EP0165281B1 - Limiteur de debit d'air comprime - Google Patents

Limiteur de debit d'air comprime Download PDF

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Publication number
EP0165281B1
EP0165281B1 EP85900124A EP85900124A EP0165281B1 EP 0165281 B1 EP0165281 B1 EP 0165281B1 EP 85900124 A EP85900124 A EP 85900124A EP 85900124 A EP85900124 A EP 85900124A EP 0165281 B1 EP0165281 B1 EP 0165281B1
Authority
EP
European Patent Office
Prior art keywords
movable element
flow rate
rate limiter
limiter according
cylindrical
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP85900124A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0165281A1 (fr
Inventor
André Legris
Yves Levenez
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Legris SA
Original Assignee
Legris SA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Legris SA filed Critical Legris SA
Publication of EP0165281A1 publication Critical patent/EP0165281A1/fr
Application granted granted Critical
Publication of EP0165281B1 publication Critical patent/EP0165281B1/fr
Expired legal-status Critical Current

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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
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • the present invention relates to a compressed air flow limiter arranged between a conventional compressed air distributor and a pneumatic cylinder.
  • the exhaust flow being limited only, the starting of the cylinders is slow, due to the large volume of air to be evacuated by the restriction and it can be accompanied by jolts. Pressure drop sensors tend to deliver end-of-travel signals that are all the more delayed as the passage restriction is important.
  • the device for adjusting the speed of a double-acting cylinder therefore consists of at least two flow restrictors, either intake or exhaust.
  • Hydraulic distributors are also known in which the drawer is self-piloting and subjected on its two faces to the action of springs.
  • this device due to the fact that it is used with incompressible liquids has passages which provide flow rates and do not allow, as in the present application where it is a matter of compressible gases, to limit the speed of a jack by controlling the air flow.
  • this known device does not allow easy adjustment of the position of the drawer by means of movable stops.
  • the device according to the present invention makes it possible to eliminate the drawbacks associated with the use of limiters and known devices for adjusting the speed of the pneumatic actuation means such as the jacks.
  • the air flow limiter comprises a body having a cylindrical housing bounded by two bottoms and in which is slidably mounted axially a movable member of revolution whose stroke is limited at each end of the housing by a member adjustable stop, said body being traversed perpendicularly to said cylindrical housing by two passage conduits supplying the actuator, said passage conduits each opening into a chamber delimited by the bottom, the cylindrical housing and the movable member, said movable member comprising a means of '' central seal ensuring the isolation between the two chambers defined at the two ends of the bistable housing, ensuring the adjustment of the opening of the passage conduits according to the position of the stop members located at the two ends of the housing, so that 'this results in an adjustment of the supply air and purge flow rates of the two air volumes of the double ef cylinder fet and this, in each direction of movement of the cylinder piston.
  • the device according to the invention makes it possible to adjust for each of the two directions of travel, both the intake flow and the exhaust air flow using a single adjustment for each direction.
  • This flow limiter arranged between a compressed air distributor and a pneumatic cylinder makes it possible to adjust the speed of the piston of a cylinder in each direction.
  • the flow limiter according to the invention is connected by its two inlet ports to the two outlet ports of a distributor and by its two outlet ports to the two inlet ports of a double-acting cylinder.
  • the reversal of the movement of the piston of the jack is a function of a sufficient pressure difference between the chambers of the regulator and the starting. of the cylinder with the double adjuster is much faster in setting for the purge than with conventional adjusters.
  • FIGS 1 and 2 there is shown an embodiment of a flow limiter which is arranged between a compressed air distributor 15 and a double-acting cylinder 5.
  • the flow limiter comprises a body 1 having a bore or housing cylindrical 1a limited by two bottoms and in which is slidably mounted an axially movable member 2 of revolution whose stroke is limited at each end of the housing by a stop member constituted by a screw 3, 4, engaged in a tapped hole 32b of a plug 32 closing off the two ends of the cylindrical housing 1a, said plug being forcibly engaged in the housing 1a with the interposition of an annular seal 32a disposed in a groove in the plug 32.
  • the head of the screws 3, 4 is engaged in a blind hole 32c provided in the plugs 32, with the interposition of an annular seal 3a, 4a.
  • the body 1 is crossed perpendicularly to the housing 1a by two passage conduits 11, 12 and 13, 14 supplying the jack 5, said conduit 11, 12 opening into a chamber 1b and said conduit 13, 14 opening into a chamber 1c.
  • the chambers 1b and 1c are delimited by the plug 32, the cylindrical housing 1a and the movable member 2, said movable member comprising a central annular seal 10, disposed in a groove 2g of said movable member and ensuring the isolation between the two chambers 1b and 1c.
  • the movable member 2 consists of a single cylindrical part (Fig. 1, 2) having a central partition 2f, delimiting on each side a recess 2c, and against which the screws 3 and 4 are likely to abut to limit the stroke of the movable member 2.
  • the body 1 of the flow limiter is connected by its half-ducts 11, 13 to the jack 5 and by its half-ducts 12, 14 to the compressed air distributor which is connected to a source P of compressed air and to exhausts EA and EB linked to the atmosphere.
  • the dispenser drawer When the dispenser drawer is in the position shown in FIGS. 1 and 2, it supplies compressed air to the semi-duct 12 thus pushing the movable member 2 which acts like a piston to the left and feeding through the housing 1 a and the half-duct 11 one of the sides of the jack 5.
  • the movable member is in abutment against the end of the screw 4 which has been adjusted beforehand to more or less close the passage orifice corresponding to the conduit 13, 14 which is connected to the chamber of the jack 5 which is located at the exhaust through the distributor 15.
  • the air flow rate escaping from the jack 5 is regulated by the orifice. delimited between the circular edge 34 of the movable member and the orifices of the half-ducts 13, 14, the position of the movable member 2 being determined by the position of the screw 4.
  • the speed of movement of the piston 5a in the jack 5 is also controlled, since this speed is a function of the resistance opposed by the air escaping from the jack by the conduit 13, 14, the orifice of which is more or less closed.
  • the adjuster of Figure 1 allows the adjustment of the flow rate on the exhaust, the intake being wide open and this in each direction.
  • the movable member 2 bi-stable in abutment to the right or to the left according to the cylinder cycle, more or less closes depending on the adjustment of the abutment screws 3, 4, the orifices for passage of the conduits 11, 12 and 13, 14 regulating thus the purge air flows in each direction.
  • the seal 10 ensuring the seal between the chambers 1b and 1c is mounted in a groove 1 formed in the body and in contact with the cylindrical outer surface of the movable member 2.
  • FIGS 3 and 4 there is shown another embodiment of the movable member 2 which consists of two identical elements 2a, 2b or complementary assembled by means of a rivet 2d or a screw, said elements delimiting between them a housing in which is disposed a seal 2e disposed around the rivet 2d. Outside the two elements 2a, 2b and on their joint plane there is provided a groove 2g intended to receive a seal 10.
  • the assembly of the elements 2a, 2b facilitates the passage of the seal 10 opposite the passage conduits 11, 12 and 13, 14, inside the housing 1a of the body 1.
  • the body 1 of Figure 2 can be made in two symmetrical or complementary parts.
  • the stop screws 3 and 4 are mounted in the plugs 32, so that their head extends outside.
  • the screws 3 and 4 are provided with locknuts 3b and 4b preventing these from unscrewing under the action of vibrations and the plugs 32 extended inside the housing 1a have grooves in which are arranged seals tightness. 3a, 4a, surrounding the rods of screws 3 and 4.
  • the caps 32 are fitted into the housing 1a with a shoulder 35 and they are held by a crimped edge 36.
  • FIG. 5 there is shown another embodiment of the movable member 2 which has in its cylindrical part holes 6, 6a and 8, 8a located on each side of the central partition 2f, said holes which move opposite orifices of the half-conduits 11 and 13, the section of which is substantially equal to that of the holes 6, 6a and 8, 8a.
  • the spacing between the holes 6, 6a and 8, 8a makes it possible to vary the proportion of the flow rates between the purge and the feed.
  • the movable member 2 includes notches 37 for the passage of the fluid towards the half-conduits 12, 14 and it is immobilized in rotation in order to maintain the holes along the same longitudinal axis.
  • FIGS 6 and 7 there is shown another embodiment of the flow limiter in which housing la is closed on one side by a plug 32 screwed into the body 1 and on the other side by a partition of the body 1.
  • the screws 3 and 4 are provided with locknuts 3b and 4b having a circular housing in which is disposed a seal 3a and 4a.
  • the movable member 2 consists of a solid cylindrical body in which are provided channels 6 and 8 which more or less seal the orifices of the half-conduits 11, 12 and 13, 14 according to the adjustment of the stop screws 3 and 4.
  • FIG. 8 represents another mobile member 2 in the body 1 of a flow limiter.
  • the movable member has two annular grooves 2h and 2i, arranged on either side of the seal 10, said grooves being arranged so that the movable member 2 is in the middle position of the housing 1a the conduits 11, 12 and 13, 14 are at their maximum opening.
  • the width of the grooves 2h, 2i is such that only the passage of the intake duct 11, 12 is reduced while the passage of the exhaust duct 13-14 remains fully open, whatever the setting of the screw stop 4. It is the same for the other alternation.
  • FIG. 9 another embodiment of the movable member 2 has been shown in which the annular grooves 2h and 2i ensure maximum opening of the conduits 11, 12 and 13, 14 when the movable member 2 occupies a middle position in housing 1a.
  • the width of the grooves 2h and 2i is such that the orifices for passage of the intake and exhaust ducts are reduced simultaneously.
  • Figure 10 there is shown another embodiment of the movable member 2, which comprises two annular grooves 2h, 2i, arranged so that the movable member occupying a middle position in the housing 1a. the conduits 11, 12 and 13, 14 are completely closed.
  • the width of the grooves is such that the two passage conduits, 11, 12 and 13, 14 are partially open, as in the previous example, for any adjustment the sections of the orifices of passage are equal or unequal according to their center distance relative to that of the conduits.
  • FIG. 11 shows a flow limiter in which the head of the screws 3 and 4 is arranged in a blind hole 32c, plugs 32, said blind hole being closed by a shutter member 31 which is force fitted and which is held by a seal 31a engaged in a groove 32d, formed in the plug 32.
  • This arrangement makes it possible to prohibit access to the screws 3 and 4 when the adjustment is made.
  • Figure 12 shows the same movable member as in Figure 8 abutting on the screw 4 and in this case only the conduit 11, 12 corresponding to the intake represents a reduced section, and therefore the speed of the cylinder piston 5 is regulated by this only restriction.
  • Figure 13 shows the same movable member as previously in abutment on the screw 4 which has been moved back from its position of Figure 12.
  • the passage section of the intake duct 11, 12 is now completely closed while the section passage of the exhaust duct 13, 14 is completely open.
  • the speed of the cylinder piston is zero.
  • FIG. 14 represents the same movable member 2 on the stop screw 4 which has been moved back with respect to the position of FIG. 13. This greater freedom of travel given to the slide causes both partial closings in the following variable proportions adjusting the screw of the ducts 11, 12 and 13, 14.
  • FIG. 15 represents the movable member 2 in abutment on the screw 4 which has been moved back to the maximum allowing the total travel of the movable member. In this position the piston of the jack 5 stops by completely closing the exhaust duct 13, 14.
  • This device therefore makes it possible, by simply adjusting the screws 3 and 4, to choose in a progressive and continuous manner the mode of adjustment of the speed of the piston of the jack in each of the half-cycles.
  • FIGs 16 to 21 there is shown another embodiment of a flow limiter in which the movable member 2 has holes 6, 6a and 8, 8a which are previously drilled on the same generator with a diameter ⁇ . Then the holes 8 and 6a are angularly enlarged by a positive value a with respect to the common drilling axis p (fig. 19) and the holes 8a, and 6 are angularly enlarged by a negative value ⁇ with respect to this same axis 13 (fig. 21).
  • a flange 48 which has slots 38, 39, in which are engaged screws 28, 29 fixed in the body 1, said flange 48 being able to pivot along the axis of the movable member 2 on the body 1 at the angles a + and a-, and be locked in the chosen position by means of the screws 28, 29.
  • the flange 48 has a finger 27 which is slidably mounted in a hole 40 in the movable member 2 in order to drive the latter in rotation when the flange 48 is acted on.
  • FIG. 18 shows under these conditions the position of the hole 8a, and of the half-duct 13 as well as that of the hole 6a and the orifice 11, these positions. being determined longitudinally by the adjustment of the stop screw 4, the intake and exhaust passages then being equal.
  • a rotation of the flange 48 by an angle a + drives the movable member 2 by means of the finger 27.
  • FIG. 20 For the same adjustment of the screw 4 it is shown in FIG. 20 that there is a preponderance of the exhaust passage 13- 8a on the admission passage 6a-11.
  • a rotation of the flange 48 and of the movable member 2 by an angle a- causes, as shown in FIG. 22, an inversion of the preponderance.
  • the geometric shape of the holes in the movable member 2 can be arbitrary and different from the circular section for better progressiveness in adjusting the opening of the passages.
  • the flow restrictors described above have the form of a double connector which is reversible as regards the orientation of its connections with a distributor and a jack.
  • a flow restrictor comprising a movable member 2 of the type shown in Figure 1 and in which are provided oblong holes 8b, 8c and 6b, 6c, the geometric centers of the holes 8b , 8c located on the same side with respect to the seal 10 are diametrically opposite, as for the holes 6b, 6c located on the other side of the seal 10.
  • the geometric centers of the holes 8b and 6b are on the same generatrix and therefore holes 8c and 6c are on the diametrically opposite generator.
  • These oblong holes extend along an axis forming with their generatrix a positive angle for the holes 8b, 8c and a negative angle for the holes 6b and 6c.
  • the distance between the geometric centers of the holes 8b, 8c and 6b, 6c is equal to the distance between the axes of the conduits 11, 12 and 13, 14.
  • the housing 1a is closed at one of its ends by a plug 32 and at the other end by a plug 26 which has at one of its ends a lug 46 perpendicular to its axis which is engaged in a groove 47 formed in the movable member 2, on a generator different from that of the holes and open at one of its ends.
  • the plug 26 has an external element 26b in the form of a hexagon for driving the plug in rotation and consequently of the movable member 2, by means of the lug 46 engaged in the groove 47 of the movable member. This arrangement makes it possible to maintain the mobile member 2 in a determined angular position, without preventing its longitudinal displacement.
  • FIG. 29 the movable member 2 is shown in a neutral angular position and in abutment against the stop screw 4, while in FIG. 30, it is abut against the abutment screw 3. In this case, the through holes are equal.
  • Figures 31 and 32 the movable member 2 which has been moved in rotation by an angle a + and for the two alternations to the left and to the right, priority is given to intake flow over exhaust.
  • FIGS. 35 to 40 Another embodiment of a flow limiter shown in FIGS. 35 to 40 comprises, as in the previous example, a rotary plug 26a, which is extended on one side by a part of hexagonal section 26c, engaged in a hole 41, of corresponding section provided at one end of the movable member 2 so that the latter can be driven in rotation and in axial translation.
  • the plug 26a is extended externally by a part 26b, in the form of a hexagon for driving the plug 26a (FIGS. 35-36 and 40).
  • the movable member 2 shown in Figure 40 has on each side of the seal 10 two grooves 8d, and 6d which are extended by two longitudinal grooves extending in opposite directions, the grooves 8e and 8f corresponding to the groove 8d and the grooves 6e and 6f corresponding to the groove 6d.
  • the grooves 8e and 8f are located on the same generator different from that mentioned above. With respect to an average generator, the axes of these grooves are offset by an angle a + and a-.
  • the width of the grooves is substantially equal to that of the diameter of the passage conduits 11,12 and 13,14 when they exit into the housing 1a of the movable member and the distance which separates them on the circle is also equal to this diameter.
  • FIG. 37 represents the movable member in abutment on the screw 4 which regulates the speed of retraction of the rod of the jack 5. In the neutral angular position shown, the values of the orifices for passage of the outward and return flow rates are equal.
  • FIG 41 there is shown a flow limiter which is identical to that of Figure 6 but which comprises two return springs 22, 23 which act on both sides of the movable member 2.
  • the springs 22, 23 which are very weak have no influence during the pressure cycles on the movable member 2; however, when the device is stopped under pressurized fluid, they allow manual actuation of the jack, particularly in the event of an accident.
  • FIG 42 there is shown an alternative embodiment of a flow limiter in which the housing 1a comprises two throttling members 33 comprising an orifice having double cones 8 and 7 which cooperate with conical parts 42, 43 and 42a , 43a of the movable member 2 and regulate the passages and therefore the flow rates.
  • the two chambers 1b, and 1c, are isolated by the seal 10 mounted on the central part of the movable member.
  • the throttling members 33 are disposed respectively between the orifices of the half-conduits 11 and 12 and between the orifices of the half-conduits 13 and 14.
  • the plugs 32 each have a blind hole 44 in which is mounted each end 45 of the movable member for guiding the latter.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sliding Valves (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Lift Valve (AREA)
  • Safety Valves (AREA)
EP85900124A 1983-11-29 1984-11-26 Limiteur de debit d'air comprime Expired EP0165281B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8319059 1983-11-29
FR8319059A FR2555703B1 (fr) 1983-11-29 1983-11-29 Perfectionnement aux limiteurs de debit d'air comprime

Publications (2)

Publication Number Publication Date
EP0165281A1 EP0165281A1 (fr) 1985-12-27
EP0165281B1 true EP0165281B1 (fr) 1988-03-02

Family

ID=9294658

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85900124A Expired EP0165281B1 (fr) 1983-11-29 1984-11-26 Limiteur de debit d'air comprime

Country Status (8)

Country Link
US (1) US4745845A (es)
EP (1) EP0165281B1 (es)
JP (1) JPS61500624A (es)
DE (1) DE3469582D1 (es)
ES (1) ES8603984A1 (es)
FR (1) FR2555703B1 (es)
IT (2) IT1179837B (es)
WO (1) WO1985002446A1 (es)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9314145D0 (en) * 1993-07-08 1993-08-18 Savair Ltd Pneumatic cylinder and control valve therefor
US7390432B2 (en) * 1998-06-30 2008-06-24 Sandia Corporation Enhanced formulations for neutralization of chemical, biological and industrial toxants
US6633015B2 (en) * 2000-12-08 2003-10-14 Doben Limited Soft-touch pneumatic drive unit
US7392734B2 (en) * 2003-11-07 2008-07-01 Japan Science And Technology Agency Actuator using fluid cylinder, method of controlling the actuator, and choke valve devices
CN102518611A (zh) * 2011-12-21 2012-06-27 上汽通用五菱汽车股份有限公司 气缸的速度调节装置
US10724553B2 (en) 2018-12-06 2020-07-28 Warner Electric Technology Llc Three position metering valve for a self-contained electro-hydraulic actuator

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3093159A (en) * 1959-06-10 1963-06-11 Nat Res Dev Hydraulic control valve
CH372931A (de) * 1959-10-27 1963-10-31 Schindler Werner Kolbensteuerventil zur mindestens teilweise stufenlosen Änderung der Geschwindigkeit in einem Druckmediumantrieb
US3119306A (en) * 1960-08-01 1964-01-28 Onsrud Machine Works Inc Contouring and profiling machines
GB968268A (en) * 1960-09-15 1964-09-02 Telehoist Ltd Improvements in or relating to fluid flow control valves
FR1533221A (fr) * 1967-01-06 1968-07-19 Dba Sa Vanne de débit à commande numérique
US3509968A (en) * 1968-03-01 1970-05-05 Jered Ind Inc Overspeed control valve assembly for a hydrostatic elevator engine
US3532119A (en) * 1968-04-01 1970-10-06 Kershaw Mfg Co Inc Pressure compensated control valve
NL6915281A (es) * 1969-10-09 1971-04-14
US3974742A (en) * 1974-10-31 1976-08-17 Caterpillar Tractor Co. Lock valve assembly

Also Published As

Publication number Publication date
ES538102A0 (es) 1986-01-01
FR2555703B1 (fr) 1986-08-14
IT1179837B (it) 1987-09-16
JPS61500624A (ja) 1986-04-03
WO1985002446A1 (fr) 1985-06-06
FR2555703A1 (fr) 1985-05-31
IT8468186A1 (it) 1986-05-29
ES8603984A1 (es) 1986-01-01
EP0165281A1 (fr) 1985-12-27
US4745845A (en) 1988-05-24
IT8468186A0 (it) 1984-11-29
DE3469582D1 (en) 1988-04-07
IT8454099V0 (it) 1984-11-29

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