting the stroke of thesleeve 5 itself in the other direction and submit to a greater thrust therim 5a having an area higher than the area of theopposite rim 5b of the sleeve-shaped element 5. - In the first application of the invention (Fig. 1, 2, 3, 4), in the recharge phase, (Fig. 1) the sleeve-shaped element works so that it can permit the moving up of
piston 7 which has two different diameters D7 (A) and (C) D8, where D7 is greater than D8, to compress a gas (e.g. nitrogen) contained in ahermetic compression chamber 11. This is possible thanks to the sleeve-shaped element which opens inlet port ofchannel 8 in the samecylindrical chamber 1 and permits the application of a pressure (p1) of hydraulic fluid onannular face 7a of area A1 of the piston causing a thrust Si=Ai . p l. - In the second phase (Fig. 2), the piston has reached almost top dead center as fixed by the
shoulder 13, thereby compressing the gas contained in thechamber 11 up to the maximum pressure P2 inferior to pi because of thethrust 51 and of the area C1 of the surface 7b greater than area A1. Meanwhile, the sleeve-shaped element 5 is forced to move down by hydraulic fluid flowing in theannular groove 3, which can press againstannular surface 5a ofelement 5, thereby causing a thrust higher than the one the same hydraulic fluid produces onopposite surface 5b of smaller area. - The inlet port of
channel 8 is thus closed andoutlet channel 9 is opened (see Fig. 3). - At this point as the thrust of high-pressure fluid on the
annular surface 7a ofpiston 7 stops and as thecylindrical chamber 1 is connected withoutlet channel 9 and 10 (Fig. 3), thepiston 7, not being forced by back pressure moves down violently striking atool 14 at a speed higher than the upstroke speed. - Piston upstroke and downstroke speed are respectively related with pump delivery capacity and with expansion speed of gas compressed in the
chamber 11. - The sleeve-
shaped element 5 surrounds the section A ofpiston 7 that enters in thechamber 1 forming a fluid tight fit. - The reversal of sliding of sleeve-
shaped element 5 to open the inlet port ofchannel 8 takes place every time the circular edge 7c of the section A ofpiston 7 makes a fluid tight seal with thecircular edge 7d of the sleeve-shaped element. - At this point, infact, the compression of hydraulic fluid remaining in the
chamber 1 by same piston, produces a thrust on the sleeve-surface 5b; because thesleeve element 5 is opposed by no back pressure, it moves thereby opening the inlet port of high-pressure channel and closing the ports ofchannel 9, so that the piston can move up pushed by the pressure of fluid on theannular surface 7a. - In the application of the control valve to the percussion apparatus shown in Fig. 5, 6, 7 and 8, the piston sleeve shaped
element 5 surrounds the head B ofpiston 7 that enters in the high-pressure chamber 1 instead of the section A. In the impact stroke (Fig. 5), the inlet ports of high-pressure channel 8 are opened while the outlet ports of low-pressure channel 9 are closed by the sleeve-shaped element 5. The piston moves down although high-pressure hydraulic fluid viachannel 12 acts at the same time on therim 7a of piston; infact, area A1 ofrim 7a is smaller than area 7b of piston. Referring to Fig. 6, whilepiston 7 moves down, section B of the piston allows the flow of high-pressure fluid to theannular chamber 3 so that the fluid itself can press oncircular surface 5a of the sleeve which, being larger than thecircular surface 5b, causes a resultant thrust which moves up the sleeve until to close the ports of high-pressure channel 8 and to open the outlet ports to low-pressure channel 9. This causes the upward movement ofpiston 7 only because of the thrust of the hydraulic fluid on theannular surface 7a of the piston (Fig. 7). - Referring to Fig. 8, when the circular edge 7c of
piston 7 comes into contact withcircular edge 5d of the sleeve making a fluid tight seal, thepiston 7 presses the hydraulic fluid remaining inchamber 1 thus causing a pressure on thecircular surface 5b of the sleeve itself, which is not opposed by back pressure. -
Sleeve 5 moves down again to open the inlet ports of high-pressure channel 8 and to permit the repeating of a new cycle. - As the
sleeve 5 moves down to open the inlet ports of the fluid, the sleeve forces the fluid which is in the annular space formed under thesurface 5a intolittle duct 15 and then via the annular recess formed bysection 7d ofpiston 7, in the low-pressure duct 16. - To increase the impact velocity, i.e. the kinetic energy of
piston 7, and for better exploitation of the capacity of the hydraulic pump, in this directional control valve according to this invention, the appliance is equipped with apneumatic accumulator 11 a of nitrogen with adiaphragm 18 and with a sequence andvelocity controlling valve 17, which exploiting the pressure decrease taking place on the beginning of recharging stroke for the higher hydraulic flow required by the recharge ofaccumulator 11a, at first closes and after throttles the outlet port of the low-pressure duct 10, in order to reduce the moving up velocity of the piston. - After recharging the accumulator, when the pressure of hydraulic fluid reaches the maximum value, the reaction of the
spring 17a is insufficient to oppose the thrust given by thelittle piston 17b and therefore theoutlet 17c of the valve is opened. - On the top dead centre, the piston impact is damped by the compressed fluid in the upper part of
chamber 1 and being part A of piston diametrically greater than the B one to make as a shoulder, byrim 13 formed in thecylindrical chamber 2A and by the fluid contained in the samecylindrical chamber 2A. - As detailed above, the fluid-tightsurfaces of the sleeve like
element 5 are very large. - The fluid-tight of inlet and outlet ports is, infact, made by the lateral outside surfaces 5e of the sleeve and 6b of flange 6 of the same sleeve.
- It should be noted that before the piston reaches its top dead centre, the
sleeve element 5 acts as a cylinder forpiston 7, moving coaxially to it in the opposite direction, thus avoiding frontal impacts againstpiston 7 and consequently stresses in the sleeve element. - Moreover, in the control valve according to the invention the fluid-tight seal of the inlet and outlet ports is made only by the sleeve like element5 and is independent from the piston wear.
Claims (4)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP82830014A EP0085279B1 (en) | 1982-01-22 | 1982-01-22 | Directional control valve to obtain in a hydraulic appliance the alternative motion of a piston operating to charge and fire a tool, specially suitable for hydraulic hammers |
AT82830014T ATE20647T1 (en) | 1982-01-22 | 1982-01-22 | CONTROL VALVE FOR THE RECIPROCATING PISTON OF A HYDRAULIC IMPACT DEVICE, ESPECIALLY FOR A HYDRAULIC HAMMER. |
DE8282830014T DE3271910D1 (en) | 1982-01-22 | 1982-01-22 | Directional control valve to obtain in a hydraulic appliance the alternative motion of a piston operating to charge and fire a tool, specially suitable for hydraulic hammers |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP82830014A EP0085279B1 (en) | 1982-01-22 | 1982-01-22 | Directional control valve to obtain in a hydraulic appliance the alternative motion of a piston operating to charge and fire a tool, specially suitable for hydraulic hammers |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0085279A1 EP0085279A1 (en) | 1983-08-10 |
EP0085279B1 true EP0085279B1 (en) | 1986-07-09 |
Family
ID=8190099
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP82830014A Expired EP0085279B1 (en) | 1982-01-22 | 1982-01-22 | Directional control valve to obtain in a hydraulic appliance the alternative motion of a piston operating to charge and fire a tool, specially suitable for hydraulic hammers |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0085279B1 (en) |
AT (1) | ATE20647T1 (en) |
DE (1) | DE3271910D1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2618092B1 (en) * | 1987-07-17 | 1989-11-10 | Montabert Ets | HYDRAULIC DISTRIBUTOR FOR A PERCUSSION APPARATUS MOUSED BY AN INCOMPRESSIBLE PRESSURE FLUID |
ES2103711T3 (en) * | 1989-10-18 | 1997-10-01 | Mauro Vitulano | METHOD FOR AUTOMATICALLY ADJUSTING THE FUNCTIONAL PARAMETERS OF A PERCUSSION HYDRAULIC DEVICE. |
SE9100092D0 (en) * | 1991-01-11 | 1991-01-11 | Aquapact Ab | HYDRAULIC PUMP DRILLER |
FR2676953B1 (en) * | 1991-05-30 | 1993-08-20 | Montabert Ets | HYDRAULIC PERCUSSION APPARATUS. |
JP3378029B2 (en) * | 1991-08-08 | 2003-02-17 | 丸善工業株式会社 | Hydraulic breaker |
FI104959B (en) | 1994-06-23 | 2000-05-15 | Sandvik Tamrock Oy | Hydraulic impact hammer |
FI107891B (en) * | 1998-03-30 | 2001-10-31 | Sandvik Tamrock Oy | Impact fluid driven impactor |
IT1312140B1 (en) * | 1999-06-22 | 2002-04-09 | Priver Ind Srl | PERCUSSION HYDRAULIC MACHINE OF INNOVATIVE CONCEPTION WORKING WITH CONSTANT HYDRAULIC PRESSURE. |
CN107524419B (en) * | 2017-09-22 | 2023-07-07 | 中国石油天然气集团有限公司 | Hydraulic jar |
US11027403B2 (en) * | 2018-06-18 | 2021-06-08 | Caterpillar Inc. | Hydraulic hammer |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1431835A (en) * | 1965-01-28 | 1966-03-18 | Montabert Ets | Percussion device |
US3766830A (en) * | 1971-03-24 | 1973-10-23 | Montabert Roger | Percussion apparatus |
FI50307C (en) * | 1974-04-20 | 1976-02-10 | Xandor Ag | Hydraulically operated impactor |
ZA763554B (en) * | 1976-05-03 | 1977-09-28 | Hydroacoustic Inc | Impact tools |
US4231434A (en) * | 1978-02-21 | 1980-11-04 | Justus Edgar J | Hydraulic impact device |
-
1982
- 1982-01-22 AT AT82830014T patent/ATE20647T1/en not_active IP Right Cessation
- 1982-01-22 EP EP82830014A patent/EP0085279B1/en not_active Expired
- 1982-01-22 DE DE8282830014T patent/DE3271910D1/en not_active Expired
Also Published As
Publication number | Publication date |
---|---|
ATE20647T1 (en) | 1986-07-15 |
EP0085279A1 (en) | 1983-08-10 |
DE3271910D1 (en) | 1986-08-14 |
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