EP3051147A1 - Flow control valve - Google Patents
Flow control valve Download PDFInfo
- Publication number
- EP3051147A1 EP3051147A1 EP16152676.9A EP16152676A EP3051147A1 EP 3051147 A1 EP3051147 A1 EP 3051147A1 EP 16152676 A EP16152676 A EP 16152676A EP 3051147 A1 EP3051147 A1 EP 3051147A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spool
- opening
- flow control
- control valve
- bore
- 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
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- 239000012530 fluid Substances 0.000 claims abstract description 43
- 238000005192 partition Methods 0.000 claims description 50
- 238000004891 communication Methods 0.000 claims description 11
- 230000002093 peripheral effect Effects 0.000 claims description 10
- 230000004913 activation Effects 0.000 claims description 4
- 230000009849 deactivation Effects 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims description 2
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000000717 retained effect Effects 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000670 limiting effect Effects 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
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
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/022—Flow-dividers; Priority valves
-
- 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
- F15B2013/008—Throttling member profiles
Definitions
- the valve body has a first port connected to a source of hydraulic fluid (serving alternatively as an inlet and an outlet port) and a pair of second ports connected to a hydraulic device and through which hydraulic fluid can flow in one direction or in the reverse one.
- a source of hydraulic fluid serving alternatively as an inlet and an outlet port
- second ports connected to a hydraulic device and through which hydraulic fluid can flow in one direction or in the reverse one.
- Each of the subsidiary spools has a partition wall with an orifice formed therein and a passage therethrough adapted to selectively register with one passage of each of two pairs of passages formed in the main spool and one formed in the valve body.
- the flow control valve When the flow control valve operates in dividing mode, the flow of hydraulic fluid introduced in the first port flows inside the main spool where it is divided into two streams into each subsidiary spool. As the fluid passes through the orifice formed in the partition wall of said subsidiary spool, the resistance offered by the orifices to the fluid flow causes the subsidiary spools to move away from each other. The hydraulic fluid flows through the passage provided in the subsidiary spool and then in through the passages provided in the main spool to be discharged through the second ports of the valve body.
- the object of the present invention is to avoid the previously mentioned drawbacks.
- the first port 21 ends in an annular groove 23 provided on the inside face of the bore 20.
- each of said second ports 22 is axially positioned between the first port 21 and one end of the valve body 2.
- Said second ports 22 extend along longitudinal axis Y1-Y'1 and Y2-Y'2 respectively, parallel to the axis Y-Y'.
- each cover 25 is provided with a recess 250 on its inner face, i.e. the face facing the bore 20.
- the passageway inside the outer spool 3 is referenced 30.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Multiple-Way Valves (AREA)
Abstract
- a valve body (2, 2', 2") having a first longitudinally extending bore (20),
- an outer spool (3) slidably positioned within said bore (20), said outer spool (3) having an axially extending passageway (30) therethrough,
- a pair of axially extending inner spools (4) slidably positioned within said passageway (30),
said valve body (2, 2', 2") having a first port (21) and a pair of second ports (22),
said outer spool (3) having at least a first opening (34) communicating with the first port (21) and with the passageway (30), and at least two pairs (350) of second openings therethrough.
Description
- The invention relates to the technical field of the flow control valves and more particularly to a flow control valve capable of serving as a flow-dividing and flow-combining valve for the synchronous operation of hydraulic devices or equipments.
- A flow control valve serving alternatively as a flow-dividing valve and as a flow-combining valve is already known from
US 3 554 213 . - This flow control valve comprises a valve body which has a longitudinally extending bore for receiving therein a longitudinally extending main spool, for sliding motion. A coil spring urges the main spool to be positioned in the centre of the bore in said valve body.
- Two subsidiary spools are disposed in end-to-end relation in an axially extending passageway provided in said main spool for sliding motion relative to each other.
- The valve body has a first port connected to a source of hydraulic fluid (serving alternatively as an inlet and an outlet port) and a pair of second ports connected to a hydraulic device and through which hydraulic fluid can flow in one direction or in the reverse one.
- Each of the subsidiary spools has a partition wall with an orifice formed therein and a passage therethrough adapted to selectively register with one passage of each of two pairs of passages formed in the main spool and one formed in the valve body.
- When the flow control valve operates in dividing mode, the flow of hydraulic fluid introduced in the first port flows inside the main spool where it is divided into two streams into each subsidiary spool. As the fluid passes through the orifice formed in the partition wall of said subsidiary spool, the resistance offered by the orifices to the fluid flow causes the subsidiary spools to move away from each other. The hydraulic fluid flows through the passage provided in the subsidiary spool and then in through the passages provided in the main spool to be discharged through the second ports of the valve body.
- In case the pressures in the two second ports are not equal then the main spool will move to the right or to the left till the pressures inside the two subsidiary spools are equalized. Then the main spool will come back to its central position.
- When the flow control valve operates in combining mode, the flow of hydraulic fluid introduced in the two second ports are combined inside the passageway of the main spool before to be discharged through the first port of the valve body. In this case, the two subsidiary spools move towards each other.
- Again, in case the pressures in the two second ports are not equal then the main spool will move to the right or to the left. The movement of the main spool (for example the rightward movement), gradually reduces the degree of opening of the right passage of the left pair of passages provided in the main spool and increases the difference of pressure between the left second port and the fluid chamber of the left subsidiary spool. This results in a reduction of pressure of fluid inside the left subsidiary spool. When the pressure of hydraulic fluid introduced into the fluid chamber of the left subsidiary spool through the left port is lower than the pressure of hydraulic fluid introduced into the fluid chamber of the right subsidiary spool through the right port, then the main spool will move to the left.
- The rightward and leftward movements of the main spool are alternatively repeated rapidly to maintain the main spool in the normal central position.
- However, such kind of flow control valve, in combining mode and for high fluid flow rate has the disadvantage to be less accurate because of the oscillations of the main spool.
- Further, theoretically the pressure drop through the orifices provided in each partition wall of said subsidiary spools should be independent from main spool axial position. Nevertheless, because of high turbulent flow, this is not always true.
- Accordingly, the object of the present invention is to avoid the previously mentioned drawbacks.
- Thus, the invention relates to a flow control valve adapted for use as a flow-dividing and flow-combining valve in hydraulic devices, comprising:
- a valve body having a longitudinally extending bore therethrough,
- an outer spool slidably positioned within said bore, said outer spool having an axially extending passageway therethrough,
- return means which tend permanently to position said outer spool centrally in the longitudinal direction of said bore,
- a pair of axially extending inner spools slidably positioned within the passageway provided in said outer spool, each inner spool having an axially extending passageway therethrough,
- According to the invention at least one second opening of each pair of two second openings of the outer spool is of non-constant longitudinal section, said section narrowing from the outer face of the outer spool on at least a part of the thickness of said second opening, so that a lateral side of said at least one second opening offers an obstacle where a part of the fluid flow entering said second opening from the second port crashes before it comes into an axially extending passageway of the inner spool.
- According to other advantageous and non-limiting features of the invention, taken alone or in combination:
- said second opening of non-constant section comprises a central drill and at least one peripheral blind drill partially overlapping said central drill and opening out only on the outer face of the outer spool, said blind drill constituting said obstacle;
- said second opening of non-constant section comprises a central drill, a blind drill spaced apart from said central drill and joined to it by a channel, the blind drill and the channel opening out on the outer face of the outer spool;
- at least one blind drill is disposed along or close to the diametrical axis of the central drill which is parallel to the longitudinal axis of the outer spool and on the side of the central drill which is the nearest of the end of the outer spool;
- the lateral wall of said second opening of non-constant section is divergent from the inner face of the outer spool to its outer face;
- said second opening of non-constant longitudinal section comprises a central drill provided with a counter bore opening out on the outer face of the outer spool;
- the second opening of non-constant longitudinal section of the outer spool has an area at the outer face of the outer spool greater than its area at the inner face of said outer spool;
- each inner spool is provided with a partition wall extending transversally across the passageway therethrough and this partition wall is provided with at least one hole therethrough, this hole affording communication between the central zone of said outer spool and the passageway therethrough of the inner spool;
- the partition wall comprises a central hole extending along the longitudinal axis of said inner spool and/or at least one peripheral hole extending parallel to this longitudinal axis (X-X');
- a partition element is disposed inside the central zone of the outer spool in front of the at least one first opening to separate the flow of hydraulic liquid circulating inside the flow control valve into two flows;
- the partition element is a portion of tube inserted in coaxial relationship with and inside the passageway of said outer spool, the tube being provided with a plane partition wall extending in a plane transversely bisecting said tube, and the tube being provided with at least one aperture on both sides of said wall, the aperture opening in front of the opening provided in the outer spool;
- the partition element is a portion of tube inserted in coaxial relationship with and inside the passageway of said outer spool, the tube being provided with a partition wall extending in a plane transversely bisecting said tube, and the tube being provided with at least one aperture on both sides of said wall, the apertures opening in front of the opening provided in the outer spool, said partition wall being provided with two cones disposed on the partition wall such that their respective basis are in contact with said partition wall;
- the flow control valve comprises an additional by-pass spool;
- said by-pass spool is in coaxial relationship with the outer spool and is mounted outside of said outer spool and inside the first bore of the valve body, said by-pass spool being slidably positionable within said bore; and
- said by-pass spool is slidably positioned within an additional longitudinally extending bore provided in said valve body parallel to said first bore of the valve body,
- the valve comprises a control spool slidably mounted inside a second bore of the valve body, parallel to the first bore receiving the by-pass spool, the first bore and the second bore being connected by at least one connecting port,
- said control spool is moveable between a so-called "activation" position in which it connects the two second ports therethrough of the valve body to a hydraulic pump of said hydraulic device and a so-called "deactivation" position in which it connects the two second ports therethrough of the valve body to a tank of hydraulic fluid of said hydraulic device.
- Additional objects as well as features and advantages of the invention will become apparent from the description set forth hereunder when considered in conjunction with the accompanying drawings, which represent several possible embodiments. On these drawings:
-
Figures 1 and 2 are longitudinal sectional views of the flow control valve according to the invention, in flow combining mode, with the outer spool respectively in central position or in offset position, -
Figure 3 is a longitudinal sectional view of the outer spool of the flow control valve according to the invention, -
Figure 4 is a perspective view of a part of the outer spool offigure 3 , -
Figure 5 is a partial longitudinal sectional view of the flow control valve offigure 1 , at a greater scale, -
Figures 6 to 20 are schematic top views or sectional views of through openings of different shapes provided inside the outer spool of the flow control valve according to the invention, -
Figures 21 and 22 are respectively a longitudinal sectional view and a perspective view of a partition element configured to be disposed inside the passageway provided inside the outer spool, -
Figure 23 is a perspective view of a second embodiment of the partition element, -
Figures 24 and 25 are circuit diagrams representing the flow control valve ofFigure 26 in two different positions of the by-pass spool, -
Figure 26 is a longitudinal sectional view of a second embodiment of the flow control valve according to the invention, which comprises a by-pass spool, -
Figures 27 is a diagram showing pressure differences ΔP between two different points of a flow control valve according to the prior art against the flow rate FR of hydraulic fluid flowing inside and this, for two boundary outer spool axial movements (two curves), -
Figure 28 is a similar diagram for a flow control valve according to the invention, -
Figure 29 is a perspective view of half of a variant embodiment of an inner spool according to a longitudinal sectional plane, -
Figure 30 is a view similar tofigure 29 but showing another variant embodiment of an inner spool, -
Figure 31 is a hydraulic circuit diagram showing the flow control valve offigure 32 , and -
Figure 32 is a view in longitudinal section of a third embodiment of the flow control valve according to the invention, which comprises a control spool. - The structure of the
flow control valve 1 according to one possible embodiment of the present invention will now be explained with reference toFigures 1 to 3 . - It is to be noted that the elements making up the flow control valve of this invention are arranged symmetrically on the left and right sides of the valve. In other words, the
flow control valve 1 comprises a plane of symmetry P1 represented by the line Y-Y' on theFigures 1 and 2 . - The
flow control valve 1 comprises avalve body 2 provided with a central tubular bore 20 (so-called "first bore") extending longitudinally along an axis X-X'. - The
valve body 2 is provided with a first throughport 21 and a pair of second throughports 22. - The
first port 21 extends along an axis Y-Y' perpendicular to the longitudinal axis X-X'. - The
first port 21 ends in anannular groove 23 provided on the inside face of thebore 20. - Thus, the
first port 21 is in fluid communication at one end with the outside of thevalve body 2 where it can be connected to a hydraulic device and at its other end with the inside of thebore 20, more precisely with theannular groove 23. - Preferably, each of said
second ports 22 is axially positioned between thefirst port 21 and one end of thevalve body 2. Saidsecond ports 22 extend along longitudinal axis Y1-Y'1 and Y2-Y'2 respectively, parallel to the axis Y-Y'. - Each
second port 22 ends at one end at the outside of thevalve body 2 and at its other end in anannular groove 24 provided on the inner face of thebore 20. - Each
second port 22 is configured to be able to be connected to a hydraulic device. - Both ends of the
bore 20 are blocked by acover 25 attached to saidvalve body 2. An O-ring 26 is mounted in saidcover 25 for providing a seal to thevalve body 2 and preventing leakage of hydraulic fluid. Also, each cover 25 is provided with arecess 250 on its inner face, i.e. the face facing thebore 20. - An
outer spool 3 of tubular shape is coaxially disposed within thebore 20. - The outer diameter of the
outer spool 3 corresponds, within a clearance, to the inner diameter of thebore 20, so that theouter spool 3 can slide inside said first bore 20. - The passageway inside the
outer spool 3 is referenced 30. - Return means 31 tend permanently to position said
outer spool 3 centrally in the longitudinal direction of said bore 20. - Preferably, said return means 31 are a compression coil spring one end of which is retained (fixed) in the
recess 250 and the other end of which is retained (fixed) in an annularinner groove 38 provided on theinner face 37 of theouter spool 3, (seefigure 3 ). - As can be best seen on
Figure 3 , theouter spool 3 has at least afirst opening 34 communicating at one end with thefirst port 21 or more precisely with theannular groove 23 provided inside thebore 20 and at its other end, with acentral zone 32 inside thepassageway 30. More preferably, saidouter spool 3 is provided with twoopenings 34 diametrically disposed or with four openings, as represented on the drawings. - Said
outer spool 3 has also at least twopairs 350 of second openings therethrough, onepair 350 on each side of saidfirst opening 34. In eachpair 350, the twosecond openings outer spool 3. Further, and as can be seen onFigure 3 , thesecond openings - In each
pair 350, the second opening which is the closest to the ends of theouter spool 3 is referenced 35b whereas the one which is the closest of thecentral area 32 is referenced 35a. - Preferably, on each side (left and right) of said
first opening 34, theouter spool 3 is provided with twopairs 350 of diametrically disposedsecond openings Figure 3 , with four pairs of second openings disposed at 90 degrees one from the other, i.e. a total of eightpairs 350 of second openings. - The particular shape of said second openings will be described more precisely later.
- Two
annular grooves 39 are provided on theinner face 37 of theouter spool 3. Their role will be described later. - As can be seen in
figures 1 and 2 , theflow control valve 1 according to the invention also comprises a pair of axially extendinginner spools 4 slidably positioned within thepassageway 30 provided in saidouter spool 3. The twoinner spools 4 are respectively positioned on both sides of thecentral zone 32 provided inside thepassageway 30. - Each
inner spool 4 has a tubular shape with anaxially extending passageway 40 therethrough. - Preferably, each
inner spool 4 is provided with apartition wall 41 extending transversally across saidpassageway 40, preferably at the end of theinner spool 4 located near thecentral zone 32. - Each
inner spool 4 is coaxial with theouter spool 3. According to a first variant embodiment, thepartition wall 41 is provided with ahole 410 therethrough, extending along the longitudinal axis X-X' for affording communication between thecentral zone 32 and theaxially extending passageway 40 of saidinner spool 4. - According to a second variant embodiment, illustrated in
figure 29 , thepartition wall 41 is pierced by acentral hole 410 coaxial to the longitudinal axis X-X' of theinner spool 4 and by several peripheral holes 410' arranged around thecentral hole 410 such that they extend parallel to the axis X-X'. In the variant offigure 29 , there are six of these peripheral holes 410', (four only being visible in the figure in section). But this number is not limited. The peripheral holes 410' are preferably arranged symmetrically relative to thecentral hole 410. - According to a third variant embodiment illustrated in
figure 30 , thepartition wall 41 comprises several peripheral holes 410', preferably at least two, arranged preferably symmetrically relative to the axis X-X', but nocentral hole 410. - The fact of having
several holes 410, 410' instead of one enables especially: - having a drop in pressure through the
partition wall 41 which is independent of the axial displacement of theinner spool 4, including in combining mode, corresponding to better precision of the control valve, - decreasing the "transition distance" after passing through the
holes 410, 410', in which the speed of the fluid decreases, - decreasing turbulence after passing through the
holes 410, 410', especially in combining mode, especially preventing the creation of recirculation zones. - Each
inner spool 4 has at least one throughopening 42 arranged therein in the lateral wall of saidinner spool 4. Preferably, eachinner spool 4 has at least twoopenings 42 diametrically disposed and more preferably fouropenings 42, as represented onFigures 1 and 2 , (disposed at 90° from each other). - Each
inner spool 4 is also provided with aplug 43 which blocks its end opposite thepartition wall 41. - Preferably, snap rings 33 are disposed inside the
grooves outer spool 3. They constitute means for limiting the extent of movement of eachinner spool 4 in the longitudinal direction within thepassageway 30 in saidouter spool 3. - The
openings 42 are arranged inside eachinner spool 4 to be in register with one of thesecond openings outer spool 3, depending on the axial position of theinner spool 4, for affording a flow pass from thepassageway 40 to thesecond port 22 provided in saidvalve body 2. - Advantageously, a
partition element 5 or 5' is disposed inside thecentral zone 32 of theouter spool 3, in front of thefirst openings 34 and between eachinner spool 4. - The function of this partition element will be described later. This
partition element 5, 5' may also act to limit the extent of movement of eachinner spool 4. - All the elements constituting the
flow control valve 1 are preferably made of metal or plastic material. - A first embodiment of the partition element (referenced 5) will now be described with reference to the
Figures 21 and 22 . Thepartition element 5 is a portion oftube 50, i.e. a tube of small length. Thetube 50 is provided with aplane partition wall 51 of circular shape extending in a plane transversally bisecting saidtube 50. Further thetube 50 is provided on both sides of thewall 51 with at least one throughaperture 52, preferablyseveral apertures 52, for example four apertures, of large dimensions, as in the example represented onFigure 22 . - A second embodiment of the partition element, referenced 5', will now be described with reference to the
Figure 23 . - The partition element 5' differs from the
partition element 5 in that the partition wall referenced 51' is provided with twocones 53, disposed on the partition wall 51' such that their respective bases are in contact with saidpartition wall 51. In other words, thetip 530 of eachcone 53 is oriented towards one of theinner spool 4. - As can be seen on
Figures 1 and 2 , thetube 50 is inserted in a coaxial relationship with theinside passageway 30 of theouter spool 3 such that the plane of thepartition wall 51 is coplanar with the plane P1 of thevalve body 2. - The
partition elements 5 or 5' act as a splitting element when theflow control valve 1 works in dividing mode. The stream of hydraulic fluid enters thefirst port 21 and thegroove 23 and then enters thecentral space 32 through thefirst openings 34. Since thepartition wall 51 is disposed in the plane of symmetry P1 of the flow control valve, the stream (flow) of hydraulic fluid is perfectly divided into two flows which are directed toward the hole(s) 410 of eachinner spool 4. - To the contrary, in combining mode, the two flows of hydraulic fluid issuing from each
inner spool 4 impact thepartition wall 51 or thecones 53 on both sides and are then directed towards the set offirst openings 34, therefore preventing that stagnation pressure from one side flow exerts an influence on the flow from the other side. - The
cones 53 promote deflection of the flow from one direction to the perpendicular direction. - In dividing mode, the pressure differential between both sides of the
partition wall 41 and the resistance offered by theholes 410 to the fluid causes the twoinner spools 4 to move away from each other in the direction of thecover 25. In this position, not represented on the Figures, theopening 42 of eachinner spool 4 is in register with thesecond opening 35b of eachpair 350 of openings. - To the contrary, in combining mode, the pressure differential across the
inner spools 4 forces them against each other, in the position represented onFigures 1 and 2 . In this position, theopening 42 registers respectively with thesecond opening 35a. - According to the invention, at least one
opening 35a on each side of the first opening(s) 34 and preferably all theopenings 35a of theouter spool 3 have a non-constant longitudinal section, said section narrowing from theouter face 36 of theouter spool 3 on at least a part of the thickness t of saidsecond opening 35a (which corresponds to the thickness of the wall of the outer spool 3), so that a lateral side of said at least onesecond opening 35a offers an obstacle where a part of the fluid flow entering saidsecond opening 35a from one of thesecond port 22 crashes before it comes into the axially extendpassageway 40 of theinner spool 4. - A first embodiment of the
second opening 35a will now be described in reference with theFigures 3 to 7 . Saidsecond opening 35a comprises acentral drill 351 provided through all the thickness t of theouter spool 3 and at least one peripheralblind drill 352 partially overlapping saidcentral drill 351 and opening out only on theouter face 36 of theouter spool 3. - As already explained before in relation with the prior art flow control valve, when a flow control valve operates in combining mode, and if the pressures in the two
second ports 22 are not equal, then theouter spool 3 will move to the right or to the left to equilibrate the pressure of hydraulic fluid introduced into thecentral space 32 and thereafter in thefirst port 21. Thereafter, when the pressure is equilibrated, the outer spool comes back to the central position represented infigure 1 . - When the
outer spool 3 is in the position represented onFigure 2 , wherein it is on the right side of the flow control valve, thesecond openings 35a of the right side of theouter spool 3 are in register with the rightsecond port 22 or the correspondingannular groove 24. To the contrary, thesecond opening 35a located on the left side of theouter spool 3 is only partly in register with the left handsecond port 22 of thevalve body 2. - When the
outer spool 3 moves back to the left, it get through an operating position represented onFigure 5 where only the peripheralblind drill 352 starts to register with thesecond port 22 of the left side of thevalve body 2. - In this situation, and as represented on
Figure 5 , the entering flow issuing from the second port 22 (arrow i) impacts on thebottom 353 of theblind drill 352, before to impact the inner face of the bore 20 (arrow j) and then to be sent back (arrow k) toward thehole 410 of theinner spool 4. The same applies if there areseveral holes 410, 410'. - With this structure and the creation of an obstacle (bottom 353), the turbulences inside the
inner spool 4 are avoided because the entering flow do not enter thepassageway 40 too abruptly, or at least is less dependent from the outer spool axial displacement. - Other shapes of
second openings 35a will now be described in relation withFigures 8 to 20 . - The
bottom 353 of theblind drill 352 may be perpendicular to the longitudinal axis Y3-Y'3 of thecentral drill 351, as represented onFigure 7 . - However, the
bottom 353 of theblind drill 352 can be tilted toward thecentral drill 351 and theinner face 37, (as represented onFigure 8 ) or tilted toward thecentral drill 351 and theouter face 36 of theouter spool 3, as represented onFigure 10 . Further, the bottom 353 can also be curved, its concavity directed towards theouter face 36 of theouter spool 3. The shape of theblind drill 352 may be a part of a circle, as represented onFigures 6 and 11 , of the same diameter as thecentral drill 351, as represented onFigure 11 , or of a smaller diameter, as represented onFigure 6 . - The
blind drill 352 may be also have a shape of a part of a ring as represented onFigure 12 . - Further, it is also possible to have several
blind drills 352, either of smaller and smaller diameters from thecentral drill 351 to the outside, as represented onFigure 13 or disposed separately as represented onFigure 16 . - When there are several
blind drills 352, they can be of the same depth, as represented onFigure 14 or of different depths as represented onFigure 15 . In this case, the outermostblind drill 352 is of lower depth than the middleblind drill 352. - The
second opening 35a can also comprise acentral drill 351 and acounter bore 353 surrounding said central drill, as represented onFigure 17 . - As represented on
Figures 18 and 19 , thesecond opening 35a can comprise acentral drill 351 and ablind drill 354 spaced a part from thecentral drill 351 and joined to it by achannel 355 opening out on theouter face 36 of theouter spool 3. Theblind drill 354 and thechannel 355 may be of same or different depths. - Further, the
bottom 353 of theblind drills - Finally, and as represented on
Figure 20 , thesecond opening 35a can have alateral wall 356 divergent from theinner face 37 of the outer spool to itsouter face 36. - In respect of the embodiment of the shape of the
second opening 35a, it has to be noted that the elements (blind drill, groove or biased wall) which constitute the obstacle are disposed or formed along the diametric axis of thecentral drill 351 which is parallel to the axis X-X' or close to it and on the side of thecentral drill 351 which is directed toward the ends of theouter spool 3. In other words, and as can be seen onFigure 3 , the obstacle element, as theblind drill 352, is provided on the left side of the left second opening or on the right side of the right second opening. - The effects of specific shapes of the
second opening 35a on the stream of hydraulic fluid will be described later. - In all the previously described embodiments, the area of the
second opening 35a is greater at theouter face 36 of theouter spool 3 than its area at theinner face 37 of said outer spool. Nevertheless, thesecond opening 35a could diverge toward theinner face 37 after the area of the obstacle. - Further, it is to be noted that the
second openings 35b could have the same shape as thesecond openings 35a. Nevertheless, it is not absolutely necessary because these second openings are used only in dividing mode and because the problems of turbulences and loss of accuracy of the valve appears only in combining mode. - The flow control valve of the invention can be used alone, as previously described or can also be used in combination with an additional by-pass spool.
- Such a by-pass spool allows using the flow-dividing and flow-combining valve according to the invention or by-passing it.
- According to a first embodiment of the invention represented on
Figure 26 , the by-pass spool 6 is disposed inside thebore 20 and outside theouter spool 3 in coaxial relationship with said bore and said outer spool. Thus, the by-pass spool 6 extends along the longitudinal axis X-X'. This embodiment of the flow control valve is referenced 1'. - The by-
pass spool 6 has anaxially extending passageway 60 therethrough. - The outer ends of the two compression helicoidal springs 31 are no more received in the
recess 250 of thecover 25 as in thevalve 1 but inplugs 61 inserted respectively at both ends of the passageway of the by-pass spool 6. - O-
rings 62 are mounted between the outside annular face of theplugs 61 and the inner cylindrical face of thepassageway 60 of the by-pass spool 6 for providing tightness of the by-pass spool 6. - The valve body is referenced 2' and differs from the
valve body 2 by the fact that anannular groove 27 opening out inside thefirst bore 20 is provided between theannular groove 23 and eachannular groove 24, to put said grooves into fluid communication. Thegrooves 27 are less deep than thegrooves - The by-
pass spool 6 of tubular shape presents an innercylindrical face 63 and an outercylindrical face 64. - The by-
pass spool 6 presents in its central area anannular groove 65 opening out inside thepassageway 60. Saidannular groove 65 is perpendicular to the axis X-X'. Further, the by-pass spool 6 comprises at least one throughopening 650 affording communication between the bottom of theinner groove 65 and theouter face 64 of the by-pass spool 6. - The by-
pass spool 6 also comprises at least one throughopening 660, (preferably two or four through openings regularly and angularly distributed), on each side of theopening 650. Theseopenings 660 communicate at one end with theannular groove 66 and at the other end with theannular grooves 24. Moreover, theouter face 64 of the by-pass spool 6 is provided with twoannular grooves 640 of X-X' axis, each of saidannular groove 640 being located between thecentral opening 650 and one of thelateral openings 660. - The by-
pass spool 6 is provided with return means, in this case a compressionhelical spring 67. - The
bore 20 of the valve body 2' is closed at its both ends by a cover 28 (on the left side ofFigure 26 ) and a cover 29 (on the right side ofFigure 26 ). O-rings covers bore 20. Thecover 29 comprises an annularinner passageway 291 for receiving thespring 67. - The
spring 67 tends permanently to position said by-pass spool 6 in a "by-pass position" represented onFigures 24 and26 , i.e. a position where the end of the by-pass spool 6 opposite to thespring 67 abuts against thecover 28. - The by-
pass spool 6 can be displaced by signal pressure on x port (seefigures 24 and 25 ) against the return force of thespring 67, slightly on the right side ofFigure 26 to be put in a "working position" represented onFigure 25 . - In both positions of the by-
pass spool 6, theopenings 660 are in register with theannular grooves 24 and thecentral opening 650 is in register with the centralannular groove 23. - In the "by-pass position" represented on
Figure 26 , the twoannular grooves 640 are respectively in register with the twoannular grooves 27 provided inside the valve body 2'. In this case, the flow of hydraulic fluid entering thefirst port 21 is directed toward theannular grooves 24 via theannular grooves ports 22, therefore by-passing theouter spool 3 and the twoinner spools 4. - To the contrary, when the by-
pass spool 6 is in "working position", with thespring 67 in compressed state and thespool 6 shifted toward the right, then the parts of theouter face 64 of the by-pass spool 6 located near the right side of theleft opening 660 and near the right side of thecentral opening 650 are in register with the bottom of theannular grooves 27, therefore closing the fluid communication between theannular groove 23 and the twoannular grooves 24. In this position, and as represented onFigure 25 , the flow of hydraulic fluid is directed toward theouter spool 3 and the twoinner spools 4. In this case the flow control valve works in flow-dividing mode and in flow-combining mode as previously described. - In a second embodiment not represented on the figures, the
outer spool 6 can be disposed inside an additional longitudinally extending bore, provided in the valve body 2', parallel to said first bore 20. - In the "by-pass position", said by-pass spool is positioned inside the additional bore to send the hydraulic fluid directly towards the
port 22. To the contrary, in its "working position", the by-pass spool leads the flow of hydraulic fluid in thefirst port 21 and the flow-control valve works as explained with thevalve 1 offigures 1 and 2 . - The flow control valve 1' provided with a by-
pass spool 6 coaxial to theouter spool 3 and which has been described in conjunction withfigure 26 can also be used, coupled to an additional control spool 7. The whole constitutes a flow control valve referenced 1" and illustrated infigure 32 . - The fact of having assembly with the concentric dividing and by-pass spools, such as illustrated in
figure 26 , heightens the compactness and consequently easily adds a third spool in parallel into the same body to obtain three different functions. - The upper part of the
valve 1" infigure 32 is identical to the valve 1' described in conjunction withfigure 26 and the same reference numerals are used to designate identical elements. Only the lower part will be described in more detail. The valve body is referenced 2". - The control spool 7 is a cylindrical element slidably mounted inside a second cylindrical bore 20', arranged inside the
valve body 2". - The control spool 7 illustrated is a so-called "freewheeling" spool. This spool 7 could be any other spool, such as especially a front step/rear step selection spool.
- The second bore 20' extends according to a longitudinal axis X1-X'1 parallel to the longitudinal axis X-X' of the
first bore 20. - These two
bores 20 and 20' are connected together by at least one connectingport 80 which extends preferably according to the axis Y-Y'. - The connecting
port 80 opens out both in anannular groove 81 made on the inner wall of the second bore 20' and also in theannular groove 23. - The
valve body 2" also comprises two annular grooves on either side of theannular groove 81. These annular grooves are referenced respectively 82 and 83 for those located to the left infigure 32 , 84 and 85 for those located to the right. Finally, a thirdannular groove 86, narrower than the others, is made to the right of thegroove 85. All these annular grooves open out inside the bore 20'. - The
annular grooves figure 32 . - The control spool 7 comprises an axial
central channel 70 from one of its ends and over part of its length. - The control spool 7 also has over its outer surface three annular grooves referenced successively from left to right 71, 72 and 73.
- The
annular grooves central channel 70 via lumens referenced respectively 74 and 75. - Finally, the
central channel 70 is connected to its cylindrical outer wall by at least onelumen 76. - The control spool 7 has at one of its ends, here to the right in
figure 32 , acylindrical head 77, of lesser diameter, around which is arranged ahelicoidal compression spring 78. Thisspring 78 is retained at one of its ends by the spool 7 and at the other by a hollow cover 29'. - The
channel 70 opens out at the opposite end of thehead 77 and is blocked by astopper 79. - Moreover, the bore 20' is also blocked by a cover 28'.
- The
helicoidal spring 78 constitutes return means which permanently tend to return the control spool 7 to a so-called "deactivation" position which is that illustrated infigure 32 . - In this deactivation position the
annular grooves 83 and 85 (and also the ports therethrough facing the outside to which they are connected), are insulated from the connectingport 80. Also, theannular groove 73 is located facing the connectingport 80 and theannular groove 84. As a consequence, theorifice 80 is in fluid communication with thegroove 84 and via thelumen 75 with thechannel 70 and with theannular groove 82. - The control spool 7 can be moved against the force exerted by the
spring 78, by introduction of hydraulic fluid at the end of the bore 20' located facing the cover 28'. It moves to the right infigure 32 to occupy a so-called "activation" position. - In this activation position, the connecting
port 80 is in fluid connection with theannular groove 83 and the port therethrough towards the outside to which it is connected. Also, theannular groove 84 is in fluid connection with theannular groove 85 via theannular groove 73 of the control spool 7. -
Figure 31 shows an example of application of theflow control valve 1", given purely by way of illustration. This application relates to hydraulic assistance of vehicle wheels. - In this case, two hydraulic motors M1 and M2 are attached respectively to two vehicle wheels, the latter not being illustrated in the figures. Each of these hydraulic motors is connected both to one of the
second ports 22 therethrough and also to a port joining theannular groove 84. - Also, a pump P of the hydraulic control circuit of these motors is attached both to the port opening out in the
annular groove 83 and also to that opening out in theannular groove 85. Finally, theannular groove 82 is attached to a tank R of hydraulic fluid. - The spool 7 is called "freewheeling" spool of the hydraulic motors, (of course, it could be any other spool, such as especially a front/rear step selection spool).
- The above hydraulic device creates hydraulic assistance for vehicle wheels or on the contrary places these wheels in freewheeling operating mode when the control spool is in the deactivated position.
- This type of assembly combines three different functions in the
same valve body 2", here the flow divider/combiner function, the by-pass function of the divider/combiner and the freewheeling function of the motors. - Such a type of assembly is advantageous as it has several spools in the same body and avoids making and machining two separate bodies and connecting them by pipes.
- Even though this has not been illustrated in the figures, it is also possible to make a flow control valve coupling the above control spool 7 with the variant embodiment of the control valve in which the by-
pass spool 6 is placed in an additional bore separate from thefirst bore 20. In this case, there are three parallel bores. - Tests were conducted to register the pressure differences ΔP between the left end of the
bore 20 surrounding thespring 31 and theport 21 as a function of different flow rates FR of hydraulic fluid inside a flow control valve according to the prior art when this valve operates in combining mode. - The results are represented in
figure 27 , where ΔP is expressed in 105 Pascals and the flow rate FR in liter per minute. The curve A represents the results obtained when the outer spool is in middle (central) position and the curve B the results obtained when the outer spool is moved on right. - As can be seen, the two curves do not overlap.
- Similar tests have been conducted with a flow control valve according to the invention such as the one represented in
figures 1 and 2 . - The results are shown in
figure 28 , where the curve C represents the results obtained when theouter spool 3 is in the middle position (seefigure 1 ) and the curve D the results obtained when theouter spool 3 is moved on right (seefigure 2 ). - As can be seen, the two curves nearly completely overlap, which means that there is less oscillations of the
outer spool 3 and that the accuracy of the valve according to the invention is better. - Finally, measurements have also been done with the two aforementioned flow control valves but in dividing mode. The obtained results showed that the flow control valve according to the invention acted like the flow control valve of the prior art, which means that the amendments done on the
second openings 35a have no negative influence in dividing mode.
said outer spool having at least a first opening communicating at one end with the first port of said valve body and at its other end with a central zone of said outer spool, the outer spool also having at least two pairs of second openings therethrough, one pair on each side of said first opening, with the two second openings of each pair being offset from one another in the longitudinal direction, so that for each pair at least one of said second openings is in communication with one of said second ports, depending on the axial position of the outer spool, in the bore,
each inner spool having at least one opening therein arranged to be in register with one of the two second openings of said outer spool, depending on the axial position of said inner spool, for affording a flow path from the passageway within said inner spool to the second port in said valve body,
Claims (17)
- A flow control valve (1, 1', 1") adapted for use as a flow-dividing and flow-combining valve in hydraulic devices, comprising:- a valve body (2, 2', 2") having a first longitudinally extending bore (20) therethrough,- an outer spool (3) slidably positioned within said bore (20), said outer spool (3) having an axially extending passageway (30) therethrough,- return means (31) which tend permanently to position said outer spool (3) centrally in the longitudinal direction of said bore (20),- a pair of axially extending inner spools (4) slidably positioned within the passageway (30) provided in said outer spool, each inner spool (4) having an axially extending passageway (40) therethrough,said valve body (2, 2', 2") having a first port (21) therethrough and a pair of second ports (22) therethrough, said first port (21) and second ports (22) communicating with the first bore (20),
said outer spool (3) having at least a first opening (34) communicating at one end with the first port (21) of said valve body (2, 2', 2") and at its other end with a central zone (32) of said outer spool (3), the outer spool (3) also having at least two pairs (350) of second openings (35a, 35b) therethrough, one pair (350) on each side of said first opening (34), with the two second openings (35a, 35b) of each pair (350) being offset from one another in the longitudinal direction, so that for each pair (350) at least one of said second openings (35a, 35b) is in communication with one of said second ports (22), depending on the axial position of the outer spool (3), in the first bore (20),
each inner spool (4) having at least one opening (42) therein arranged to be in register with one of the two second openings (35a, 35b) of said outer spool (3), depending on the axial position of said inner spool (4), for affording a flow path from the passageway (40) within said inner spool (4) to the second port (22) in said valve body (2, 2', 2"),
characterized in that at least one second opening (35a) of each pair (350) of two second openings (35a, 35b) of the outer spool (3) is of non-constant longitudinal section, said section narrowing from the outer face (36) of the outer spool (3) on at least a part of the thickness (t) of said second opening (35a), so that a lateral side (352, 353, 354, 355, 356) of said at least one second opening (35a) offers an obstacle where a part of the fluid flow entering said second opening (35a) from the second port (22) crashes before it comes into an axially extending passageway (40) of the inner spool (4). - A flow control valve (1, 1', 1") according to claim 1, characterized in that said second opening (35a) of non-constant section comprises a central drill (351) and at least one peripheral blind drill (352) partially overlapping said central drill (351) and opening out only on the outer face (36) of the outer spool (3), said blind drill (352) constituting said obstacle.
- A flow control valve (1, 1', 1") according to claim 1, characterized in that said second opening (35a) of non-constant section comprises a central drill (351), a blind drill (354) spaced apart from said central drill (351) and joined to it by a channel (355), the blind drill (354) and the channel (355) opening out on the outer face (36) of the outer spool (3).
- A flow control valve (1, 1', 1") according to claim 2 or claim 3, characterized in that the at least one blind drill (352, 354) is disposed along or close to the diametrical axis of the central drill (351) which is parallel to the longitudinal axis (X-X') of the outer spool (3) and on the side of the central drill (351) which is the nearest of the end of the outer spool (3).
- A flow control valve (1, 1', 1") according to claim 1, characterized in that the lateral wall (356) of said second opening (35a) of non-constant section is divergent from the inner face (37) of the outer spool (3) to its outer face (36).
- A flow control valve (1, 1', 1") according to claim 1, characterized in that said second opening (35a) of non-constant longitudinal section comprises a central drill (351) provided with a counter bore (353) opening out on the outer face (36) of the outer spool (3).
- A flow control valve (1, 1', 1") according to any of the preceding claims, characterized in that the second opening (35a) of non-constant longitudinal section of the outer spool (3) has an area at the outer face (36) of the outer spool (3) greater than its area at the inner face (37) of said outer spool (3).
- A flow control valve (1, 1', 1") according to any of the preceding claims, characterized in that each inner spool (4) is provided with a partition wall (41) extending transversally across the passageway (40) therethrough and in that this partition wall (41) is provided with at least one hole (410, 410') therethrough, this hole (410, 410') affording communication between the central zone (32) of said outer spool (3) and the passageway (40) therethrough of the inner spool (4).
- A flow control valve (1, 1', 1") according to claim 8, characterized in that the partition wall (41) comprises a central hole (410) extending along the longitudinal axis (X-X') of said inner spool (4) and/or at least one peripheral hole (410') extending parallel to this longitudinal axis (X-X').
- A flow control valve (1, 1', 1") according to any of the preceding claims, characterized in that a partition element (5, 5') is disposed inside the central zone (32) of the outer spool (3) in front of the at least one first opening (34) to separate the flow of hydraulic liquid circulating inside the flow control valve (1, 1') into two flows.
- A flow control valve (1, 1', 1") according to claim 10, characterized in that the partition element (5) is a portion of tube (50) inserted in coaxial relationship with and inside the passageway (30) of said outer spool (3), the tube (50) being provided with a plane partition wall (51) extending in a plane transversely bisecting said tube (50), and the tube (50) being provided with at least one aperture (52) on both side of said wall (51), the apertures (52) opening in front of the opening (34) provided in the outer spool (3).
- A flow control valve (1, 1', 1") according to claim 10, characterized in that the partition element (5') is a portion of tube (50) inserted in coaxial relationship with and inside the passageway (30) of said outer spool (3), the tube (50) being provided with a partition wall (51') extending in a plane transversely bisecting said tube (50), and the tube (50) being provided with at least one aperture (52) on both sides of said wall (51'), the apertures (52) opening in front of the opening (34) provided in the outer spool (3), said partition wall (51') being provided with two cones (53) disposed on the partition wall (51') such that their respective basis are in contact with said partition wall (51').
- A flow control valve (1', 1") according to any of the preceding claims, characterized in that it comprised an additional by-pass spool (6).
- A flow control valve (1', 1") according to claim 13, characterized in that said by-pass spool (6) is in coaxial relationship with the outer spool (3) and is mounted outside of said outer spool (3) and inside the first bore (20) of the valve body (2, 2', 2"), said by-pass spool (6) being slidably positioned within said first bore (20).
- A flow control valve (1', 1") according to claim 13, characterized in that said by-pass spool (6) is slidably positioned within an additional longitudinally extending bore provided in said valve body (2', 2") parallel to said first bore (20) of the valve body (2').
- A flow control valve (1") according to claim 14 or 15, characterized in that it comprises a control spool (7), slidably mounted inside a second bore (20') of the valve body (2, 2', 2"), parallel to the first bore (20) receiving the by-pass spool (6), the first bore (20) and the second bore (20') being connected by at least one connecting port (80).
- A flow control valve (1") according to claim 16, characterized in that said control spool (7) is moveable between a so-called "activation" position in which it connects the two second ports (22) therethrough of the valve body (2, 2', 2") to a hydraulic pump of said hydraulic device and a so-called "deactivation" position in which it connects the two second ports (22) therethrough of the valve body (2, 2', 2") to a tank of hydraulic fluid of said hydraulic device.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1550708A FR3032254B1 (en) | 2015-01-29 | 2015-01-29 | FLOW CONTROL VALVE |
FR1560112A FR3032244B1 (en) | 2015-01-29 | 2015-10-22 | FLOW CONTROL VALVE. |
Publications (2)
Publication Number | Publication Date |
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EP3051147A1 true EP3051147A1 (en) | 2016-08-03 |
EP3051147B1 EP3051147B1 (en) | 2018-01-17 |
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ID=55129798
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP16152676.9A Active EP3051147B1 (en) | 2015-01-29 | 2016-01-26 | Flow control valve |
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EP (1) | EP3051147B1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107489787A (en) * | 2017-08-15 | 2017-12-19 | 徐州工业职业技术学院 | A kind of revolving valve, revolution hydraulic pressure reversing control system |
FR3055939A1 (en) * | 2016-09-13 | 2018-03-16 | Poclain Hydraulics Ind |
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GB1123256A (en) * | 1965-09-02 | 1968-08-14 | Short Brothers & Harland Ltd | Improvements in spool valves for fluid pressure operated apparatus |
US3554213A (en) | 1969-04-14 | 1971-01-12 | Masao Yoshino | Flow control valve |
JPS4730019U (en) * | 1971-04-30 | 1972-12-05 | ||
JPS5676704A (en) * | 1979-11-27 | 1981-06-24 | Uchida Yuatsu Kiki Kogyo Kk | Change-over valve with flow collecting and dividing function |
EP2476915A1 (en) * | 2011-01-14 | 2012-07-18 | Fluidesign | Bypass flow divider with three or four branches for hydraulic use |
-
2016
- 2016-01-26 EP EP16152676.9A patent/EP3051147B1/en active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1123256A (en) * | 1965-09-02 | 1968-08-14 | Short Brothers & Harland Ltd | Improvements in spool valves for fluid pressure operated apparatus |
US3554213A (en) | 1969-04-14 | 1971-01-12 | Masao Yoshino | Flow control valve |
JPS4730019U (en) * | 1971-04-30 | 1972-12-05 | ||
JPS5676704A (en) * | 1979-11-27 | 1981-06-24 | Uchida Yuatsu Kiki Kogyo Kk | Change-over valve with flow collecting and dividing function |
EP2476915A1 (en) * | 2011-01-14 | 2012-07-18 | Fluidesign | Bypass flow divider with three or four branches for hydraulic use |
Non-Patent Citations (1)
Title |
---|
"Flow Divider / Combiner SAE 16-Cartridge ? 350 bar ST16-01", HANDBOOK HYDAC INTERNATIONAL,, 1 January 2004 (2004-01-01), pages 1 - 2, XP007909931, DOI: HTTP://PDDOCSERV/SPECDOCS/DATA/HANDBOOKS/HYDAC/2004/E5967-1-0-07-04_ST16-01.PDF * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3055939A1 (en) * | 2016-09-13 | 2018-03-16 | Poclain Hydraulics Ind | |
CN107489787A (en) * | 2017-08-15 | 2017-12-19 | 徐州工业职业技术学院 | A kind of revolving valve, revolution hydraulic pressure reversing control system |
CN107489787B (en) * | 2017-08-15 | 2018-11-09 | 徐州工业职业技术学院 | A kind of revolving valve, revolution hydraulic pressure reversing control system |
Also Published As
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