WO1994019612A1 - Clapet de commande rapide et lente utilisant la pression hydraulique et penumatique - Google Patents

Clapet de commande rapide et lente utilisant la pression hydraulique et penumatique Download PDF

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Publication number
WO1994019612A1
WO1994019612A1 PCT/KR1993/000019 KR9300019W WO9419612A1 WO 1994019612 A1 WO1994019612 A1 WO 1994019612A1 KR 9300019 W KR9300019 W KR 9300019W WO 9419612 A1 WO9419612 A1 WO 9419612A1
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WO
WIPO (PCT)
Prior art keywords
high speed
low speed
solenoid
piston
spool
Prior art date
Application number
PCT/KR1993/000019
Other languages
English (en)
Inventor
Young Chool Kang
Original Assignee
Young Chool Kang
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 Young Chool Kang filed Critical Young Chool Kang
Priority to AU36490/93A priority Critical patent/AU3649093A/en
Publication of WO1994019612A1 publication Critical patent/WO1994019612A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
    • F16K31/0679—Electromagnet aspects, e.g. electric supply therefor with more than one energising coil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides

Definitions

  • the invention relates to a high speed and low speed control valve
  • Fig. 1 illustrates technologies described in above mentioned
  • Japanese Utility Model Laid-Open Publication but they have problems that a speed of movement of a spool is changed according to a pressure and a flow rate entering from a pump P and that a forward movement of a low speed piston 6 is impossible in the case where a high speed piston cylinder inside 3 is filled with a hydraulic oil.
  • the present invention not only solves all the above mentioned problems but also has advantages that there is a great benefit in cost reduction because all the parts assembled in an exterior body except solenoids 1, 2 shown in Fig. 1 can be omitted, and that an efficiency is increased.
  • the present invention provides a first embodiment of a high speed and low speed control valve utilizing hydraulic and pneumatic pressure in which a right side high speed solenoid, a right side low speed solenoid, a left side high speed solenoid and a left side low speed solenoid are constructed on the left and right sides of a spool on an axis same as that of the spool to enable a high speed and low speed control, a right side high speed piston in the form of an annular rod having two steps exists in the right side high speed solenoid, a right side low speed piston having a right side speed adjusting bolt exists in the right side low speed solenoid, a left side high speed piston in the form of an annular rod having two steps exists in the left side high speed solenoid, and a left side low speed piston having a left side speed adjusting bolt exists in the left side low speed solenoid.
  • Thr present invention further provides a hydraulic and pneumatic
  • the robot in which a high speed nd low speed control valve utilizing a hydraulic and pneumatic pressure is applied to a working robot.
  • the robot is composed of a computer control means, an encoder, a driving means and a hydraulic and pneumatic control valve of the present invention. This facilitates easy manufacturing of the working robot utilizing hydraulic and pneumatic pressure because a hydraulic and pneumatic control valve of the present invention is invented breaking the conventional conception that the hydraulic pressure provides poor original position control and poor precision.
  • Fig. 15 shows an embodiment of a working robot of the present invention which is workable in picking up two things and moving them across a 3 -dimensional space by utilizing six systems, each system being composed of a computer control means, an encoder, a driving means and a hydraulic and pneumatic valve.
  • Fig. 1 is a section drawing of a conventional two -stage flow rate adjusting valve
  • Fig. 2 shows a first embodiment of a high speed and low speed control valve utilizing hydraulic and pneumatic pressure of the present invention
  • Fig. 3 shows a condition of the first embodiment of the present invention in which a right side low speed solenoid is actuated
  • Fig. 4 shows a condition of the first embodiment of the present invention in which a left side low speed solenoid is actuated
  • Fig. 5 shows a condition of the first embodiment of the present invention in which a right side high speed solenoid is actuated
  • Fig. 6 shows a condition of the first embodiment of the present invention in which a left side high speed solenoid is actuated
  • Fig. 7 is a section drawing of a second embodiment of a high speed and low speed control valve utilizing hydraulic and pneumatic pressure of the present invention
  • Fig. 8 shows a condition of the second embodiment of the present invention in which a right side low speed solenoid is actuated
  • Fig. 9 shows a condition of the second embodiment of the present
  • Fig. 10 is a section drawing of a third embodiment of a high speed and low speed control valve utiKzing hydraulic and pneumatic pressure of the present invention.
  • Fig. 11 shows a condition of the third embodiment of the present invention in which a left side low speed solenoid is actuated
  • Fig. 12 shows a condition of the third embodiment of the present invention in which a left side high speed solenoid is actuated
  • Fig. 13 shows application circuit diagrams of the first embodiment of the present invention
  • Fig. 14 shows application circuit diagrams of the second and third embodiments of the present invention
  • Fig. 15 shows a construction drawing of a working robot having a high speed and low speed control valve utilizing hydraulic and pneumatic pressure.
  • Fig. 2 shows a first embodiment of a high speed and low speed control valve utihzing hydraulic and pneumatic pressure of the present invention, in which valve two solenoids are mounted on each of left and right sides in a line.
  • the inner solenoid 20 is a right side high speed solenoid
  • the outer solenoid 21 is a right side low speed solenoid.
  • the right side high speed solenoid 20 wraps the outside of a right side high speed piston 12
  • the right side low speed solenoid 21 wraps the outside of a right side low speed piston 13 in which a right side speed adjusting bolt 14 is fitted.
  • a right side oil leakage prevention bolt 25 is provided on the outer end of the right side low speed piston 13, and the bolt 25 is attached to a right side solenoid fixing nut 40, and the inside of the right side low speed piston 13 is screw threaded. In that screw thread is screwed the right side speed adjusting bolt 14.
  • the right side speed adjusting bolt 14 is so constructed as to be set in the right side low speed piston 13 by putting a long wrench into a speed adjusting bolt hole 41.
  • On top of the right side low speed piston 13 is longitudinally formed a key way 43 which is guided by a low speed piston rotation prevention key 42 formed in a cylinder.
  • the right side high speed piston 12 has a center recess through which the right side push rod 15 can slide, and has a shape of an annular rod having two steps.
  • a forward step of the annular rod that is, a left side step of smaller outer diameter can abut an end of a right side projection 76, and a portion of larger outer diameter can slide left and right in the cylinder.
  • the right side push rod 15 which slides in the right side high speed piston 12 can slide left and right between the right side end of the spool right side projection 76 and the left side end of the right side speed adjusting bolt 14.
  • the spool 10 is comprised of a left side land 48, a middle land 49, a right side land 50 and left and right side projections 77, 76.
  • the right side projection 76 is wrapped by a right side washer 17, and the washer 17 is supported elastically by a right side return spring 16.
  • inlet port P connected from a pump
  • inlet port P connected from a pump
  • cylinder port A of the cylinder head of the hydrauhc cylinder 44 and a cylinder port B of the cylinder rod of the hydrauhc cylinder 44 respectively.
  • left side T port 45 and a right side T port 46 On the left and right sides of the cylinder port A of the cylinder head and the cylinder port B of the cylinder rod are there a left side T port 45 and a right side T port 46, and the left side T port 45 and the right side T port 46 are connected to each other by a path 47.
  • An outlet port (T port) through which the hydrauhc oil flows out is formed by the left side T port 45, the right side T port 46 and the path 47.
  • Fig. 2 shows a condition of the first embodiment of the present invention in which the spool 10 is in the neutral state, and at this time the inlet port P is completely closed by the middle land 49, and the cyhnder port A of the head of the hydrauhc cyhnder 44 and the cyhnder port B of the hydrauhc cyhnder 44 rod are completely opened, and the left side T port 45 is completely closed by the left side land 48 and the right side T port 46 is completely closed by the right side land 50.
  • a drain 65 for removing the hydrauhc oil when it leaks into the right side space of the right side washer 17.
  • the left side of the spool 10 is symmetrical to the right side of the spool 10, and therefore the description thereof is omitted.
  • a terminal box 23 On the middle top of the valve of the first embodiment of the present invention is there a terminal box 23 in which cables connected to four solenoids are positioned, and a terminal cover 24 is positioned on the box 23.
  • Fig. 3 shows a condition of the first embodiment of the present invention in which the right side low speed solenoid 21 is actuated.
  • the right side low speed solenoid 21 When the right side low speed solenoid 21 is actuated, the right side low speed piston 13 is moved left by an electro-magnetic force until the left side end of the right side low speed piston 13 abuts a cyhnder wall, and at this time, the right side speed adjusting bolt 14 fixed in the right side low speed piston 13 by the thread is also moved left. Then the left end of the right side speed adjusting bolt 14 moves the right side push rod 15 left which in turn pushes the end of the right side projection 76 of the spool 10 which then is slided left.
  • the right side low speed solenoid 21 When the right side low speed solenoid 21 is actuated, the right side low speed piston 13 is moved left by an electro-magnetic force until the left side end of the right side low speed piston 13 abuts a cyhnder wall,
  • hydrauhc oil from the pump is fed to the cyhnder port B of the hydrauhc cyhnder rod through the inlet port P so that the piston is moved from the right to the left.
  • the hydrauhc oil flows out to the outlet port (T port) through the cyhnder port A of the head of the
  • FIG. 4 shows a condition of the first embodiment of the present invention in which the left side low speed solenoid 36 is actuated.
  • the left side low speed solenoid 36 has an electro -magnetic force
  • the left side low speed piston 28 is moved right until it abuts the wall of the left side cyhnder 26, and accordingly, the left side push rod 30 is moved right making the spool 10 slide right.
  • the hydraulic oil from the pump is fed to the cyhnder port A of the head of hydraulic cyhnder 44 through the inlet port P so that the piston is moved from the left to the right.
  • the hydrauhc oil which was at the right side of the piston in the cyhnder flows out to the outlet port (T port) through the cyhnder port B of the hydrauhc cyhnder rod and the right side T port 46. At this time, the piston is moved from the left to the right at low speed.
  • Fig. 5 shows a condition of the first embodiment of the present invention in which the right side high speed solenoid 20 is actuated.
  • the right side high speed solenoid 20 When the right side high speed solenoid 20 is actuated, the right side high speed piston 12 is moved left until the stepped shoulder of the right side high speed piston 12 abuts a cyhnder wall, and accordingly, the spool 10 is slided left.
  • the hydrauhc oil from the pump is fed to the cyhnder port B of the hydrauhc cyhnder rod through the inlet port P so that the piston is moved from the right to the left.
  • the hydrauhc oil which was at the left side of the piston flows out from the cyhnder 44 to the outlet port (T port) through the cylinder port A of the head of the hydrauhc cyhnder and the left side T port 45. At this time, the piston of the cyhnder 44 is moved from the right to the left at high speed.
  • Fig. 6 shows a condition of the first embodiment of the present invention in which the left side high speed solenoid 35 is actuated.
  • the left side high speed solenoid 35 has an electro -magnetic force
  • the left side high speed piston 27 is moved right until the stepped shoulder of the left side high speed piston 27 abuts a cyhnder wall, and accordingly, the spool 10 is slided right.
  • the hydrauhc oil from the pump is fed to the cyhnder port A of the head of the hydraulic cyhnder 44 through the inlet port P so that the piston is moved from the left to the right.
  • the hydrauhc oil which was at the right side of the piston flows out from the cyhnder 44 to the outlet port (T port) through the cyhnder port B of the hydrauhc cyhnder 44 rod and the right side T port 46. At this time, the piston of the cyhnder 44 is moved from the left to the right at high speed.
  • a displacement of the spool at the time of high speed motion is larger than that at the time of low speed motion, therefore an amount of the hydrauhc oil entering from the pump is larger at the time of high speed motion than that at the time of low speed motion, and accordingly the speed of the piston of the cyhnder 44 is increased.
  • the space surrounding the right side projection 76 of the spool 10 does not require the presence of the hydrauhc oil, and if the hydrauhc oil enters the space due to a leakage, the oil is
  • Fig. 7 is a section drawing of the second embodiment of a high speed and low speed control valve utihzing hydrauhc and pneumatic pressure of the present invention.
  • the valve is constructed in such a way that there are two solenoids at the right side, a cover at the left side and a spool 10 in the middle, and among the two solenoids at the right side, the inner solenoid 20 is a right side high speed solenoid and the outer solenoid 21 is a right side low speed solenoid.
  • the right side high speed solenoid 20 wraps the outside of a right side high speed piston 12, and the right side low speed solenoid 21 wraps the outside of a right side low speed piston 13 in which a right side speed adjusting bolt 14 is fitted.
  • a right side oil leakage prevention bolt 25 is provided on the outer end of the right side low speed piston 13, and the bolt 25 is attached to a right side solenoid fixing nut 40, and the inside of the right side low speed piston 13 is screw threaded. In that screw thread is screwed the right side speed adjusting bolt 14.
  • the right side speed adjusting bolt 14 is so constructed as to be set in the right side low speed piston 13 by putting a long wrench into a speed adjusting bolt hole 41.
  • On tope of the right side low speed piston 13 is longitudinally formed a key way 43 which is guided by a low speed piston rotation prevention key 42 formed in a cyhnder.
  • the right side high speed piston 12 has a center recess through which the right side push rod 15 can shde, and has a shape of an annular rod having two steps.
  • a forward step of the annular rod that is, a left side step of smaller outer diameter can abut an end of a right side projection 76 of the spool 10, and a portion of larger outer diameter can shde left and right in the cyhnder.
  • the right side push rod 15 which slides in the right side high speed piston 12 can slide left and right between the right side end of the spool right side projection 76 and the left side end of the right side speed adjusting bolt 14.
  • the spool 10 is comprised of a left side land 48, a middle land 49, a right side land 50 and left and right side projections 77, 76.
  • the right side projection 76 is wrapped by a right side washer 17, and the washer 17 is supported elastically by a right side return spring 16.
  • the left end of the left side land 48 is supported elastically by a left side return spring 31 via a left side washer 32.
  • the inlet port P At the left and right sides of the inlet port P are there a cyhnder port A of the cyhnder head of the hydrauhc cyhnder 44 and a cyhnder port B of the cyhnder rod of the hydrauhc cyhnder 44 respectively, and in the middle is an inlet port P connected from a pump.
  • On the left side of the cyhnder port A of the cyhnder head On the left side of the cyhnder port A of the cyhnder head is a left side T port 45 and on the right side of the cyhnder port B of the cyhnder rod is a right side T port 46, and the left side T port 45 and the right side T port 46 are connected to each other by a path 47.
  • FIG. 7 shows the neutral state of the second embodiment, where the cyhnder port A of the cyhnder head and the inlet port P are opened half and the cyhnder port B of the cyhnder rod is completely
  • the hydrauhc oil entering form the pump fills the left portion of the cyhnder 44 through the inlet port P and the cyhnder port A of the cyhnder head and the hydrauhc oil which was at the right side of the piston of the cyhnder 44 is discharged to the outlet port (T port) through the cyhnder port B of the cyhnder rod and the right side T port 46, so that the piston of the cyhnder is moved from the left to the right.
  • the left end of the bolt 14 moves the right side push rod 15 to the left, the rod 15 pushes the end of the right side projection 76, so that the spool 10 is shded to the left.
  • the hydrauhc oil from the pump enters the right side of the cylinder 44 piston through the inlet port opened half and the cyhnder port B of the hydrauhc cyhnder rod, and the hydrauhc oil which was at the left side of the cyhnder 44 piston is discharged to the outlet port (T port) through the cyhnder port A of the cyhnder head and the left side T port 45. Therefore, the piston is moved from the right to the left at low speed.
  • Fig. 9 shows a condition of the second embodiment of the present invention in which the right side high speed solenoid 20 is actuated.
  • the right side high speed solenoid 20 is actuated to have the
  • the right side high speed piston 12 is moved left until the stepped shoulder of the left side high speed piston 12 abuts a cyhnder wall, and accordingly, the spool 10 is shded left.
  • the hydrauhc oil from the pump is fed to the right side of the cyhnder 44 piston via the cyhnder port B of the hydrauhc cyhnder rod through the inlet port P and the hydrauhc oil which was at the left side of the piston flows out to the outlet port (T port) through the cyhnder port A of the head of the hydrauhc cyhnder and the left side T port 45.
  • the piston of the cyhnder 44 is moved from the right to the left at high speed.
  • FIG. 8 A difference between Fig. 8 and Fig. 9 is that the displacement of the spool 10 is larger at the time of actuating the right side high speed solenoid 20 than at the time of actuating the right side low speed solenoid 21 so that the entrance of the inlet port P becomes larger and the amount of the hydrauhc oil entering from the pump also becomes larger to make the piston of the cyhnder 44 move at high speed.
  • Fig. 10 is a section drawing of a third embodiment of a high speed and low speed control valve untihzing hydrauhc and pneumatic pressure of the present invention
  • Fig. 11 shows a condition of the third embodiment of the present invention in which a left side low speed solenoid is actuated
  • Fig. 12 shows a condition of the third embodiment of the present invention in which a left side high speed solenoid is actuated.
  • the third embodiment shown in Figs. 10, 11 and 12 is actuated in the same way as the second embodiment shown in Figs. 7, 8 and 9.
  • Fig. 13 shows application circuit diagrams of the first embodiment of the present invention
  • Fig. 14 shows application circuit diagrams of the second and third embodiments of the present invention.
  • Fig. 15 shows a construction drawing of a working robot having
  • a high speed and low speed control valve utihzing hydraulic and pneumatic pressure In the prior art, working robots are constructed of NC servo motors. However, due to a high speed and low speed control valve utihzing hydrauhc and pneumatic pressure of the present invention, a position control is assured and precision control becomes possible so that robots utihzing hydrauhc and pneumatic pressure can be constructed.
  • the working robot utihzing hydrauhc valve not only has stronger power but also makes the repair easy at the time of failure and significantly reduces the manufacturing unit price.
  • the working robot is constructed in such a way that if work data are input form the outside by utihzing a computer, the computer instructs such data to an encoder and a hydrauhc and pneumatic valve, and a feeding mechanism constructed of a hydrauhc motor or a cyhnder performs a work according to the actuation of the hydrauhc valve, and a result of the work is input again to the encoder, then the encoder inputs the result to the computer.
  • Fig. 15 shows an embodiment of above described working robot which comprises a straight hne feeding mechanism consisting of a high speed and low speed control valve 78 of the first embodiment utilizing hydrauhc and pneumatic pressure of the present invention, an encoder 59 and a hydrauhc motor 66, a horizontal plane rotating mechanism consisting of a high speed and low speed control valve 79 of the first embodiment, an encoder 70 and a hydrauhc motor 58, a vertical plane rotating mechanism consisting of a high speed and low speed control valve 80 of the first embodiment, an encoder 56 and a hydrauhc motor 54, a rotating mechanism consisting of a high speed and low speed control valve 81, an encoder 53 and a hydrauhc motor 73, a high speed and low speed control valve 82 of the second embodiment, an encoder and a right side finger 74, a high speed and low speed control valve 83 of the second embodiment, an encoder and a left side finger 75.
  • the high speed and low speed control can be achieved by a simple technical construction.
  • speed change of the high speed and low speed an abrupt change from the high speed to the low speed or vice versa can impart a harmful impact to a machine.
  • the present invention can prevent an abrupt speed change by actuating high speed and low speed solenoids simultaneously form a constant time period so that the impact is not imparted to the machine. That is, a damage absorption is possible by providing a speed transition region having a gentle slope.
  • a driving without a fluctuation is made possible by controlling the flow rate to the outlet port (T port) across the entire of the present invention.
  • the inside pressure of the cyhnder connected to the T port can be increased by controlling the outlet flow rate to the outlet port (T port) by constructing the spool 10 to be small, thereby making the driving without fluctuation possible.
  • the present invention can utilize the hydraulic and pneumatic pressure, and when the speed adjustment is necessary, it can be achieved by moving the speed adjusting bolt
  • the present invention has great advantages that the speed of the spool 10 does not change with the pressure of the pump and that the position control is assured and the precision control is possible because the spool 10 is directly controlled by the solenoid.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)

Abstract

Premier mode de réalisation d'un clapet de commande rapide et lente utilisant la pression hydraulique et pneumatique, selon lequel un électroaimant rapide de droite (20), un électroaimant lent de droite (21), un électroaimant rapide de gauche (35) et un électroaimant lent de gauche (36) sont montés de part et d'autre d'une bobine (10) et sur le même axe que celle-ci, afin de permettre une commande rapide et lente; un piston rapide de droite (12) sous forme de tige annulaire à deux épaulements est prévu dans l'électroaimant rapide de droite (20); un piston lent de droite (13) possédant un axe (14) de régulation de vitesse de droite est prévu dans l'électroaimant lent de droite (21); un piston rapide de gauche (29) sous forme de tige annulaire à deux épaulements est prévu dans l'électroaimant rapide de gauche (35); et un piston lent de gauche (29) possédant un axe (14) de régulation de vitesse de gauche est prévu dans l'électroaimant lent de gauche (36). On a également prévu un deuxième mode de réalisation ou un troisième mode de réalisation, selon lequel une bobine (10) dotée d'une surépaisseur de gauche (48), d'une surépaisseur centrale et d'une surépaisseur de droite (49; 50), et de parties sailllantes de gauche et de droite (76; 77), un piston rapide sous forme de tige annulaire à deux épaulements, et un piston lent possédant un axe de régulation de vitesse, sont disposés successivement sur l'axe de la bobine; une tige de pression est prévue dans le piston rapide; un électroaimant rapide entoure la face extérieure du piston rapide; et un électroaimant lent entoure la face extérieure du piston lent.
PCT/KR1993/000019 1993-02-17 1993-03-12 Clapet de commande rapide et lente utilisant la pression hydraulique et penumatique WO1994019612A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU36490/93A AU3649093A (en) 1993-02-17 1993-03-12 High speed and low speed control valve utilizing hydraulic and pneumatic pressure

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1993/2147 1993-02-17
KR1019930002147A KR940020027A (ko) 1993-02-17 1993-02-17 유,공압을 이용한 고속,저속 제어밸브

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WO1994019612A1 true WO1994019612A1 (fr) 1994-09-01

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KR (1) KR940020027A (fr)
AU (1) AU3649093A (fr)
WO (1) WO1994019612A1 (fr)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
WO2005124207A1 (fr) * 2004-06-21 2005-12-29 Robertshaw Controls Company Soupape a debit variable
EP1785654A1 (fr) * 2005-11-10 2007-05-16 OIL CONTROL S.p.A. Electrovanne à trois voies
US7806140B2 (en) 2006-04-18 2010-10-05 Robertshaw Controls Company Power saving locking coil

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US4310143A (en) * 1978-11-29 1982-01-12 Gresen Manufacturing Company Electrically controlled proportional valve
DE3038338A1 (de) * 1980-10-10 1982-05-06 Zahnräderfabrik Renk AG, 8900 Augsburg Elektro-magnetisches mehrwegeventil
US4565219A (en) * 1982-09-13 1986-01-21 The Oilgear Japan Company Multiple-position solenoid-operated control valve
DE3540553A1 (de) * 1985-11-15 1987-05-27 Reinhard Ing Grad Kucharzyk Geraeuscharm steuerndes wegeventil
DE3708248A1 (de) * 1987-03-13 1988-09-22 Herion Werke Kg Wegeventil
US4842020A (en) * 1988-07-29 1989-06-27 Humphrey Products Company Double-solenoid single-stem four-way valve
US4949741A (en) * 1989-01-10 1990-08-21 Vickers, Incorporated Power transmission
US4953590A (en) * 1988-04-22 1990-09-04 Tokyo Keiki Company Ltd. Electromagnetic directional control valve

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4310143A (en) * 1978-11-29 1982-01-12 Gresen Manufacturing Company Electrically controlled proportional valve
DE3038338A1 (de) * 1980-10-10 1982-05-06 Zahnräderfabrik Renk AG, 8900 Augsburg Elektro-magnetisches mehrwegeventil
US4565219A (en) * 1982-09-13 1986-01-21 The Oilgear Japan Company Multiple-position solenoid-operated control valve
DE3540553A1 (de) * 1985-11-15 1987-05-27 Reinhard Ing Grad Kucharzyk Geraeuscharm steuerndes wegeventil
DE3708248A1 (de) * 1987-03-13 1988-09-22 Herion Werke Kg Wegeventil
US4953590A (en) * 1988-04-22 1990-09-04 Tokyo Keiki Company Ltd. Electromagnetic directional control valve
US4842020A (en) * 1988-07-29 1989-06-27 Humphrey Products Company Double-solenoid single-stem four-way valve
US4949741A (en) * 1989-01-10 1990-08-21 Vickers, Incorporated Power transmission

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005124207A1 (fr) * 2004-06-21 2005-12-29 Robertshaw Controls Company Soupape a debit variable
JP2008503694A (ja) * 2004-06-21 2008-02-07 ロバートショウ コントロールズ カンパニー 可変流量バルブ
US7455073B2 (en) 2004-06-21 2008-11-25 Robertshaw Controls Company Variable flow valve
EP1785654A1 (fr) * 2005-11-10 2007-05-16 OIL CONTROL S.p.A. Electrovanne à trois voies
US7806140B2 (en) 2006-04-18 2010-10-05 Robertshaw Controls Company Power saving locking coil

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AU3649093A (en) 1994-09-14
KR940020027A (ko) 1994-09-15

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