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EP0164741B1 - Valve de priorité - Google Patents

Valve de priorité Download PDF

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Publication number
EP0164741B1
EP0164741B1 EP85107241A EP85107241A EP0164741B1 EP 0164741 B1 EP0164741 B1 EP 0164741B1 EP 85107241 A EP85107241 A EP 85107241A EP 85107241 A EP85107241 A EP 85107241A EP 0164741 B1 EP0164741 B1 EP 0164741B1
Authority
EP
European Patent Office
Prior art keywords
pressure
priority valve
valve according
spring
spool
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP85107241A
Other languages
German (de)
English (en)
Other versions
EP0164741A3 (en
EP0164741A2 (fr
Inventor
Richard Arthur Wittren
James Anton Miller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deere and Co
Original Assignee
Deere and Co
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
Priority claimed from US06/621,359 external-priority patent/US4556078A/en
Priority claimed from US06/621,329 external-priority patent/US4541451A/en
Application filed by Deere and Co filed Critical Deere and Co
Priority to AT85107241T priority Critical patent/ATE38880T1/de
Publication of EP0164741A2 publication Critical patent/EP0164741A2/fr
Publication of EP0164741A3 publication Critical patent/EP0164741A3/de
Application granted granted Critical
Publication of EP0164741B1 publication Critical patent/EP0164741B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves

Definitions

  • the invention relates to a priority valve for a primary and a secondary consumer with a slide and with a spring, the slide due to the action of the spring and the operating pressure of the primary consumer at one end against an acting force acting on the slide at the other end, in particular achieved by loading the slide on the other hand, with the pressure of the pressure source, into a position that interrupts the connection between the pressure source and the secondary consumer.
  • This known priority valve (US-A-3 979 908) is connected via a control valve to the primary and the secondary consumer and supplies both more or less hydraulic fluid depending on the pressure at the primary consumer.
  • a spring extends between the slide and a screw stopper acting as a stop, which always prestresses the slide in a position which allows the pressure fluid to flow to the primary consumer, the pressure building up between the control valve and the primary consumer being introduced into a space accommodating the spring.
  • a throttle and a branch to a pressure relief valve are inserted, which opens under a predetermined maximum pressure which results when the control valve is open to the primary consumer, which Primary consumer itself is blocked.
  • the pressure between the primary consumer and the throttle is higher than that between the throttle and the space, the level of which depends on the setting of the pressure relief valve.
  • this pressure difference enables the slide to be displaced against the action of the spring and the pressure behind the throttle in a position allowing a flow of hydraulic fluid to the secondary consumer when the primary consumer is blocked in the operating state.
  • This known priority valve has the disadvantage that, in order to achieve the supply of hydraulic fluid to the secondary consumer, if the primary consumer is blocked, hydraulic fluid must be drained via the pressure relief valve to a reservoir.
  • the object on which the invention is based is seen in designing the priority valve in such a way that discharge of pressure fluid to a collection container for control purposes is avoided.
  • This object has been achieved in that, depending on the operating pressure applied to the primary consumer and as soon as this is exceeded by a predetermined value, the effect of the spring can be canceled and the slide can be moved into a position which results in a connection between the pressure source and the secondary consumer.
  • the additional spring ensures continuous control of the pressure fluid flow when the primary consumer is blocked in the operating state, thus avoiding abrupt controls.
  • the advantageous measures provided according to claim 5 ensure that under normal circumstances, d. H. if a pressure is required on the primary consumer in its operating state, which does not allow a hydraulic fluid supply to the secondary consumer, a hydraulic fluid supply to the secondary consumer is first prevented.
  • the strength values and the preload of the spring and the further spring are coordinated with one another in such a way that in a normal situation, as has been described above, only the spring but not the further spring can be compressed, which means that only the slide , but the stop cannot be moved.
  • the additional force used according to the invention is obtained in a simple manner in that the stop is designed as a plunger and thus a displacement into one at the same pressure on both sides Direction.
  • the slide is provided with a driver on which the stop can be brought into contact in one direction of movement, then it follows that the control function by including the primary consumer pressure is only affected if the stop moves in the corresponding direction.
  • FIG. 1 shows a priority valve 10 according to the invention within a hydraulic circuit, which contains a pressure source 12, for example a pump with a constant or variable delivery quantity, and one or more primary or priority consumers 14, to which hydraulic fluid is supplied directly from the pressure source 12.
  • a pressure source 12 for example a pump with a constant or variable delivery quantity
  • primary or priority consumers 14 to which hydraulic fluid is supplied directly from the pressure source 12.
  • the steering system is one of the primary consumers 14.
  • secondary consumers 16 are operated from the pressure source 12.
  • Secondary consumers 16 typically include hydraulic cylinders for operating trailer couplings or hydraulic motors for moving additional devices. If it is also not shown in the drawing, the primary and secondary consumers 14 and 16 each represent the end consumer, between whom and the pressure source 12 or the priority valve 10 there is still a control valve which is in a hydraulic fluid flow to the Primary or secondary consumer 14 or 16 enabling or in a preventing this position can be brought.
  • the priority valve 10 is arranged downstream of the primary consumer 14 and upstream of the secondary consumer 16 and has a housing 18, into which a first and a second bore 20 and 22 are made.
  • a space or a spring chamber 24 is provided, which extends coaxially to the second bore 22 and is connected to a collecting container 28 via a leakage oil passage 26.
  • a plug 30 and a plug 32 are provided on the housing 18, each closing off the first bore 20 and the spring chamber 24.
  • the first bore 20 forms the actual housing bore, and the second bore 22 serves as a sliding fit.
  • the first bore 20 is connected to the pressure source 12 via an inlet 34 and to the secondary consumer 16 via an outlet 36.
  • a slide or valve slide 38 is provided within the first bore 20 and is movable between the first and second ends 40 and 42 of the first bore 20.
  • the valve spool 38 is provided with an inner or blind bore 44, which opens towards the second end 42 of the first bore 20 and has an annular groove (not shown in more detail) on its inner circumference, into which a retaining ring 46, which, as explained later, serves as a driver , is used.
  • an annular groove 48 is provided on the outer circumference of the valve slide 38, which is in constant communication with the inlet 34 and via an opening or flow channel 49 with the first end 40 of the first bore 20.
  • the flow channel 49 connects the first end 40 to the annular groove 48, so that the pressure fluid coming from the pressure source 12 is directed to the first end and can thus act on the end of the valve spool 38 which is located thereon.
  • This flow channel 49 can be provided with a constriction 51 so as to be able to determine the liquid flow to or from the first end 40.
  • the valve spool 38 is slidable between a first position and a second position in the first bore 20, wherein in the first position it prevents a pressure fluid flow from the inlet 34 to the outlet 36 and in the second position enables a pressure fluid flow between them.
  • a pin or piston 50 designed as a plunger is movably received, which has an enlarged first and an enlarged second end 52 and 54, which are hereinafter referred to as head part 52 and foot part 54 and of which head part 52 acts as a stop serves.
  • the head part 52 extends in the first bore 20 and the foot part 54 in the spring chamber 24.
  • the pin 50 preferably has an outer diameter which almost corresponds to the inner diameter of the second bore 22, so as to minimize the pressure fluid leakage from the first bore 20 into the spring chamber 24 to keep possible.
  • a certain flow of hydraulic fluid takes place along the pin 50 in the spring chamber 24, which then flows through the leakage oil passage 26 the collecting container 28 takes place.
  • one or more annular grooves 56 are provided on the outer circumference of the pin 50 in a uniform distribution over its length, which make it possible that in the annular gap between the pin 50th and the second bore 22 enclosed hydraulic fluid evenly distributed on the outer circumference of the pin 50 and thus minimizes the leakage oil flow along its length and reduces the frictional forces acting on the pin 50.
  • the priority valve 10 further includes a first spring 58 which is arranged in the first bore 20 between the valve slide 38 and the head part 52 of the pin 50, the head part 52 now acting as a stop.
  • a second or further spring 60 with a greater bias than the first extends in the spring chamber 24 and is supported on one end on the foot part 54 and on the other end on the plug 32. Due to the higher preload of the second spring 60, one can be sure that the pin 50 is pushed to the left with a view of the drawing, that is, into the first bore 20, as long as there is no hydraulic fluid with a certain pressure at its first end 40 .
  • the outer diameter of the head part 52 is larger than the inner diameter of the locking ring 46 in the inserted state, so that due to a movement in the drawing to the right of the pin 50 over the contact of the head part 52 the valve slide 38 to the right can move along. This could happen if the forces acting on the pin 50, that is to say on its head part 52, resulting from the pressure of the pressure fluid at the second end of the first bore 20 and the action of the first spring 58, are greater than those on the pin Foot part 54 acting on the part of the second spring 60.
  • the priority valve 10 contains a load signal line 62, which establishes a connection between the primary consumer 14 and the second end 42 of the first bore 20.
  • the load signal line 62 engages the primary consumer 14 at a location which lies in a control valve (not shown) for controlling the primary consumer 14 and is only pressurized with pressurized fluid when a pressure medium inflow to the primary consumer 14 is opened, i. H. when it is put into an operating state.
  • An example of the arrangement of the load signal line 62 which is itself not the subject of this invention, is given in European publication 0 141 074 with the signal line 46, a hydraulic system described there having to be adapted to use the priority valve according to the invention if necessary.
  • the liquid pressure prevailing in the load signal line 62 is less than or equal to the pressure in the inlet 34.
  • the control valve in front of the primary consumer 14 acts as a throttle when flowing through the pressure fluid, which leads to a pressure drop between the pressure source 12 and the load signal line 62.
  • the load signal line 62 that is to say normally atmospheric pressure. If the primary consumer 14 is supplied with as much hydraulic fluid as possible, the pressure drop to the primary consumer 14 is relatively small due to the open, i.e.
  • valve spool 38 remains in its first position, since the pressure difference between the first and the second end 40 and 42 in the first bore 20 is not sufficient to move the valve slide 38 to the right against the action of the first spring 58 to its second position. In this first position, the opening between the inlet 34 and the outlet 36 is blocked, so that it is ensured that the greatest possible amount of liquid is supplied to the primary consumer 14.
  • the pressure difference increases on the way to the primary consumer 14, with the result that, as explained below, the valve slide 38 moves to the right into its second one Moves position in which it allows liquid flow from the inlet 34 to the secondary consumer 16.
  • the displacement arises because at the second end of the bore and thus also in the inner bore 44 there is the pressure coming from the control valve of the primary consumer 14, which is lower by the pressure drop resulting from the throttling in the control valve than that prevailing at the inlet 34 .
  • the pin 50 will continue to move to the right even after it engages the snap ring 46 because the pressure building up in the inner bore 44 will approach the pressure at the second end of the first bore 20, namely, the head portion 52 continuously and hardly noticeably stands out from the locking ring 46 in order to enable pressure equalization between the second end and the inner bore 44. It would also be conceivable to introduce openings in the locking ring 46 for pressure equalization, although there is already a small gap between the ends of the expanded locking ring 46. However, it can be seen that as soon as the head part 52 rests on the locking ring 46, the spring 58 becomes ineffective. It can be assumed that in such a situation the pressure in the load signal line 62 and in the inlet 34 is the same.
  • the pressure-exposed side of the valve spool 38 at the second end 42 is smaller in area by the cross-sectional area of the pin 50 between its head and foot parts 52 and 54 than the side of the valve spool 38 facing the first end 40 when the head part 52 comes to rest, so that due to the pressure balance on the left and right of the valve spool 38 this is additionally displaced to its right by the pressure at the first end 40 to its second position.
  • pin 50 only moves the valve spool 38 to the right when the pressure required for this reaches a value which is above the maximum pressure required for the primary consumer 14 and below the maximum pressure which can be built up by the pressure source 12 lies.
  • pin 50 would function as a conventionally used pressure relief valve and control throttle.
  • This priority valve 10 contains a housing 18' which differs from that shown in FIG. 1 in that it does not contain a spring chamber 24. Instead, a second spring 60 'is provided between the head part 52' of a pin 50 'and the right end face of the first bore 20.
  • the pin 50 'itself is elongated and contains an annular groove 64 which is made on its outer circumference near its right end.
  • a set screw 66 is held in the housing 18 'and is aligned with the annular groove 64.
  • the annular groove 64 has a right end surface 68 and is dimensioned such that the set screw 66 strikes this end surface 68 when the pin 50 'is moved to the left and prevents further movement of the pin 50' to the left.
  • the set screw 66 and the annular groove 64 accordingly serve as a stop and are functionally comparable to that of the foot part 54 of the pin 50 in FIG. 1.
  • the pin 50 ' can also be provided in its right end region with a groove 67, which avoids evasion of enclosed hydraulic fluid located in the annular groove 64 to the collecting container 28.
  • a smaller plug 32 ' has also been used to close the second bore 22'.
  • the flow channel 49 was replaced by an opening or passage 70, which is provided on the outer circumference of the valve slide 38 '. Apart from these minor changes, the function and the effect of both priority valves 10 and 10 'are the same.
  • FIG. 3 also shows a priority valve 110 according to the invention within a hydraulic circuit, which contains a pressure source 112, for example a pump with a constant or variable delivery rate, and one or more primary or priority consumers 114, to which hydraulic fluid from the pressure source 112 passes through the priority valve 110 is fed.
  • a pressure source 112 for example a pump with a constant or variable delivery rate
  • primary or priority consumers 114 to which hydraulic fluid from the pressure source 112 passes through the priority valve 110 is fed.
  • the steering is one of the primary consumers 114.
  • secondary consumers 116 are operated from the pressure source 112 via the priority valve 110.
  • Secondary consumers 116 typically include hydraulic cylinders for operating trailer couplings or hydraulic motors for moving Accessories.
  • the primary and secondary consumers 114 and 116 each represent the end consumer, between whom and the pressure source 112 or the priority valve 110 there is still a control valve, which in a hydraulic fluid flow to the Primary or secondary consumer 114 or 116 is enabled or brought into a position preventing this.
  • the priority valve 110 has a housing 118, into which a first and a second bore 120 and 122 are made.
  • a space or a spring chamber 124 is provided, which extends coaxially to the second bore 122 and is connected to a collecting container 128 via a leakage oil passage 126.
  • a plug 130 and a plug 132 are provided on the housing 118, each closing off the first bore 120 and the spring chamber 124.
  • the first bore 120 forms the actual housing bore
  • the second bore 122 serves as a sliding fit.
  • the first bore 120 is connected to the pressure source 112 via an inlet 134, to the primary consumer 114 via a first outlet 135 and to the secondary consumer 116 via an outlet 136.
  • a slide or valve slide 138 is provided within the first bore 120 and is movable between the first and second ends 140 and 142 of the first bore 120.
  • the valve slide 138 is provided with an inner or blind bore 144, which opens towards the second end 142 of the first bore 120 and has an annular groove (not shown in more detail) on its inner circumference, into which a retaining ring 146, which, as explained later, serves as a driver , is used.
  • annular groove 148 is provided on the outer circumference of the valve slide 138, which is in constant communication with the inlet 134 and with at least one of the outlets 135 and 136.
  • the valve spool 138 also includes an opening or flow channel 150, which connects the first end 140 to the first outlet 135, so that the pressure fluid coming from the pressure source 112 can act on the end of the valve spool 138 which is located there and the valve spool 138 to the right into one can move second position.
  • This flow channel 150 can be provided with a constriction 152 so as to be able to determine the liquid flow to or from the first end 140.
  • the valve spool 138 is slidable between a first position and a second position in the first bore 120, in the first position allowing hydraulic fluid flow from the inlet 134 to the first outlet 135 while preventing the hydraulic fluid flow to the second outlet 136 and in the second position allows fluid flow between the inlet 134 and the second outlet 136 while blocking the fluid flow to the first outlet 135.
  • a pin or piston 154 designed as a plunger is movably received in the second bore 122 and has an enlarged first and an enlarged second end 156 and 158, which are referred to below as the head part 156 and foot part 158 and of which the head part 156 acts as a stop serves.
  • the head portion 156 extends in the first bore 120 and the foot portion 158 in the spring chamber 124.
  • the pin 154 In addition to the outer diameter of the head and foot parts 156 and 158, the pin 154 preferably has an outer diameter which almost corresponds to the inner diameter of the second bore 122, so that pressure fluid leakage from the first bore 120 into the spring chamber 124 is as small as possible to keep possible. However, it can be assumed that there is a certain flow of hydraulic fluid along the pin 154 into the spring chamber 124, which then finds its way to the reservoir 128 via the leakage oil passage 126.
  • one or more annular grooves 160 are provided on the outer circumference of the pin 154 in a uniform distribution over its length, which enable the annular gap between the pin 154 to be located and the second bore 122 enclosed hydraulic fluid evenly distributed on the outer circumference of the pin 154 and thus minimizes the leakage oil flow along its length and reduces the frictional forces acting on the pin 154.
  • the priority valve 110 also contains a first spring 162, which is arranged in the first bore 120 between the valve slide 138 and the head part 156 of the pin 154, the head part 156 now acting as a stop.
  • a second or further spring 164 with a greater bias than the first extends in the spring chamber 124 and is supported at one end on the foot part 158 and at the other end on the plug 132. Due to the higher pretension of the second spring 164, one can be sure that the pin 154 is pushed to the left in the drawing, that is, into the first bore 120, as long as there is no hydraulic fluid with a certain pressure at its first end 140 .
  • the outer diameter of the head part 156 of the pin 154 is dimensioned such that it can enter the blind bore 144 of the valve slide 138 and is larger than the inner diameter of the locking ring 146 in the inserted state, so that due to one in the drawing to the right Directed movement of the pin 154 on the system of the head part 156, which can also move the valve slide 138 to the right. This could happen if the forces acting on the left on the pin 154, that is to say on its head part 156, resulting from the pressure of the pressure fluid at the second end 142 of the first bore 120 and the action of the first spring 162, are greater than those on force acting on the foot part 158 from the second spring 164.
  • the priority valve 110 contains a load signal line 166, which establishes a connection between the primary consumer 114 and the second end 142 of the first bore 120.
  • the load signal line 166 engages the primary consumer 114 at a location that lies in a control valve (not shown) for controlling the primary consumer 114 and is only pressurized with pressurized fluid when a pressure medium flow to the primary consumer 114 is opened, i. H. when it is put into an operating state.
  • An example of the arrangement of the load signal line 166 which is not itself the subject of this invention, is given in European publication 0 141 074 with the signal line 46, a hydraulic system described there having to be adapted to use the priority valve according to the invention if necessary.
  • the fluid pressure in the load signal line 166 is less than or equal to the pressure in the inlet 134.
  • the control valve in front of the primary consumer 114 acts as a throttle when flowing through the pressure fluid, which leads to a pressure drop between the pressure source 112 and the load signal line 166.
  • the load signal line 166 that is to say normally atmospheric pressure. If the primary consumer 114 is supplied with as much hydraulic fluid as possible, the pressure drop to the primary consumer 114 is relatively small due to the open, i.e.
  • valve spool 138 In this first position, the opening between the inlet 134 and the first outlet 135 is enlarged while the passage to the secondary consumer 116 is blocked, so that it is ensured that the greatest possible amount of liquid is supplied to the primary consumer 114.
  • the pressure difference increases on the way to the primary consumer 114, with the result that, as explained below, the valve spool 138 turns right into its second one Shifts position to allow fluid flow from inlet 134 to both first and second outlets 135 and 136.
  • the valve spool 138 moves further to the right, the opening to the second outlet 136 increases while the opening to the first outlet 135 decreases.
  • the shift arises because at the second end 142 of the first bore 120 and thus also in the inner bore 144 there is the pressure coming from the control valve of the primary consumer 114, which is lower than the pressure drop resulting from the throttling in the control valve Inlet 134 prevailing.
  • valve spool 138 turns right into moved his second position.
  • the pin 154 will continue to move to the right even after it engages the snap ring 146 because the pressure building up in the inner bore 144 will approach the pressure at the second end 142 of the first bore 120, namely by the head portion 156 continuously and barely noticeably stands out from the circlip 146 to allow pressure equalization between the second end and the inner bore 144. It would also be conceivable to introduce openings in the locking ring 146 for pressure equalization, although there is already a small gap between the ends of the expanded locking ring 146. However, it can be seen that as soon as the head portion 156 abuts the locking ring 146, the first spring 162 becomes ineffective.
  • the pressure in the load signal line 166 and in the inlet 134 is the same. It can also be seen that the pressure-exposed side of the valve spool 138 at the second end 142 is smaller in area by the cross-sectional area of the pin 154 between its head and foot parts 156 and 158 than the side of the valve spool 138 facing the first end 140 when the head part 156 comes to rest, so that due to the pressure equilibrium to the left and right of the valve spool 138, the latter is additionally shifted to the right into its second position by the pressure at the first end 140.
  • This priority valve 110 contains a housing 118' which differs from that shown in FIG. 3 in that it does not contain a spring chamber 124. Instead, a second spring 164 'is provided between the head portion 156' of a pin 154 'and the right end face of the first bore 120.
  • the pin 154 'itself is elongated and contains an annular groove 168 which is made on its outer circumference near its right end.
  • a set screw 170 is held in the housing 118 'and is aligned with the annular groove 168.
  • the annular groove 168 has a right end surface 172 and is dimensioned such that the set screw 170 strikes this end surface 172 when the pin 154 'moves to the left and prevents further movement of the pin 154' to the left.
  • the set screw 170 and the annular groove 168 accordingly serve as a stop and are functionally comparable to that of the foot part 158 of the pin 154 in FIG. 3.
  • the pin 154 'can also be provided in its right end region with a groove 173, which prevents it from evading of enclosed hydraulic fluid located in the annular groove 168 to the collecting container 128.
  • a smaller plug 132 ' has also been used to close the second bore 122'.
  • the flow channel 150 was replaced by an opening or passage 174, which is provided on the outer circumference of the valve slide 138 '. Apart from these minor changes, the function and effect of both priority valves 110 and 110 'are the same.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)

Claims (18)

1. Valve de priorité (10, 10',110, 110') comportant des raccords (34, 36, 62, 134, 135, 136) pour une source de pression (12, 112), un appareil utilisateur primaire et un appareil utilisateur secondaire (14,114 et 16,116), comportant un tiroir (38, 38', 138, 138') et comportant un ressort (58, 162), le tiroir (38, 38', 138, 138') pouvant être en raison de l'action du ressort (58, 162) et de la pression de fonctionnement de l'appareil utilisateur primaire (14, 114) à une extrémité, contre une force de réglage agissant sur le tiroir (38) à l'autre extrémité, obtenue en particulier par l'action sur le tiroir (38) à l'autre extrémité de la pression de la source de pression (12), passer dans une position interrompant la communication entre la source de pression (12, 112) et l'appareil utilisateur secondaire (16, 116), caractérisée en ce qu'en fonction de la pression de fonctionnement présente sur l'appareil utilisateur primaire (14, 114) et, dès que celle-ci est dépassée d'une valeur prédéterminée, l'action du ressort (58, 162) peut être supprimée et le tiroir (38, 38',138, 138') passer dans une position assurant la communication entre la source de pression (12, 112) et l'appareil utilisateur secondaire (16, 116).
2. Valve de priorité suivant la revendication 1, le ressort (58, 162) s'étendant entre le tiroir (38, 38',138,138') et une butée (52,156), caractérisée en ce que la butée (52,156) peut être déplacée en fonction de la pression de fonctionnement de l'appareil utilisateur primaire (14, 114).
3. Valve de priorité suivant la revendication 2, caractérisée en ce que la butée (52,156) est reliée à un piston (50, 154) sur lequel peut agir, à une extrémité, la pression de fonctionnement de l'appareil utilisateur primaire (14,114) pour décharger le ressort (58, 162).
4. Valve de priorité suivant la revendication 3, caractérisée en ce que la butée (52,156) peut être déplacée contre l'action d'un autre ressort (60, 60', 164, 164').
5. Valve de priorité suivant la revendication 4, caractérisée en ce qu'à l'état sans pression de la valve de priorité (10, 10', 110, 110'), la précontrainte de l'autre ressort (60, 60',164,164') est supérieure à celle du ressort (58, 162).
6. Valve de priorité suivant la revendication 2, caractérisée en ce que la butée (52, 156) se présente sous la forme d'un piston plongeur et peut être reliée au tiroir (38, 38', 138, 138')
7. Valve de priorité suivant la revendication 6, caractérisée en ce que le tiroir (38, 38',138, 138') comporte un entraîneur (46, 146) avec lequel la butée (52, 156) peut être amenée en contact dans un sens de déplacement.
8. Valve de priorité suivant une ou plusieurs des revendications précédentes, caractérisée en ce que la butée (52, 156) est un piston (50, 50', 154, 154') s'étendant à l'intérieur de l'alésage (20, 120) du boîtier, comportant une tige et une section de tête (52, 156), la tige s'étendant dans un compartiment (24,124) auquel ne peut pas s'appliquer la pression de fonctionnement de l'appareil utilisateur primaire ou secondaire (14, 114 ou 16,116).
9. Valve de priorité suivant la revendication 8, caractérisée en ce que la tige est guidée dans une chambre de glissement (22,22', 122, 122') et comporte des sillons de détente de pression (56, 160).
10. Valve de priorité suivant la revendication 8, caractérisée en ce que le piston (50, 50', 154, 154') comporte en outre une section de pied (54,158) qui est placée dans le compartiment (24,124) et sur laquelle agit l'autre ressort (60, 60', 164, 164').
11. Valve de priorité suivant la revendication 10, caractérisée en ce que la section de pied (54,158) peut être amenée à être placée dans le compartiment (24,124).
12. Valve de priorité suivant la revendication 8, caractérisée en ce que l'autre ressort (60, 60', 164, 164') s'étend entre la section de tête (52, 156) et une section de boîtier fixe (42, 142).
13. Valve de priorité suivant une ou plusieurs des revendications précédentes, le tiroir (38, 38', 138, 138') comportant au moins une rainure annulaire (48,148) entre deux épaisseurs de matière, par laquelle du liquide sous pression peut être amené à l'appareil utilisateur secondaire (16, 116), caractérisée en ce que l'épaisseur de matière située du côté de l'autre extrémité (40, 140) du tiroir (38, 38', 138,138') comporte un percement.
14. Valve de priorité suivant la revendication 13, caractérisée en ce qu'un rétrécissement (51, 152) est prévu dans le percement (49, 70, 150, 174).
15. Valve de priorité suivant une ou plusieurs des revendications précédentes, le tiroir (38, 38', 138, 138') recevant à son autre extrémité la pression établie par la source de pression (12, 112) et amenée à une valve de commande devant commander l'appareil utilisateur primaire (14, 114), caractérisée en ce que le tiroir (38, 38', 138, 138') reçoit à une première extrémité, par l'intermédiaire d'une conduite de signaux de charge (62,166), la pression de fonctionnement présente sur l'appareil utilisateur primaire (14, 114).
16. Valve de priorité suivant la revendication 7, caractérisée en ce que le tiroir (38, 38', 138,138') comporte un alésage borgne (44,144) dans lequel s'étend la section de tête (52,156) du piston (50, 50', 154, 154') et qui comprend une rainure annulaire pour la réception d'un circlip (46, 146) avec lequel la section de tête (52, 156) peut être amenée en contact.
17. Valve de priorité suivant une ou plusieurs des revendications précédentes, caractérisée en ce que le ressort (58,162) et l'autre ressort (60, 60', 164, 164') sont montés l'un derrière l'autre.
18. Valve de priorité suivant la revendication 1, caractérisée en ce que l'appareil utilisateur primaire (14, 114) est relié en permanence à la source de pression (12, 112).
EP85107241A 1984-06-15 1985-06-12 Valve de priorité Expired EP0164741B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85107241T ATE38880T1 (de) 1984-06-15 1985-06-12 Prioritaetsventil.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US06/621,359 US4556078A (en) 1984-06-15 1984-06-15 Priority valve
US621359 1984-06-15
US06/621,329 US4541451A (en) 1984-06-15 1984-06-15 Priority valve
US621329 1984-06-15

Publications (3)

Publication Number Publication Date
EP0164741A2 EP0164741A2 (fr) 1985-12-18
EP0164741A3 EP0164741A3 (en) 1986-12-17
EP0164741B1 true EP0164741B1 (fr) 1988-11-23

Family

ID=27088927

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85107241A Expired EP0164741B1 (fr) 1984-06-15 1985-06-12 Valve de priorité

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EP (1) EP0164741B1 (fr)
DE (1) DE3566439D1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1988008086A1 (fr) * 1987-04-04 1988-10-20 Zahnradfabrik Friedrichshafen Ag Systeme hydraulique de regulation de pression, notamment pour boite de vitesses couplable sous charge de vehicules a moteur
DE9314272U1 (de) * 1993-09-22 1993-11-11 Lanny, Michael, 75323 Bad Wildbad Regelventil
DE102013005665A1 (de) 2013-04-03 2014-10-09 Volkswagen Aktiengesellschaft Hochdruckeinspritzsystem und Verfahren zum Betreiben eines Hochdruckeinspritzsystems

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0141074A2 (fr) * 1983-08-12 1985-05-15 Deere & Company Système hydraulique comprenant une pompe, une soupape, une conduite d'alimentation et une conduite de commande

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3349670A (en) * 1965-12-20 1967-10-31 Deere & Co Hydraulic control valve
US3979908A (en) * 1975-09-29 1976-09-14 The Cessna Aircraft Company Priority flow valve

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0141074A2 (fr) * 1983-08-12 1985-05-15 Deere & Company Système hydraulique comprenant une pompe, une soupape, une conduite d'alimentation et une conduite de commande

Also Published As

Publication number Publication date
EP0164741A3 (en) 1986-12-17
DE3566439D1 (en) 1988-12-29
EP0164741A2 (fr) 1985-12-18

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