CA1195586A - Proportional control valve - Google Patents
Proportional control valveInfo
- Publication number
- CA1195586A CA1195586A CA000433238A CA433238A CA1195586A CA 1195586 A CA1195586 A CA 1195586A CA 000433238 A CA000433238 A CA 000433238A CA 433238 A CA433238 A CA 433238A CA 1195586 A CA1195586 A CA 1195586A
- Authority
- CA
- Canada
- Prior art keywords
- valve
- fluid
- bore
- sleeve
- inlet
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
- F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow 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
- 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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
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- 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
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
- F16K31/406—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston
- F16K31/408—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston the discharge being effected through the piston and being blockable by an electrically-actuated member making contact with the piston
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Magnetically Actuated Valves (AREA)
- Control Of Fluid Pressure (AREA)
Abstract
A PROPORTIONAL CONTROL VALVE
Abstract of the Disclosure A proportional control valve is described having a housing with a bore formed therein. Communicating with the bore is a fluid inlet and a fluid outlet, the opening therebetween being controlled by a first valve. When the first valve is in a closed position, fluid flow between the inlet and the outlet is prevented and when the first valve is in an open position, fluid flow therebetween is permitted. The first valve contains passages therein which communicate between the fluid inlet and the fluid outlet. Also positioned within the bore is a second valve which is aligned with one of the passages formed in the first valve. As the second valve is moved to a closed position, fluid flow through the passage is cut off and as the second valve is opened, fluid flow through the passage is permitted. A
sleeve is also positioned within the bore which is constructed of a non-magnetic section sandwiched between two magnetic end sections. The sleeve contacts the first valve and is formed such that the non-magnetic section surrounds a portion of the second valve. The proportional control valve also contains an electromagnet for linearly moving the second valve in response to an input signal. Movement of the second valve creates a fluid flow path across the first valve and establishes a pressure differential which causes the first valve to follow the movement of the second valve. Likewise, movement of the first valve causes the sleeve to move in a light direction thereby providing an essentially constant air gap between the upper surface of the second valve and the end of the sleeve. This constant air gap is beneficial in that it permits the stroke of the first valve to be increased without increasing the power input to the electromagnet.
Abstract of the Disclosure A proportional control valve is described having a housing with a bore formed therein. Communicating with the bore is a fluid inlet and a fluid outlet, the opening therebetween being controlled by a first valve. When the first valve is in a closed position, fluid flow between the inlet and the outlet is prevented and when the first valve is in an open position, fluid flow therebetween is permitted. The first valve contains passages therein which communicate between the fluid inlet and the fluid outlet. Also positioned within the bore is a second valve which is aligned with one of the passages formed in the first valve. As the second valve is moved to a closed position, fluid flow through the passage is cut off and as the second valve is opened, fluid flow through the passage is permitted. A
sleeve is also positioned within the bore which is constructed of a non-magnetic section sandwiched between two magnetic end sections. The sleeve contacts the first valve and is formed such that the non-magnetic section surrounds a portion of the second valve. The proportional control valve also contains an electromagnet for linearly moving the second valve in response to an input signal. Movement of the second valve creates a fluid flow path across the first valve and establishes a pressure differential which causes the first valve to follow the movement of the second valve. Likewise, movement of the first valve causes the sleeve to move in a light direction thereby providing an essentially constant air gap between the upper surface of the second valve and the end of the sleeve. This constant air gap is beneficial in that it permits the stroke of the first valve to be increased without increasing the power input to the electromagnet.
Description
1~ 5 ~
1 A PROPORTIO~AL CONTROL VALVE
Field of the Invention This invention relates to a proportional control valve for regulating fluid flow between two functions.
Background of the Invention Various types of proportional control valves e~ist ~hich use multiple valves which are electromagnetically actuated.
Examples of such are described in U.S. Patents 3,893,471 issued to Byers~ Jr.; and 4,300,873 issued to Mowbray et al. In these types of proportional control valves, the force which can be developed by a given size solenoid i5 inversely proportional to the air gap across which the magnetic flux must jump for any given current. The prior art valves have modified the magnetic characteristics to obtain a constant force over a wide air gap thereby producing a linear relationship between input current and valve stroke. By doing so, the effect of the air gap is minimized and the ~aximum useable force level is sacrificed.
This means that the valve stroke and thus the flow capacity of the valve can only be increased by increasing the power input to the valve, which is not feasible in many instances~
Now, a proportional control valve has been invented which utilizes an essentially constant and small air gap across which a magnetic flux crosses such that an increased force is obtainable thereby increasing the length of stroke of the 25 valve.
Summary of the Invention Briefly, this invention relates to a proportional control valve having a housing with a bore formed therein and having a fluid inlet and a fluid outlet communicating with the bore.
30 Positioned within the bore are first and second valves, ~ith the first valve located between the fluid inlet and the fluid outlet. The first valve has passages formed therein to permit fluid flow across it and is movable between a closed position blocking fluid flow from the inlet to the outlet and an open 35 position permitting fluid flow from the inlet to the outlet.
The second valve is positioned above the first valve and is aligned with one of the passages formed in the first valve. The second valve is also movable be~ween a closed position blocking fluid flow thro~gh the aligned passage and an open position ~0 permitting fluid flow therethrough. Surrounding the second $~
f~
~5~
1 ~alve and contacting an upper portion of the first valve is a sleeve having a magnetic end section which is axially spaced apart from an upper surface of the second valve and a non-magnetic section which surrounds a portion of the second valve.
The control valve also includes an electromagnetic member for linearly moving the second valve. As the second valve moves upward, a flow path is formed from the fluid inlet through the first valve to the fluid outlet. This flow path establishes a pressure differential across the ~irst valve which causes the first valve to ~ollow the upward movement of the second valve.
~s the first valve moves upward the sleeve moves in a like direction thereby providing an essentially constant air gap between the upper surface of the second valve and the end of the sleeve. By maintaining a constant air gap, the stroke of the first valve can be increased without increasing the power input to the electromagnetic member.
The general object of this invention is to provide a proportional control valve for regulating fluid flow between two functions. ~ more specific object of this invention is to 20 provide a proportional control valve which utilizes an essentially constant and small air gap across which a magnetic flux crosses, such that an increased force is obtainable thereby increasing the length of stroke of the valve.
Another object of this invention is to provide a 25 proportional control valve having a pair of interacting poppet members which exhibit a position feedback characteristic.
Still another object of this invention is to provide a proportional control valve which is less prone to contamination than conventional spool valves~ -Still further, an object of this invention is to provide aproportional control valve which is easy to manufacture and economical to build.
Other objects and advantages of the present invention will become more apparent to those skilled in the art in view of the 35 following description and the accompanying drawings.
Brief Description of the Drawings Fig. 1 is a schematic view of the proportional control valve having an essentially constant air gap across which the magnetic flux crosses and having a pair of valves both shown in a down or 40 closed position.
s~i 1 Fig. 2 is a schematic view of the proportional control valve showing the top valve in a raised position~
Fig. 3 is a schematic view of the proportional control valve showing both valves in a raised position.
Fig. 4 is a schematic view of a three-way proportional control valve using two valve cartridges for controlling the movement of a load therebetween.
Fig. 5 is a schematic view of a Eour-way proportional control valve using four valve cartridges.
Detailed Description of the Preferred Em _dimellt Referring to Figs. 1-3, a proportional control valve 10 is shown having a housing 12 with a bore 14 formed therein. Formed on an inner surface of the bore 14 is a valve seat 16.
Communicating with the bore 14 is a fluid inlet 18 and a fluid outlet 20. The fluid inlet 18 is connected to a fluid reservoir 22 by a fluid pump 24 and a check valve 26. The fluid outlet 20, on the other hand, is connected to an output function 28.
In an agricultural or industrial vehicle, the output function 28 could be one or more hydraulic cylinders or motors which raise or lower an attached implement.
Positioned within the bore 14 between the fluid inlet 18 and the fluid outlet 20 is a first valve 30, preferably a poppet valve. The first valve 30 has a top surface 32 and a bottom surface 34~ A lower peripheral surface 36 on the first valve 30 is mateable with the valve seat 16. Preferably, the net effective area of the bottom surface 34 over which a pressurized fluid can act, is approximately equal to the net effective area of the top surface 32 over which a pressurized fluid can act.
The importance of having approximately equal net effective areas 30 on both the top and bottom surfaces, 32 and 34 respectively, will be explained shortly when describing the operation of the proportional control valve 10. The first valve 30 divides the bore 14 into two spaced apart cavities, denoted as a supply cavity 37 and a control cavity 39. The supply cavity 37 is 35 located below the bottom surface 34 of the first valve 30 while the control cavity 39 is located above the top surface 32 of the Eirst valve 30.
Formed within the first valve 30 is a first fluid passage 38 and a second fluid passage 40. The first fluid passage 38 extends from the top surface 32 to the bottom surface 34 and ~, ~ _ 3 _ i , l functions as a restriction Rl therebetween to create a pressure drop across tlle first valve 30. In order to obtain a more desirable pressure drop for different pressure valves~ a plug 42 containing a pre-sized orifice 44 can be inserted into the first passage 38. In either case, a pressure drop is created across the first valve 30, with the high pressure generally being present at the bottom surface 34O
The second fluid passage 40 extends from the top surface 32 of the first valve 30 to an exterior point 46 on the first valve 30 which is located between the top and bottom surfaces, 32 and 34 respectively. The exterior point 46 is always in fluid communication with the fluid outlet 20 regardless of the position of the first valve 30 within the bore 14~ A plug 48, which contains a pre-sized orifice 50, can also be inserted into the second passage 40 to serve the same function as the plug 42 and creates a restriction denoted R~.
The first valve 30 is movable through a limited range by fluid pressure between a closed position wherein the lower peripheral surface 36 is resting on the valve seat 16 and an 20 open position wherein the lower peripheral surface 36 is spaced apart from the valve seat 16.
A second valve 52, preferably a poppet valve, having a top surface 53 is positioned in the bore 14 adjacent to the top surface 32 of the first valve. The second valve 52 is aligned 25 with the entrance to the second passage 40 and is linearly movable between a closed position blocking fluid flow through the second passage 40 and an open position, as shown in Fig. 2, permitting fluid flow through the second passage 40. The size and configuration of a lower tip 54 of the second valve 52 can 30 be designed such that a flow restriction R2 creates flow forces around the tip 54 to produce a pressure compensated flow control across the entire valve lO.
The proportional conteol valve lO also includes a sleeve 56 which is positioned in the bore 14 and contacts the top surface 32 of the first valve 30. The sleeve 56 is constructed of a magnetic end member 57, a non-magnetic tubular section 58 and a magnetic tubular section 59. The magnetic end member 57 is spaced away from the top surface 53 of the second valve 52 such that a small air gap 60 is formed therebetween. This small air - 4 ~
gap 60 will stay relatively constant throughout the operation of the valve 10. The non-magnetic tubular section 58 is arranged about a top portion 62 of the second valve 52 so as to permit a madnetic flux produced by an electromagnetic element 64, such as a solenoid, to linerly move the second valve 52 upward when the electromagnetic element 64 is energized by an input signal 65.
As is well known to those skilled in the electrical art, the second valve 52 acts as an armature and is pulled upward by the magnetic flux when current is supplied to the electromagnetic element 64.
The electromagnetic element 64 includes a coil 66 which is enclosed by a cap 68. The coil 66 partiallu encircles a support member 70 which is constructed of a non-magnetic member 74 sandwiched between two magnetic members 72 and 76. The non-magnetic member 74 is radially aligned with the non-magnetic section 58 of the sleeve 56 so as to enable the magnetic flux to form a loop from the coil 66 through the magnetic members 76 and 59, the top portion 62 of the second valve 52, across the air gap 60 and into the magnetic end member 57 of the sleeve 56. By maintaining an essentially constant and small air gap 60 acros which th emagnetic flux crosses, a larger force can be obtained which will increase the length of stroke of the first valve 30.
This translates into an increased flow capacity between the fluid ubket 18 and the fluid outlet 20, denoted as R3 in Fig.
3.
Lastly, the proportional control valve 10 contains a pair of springs 78 and 80 which ar epositioned in the bore 14. The 32 of the first valve 30 while the spring 80 presses against the top surface 53 of the second valve 52 to contantly urge the second valve 53 of the second valve 52 to constantly urge the second valve 52 downward against the first valve 30. Both of the springs 78 and 80 help assure thathe air gap 60 will remain essentially constant at all times. In addition, the spring 78 also assists in urging the first valve 30 back towards it closed position once the pressure differentialy across the first valve 30 decreases thereb assuring that the first valve 30 will not be stuck in an open or partially open position.
3~
1 Operation The operation of the proportional control valve 10 will be described starting with Fig. 1 wherein both the first and second valves, 30 and 52 respectively, are in the down or closed posltions. The pressurized fluid from the pump 24 will fill the supply cavity 37, the first passage 38 and the control cavity 39 but since there i5 no flow path between the fluid inlet 18 and the fluid outlet 20, there will be no pressure drop across the first valve 30. This equilibrium of pressure on the first valve 30 along with the force of the spring 78 will assure that the Eirst valve 30 remains seated against the valve seat 16.
In order to facilitate fluid flow through the valve 10, the electrical input signal 65 is triggered to energize the electromagnetic element 64. The coil 66 of the e].ectromagnetic element 64 then produces a magnetic flux which pulls the second valve 52 upward so that a flow path is established through the second passage 40, see Fig. 2. The amount that the second valve 52 moves upward is directly related to the amount of current supplied to the electromagnetic element 640 It should be noted that the flow path will be Erom the fluid inlet 18 to the fluid outlet 20. A reverse flow is prevented by the presence of the check valve 26.
As fluid flows out of the control cavity 39, a pressure differential is created across the first valve 30 such that the 25 pressure on the bottom surface 34 is greater than the pressure on the top surface 32. When this pressure difference exceeds the downward biasing force in the spring 78, the first valve 30 will move upward away from the valve seat 16, see Fig. 3. In so doing, the third fluid opening R3 is formed between the fluid inlet 18 and fluid outlet 20. As the first valve 30 moves upward, it moves the sleeve 56 in a like direction so that the air gap 60 will remain essentially constant. The only possible variation in the height of the air gap 60 will occur upon the initial movement o:E the second valve 52~
In actual operation, the first valve 30, the second valve 52 and the sleeve 56 will move upward and downward simultaneously once a pressure di:Eferential is created across the first valve 30. This corresponding linear movement of the two valves~ 30 and 52, creates a position feedback characteristic in the 1 proportional control va~ve lO. The position feedback is a result of the variable orifice R2 which is formed at the entrance to the second passage 40. Should the pressure of the incoming fluid drop, the first valve 30 would move downward due to the reduced pressure impinging on the bottom surface 34. As the first valve 30 moves downward, the size of the opening R3 would decrease thereby restricting the outflow of fluid from the supply cavity 37. At the same time, the si2e of the variable orifice R2 will increasel thereby decreasing the pressurized force acting on the top surface 32. Almost instantaneously~ the first valve 30 will move to an equilibrium position. Such compensating movement is referred to as position feedback and will occur should the second valve 52 be moved or should the pressure across the proportional control valve 10 change.
Alternative Arrangements The proportional control valve lO can be combined with one or more control valves to produce multiple control valves, such as three~way and four-way valves. In Fig. 4, two control valves or cartridges designated 10' and 10'' have been connected together to form a three-way valve such that the output of the control cartridye 10' is directed by conduit 82 to a function 84. The function 84 is depicted as a hydraulic cylinder 86 having a piston 88 with a piston rod 90 connected to a load.
The conduit 82 is also connected to the supply _avity 37 of the control cartridge 10'' by a conduit 92. In Fig. 4, both of the control cartridges 10' and 10'', have their respective first and second valves 30 and 52 positioned in a down position such that no fluid is permitted to flow through them. The load therefore cannot move the piston 88 because the fluid within the hydraulic cylinder 86 has no place to go. This corresponds to a neutral position. When the first cartridge 10' has its valves 30 and 52 in the open position, such that fluid flow is permitted from the pump 24 through the conduit 82 to the hydraulic cylinder 86 and when the second cartridge 10 " has its valves in the closed 35 position, the piston 88 will be moved upwards. Likewise, when the cartridge 10' has its valves 30 and 52 in the closed position and the cartridge 10'' has its valves 30 and 52 in an open position, fl~id is permitted to flow out of the hydraulic cylinder 86 thereby permitting the piston 88 to move downwards.
5~
l Turning now to Fig. 5, an example of a Eour-way control valve is depicted where.in four control valves or cartridges, denoted as lOa~ lOb, lOc and lOd, are arranged to actuate a double-acting piston 94 The piston 94 is positioned within a hydraulic cylinder 96 and is connected by a single piston rod 98 to a load lOOo In the position shown, the valves within the first cartridge lOa are open permitting pressurized fluid to flow from the pump 2~ through a conduit 102 into a chamber 104 which is located on the left hand side of the piston 94. The valves within the second cartridge lOb are also open such that fluid in a chamber 106, located on the r.ight-hand side of the piston 94, can flow through a conduit 108 and through a return conduit llO to the reservoir 22. The valves within the cartridges lOc and lOd remain closed during this segment of the cycle but both will be opened when cartridges lOa and lOb are closed to permit the piston 94 to move back to the leEt. The four-way control valve has four modes, in the first or neutral mode all the valves within the cartridges lOa, l~b, lOc and lOd are closed. In the second mode, that described above, the valves within the cartridges lOa and lOb are open and the valves within the cartridges lOc and lOd are closed, thereby forcing the piston 94 to the right. In the third mode, the valves within the cartridges lOa and lOb are closed and the valves within the cartridges lOc and lOd are open, thereby forcing the 25 piston 94 to the left. And in the fourth or float mode, the valves within the cartridges lOa and lOc are closed and the valves within the cartridges lOb and lOd are open, thereby allowing the piston to move in either direction depending on the pressure differential across the piston 94.
It should be noted that various combinations and arrangements using a plurality of proportional control valves 10 or cartridges are possible.
While this invention has been described in conjunction with a specific embodiment and in two different arrangements, it is 35 to be understood that many alternatives, modifications, and variations will be apparent to those skilled in the art in light of the aforegoing description. Accordingly, this invention is intended to embrace al] such alternatives, modifications, and variations which fall within the spirit and scope of the appended claims.
1 A PROPORTIO~AL CONTROL VALVE
Field of the Invention This invention relates to a proportional control valve for regulating fluid flow between two functions.
Background of the Invention Various types of proportional control valves e~ist ~hich use multiple valves which are electromagnetically actuated.
Examples of such are described in U.S. Patents 3,893,471 issued to Byers~ Jr.; and 4,300,873 issued to Mowbray et al. In these types of proportional control valves, the force which can be developed by a given size solenoid i5 inversely proportional to the air gap across which the magnetic flux must jump for any given current. The prior art valves have modified the magnetic characteristics to obtain a constant force over a wide air gap thereby producing a linear relationship between input current and valve stroke. By doing so, the effect of the air gap is minimized and the ~aximum useable force level is sacrificed.
This means that the valve stroke and thus the flow capacity of the valve can only be increased by increasing the power input to the valve, which is not feasible in many instances~
Now, a proportional control valve has been invented which utilizes an essentially constant and small air gap across which a magnetic flux crosses such that an increased force is obtainable thereby increasing the length of stroke of the 25 valve.
Summary of the Invention Briefly, this invention relates to a proportional control valve having a housing with a bore formed therein and having a fluid inlet and a fluid outlet communicating with the bore.
30 Positioned within the bore are first and second valves, ~ith the first valve located between the fluid inlet and the fluid outlet. The first valve has passages formed therein to permit fluid flow across it and is movable between a closed position blocking fluid flow from the inlet to the outlet and an open 35 position permitting fluid flow from the inlet to the outlet.
The second valve is positioned above the first valve and is aligned with one of the passages formed in the first valve. The second valve is also movable be~ween a closed position blocking fluid flow thro~gh the aligned passage and an open position ~0 permitting fluid flow therethrough. Surrounding the second $~
f~
~5~
1 ~alve and contacting an upper portion of the first valve is a sleeve having a magnetic end section which is axially spaced apart from an upper surface of the second valve and a non-magnetic section which surrounds a portion of the second valve.
The control valve also includes an electromagnetic member for linearly moving the second valve. As the second valve moves upward, a flow path is formed from the fluid inlet through the first valve to the fluid outlet. This flow path establishes a pressure differential across the ~irst valve which causes the first valve to ~ollow the upward movement of the second valve.
~s the first valve moves upward the sleeve moves in a like direction thereby providing an essentially constant air gap between the upper surface of the second valve and the end of the sleeve. By maintaining a constant air gap, the stroke of the first valve can be increased without increasing the power input to the electromagnetic member.
The general object of this invention is to provide a proportional control valve for regulating fluid flow between two functions. ~ more specific object of this invention is to 20 provide a proportional control valve which utilizes an essentially constant and small air gap across which a magnetic flux crosses, such that an increased force is obtainable thereby increasing the length of stroke of the valve.
Another object of this invention is to provide a 25 proportional control valve having a pair of interacting poppet members which exhibit a position feedback characteristic.
Still another object of this invention is to provide a proportional control valve which is less prone to contamination than conventional spool valves~ -Still further, an object of this invention is to provide aproportional control valve which is easy to manufacture and economical to build.
Other objects and advantages of the present invention will become more apparent to those skilled in the art in view of the 35 following description and the accompanying drawings.
Brief Description of the Drawings Fig. 1 is a schematic view of the proportional control valve having an essentially constant air gap across which the magnetic flux crosses and having a pair of valves both shown in a down or 40 closed position.
s~i 1 Fig. 2 is a schematic view of the proportional control valve showing the top valve in a raised position~
Fig. 3 is a schematic view of the proportional control valve showing both valves in a raised position.
Fig. 4 is a schematic view of a three-way proportional control valve using two valve cartridges for controlling the movement of a load therebetween.
Fig. 5 is a schematic view of a Eour-way proportional control valve using four valve cartridges.
Detailed Description of the Preferred Em _dimellt Referring to Figs. 1-3, a proportional control valve 10 is shown having a housing 12 with a bore 14 formed therein. Formed on an inner surface of the bore 14 is a valve seat 16.
Communicating with the bore 14 is a fluid inlet 18 and a fluid outlet 20. The fluid inlet 18 is connected to a fluid reservoir 22 by a fluid pump 24 and a check valve 26. The fluid outlet 20, on the other hand, is connected to an output function 28.
In an agricultural or industrial vehicle, the output function 28 could be one or more hydraulic cylinders or motors which raise or lower an attached implement.
Positioned within the bore 14 between the fluid inlet 18 and the fluid outlet 20 is a first valve 30, preferably a poppet valve. The first valve 30 has a top surface 32 and a bottom surface 34~ A lower peripheral surface 36 on the first valve 30 is mateable with the valve seat 16. Preferably, the net effective area of the bottom surface 34 over which a pressurized fluid can act, is approximately equal to the net effective area of the top surface 32 over which a pressurized fluid can act.
The importance of having approximately equal net effective areas 30 on both the top and bottom surfaces, 32 and 34 respectively, will be explained shortly when describing the operation of the proportional control valve 10. The first valve 30 divides the bore 14 into two spaced apart cavities, denoted as a supply cavity 37 and a control cavity 39. The supply cavity 37 is 35 located below the bottom surface 34 of the first valve 30 while the control cavity 39 is located above the top surface 32 of the Eirst valve 30.
Formed within the first valve 30 is a first fluid passage 38 and a second fluid passage 40. The first fluid passage 38 extends from the top surface 32 to the bottom surface 34 and ~, ~ _ 3 _ i , l functions as a restriction Rl therebetween to create a pressure drop across tlle first valve 30. In order to obtain a more desirable pressure drop for different pressure valves~ a plug 42 containing a pre-sized orifice 44 can be inserted into the first passage 38. In either case, a pressure drop is created across the first valve 30, with the high pressure generally being present at the bottom surface 34O
The second fluid passage 40 extends from the top surface 32 of the first valve 30 to an exterior point 46 on the first valve 30 which is located between the top and bottom surfaces, 32 and 34 respectively. The exterior point 46 is always in fluid communication with the fluid outlet 20 regardless of the position of the first valve 30 within the bore 14~ A plug 48, which contains a pre-sized orifice 50, can also be inserted into the second passage 40 to serve the same function as the plug 42 and creates a restriction denoted R~.
The first valve 30 is movable through a limited range by fluid pressure between a closed position wherein the lower peripheral surface 36 is resting on the valve seat 16 and an 20 open position wherein the lower peripheral surface 36 is spaced apart from the valve seat 16.
A second valve 52, preferably a poppet valve, having a top surface 53 is positioned in the bore 14 adjacent to the top surface 32 of the first valve. The second valve 52 is aligned 25 with the entrance to the second passage 40 and is linearly movable between a closed position blocking fluid flow through the second passage 40 and an open position, as shown in Fig. 2, permitting fluid flow through the second passage 40. The size and configuration of a lower tip 54 of the second valve 52 can 30 be designed such that a flow restriction R2 creates flow forces around the tip 54 to produce a pressure compensated flow control across the entire valve lO.
The proportional conteol valve lO also includes a sleeve 56 which is positioned in the bore 14 and contacts the top surface 32 of the first valve 30. The sleeve 56 is constructed of a magnetic end member 57, a non-magnetic tubular section 58 and a magnetic tubular section 59. The magnetic end member 57 is spaced away from the top surface 53 of the second valve 52 such that a small air gap 60 is formed therebetween. This small air - 4 ~
gap 60 will stay relatively constant throughout the operation of the valve 10. The non-magnetic tubular section 58 is arranged about a top portion 62 of the second valve 52 so as to permit a madnetic flux produced by an electromagnetic element 64, such as a solenoid, to linerly move the second valve 52 upward when the electromagnetic element 64 is energized by an input signal 65.
As is well known to those skilled in the electrical art, the second valve 52 acts as an armature and is pulled upward by the magnetic flux when current is supplied to the electromagnetic element 64.
The electromagnetic element 64 includes a coil 66 which is enclosed by a cap 68. The coil 66 partiallu encircles a support member 70 which is constructed of a non-magnetic member 74 sandwiched between two magnetic members 72 and 76. The non-magnetic member 74 is radially aligned with the non-magnetic section 58 of the sleeve 56 so as to enable the magnetic flux to form a loop from the coil 66 through the magnetic members 76 and 59, the top portion 62 of the second valve 52, across the air gap 60 and into the magnetic end member 57 of the sleeve 56. By maintaining an essentially constant and small air gap 60 acros which th emagnetic flux crosses, a larger force can be obtained which will increase the length of stroke of the first valve 30.
This translates into an increased flow capacity between the fluid ubket 18 and the fluid outlet 20, denoted as R3 in Fig.
3.
Lastly, the proportional control valve 10 contains a pair of springs 78 and 80 which ar epositioned in the bore 14. The 32 of the first valve 30 while the spring 80 presses against the top surface 53 of the second valve 52 to contantly urge the second valve 53 of the second valve 52 to constantly urge the second valve 52 downward against the first valve 30. Both of the springs 78 and 80 help assure thathe air gap 60 will remain essentially constant at all times. In addition, the spring 78 also assists in urging the first valve 30 back towards it closed position once the pressure differentialy across the first valve 30 decreases thereb assuring that the first valve 30 will not be stuck in an open or partially open position.
3~
1 Operation The operation of the proportional control valve 10 will be described starting with Fig. 1 wherein both the first and second valves, 30 and 52 respectively, are in the down or closed posltions. The pressurized fluid from the pump 24 will fill the supply cavity 37, the first passage 38 and the control cavity 39 but since there i5 no flow path between the fluid inlet 18 and the fluid outlet 20, there will be no pressure drop across the first valve 30. This equilibrium of pressure on the first valve 30 along with the force of the spring 78 will assure that the Eirst valve 30 remains seated against the valve seat 16.
In order to facilitate fluid flow through the valve 10, the electrical input signal 65 is triggered to energize the electromagnetic element 64. The coil 66 of the e].ectromagnetic element 64 then produces a magnetic flux which pulls the second valve 52 upward so that a flow path is established through the second passage 40, see Fig. 2. The amount that the second valve 52 moves upward is directly related to the amount of current supplied to the electromagnetic element 640 It should be noted that the flow path will be Erom the fluid inlet 18 to the fluid outlet 20. A reverse flow is prevented by the presence of the check valve 26.
As fluid flows out of the control cavity 39, a pressure differential is created across the first valve 30 such that the 25 pressure on the bottom surface 34 is greater than the pressure on the top surface 32. When this pressure difference exceeds the downward biasing force in the spring 78, the first valve 30 will move upward away from the valve seat 16, see Fig. 3. In so doing, the third fluid opening R3 is formed between the fluid inlet 18 and fluid outlet 20. As the first valve 30 moves upward, it moves the sleeve 56 in a like direction so that the air gap 60 will remain essentially constant. The only possible variation in the height of the air gap 60 will occur upon the initial movement o:E the second valve 52~
In actual operation, the first valve 30, the second valve 52 and the sleeve 56 will move upward and downward simultaneously once a pressure di:Eferential is created across the first valve 30. This corresponding linear movement of the two valves~ 30 and 52, creates a position feedback characteristic in the 1 proportional control va~ve lO. The position feedback is a result of the variable orifice R2 which is formed at the entrance to the second passage 40. Should the pressure of the incoming fluid drop, the first valve 30 would move downward due to the reduced pressure impinging on the bottom surface 34. As the first valve 30 moves downward, the size of the opening R3 would decrease thereby restricting the outflow of fluid from the supply cavity 37. At the same time, the si2e of the variable orifice R2 will increasel thereby decreasing the pressurized force acting on the top surface 32. Almost instantaneously~ the first valve 30 will move to an equilibrium position. Such compensating movement is referred to as position feedback and will occur should the second valve 52 be moved or should the pressure across the proportional control valve 10 change.
Alternative Arrangements The proportional control valve lO can be combined with one or more control valves to produce multiple control valves, such as three~way and four-way valves. In Fig. 4, two control valves or cartridges designated 10' and 10'' have been connected together to form a three-way valve such that the output of the control cartridye 10' is directed by conduit 82 to a function 84. The function 84 is depicted as a hydraulic cylinder 86 having a piston 88 with a piston rod 90 connected to a load.
The conduit 82 is also connected to the supply _avity 37 of the control cartridge 10'' by a conduit 92. In Fig. 4, both of the control cartridges 10' and 10'', have their respective first and second valves 30 and 52 positioned in a down position such that no fluid is permitted to flow through them. The load therefore cannot move the piston 88 because the fluid within the hydraulic cylinder 86 has no place to go. This corresponds to a neutral position. When the first cartridge 10' has its valves 30 and 52 in the open position, such that fluid flow is permitted from the pump 24 through the conduit 82 to the hydraulic cylinder 86 and when the second cartridge 10 " has its valves in the closed 35 position, the piston 88 will be moved upwards. Likewise, when the cartridge 10' has its valves 30 and 52 in the closed position and the cartridge 10'' has its valves 30 and 52 in an open position, fl~id is permitted to flow out of the hydraulic cylinder 86 thereby permitting the piston 88 to move downwards.
5~
l Turning now to Fig. 5, an example of a Eour-way control valve is depicted where.in four control valves or cartridges, denoted as lOa~ lOb, lOc and lOd, are arranged to actuate a double-acting piston 94 The piston 94 is positioned within a hydraulic cylinder 96 and is connected by a single piston rod 98 to a load lOOo In the position shown, the valves within the first cartridge lOa are open permitting pressurized fluid to flow from the pump 2~ through a conduit 102 into a chamber 104 which is located on the left hand side of the piston 94. The valves within the second cartridge lOb are also open such that fluid in a chamber 106, located on the r.ight-hand side of the piston 94, can flow through a conduit 108 and through a return conduit llO to the reservoir 22. The valves within the cartridges lOc and lOd remain closed during this segment of the cycle but both will be opened when cartridges lOa and lOb are closed to permit the piston 94 to move back to the leEt. The four-way control valve has four modes, in the first or neutral mode all the valves within the cartridges lOa, l~b, lOc and lOd are closed. In the second mode, that described above, the valves within the cartridges lOa and lOb are open and the valves within the cartridges lOc and lOd are closed, thereby forcing the piston 94 to the right. In the third mode, the valves within the cartridges lOa and lOb are closed and the valves within the cartridges lOc and lOd are open, thereby forcing the 25 piston 94 to the left. And in the fourth or float mode, the valves within the cartridges lOa and lOc are closed and the valves within the cartridges lOb and lOd are open, thereby allowing the piston to move in either direction depending on the pressure differential across the piston 94.
It should be noted that various combinations and arrangements using a plurality of proportional control valves 10 or cartridges are possible.
While this invention has been described in conjunction with a specific embodiment and in two different arrangements, it is 35 to be understood that many alternatives, modifications, and variations will be apparent to those skilled in the art in light of the aforegoing description. Accordingly, this invention is intended to embrace al] such alternatives, modifications, and variations which fall within the spirit and scope of the appended claims.
Claims (9)
PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A proportional control valve comprising:
a) a housing having a bore formed therein;
b) a fluid inlet and a fluid outlet communicating with said bore;
c) a first valve positioned within said bore between said fluid inlet and said fluid outlet having passage means formed therein, said first valve being movable between a closed position blocking fluid flow from said inlet to said outlet and an open position permitting fluid flow from said inlet to said outlet;
d) a second valve positioned within said bore adjacent to said first valve and aligned with one of said passage means therein, said second valve being movable between a closed position blocking fluid flow through said aligned passage means and an open position permitting fluid flow through said aligned passage means;
e) a sleeve positioned within said bore which contacts said first valve, said sleeve having a non-magnetic section which surrounds a portion of said second valve and a magnetic end section which is axially spaced apart from an upper surface of said second valve; and f) electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a fluid flow path across said first valve and establishes a pressure differential thereacross causing movement of said first valve to follow movement of said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means.
a) a housing having a bore formed therein;
b) a fluid inlet and a fluid outlet communicating with said bore;
c) a first valve positioned within said bore between said fluid inlet and said fluid outlet having passage means formed therein, said first valve being movable between a closed position blocking fluid flow from said inlet to said outlet and an open position permitting fluid flow from said inlet to said outlet;
d) a second valve positioned within said bore adjacent to said first valve and aligned with one of said passage means therein, said second valve being movable between a closed position blocking fluid flow through said aligned passage means and an open position permitting fluid flow through said aligned passage means;
e) a sleeve positioned within said bore which contacts said first valve, said sleeve having a non-magnetic section which surrounds a portion of said second valve and a magnetic end section which is axially spaced apart from an upper surface of said second valve; and f) electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a fluid flow path across said first valve and establishes a pressure differential thereacross causing movement of said first valve to follow movement of said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means.
2. The proportional control valve of claim 1 wherein said electromagnetic means is a solenoid valve.
3. The proportional control valve of claim 1 wherein a longer stroke is obtainable for said first valve without increasing the power input to said electromagnetic means.
4. The proportional control valve of claim 1 wherein said second valve is linearly movable proportional to the amount of current supplied to said electromagnetic means.
5. A propositional control valve comprising:
a) a housing having a bore formed therein and with a valve seat formed about an inner surface of said bore;
b) a fluid inlet and a fluid outlet communicating with said bore;
c) a first valve positioned within said bore between said fluid inlet and said fluid outlet, said first valve having a top surface and a bottom surface with the net effective area of said top surface being appproximately equal to the net effective area of said bottom surface, a lower peripheral surface located about said bottom surface which is mateable with said valve seat, a first passage extending from said top surface to an and a second passage extending from said top surface to an exterior point on said first valve located between said top and bottom surfaces, said exterior point being in constant communication with said fluid outlet, said first valve being movable by fluid pressure between a first position wherein said lower peripheral surface is resting on said valve seat and a second position wherein said lower peripheral surface is away from said valve seat;
d) a second valve positioned within said bore adjacent to said top surface of said first valve and aligned with said second passage therein, said second valve being movable between a closed position blocking fluid flow through said second passage of said first valve and an open position permitting fluid flow through said second passage;
e) a sleeve positioned within said bore which contacts said top surface of said first valve, said sleeve having a non-magnetic section which surrounds a top portion of said second valve and a magnetic end section which is axially spaced a predetermined distance away from an upper surface of said second valve;
g) electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a flow path across said first valve and establishes a pressure differential thereacross causing said first valve to follow said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means.
a) a housing having a bore formed therein and with a valve seat formed about an inner surface of said bore;
b) a fluid inlet and a fluid outlet communicating with said bore;
c) a first valve positioned within said bore between said fluid inlet and said fluid outlet, said first valve having a top surface and a bottom surface with the net effective area of said top surface being appproximately equal to the net effective area of said bottom surface, a lower peripheral surface located about said bottom surface which is mateable with said valve seat, a first passage extending from said top surface to an and a second passage extending from said top surface to an exterior point on said first valve located between said top and bottom surfaces, said exterior point being in constant communication with said fluid outlet, said first valve being movable by fluid pressure between a first position wherein said lower peripheral surface is resting on said valve seat and a second position wherein said lower peripheral surface is away from said valve seat;
d) a second valve positioned within said bore adjacent to said top surface of said first valve and aligned with said second passage therein, said second valve being movable between a closed position blocking fluid flow through said second passage of said first valve and an open position permitting fluid flow through said second passage;
e) a sleeve positioned within said bore which contacts said top surface of said first valve, said sleeve having a non-magnetic section which surrounds a top portion of said second valve and a magnetic end section which is axially spaced a predetermined distance away from an upper surface of said second valve;
g) electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a flow path across said first valve and establishes a pressure differential thereacross causing said first valve to follow said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means.
6. The proportional control valve of claim 5 wherein said electromagnetic means is a solenoid valve.
7. The proportional control valve of claim 5 wherein said second valve is linearly movable proportional to the amount of current supplied to said electromagnetic means.
8. A three-way proportional control valve comprising:
a) two independent cartridges each having a housing with a bore formed therein, a fluid inlet and a fluid outlet communicating with said bore, a first valve positioned within said bore between said fluid inlet and said fluid outlet and having passage means formed therein, said first valve being movable between a closed position blocking fluid flow from said inlet to said outlet and an open position permitting fluid flow from said inlet to said outlet, a second valve positioned within said bore adjacent to said first valve and aligned with one of said passage means therein, said second valve being movable between a closed position blocking fluid flow through said aligned passage means and an open position permitting fluid flow through said aligned passage means, a sleeve positioned within said bore which contacts said first valve, said sleeve having a non-magnetic section which surrounds a portion of said second valve and a magnetic end section which is axially spaced apart from an upper surface of said second valve, and electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a flow path across said first valve and establishes a pressure differential thereacross causing said first valve to follow said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means;
b) a hydraulic cylinder enclosing a reciprocating piston and having a fluid opening at one end, said piston being connected by a piston rod to an output function;
c) a conduit connecting said fluid outlet of a first of said cartridges to both said fluid opening in said hydraulic cylinder and to said fluid inlet of said second cartridge;
d) a source of pressurized fluid connected to said fluid inlet of said first cartridge; and e) a reservoir for holding a quantity of fluid, said reservoir connected to both said source of pressurized fluid and to said fluid outlet of said second cartridge, wherein movement of said valves within said cartridges can control the movement and position of said piston within said hydraulic cylinder.
a) two independent cartridges each having a housing with a bore formed therein, a fluid inlet and a fluid outlet communicating with said bore, a first valve positioned within said bore between said fluid inlet and said fluid outlet and having passage means formed therein, said first valve being movable between a closed position blocking fluid flow from said inlet to said outlet and an open position permitting fluid flow from said inlet to said outlet, a second valve positioned within said bore adjacent to said first valve and aligned with one of said passage means therein, said second valve being movable between a closed position blocking fluid flow through said aligned passage means and an open position permitting fluid flow through said aligned passage means, a sleeve positioned within said bore which contacts said first valve, said sleeve having a non-magnetic section which surrounds a portion of said second valve and a magnetic end section which is axially spaced apart from an upper surface of said second valve, and electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a flow path across said first valve and establishes a pressure differential thereacross causing said first valve to follow said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means;
b) a hydraulic cylinder enclosing a reciprocating piston and having a fluid opening at one end, said piston being connected by a piston rod to an output function;
c) a conduit connecting said fluid outlet of a first of said cartridges to both said fluid opening in said hydraulic cylinder and to said fluid inlet of said second cartridge;
d) a source of pressurized fluid connected to said fluid inlet of said first cartridge; and e) a reservoir for holding a quantity of fluid, said reservoir connected to both said source of pressurized fluid and to said fluid outlet of said second cartridge, wherein movement of said valves within said cartridges can control the movement and position of said piston within said hydraulic cylinder.
9. A four-way proportional control valve comprising:
a) four independent cartridges each having a housing with a bore formed therein, a fluid inlet and a fluid outlet communicating with said bore, a first valve positioned within said bore between said fluid inlet and said fluid outlet and having passage means formed therein, said first valve being movable between a closed position blocking fluid flow from said inlet to said outlet and an open position permitting fluid flow from said inlet to said outlet, a second valve positioned within said bore adjacent to said first valve and aligned with one of said passage means therein, said second valve being movable between a closed position blocking fluid flow through said aligned passage means and an open position permitting fluid flow through said aligned passage means, a sleeve positioned within said bore which contacts said first valve, said sleeve having a non-magnetic section which surrounds a portion of said second valve and a magnetic end section which is axially spaced apart from an upper surface of said second valve, and electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a flow path across said first valve and establishes a pressure differential thereacross causing said first valve to follow said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means;
b) a reservoir for holding a quantity of fluid;
c) a pump connected to said reservoir for supplying pressurized fluid to said fluid inlet of a first of said cartridges;
d) a hydraulic cylinder enclosing a piston which has an attached piston rod connected to an output function, said piston partitioning said hydraulic cylinder into first and second fluid chambers;
e) a first conduit connecting said fluid outlet of said first cartridge to said first chamber of said hydraulic cylinder;
f) a second conduit connecting said fluid inlet of a second of said cartridges to said second chamber of said hydraulic cylinder;
g) a third conduit connecting said fluid outlet of said second cartridge to said reservoir;
h) a fourth conduit connecting said fluid inlet of a third of said cartridges to said pump;
i) a fifth conduit connecting said fluid outlet of said third cartridge to said second chamber of said hydraulic cylinder;
j) a sixth conduit connecting said fluid inlet of a fourth of said cartridges to said first chamber of said hydraulic cylinder; and k) a seventh conduit connecting said fluid outlet of said fourth cartridge to said reservoir, wherein movement of said valves within said cartridges can control the movement and position of said piston within said hydraulic cylinder.
a) four independent cartridges each having a housing with a bore formed therein, a fluid inlet and a fluid outlet communicating with said bore, a first valve positioned within said bore between said fluid inlet and said fluid outlet and having passage means formed therein, said first valve being movable between a closed position blocking fluid flow from said inlet to said outlet and an open position permitting fluid flow from said inlet to said outlet, a second valve positioned within said bore adjacent to said first valve and aligned with one of said passage means therein, said second valve being movable between a closed position blocking fluid flow through said aligned passage means and an open position permitting fluid flow through said aligned passage means, a sleeve positioned within said bore which contacts said first valve, said sleeve having a non-magnetic section which surrounds a portion of said second valve and a magnetic end section which is axially spaced apart from an upper surface of said second valve, and electromagnetic means for linearly moving said second valve, wherein movement of said second valve creates a flow path across said first valve and establishes a pressure differential thereacross causing said first valve to follow said second valve, movement of said first valve causing said sleeve to move in a like direction thereby providing an essentially constant air gap between said upper surface of said second valve and said end of said sleeve such that the stroke of said first valve can be increased without increasing the power input to said electromagnetic means;
b) a reservoir for holding a quantity of fluid;
c) a pump connected to said reservoir for supplying pressurized fluid to said fluid inlet of a first of said cartridges;
d) a hydraulic cylinder enclosing a piston which has an attached piston rod connected to an output function, said piston partitioning said hydraulic cylinder into first and second fluid chambers;
e) a first conduit connecting said fluid outlet of said first cartridge to said first chamber of said hydraulic cylinder;
f) a second conduit connecting said fluid inlet of a second of said cartridges to said second chamber of said hydraulic cylinder;
g) a third conduit connecting said fluid outlet of said second cartridge to said reservoir;
h) a fourth conduit connecting said fluid inlet of a third of said cartridges to said pump;
i) a fifth conduit connecting said fluid outlet of said third cartridge to said second chamber of said hydraulic cylinder;
j) a sixth conduit connecting said fluid inlet of a fourth of said cartridges to said first chamber of said hydraulic cylinder; and k) a seventh conduit connecting said fluid outlet of said fourth cartridge to said reservoir, wherein movement of said valves within said cartridges can control the movement and position of said piston within said hydraulic cylinder.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US47485982A | 1982-08-05 | 1982-08-05 | |
| US474,859 | 1982-08-05 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1195586A true CA1195586A (en) | 1985-10-22 |
Family
ID=23885229
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000433238A Expired CA1195586A (en) | 1982-08-05 | 1983-07-26 | Proportional control valve |
Country Status (12)
| Country | Link |
|---|---|
| EP (1) | EP0100973B1 (en) |
| JP (1) | JPS5962784A (en) |
| AR (1) | AR243659A1 (en) |
| AT (1) | ATE22970T1 (en) |
| AU (1) | AU561909B2 (en) |
| BR (1) | BR8304211A (en) |
| CA (1) | CA1195586A (en) |
| DE (1) | DE3367002D1 (en) |
| DK (1) | DK358583A (en) |
| ES (1) | ES524741A0 (en) |
| MX (1) | MX156707A (en) |
| ZA (1) | ZA835777B (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU594495B2 (en) * | 1986-09-02 | 1990-03-08 | Fumakilla Limited | Heat fumigation apparatus |
| SE459271B (en) * | 1987-10-27 | 1989-06-19 | Bahco Hydrauto Ab | Pressure medium VALVE |
| US5222186A (en) * | 1991-12-06 | 1993-06-22 | Globol Gmbh | Electrical apparatus for vaporizing of active substances |
| CN2166101Y (en) * | 1993-04-20 | 1994-05-25 | 卜冠华 | Spice solvent gas generator |
| WO1996012111A1 (en) * | 1994-10-15 | 1996-04-25 | Mannesmann Rexroth Gmbh | Process for operating a precontrolled 2/2-way seat valve and precontrolled 2/2-way seat valve for operation according to the process |
| WO1998038430A1 (en) * | 1997-02-27 | 1998-09-03 | Mannesmann Rexroth Ag | Pilot stop valve |
| US5878647A (en) * | 1997-08-11 | 1999-03-09 | Husco International Inc. | Pilot solenoid control valve and hydraulic control system using same |
| US9360027B2 (en) * | 2011-03-21 | 2016-06-07 | Danfoss A/S | Proportional control valve |
| JP5701825B2 (en) * | 2012-08-08 | 2015-04-15 | 株式会社鷺宮製作所 | Flow control valve |
| CN113446280B (en) * | 2021-06-30 | 2024-06-25 | 北京航空航天大学宁波创新研究院 | A bidirectional differential pressure controller and hydraulic equipment |
| CN115899360B (en) * | 2023-02-16 | 2023-09-01 | 山东泰展机电科技股份有限公司 | Solenoid valve and gas circuit control system |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3114532A (en) * | 1960-08-12 | 1963-12-17 | Bendix Corp | Pilot type solenoid valve |
| BE694157A (en) * | 1966-05-14 | 1967-07-31 | ||
| DE2835771A1 (en) * | 1978-08-16 | 1980-02-28 | Schwelm & Towler Hydraulics | ARRANGEMENT FOR CONTROLLING A CARTRIDGE ELEMENT |
| DE2915783C2 (en) * | 1979-04-19 | 1986-07-03 | Vickers Systems GmbH, 6380 Bad Homburg | For safety reasons, work-monitored valve arrangement |
| AU1467783A (en) * | 1982-06-01 | 1983-12-08 | Deere & Company | Control valve |
-
1983
- 1983-07-14 AU AU16842/83A patent/AU561909B2/en not_active Ceased
- 1983-07-26 CA CA000433238A patent/CA1195586A/en not_active Expired
- 1983-07-29 EP EP83107471A patent/EP0100973B1/en not_active Expired
- 1983-07-29 DE DE8383107471T patent/DE3367002D1/en not_active Expired
- 1983-07-29 AT AT83107471T patent/ATE22970T1/en not_active IP Right Cessation
- 1983-08-04 AR AR83293811A patent/AR243659A1/en active
- 1983-08-04 ES ES524741A patent/ES524741A0/en active Granted
- 1983-08-05 DK DK358583A patent/DK358583A/en not_active Application Discontinuation
- 1983-08-05 JP JP58143610A patent/JPS5962784A/en active Granted
- 1983-08-05 BR BR8304211A patent/BR8304211A/en unknown
- 1983-08-05 ZA ZA835777A patent/ZA835777B/en unknown
- 1983-08-05 MX MX198309A patent/MX156707A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| DE3367002D1 (en) | 1986-11-20 |
| JPS5962784A (en) | 1984-04-10 |
| EP0100973B1 (en) | 1986-10-15 |
| EP0100973A1 (en) | 1984-02-22 |
| ATE22970T1 (en) | 1986-11-15 |
| ES8405912A1 (en) | 1984-06-16 |
| AU561909B2 (en) | 1987-05-21 |
| JPH0327794B2 (en) | 1991-04-17 |
| AU1684283A (en) | 1984-02-09 |
| ZA835777B (en) | 1985-03-27 |
| DK358583D0 (en) | 1983-08-05 |
| BR8304211A (en) | 1984-03-13 |
| AR243659A1 (en) | 1993-08-31 |
| DK358583A (en) | 1984-02-06 |
| ES524741A0 (en) | 1984-06-16 |
| MX156707A (en) | 1988-09-27 |
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Legal Events
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| MKEC | Expiry (correction) | ||
| MKEX | Expiry |