EP2897769A1 - Breaker for excavators with optimized hydraulic circuit - Google Patents
Breaker for excavators with optimized hydraulic circuitInfo
- Publication number
- EP2897769A1 EP2897769A1 EP13801778.5A EP13801778A EP2897769A1 EP 2897769 A1 EP2897769 A1 EP 2897769A1 EP 13801778 A EP13801778 A EP 13801778A EP 2897769 A1 EP2897769 A1 EP 2897769A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- breaker
- thrust chamber
- active
- diameter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000007788 liquid Substances 0.000 claims abstract description 19
- 238000006073 displacement reaction Methods 0.000 claims description 18
- 239000012528 membrane Substances 0.000 claims description 4
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 239000002184 metal Substances 0.000 claims 2
- 208000028659 discharge Diseases 0.000 description 15
- 239000000463 material Substances 0.000 description 8
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000003534 oscillatory effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000008207 working material Substances 0.000 description 1
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
- B25D9/06—Means for driving the impulse member
- B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
-
- 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
- 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
- B25D9/18—Valve arrangements therefor involving a piston-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
- B25D9/16—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
- B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
- B25D9/265—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof with arrangements for automatic stopping when the tool is lifted from the working face or suffers excessive bore resistance
-
- 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 present invention relates to a breaker for excavators with optimized hydraulic circuit
- the principal function of the accumulator (14) is to accumulate oil in the passive step (when the piston goes from PMI to PMS) in order to return it in active step when the flow rate needed in the thrust chamber (11) is greater than the one provided at the inlet (13) of the breaker.
- (11) acts on the upper surface (151) of a piston (15) which transmits the force exerted by the oil to the tool (16) which is used to break.
- a distributor (17) is concentric with respect to the piston (15). The distributor is needed to put the active thrust chamber (11) alternately in communication with both the portion under low pressure of the circuit (18) connected to the return under low pressure of the oil, and with the inlet under high pressure (13) .
- the thrust chamber (11) is separated from the portion under low pressure (18) of the hydraulic circuit of the distributor (17).
- a passive thrust chamber (20) connected to the oil supply under pressure through a series of ducts (21) .
- ducts (21) Only for illustration, in figure 1 it is shown only one duct which connects the passive thrust chamber to the supplying circuit, but it is also possible to use different configurations, for example three ducts arranged at 120°.
- the system is such that, in that position, the piston (15) leaves free the lower portion of the distributor (17).. Since the lower portion of the distributor (17) is greater than the upper one, the resultant of the forces acting on the distributor is such that it is moved upwards. In its vertical movement the distributor (17) closes first the high pressure gap and than leaves free the discharge gap of the active thrust chamber (11), thus disconnecting the active thrust chamber (11) from the high pressure circuit and connecting it to the low pressure one. In this way, the new resultant of the forces acting on the piston (15) is such that it is thrust upwards and it is put again in the starting position, reestablishing the cycle as well.
- the bypass (19) serves when the distributor, while going down, closes the discharge gap.
- the piston (15) acts on a tool (16) used to break the material being worked.
- the tool (16) is provided with a groove (163) whose ends (161, 162) define the maximum axial amplitude possible allowed by the tool.
- a tool-stopper (25) integral with the breaker (1), which limits the axial amplitude allowed by the tool (16).
- the breakers for excavators known at the state of the art have many drawbacks, among which the fact that the described functioning is independent of the fact that the bit of the tool (16) is actually working material or not. This is a problem since the force as a whole exerted by the pressure of the liquid provided in the active thrust chamber (11) on the piston (15) and so on the tool (16), which should serve to break the material being worked, when the bit idles is discharged on the tool- stopper (25) , thus subjecting it to high stresses which can lead shortly to deformation of the same and so to expensive machine-stop times.
- step of the cycle when the thrust chamber is put under pressure by the oil of the circuit under high pressure, pushing the piston downwards to strike the tool, it is needed to guarantee that the chamber is under pressure for the whole active step notwithstanding the expansion due to the piston going down.
- the hydraulic circuit of the breaker is such that it guarantees, once the conditions of flow rate and supplying pressure determined by the excavator on which the breaker is mounted are fixed, the passage of the flow rate needed to fill the volume of the thrust chamber constantly.
- a hammer of 200 kg according to the present invention uses flow rates between 40-45 1/min .
- aim of the present invention is to provide a piston with optimized geometry to increase the mass of the same piston in case of equal breaker dimension.
- the present invention provides a breaker for excavators which solves the problems of the state of the art, and in particular which is provided with a system which allows to disconnect automatically the tool from the high pressure circuit when not actually working on the material to be destroyed.
- the breaker object of the present invention aims at providing a hydraulic circuit optimized to guarantee a correct functioning of the breaker with low oil flow rates.
- the invention realizes the prefixed aims since it is a hydraulic breaker for excavator comprising a configuration such that it can slide alternatively, inside said breaker under the thrust of a hydraulic liquid contained in a circuit comprising at least a first thrust chamber, said active, and a second thrust chamber, said passive, characterized in that the piston is provided, at the active thrust chamber, with a projection with diameter (C) smaller than the diameter (A) of the thrust chamber, said projection being contained in the active thrust chamber as a whole, and having, preferably, an axial extension equal to at least half diameter of said thrust chamber.
- the invention provides a breaker for excavator with a by-pass system to avoid idle working.
- Said bypass system comprises a bypass between the high pressure portion and the low pressure portion of the hydraulic circuit, configured such that, in the normal working conditions (so with a resistance provided by the tool by the material being worked) the bypass is closed by the piston. Without resistance provided by the material being worked to the tool, the tool (and so the piston) is subject to a greater axial amplitude. In this case the bypass is freed and the high pressure circuit is put in communication through the bypass gap with the low pressure circuit. In this way, inside the breaker there is only low pressure, the piston is blocked in its position at P I and cannot go up again any more. The breaker stops functioning. When the operator positions the breaker against the material to be worked again, the bypass is closed and the normal functioning, previously described, is reestablished .
- Figure 1 shows an embodiment of a breaker known at the state of the art, and whose functioning was described at the beginning.
- Figure 2 shows a preferred embodiment of the breaker according to the present invention.
- Figure 3 shows a detail of the embodiment of the discharge gaps according to another preferred embodiment of the breaker according to the present invention.
- Figure 4 shows a detail of an embodiment of the discharge gaps according to the known state of the art .
- Figure 5 shows a detail of the discharge bypass comprised in the breaker according to the present invention
- Figure 6 shows a detail of the oil supplying system of a preferred embodiment of the breaker according to the present invention.
- Figure 7 shows a graph with the flow of the pressure in the thrust chamber and of the discharge pressure during the typical cycle of a breaker known at the state of the art
- Figure 8 shows a preferred embodiment of the piston according to the present invention.
- Figure 9 shows the piston shown in figure 8 mounted inside a breaker according to the present invention.
- Figure 10 and figure 11 show two embodiments of breakers for excavators known at the state of the art, described in EP1964647 and US4281587.
- the piston (15) according to the present invention is symmetrically shaped around an axis (150) and is provided with three diameter discontinuities which define four different diameter sections (A, B, C, D) .
- the discontinuity between the greater diameter section (B) and the smaller diameter section (D), when the piston (15) is mounted in the breaker (1) as it is shown in figures 2, 9, 5 faces the passive thrust chamber (20) .
- the circular crown deriving from the discontinuity defines the surface on which the pressure of the liquid present in the thrust chamber (20) acts in axial direction.
- the section with diameter (A) which in the piston according to the present invention is smaller than the diameter (B) , is in the active thrust chamber and defines the thrust surface in axial direction of the liquid under pressure.
- Another diameter section (C) said diameter (C) being smaller than the diameter of the active thrust surface (A) allows to occupy at least partially the volume of the active thrust chamber, increasing the mass of the piston in case of equal dimensions of the breaker (1) and piston displacement .
- the piston is provided with a projection at the active thrust chamber.
- the projection which is actually a piston section with smaller diameter of the active thrust chamber diameter, is extended beyond the upper limit of the active thrust chamber.
- the liquid under pressure acts on a surface having circular crown shape defined outside by the diameter of the active thrust chamber and inside by the diameter of the projection.
- the piston is provided with a projection with diameter (C) smaller than the diameter (A) of the thrust chamber. Said projection, contrary to what happens in the embodiments of the state of the art, is contained as a whole in the active thrust chamber.
- the liquid under pressure can act on a circular surface defined by the diameter (A) of the thrust chamber (increasing the force exerted at equal pressure) , but the reduction in piston mass is limited at the minimum.
- the axial extension of the projection is equal to at least the half of the diameter of the thrust chamber.
- this measure increases the force exerted by the piston (15) on the tool (16) .
- the presence of the projection with diameter (C) by reducing the volume of the active thrust chamber (11) when the piston is around its upper dead point and the gap under high pressure is freed, allows a more rapid pressurization of the active thrust chamber ( 11 ) .
- the breaker for excavator comprises a piston (15), which acts on the tool (16) according to what described at the beginning.
- the high pressure supplying circuit of the breaker comprises an inlet (13) connected with the active thrust chamber (11), and through the duct (21), with the passive thrust chamber (20) .
- the supplying circuit is also provided with an annular groove (22) communicating with the high pressure circuit.
- the shape of the piston (15) according to the present invention is such that the side surface of the piston is provided with some diameter discontinuities and in particular the piston in the upper portion has a diameter (A) W smaller than the cylinder in which it slides, so that it is created a recess between the piston (15), the cylinder and the reduction bushing (24) arranged between the piston and the cylinder, where it is obtained the duct (23) .
- the diameter (B) of the piston (15) is such that the piston (15) slides in the seat obtained in the body of the breaker (1) , and at the same time that the sealing with respect to the. bypass is obtained, comprising the annular groove (22) or a series of holes provided in radial direction on the inner surface of the sliding seat of the piston.
- the groove is not communicating with other ducts other than the supplying duct (21) .
- the annular groove (22) can be substituted by one or more holes provided in radial direction, or by ducts of other shape, as long as they are useful to the aim.
- the portion of the piston with smaller diameter (A) is at the annular groove (22) .
- the annular groove (22) communicates, through the duct (23) , with the return under low pressure of the oil (18) .
- the just described breaker can be modified as better described in the following.
- the variations with respect to the known state of the art aim at reducing the piston displacement in case of equal force exerted, at optimizing the ratio between the accumulator volume and the piston displacement, in addition to the layout of the high and low pressure circuits in order to reduce the charge loss and at the same to avoid pressure peaks.
- the piston displacement of a breaker is given by the upper surface of the piston, i.e. the surface of the active thrust chamber, for its stroke.
- the piston (15) is provided with a diameter of active thrust smaller than the one of passive thrust (A ⁇ B) . It is particularly useful to act on the diameter instead on the stroke to reduce the piston displacement, because, since the piston displacement is proportional to the diameter squared, to intervene on the diameter has a greater action than to intervene on the stroke. Reducing the diameter of the active thrust chamber, and maintaining however unaltered the mass of the piston (15), since this one determines the kinetic energy for the breaking, it is needed to increase the diameter of the piston
- the increase in length can be in fact disadvantageous for dimension reasons and also because too thin pistons are not apt to transmit the striking energy to the tool, which has dimensions more or less fixed for commercial reasons.
- the piston has a diameter about the same as the tool, but never lower, in order to maximize the striking energy transmission. Therefore, the variations of diameter of the piston allow the interface with the tool to be maintained unvaried optimized to transmit the . striking energy, without modifying the tools and without increasing the axial dimensions of the breaker. This allows also to use yet existing tools for breakers known at the state of the art with pistons with the same weight.
- a fundamental element for the breaker performance is the accumulator. It has to be able to provide in active step the needed flow rate to pressurize the active thrust chamber, but it is important to make so that the variation between the maximum and minimum pressure is the lowest possible W so that the membrane is not stressed and to stabilize the functioning range of the breaker, thus avoiding too high pressure variations which have effect on the oil pump functioning.
- the greater the pressure under which the circuit works the lower the flow rate supplied by the oil supplying pump. For this reason, it is ideal to work with a constant supplying pressure during all the cycle.
- the breaker according to the present invention even reducing the piston displacement of the breaker with respect to what known at the state of the art at equal force exerted by the breaker, there have been maintained accumulators with volumes similar to those traditionally used on breakers known at the state of the art.
- the ratio between the volume of the accumulator and the hammer piston displacement according to the present invention is preferably between 10 and 14, contrary to what known at the state of the art, in which such ratio is lower than 10.
- the ratio between the area of the inlet gap and piston displacement is greater than 1.5E-02m ⁇ 1 .
- the low pressure circuit of the breaker according to the present invention is modified with respect to the known state of the art.
- the low pressure circuit is in fact connected to the high circuit through the ratio of the active and passive thrust areas of the piston.
- passive step the piston is subject to the action of two forces acting in vertical direction. The first, which brings it again upwards is given by the product of the high pressure for the passive thrust chamber.
- the other force is given by the product of the pressure in the active thrust chamber, which in this step is connected with the low pressure portion of the hydraulic circuit, for the active thrust area. Since the active thrust area is greater than the passive one, it follows that in order to make the piston go up again from PMI to
- the high pressure cannot be lower than a minimum value, in function of the ratio of the two areas multiplied for the pressure in the thrust chamber in this step.
- the active thrust chamber is in connection with the high pressure.
- the distributor begins to go up and closes the high pressure. From now on until the moment in which it opens the discharge gaps there are generally 4-6 mm of stroke in which the distributor goes up and all the gaps are closed.
- the thrust chamber is better pressurized and so it reaches final higher
- the low pressure circuit of the breaker according to the present invention eliminates the annular chamber around the piston. Referring to the figure 3, while the distributor goes down from PMS to PMI, the oil is first discharged through the primary discharge gap (50) and when this is closed through the secondary one (40) .
- the secondary gap (40) is normally closed by -the piston, but during the active step, while the piston goes down, at a certain point, the secondary gap is freed and put in communication with an annular chamber (42) obtained in the piston which in turn is in communication with the discharge.
- the oil reaches the discharge passing through a chamber
- the secondary discharge gap (40) is directly in connection with the discharge, through an annular compensation chamber (41) obtained in the body of the breaker and not in the piston.
- the compensation chambers are aimed at attenuating possible pressure peaks when the distributor begins again its going up. In this step, in fact, until the distributor does not close the high pressure gap, the low circuit is in communication with the high one through the secondary discharge gap. This step is very short ( ⁇ 1 ms) , but it can be created a pressure peak in the low circuit.
- the compensation chambers serve to attenuate such peak.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Automation & Control Theory (AREA)
- Percussive Tools And Related Accessories (AREA)
- Fluid-Pressure Circuits (AREA)
- Earth Drilling (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT000055A ITBA20120055A1 (en) | 2012-09-24 | 2012-09-24 | SHOCK EXTRACTOR WITH PISTON AND OPTIMIZED HYDRAULIC CIRCUIT |
PCT/IB2013/058811 WO2014045264A1 (en) | 2012-09-24 | 2013-09-24 | Breaker for excavators with optimized hydraulic circuit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2897769A1 true EP2897769A1 (en) | 2015-07-29 |
EP2897769B1 EP2897769B1 (en) | 2021-10-20 |
Family
ID=47045071
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13801778.5A Active EP2897769B1 (en) | 2012-09-24 | 2013-09-24 | Breaker for excavators with optimized hydraulic circuit |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2897769B1 (en) |
ES (1) | ES2904312T3 (en) |
IT (1) | ITBA20120055A1 (en) |
WO (1) | WO2014045264A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4345216A1 (en) * | 2022-09-27 | 2024-04-03 | Tecna Group Srl | Breaker with optimized hydraulic circuit |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES469097A1 (en) | 1978-03-31 | 1980-06-16 | Crespo Jose T G | Hydraulic apparatus for producing impacts |
JPS5517791U (en) * | 1978-07-21 | 1980-02-04 | ||
DE3400302A1 (en) * | 1984-01-03 | 1985-08-29 | Mannesmann AG, 4000 Düsseldorf | HYDRAULIC ACTUATOR |
JPS62163593U (en) * | 1986-04-07 | 1987-10-17 | ||
ES2103711T3 (en) * | 1989-10-18 | 1997-10-01 | Mauro Vitulano | METHOD FOR AUTOMATICALLY ADJUSTING THE FUNCTIONAL PARAMETERS OF A PERCUSSION HYDRAULIC DEVICE. |
JP3672978B2 (en) * | 1995-09-14 | 2005-07-20 | 古河機械金属株式会社 | Hydraulic striking mechanism |
WO1999005363A1 (en) * | 1997-07-23 | 1999-02-04 | Hydroacoustics, Inc. | Vibratory pavement breaker |
US6155353A (en) * | 1999-07-23 | 2000-12-05 | Ottestad; Jack B. | Impact tool |
FI20010976A (en) * | 2001-05-09 | 2002-11-10 | Sandvik Tamrock Oy | Method of impact control cycle and impactor |
FI121978B (en) * | 2009-12-21 | 2011-06-30 | Sandvik Mining & Constr Oy | Method for determining the degree of use of a refractive hammer, refractive hammer and measuring device |
US8939227B2 (en) * | 2010-12-23 | 2015-01-27 | Caterpillar Inc. | Pressure protection valve for hydraulic tool |
-
2012
- 2012-09-24 IT IT000055A patent/ITBA20120055A1/en unknown
-
2013
- 2013-09-24 EP EP13801778.5A patent/EP2897769B1/en active Active
- 2013-09-24 ES ES13801778T patent/ES2904312T3/en active Active
- 2013-09-24 WO PCT/IB2013/058811 patent/WO2014045264A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2014045264A1 * |
Also Published As
Publication number | Publication date |
---|---|
ES2904312T3 (en) | 2022-04-04 |
EP2897769B1 (en) | 2021-10-20 |
ITBA20120055A1 (en) | 2014-03-25 |
WO2014045264A1 (en) | 2014-03-27 |
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