EP2834544A1 - Load holding valve - Google Patents
Load holding valveInfo
- Publication number
- EP2834544A1 EP2834544A1 EP13723239.3A EP13723239A EP2834544A1 EP 2834544 A1 EP2834544 A1 EP 2834544A1 EP 13723239 A EP13723239 A EP 13723239A EP 2834544 A1 EP2834544 A1 EP 2834544A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- piston
- seat
- opening
- pressurized fluid
- 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
Classifications
-
- 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
Definitions
- the invention relates to a load-holding valve traversed by a pressurized fluid.
- the load-holding valves are piloted valves that are typically employed in the field of the earthmoving machines. These valves are arranged for holding suspended loads being also very heavy, such as, for example, an excavator articulated arm, as well as for keeping the above-mentioned loads suspended in a desired position for a preset time interval.
- valves are fed and traversed by a pressurized fluid, which is sent to an actuator, generally a double-action hydraulic piston, which in turn is connected to the arm to be supported.
- actuator generally a double-action hydraulic piston
- the known valves comprise a main channel, extending longitudinally along a valve body, inside which various known components - among which a piston and a seat are received, both being longitudinally movable - arranged to permit or prevent the passage of said pressurized fluid as a function of their mutual arrangement.
- a plurality of openings is obtained in the valve body, each of which is in communication with the main channel through a respective duct, and it is arranged to permit said pressurized fluid entering in or exiting from the valve. Therefore, the known valves comprise a first opening and a second opening through which, in a lifting step of the load, the pressurized fluid respectively enters the valve body and exits from the latter to reach the actuator. On the contrary, in a lowering step of the load, the pressurized fluid enters the valve through the second opening and exits the valve through the first opening.
- piloting step further pressurized fluid is delivered into the valve body through a piloting opening, which further pressurized fluid acts on the piston and pushes it in such a position as to permit the above-mentioned fluid flow from the second opening to the first opening.
- a thrust force further acts, which is exerted by the pressurized fluid flow entering the valve through the second opening.
- the piloting force exerted on the piston by the further pressurized fluid is concordant with the above-mentioned thrust force, so that both the above-mentioned forces are able to overcome an elastic force that is opposite them and that is exerted by a spring on the piston.
- a further object is to provide a load-holding valve in which it is possible to compensate for pressure increases of the fluid entering the valve to avoid corresponding speed increases during the lowering of the suspended load.
- a load-holding valve as defined in claim 1 is provided.
- the invention will be able to be better understood and implemented with reference to the appended drawings, which show an exemplary, non-limiting embodiment thereof, in which:
- Figs. 1-3 show a piloted valve 1 in a first operative configuration K .(Figs. 1 and 3) and in a second operative configuration J (Fig. 2).
- the valve 1 comprises a body 2 provided with a plurality of openings through which the pressurized fluid can enter, or exit from, the valve 1. Therefore, these openings enable the valve 1 to be connected to a hydraulic circuit of a machine (not shown), for example, an earthmoving machine.
- a first opening 3, a piloting opening 4, and a second opening 5 are visible, the function of which will be explained in detail herein below.
- the first opening 3 is connected to the cavity 8 by means of a first channel 3 a
- the piloting opening 4 is connected to the cavity 8 by means of a piloting channel 4a
- the second opening 5 is connected to the cavity 8 by means of a second channel 5a.
- the latter is a through channel connecting two opposite walls of the body 2, and it is closed - on an opposite side to the second opening 5 - by a safety valve 10, the function of which will be explained in more detail herein below.
- the piloting channel 4a comprises a first portion 4b, which is orthogonal to the axis A, and a second portion 4c, communicating with the first portion 4b and leading into the cavity 8.
- the first portion 4b may comprise a dowel 6 arranged for being traversed by the pressurized fluid.
- a second sealing member 20 is arranged, for example, an "O-ring" in polymeric material, which enables the cavity 8 to be sealingly closed.
- the containing element 16 is provided with an internal end 21 , on which a plurality of passages is made.
- the passages are shaped as half-circular recesses, and they are obtained in sequence on an end edge of the end 21, which is shaped as a hollow cylinder.
- the valve 1 further comprises a piston 30, extending in a substantially parallel manner to the first longitudinal axis A and being received inside the cavity 8.
- the approximately cylindrical piston 30 is bidirectionally movable according to the directions indicated by the arrows X and Y, parallel to the axis A.
- the piston 30 comprises a head portion 32, which is enclosed inside the containing element 16, an intermediate portion 33, and an end portion 34.
- the intermediate portion 33 has a transversal dimension that is less than the head portion 32 and the end portion 34.
- a connecting portion 52 is interposed, arranged near the end 21, and comprising a first zone 52a and a second zone 52b, both having an approximately frusto-conical shape (Fig. 3).
- first zone 52a and the second zone 52b can be shaped in a different manner, while maintaining a transverse dimension greater than the adjacent head portion 32 and intermediate portion 33.
- a spring 41 is housed, acting on a centering member 42 pressing on the piston 30, particularly on a bottom wall of the head portion 32.
- the centering member 42 is substantially conical-shaped, i.e., it is shapingly coupled with the above-mentioned bottom wall, and it ensures that the elastic force FEL exerted by the spring 41 on the piston 30 is balanced, i.e., substantially directed along the axis A.
- the spring 41 is pre-loaded, and it is kept compressed by a thrust member 43, which is fixed to the internal side wall of the containing element 16 by a threaded coupling 67. On the thrust member 43, a plug 44 is screwed, by acting on which an operator can adjust the spring 41 preload.
- An annular seat 23 is made in the external wall 22b, in which a second sealing member 24 (Fig. 3) is housed, which enables the passage of the pressurized fluid to be prevented outside the seat 22.
- the seat 22 surrounds the piston 30, particularly near the second zone 52b and the part of intermediate portion 33 contiguous thereto. Therefore, according to the position of the piston 30, the latter can completely occlude, or not, a passage zone A s for the pressurized fluid, which is interposed between the seat 22 and the piston 30. More precisely, the passage zone A s is overall defined by the seat 22 and the piston 30 when the second zone 52b does not contact, i.e., it is spaced apart from, the internal wall 22a of the seat 22, thus enabling the passage of the pressurized fluid from the second channel 5a towards the first channel 3a. On the contrary, when the second zone 52b contacts the internal walls of the seat 22, the passage zone A s is absent, and the passage of the pressurized fluid from the second channel 5a towards the first channel 3a is prevented.
- the movable seat 22 is bidirectionally movable according to the directions X and Y, parallel to the axis A.
- the movable seat 22 is moved along the direction Y by the pressurized fluid and it is moved along the direction X owing to the presence of a spring 25, arranged inside the movable seat 22 and acting on the latter.
- the spring 25 can be arranged outside the movable seat 22.
- the end portion 34 of the piston 30 is received in a portion of the cavity 8 having substantially the same radial dimension.
- the end portion 34 has a maximum transverse dimension D P and comprises a piloting face 37 (Fig. 2).
- the end portion 34 further comprises an annular face 47, which is frustoconical- shaped.
- the annular face 47 is opposite the piloting face 37 and it faces the intermediate portion 33.
- the end portion 34 abuts on a shoulder 60 (shown in Fig. 2) of the cavity 8 and the connecting portion 52 contacts the seat 22.
- a groove is made, which acts as a seat for a third sealing member 35, for example, an O-ring.
- the first part 30a is first positioned by inserting the head portion 32 inside the containing element 16, then the movable seat 22 and the spring 25 are positioned, finally the second part 30b is positioned, which is screwed to the first part 30a.
- the safety valve 10 of a known type, is a maximum pressure valve detecting the fluid pressure in the second channel 5a (i.e., of the fluid arriving near to the intermediate zone 33) and it opens if the above-mentioned pressure exceeds a predetermined threshold value.
- a predetermined threshold value is a value set by the used acting on adjustment means with which the safety valve 10 is provided, and it can be equal to 350 bars.
- the safety valve 10 opens, and a portion of the above-mentioned fluid enters the connection channel 26 to subsequently reach the piloting channel 4a. In the latter, the above-mentioned portion of the fluid traverses the dowel 6, with consequent pressure drop in the fluid.
- the piloting step is not controlled by the operator, but it is automatically started by the valve 1 owing to the presence of the safety valve 10.
- valve 1 The operation of the valve 1 is described herein below, with particular reference to the case in which the latter is comprised in an earthmoving machine.
- the pressurized fluid for example an oil provided with suitable chemical-physical characteristics, enters the valve 1 through the first opening 3 communicating with the cavity 8 through the first channel 3 a.
- the pressurized fluid traverses the passage zone As and it can flow, inside the movable seat 22, towards the second channel 5a.
- the fluid exits the body 2 and moves towards actuating means (not illustrated), which is comprised in the machine and which, in this manner, is actuated to lift the load.
- valve 1 When the load has to be lowered, the valve 1 is initially in the first operative configuration K and the pressurized fluid exiting from the actuating means enters the valve 1 through the second opening 5. The flow of this fluid causes the movable seat 22 to move in the direction X until abutting on the end 21 of the containing element 16 (Fig. 2).
- the piston 30 moves inwards the containing element 16, so that the connecting portion 52 does not abut anymore on the end 21 of the containing element 16.
- the passage zone As is defined, and the half-circular passages made in the end 21 are not closed by the connecting portion 52 anymore.
- the pressurized fluid entering from the second opening 5 can thus traversing the passage zone A s and the above-mentioned half-circular passages - after flowing in the second channel 5a and a portion of the first cavity 8 (inside the seat 22) - to exit subsequently the body 2 of the valve 1 through the first opening 3.
- the further pressurized fluid is no more supplied to the piloting opening 4.
- Fig. 3 the elastic force F E L, the thrust force Fs, and the piloting force Fp, are shown, all of which being substantially parallel to the longitudinal axis A.
- the elastic force FE L and the thrust force Fs are concordant and push the piston 30 in the direction Y, while the piloting force F P , opposite the other two, pushes the piston 30 in the direction X.
- the thrust force Fs opposes the piloting force F P .
- the pressurized fluid entering the second channel 5a is distributed in the valve 1 so that it acts on both the annular face 47 of the end portion 34, and on a portion 46 of the frusto-conical second zone 52b positioned inside the seat 22 when the valve 1 is in the operative configuration K (Fig. 3), i.e., when the connecting portion 52 contacts the seat 22.
- the area of the annular face 47 is greater than the area of the portion 46, and therefore the resulting thrust force F s is directed so as to oppose the piloting force Fp.
- the valve 1 closure is ensured by the thrust force Fs that continues to oppose the piloting force Fp (an effect that cannot be obtained in the known valves).
- the piston 30 can move in the direction Y so as to contact the movable seat 22 and to stop the lowering of the suspended load.
- this orientation of the thrust force Fs avoids that, when there are very high pressures of the fluid entering the valve from the actuating means (which typically occurs when the suspended load is very inclined), the load moves very quickly.
- the valve 1 is able to adjust the flow rate of the pressurized fluid entering the valve 1 through the second opening 5a and exiting the valve 1 through the first opening 3a, i.e., during the lowering step of the suspended load.
- a load-holding valve 1 is provided in which it is possible to compensate for pressure increases of the fluid entering the valve from the actuating means (through the second channel 5a) to avoid corresponding speed increases during the lowering of the suspended load. This is achieved owing to the orientation of the force Fs that tends to push the piston 30 in the direction Y, so as to avoid that the passage zone As becomes excessively large, so as to adjust the flow rate of pressurized fluid entering the valve through the second opening 5 a and exiting the valve through the first opening 3 a.
- This adjustment of the fluid flow rate is automatically performed by the valve 1, as described above, and it is therefore an accurate and reliable adjustment of the fluid flow rate.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT000087A ITMO20120087A1 (en) | 2012-04-02 | 2012-04-02 | LOAD DISPLACEMENT VALVE |
PCT/IB2013/052542 WO2013150431A1 (en) | 2012-04-02 | 2013-03-29 | Load holding valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2834544A1 true EP2834544A1 (en) | 2015-02-11 |
EP2834544B1 EP2834544B1 (en) | 2016-05-25 |
Family
ID=46022542
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13723239.3A Active EP2834544B1 (en) | 2012-04-02 | 2013-03-29 | Load holding valve |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2834544B1 (en) |
IT (1) | ITMO20120087A1 (en) |
WO (1) | WO2013150431A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2016070450A (en) * | 2014-10-01 | 2016-05-09 | ナブテスコ株式会社 | Hydraulic valve |
CN110748518B (en) * | 2019-11-05 | 2021-04-06 | 山东金利液压科技有限公司 | Excavator load keeps valve |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006250239A (en) * | 2005-03-10 | 2006-09-21 | Kawasaki Precision Machinery Ltd | Seat block and valve device |
DE102008002539A1 (en) * | 2008-06-19 | 2009-12-24 | Robert Bosch Gmbh | Control valve for a vehicle brake system and corresponding vehicle brake system |
-
2012
- 2012-04-02 IT IT000087A patent/ITMO20120087A1/en unknown
-
2013
- 2013-03-29 EP EP13723239.3A patent/EP2834544B1/en active Active
- 2013-03-29 WO PCT/IB2013/052542 patent/WO2013150431A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2013150431A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2013150431A1 (en) | 2013-10-10 |
ITMO20120087A1 (en) | 2013-10-03 |
EP2834544B1 (en) | 2016-05-25 |
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