EP0377544A1 - Proportional directional valve for controlling hydraulic actuators - Google Patents

Proportional directional valve for controlling hydraulic actuators Download PDF

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Publication number
EP0377544A1
EP0377544A1 EP90420007A EP90420007A EP0377544A1 EP 0377544 A1 EP0377544 A1 EP 0377544A1 EP 90420007 A EP90420007 A EP 90420007A EP 90420007 A EP90420007 A EP 90420007A EP 0377544 A1 EP0377544 A1 EP 0377544A1
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EP
European Patent Office
Prior art keywords
piston
rod
spring
receiver
loaded
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.)
Withdrawn
Application number
EP90420007A
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German (de)
French (fr)
Inventor
Maurice Tardy
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Individual
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Individual
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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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the present invention relates to a proportional distributor for controlling hydraulic receivers.
  • proportional distributors for controlling hydraulic receivers.
  • An advantage of the proportional distributor is that it allows independence of simultaneous movements in the different receivers.
  • this type of device has limits, since this independence of movement no longer exists when the sum of the flow rates of the receivers used simultaneously is greater than the flow rate of the pump.
  • the flow preferably going to the least loaded receiver.
  • Figure 1 of the accompanying schematic drawing shows a partial view in section of a proportional distributor.
  • the distributor is arranged symmetrically with respect to the axis Y′Y.
  • the main drawer of the distributor is mounted in a bore formed in the body 3 , this bore comprising a certain number of annular grooves, while the drawer 2 also comprises annular grooves opening into its wall.
  • this distributor is intended to supply a receiver designated by the general reference 4 , which can be constituted for example by a jack.
  • the body 3 has a second bore inside which a compensator slide 5 is slidably mounted subject to the load of a spring 6 .
  • the hydraulic fluid is conveyed by a pump 7 from a reservoir 8 .
  • n of receivers is equal to 2.
  • the least loaded receiver receiving a flow rate Q1 will receive the entire flow rate necessary for it.
  • the most loaded receiver will receive a flow of a value Q - Q1, which is less than Q2, the theoretical flow required for this second receiver.
  • the document FR. A. 2,587,419 relates to a device allowing the reduction of the flow rate of the least loaded receptor (s), by reducing the calibration of the pressure balance of the compensators. This reduction in the calibration is obtained by implementing a correction pressure, of value less than the pressure of the busiest user, generated by a valve which should be controlled, depending on the direction of variation sought for correction pressure. It is a complex and expensive solution, which cannot be mounted on existing facilities.
  • the object of the invention is to provide a proportional distributor with which it is possible to have simultaneity of movements, whatever the relative loads of the receivers.
  • the proportional distributor which it concerns comprising means reducing the flow rate of the least loaded receiver (s) as a function of the load of the most loaded receiver (s), is characterized in that these means use the pressure of the or the most loaded receivers 24, which is applied directly to each compensator slide 5 supplying the receivers 4, 24, and which acts against the action of the spring 6.
  • each compensator drawer consist of a rod coaxial with this drawer and bearing on the face thereof opposite to that on which the calibration spring acts, and whose free end is equipped with a piston on which the pressure of the fluid supplying the most loaded receiver is applied.
  • the rod acting on the compensator slide is surrounded by a spring bearing, on the one hand, in a bore formed in the body and, on the other hand, on the face of the piston opposite to that on which the pressure of the fluid supplying the most loaded receiver acts.
  • a spring bearing on the one hand, in a bore formed in the body and, on the other hand, on the face of the piston opposite to that on which the pressure of the fluid supplying the most loaded receiver acts.
  • the rod acting on the compensator slide is surrounded by a spring bearing, on the one hand, in the bottom of a bore formed in the body and, on the other hand, on a washer disposed inside this bore, traversed by the rod and whose movement towards the piston is limited by a stop, the distance between the washer and the stop being such that during the displacement of the piston and the rod, the piston first comes to bear against the washer and before possibly moving the latter axially against the action of the spring.
  • this threshold corresponding to the abutment of the piston against the washer actuated by the spring.
  • the means intended to limit the action of the fluid pressure on the rod consist of a hydraulically driven piston.
  • the compensator drawer is equipped, on its face opposite to that associated with a calibration spring, with a rod on which is capable of acting against the action of the spring taring the core of an electromagnet.
  • At least one element with a "or" function for supplying power to the piston placed at the end of the rod from the busiest fluid circuit. If the number of receivers is n, the number of elements with "or" function is n - 1. In all cases, this is a simple, reliable and inexpensive installation, which can also be mounted on existing devices.
  • FIG. 2 represents a system similar to that of FIG. 1 in which the same elements are designated by the same references as above.
  • the system comprises a first receiver 4 which can be considered to be the least loaded. It is supplied with fluid by a flow Q1 supplied under a pressure P1.
  • the second receiver 24 is the busiest receiver; the pump supplies it with a flow rate Q2 under a pressure P2.
  • each compensator drawer 5 is supported, coaxially with the latter, a rod 16 whose end face forms a piston 17 of section s, on which the pressure P2 is applied of the busiest receiver 24 .
  • the selection of this pressure is carried out by means of a member 18 with "or" function.
  • Selecting section s allows you to adjust the level of correction.
  • FIG. 3 represents an alternative embodiment in which a spring 19 coaxially surrounding the rod 16 and housed inside a bore 20 bears, on the one hand, on the bottom of the bore and, on the other hand part, against the face of the piston 17 opposite to that against which the fluid pressure is exerted.
  • the opposing force of the spring 19 makes it possible to modify the correction law resulting from the pressure P2 on the piston 17 .
  • the spring 19 housed inside the bore 20 , bears not directly against the piston 17 , but against a washer 21 freely traversed by the rod 16 and whose the movement towards the piston 17 is limited by a circlip 22 .
  • the piston 17 comes into contact with the washer 21 , it encounters an additional opposing force equal to the preload value of the spring 19 .
  • FIG. 5 represents an alternative embodiment in which at mid-length of the rod 16 is disposed a piston 23 mounted inside a chamber 25 inside which a fluid pressure Pc is established. This fluid pressure generates a force antagonistic to that exerted by the fluid under a pressure P2 on the piston 17 .
  • FIG. 6 represents an alternative embodiment in which the force opposing the calibration spring is provided by an electromagnet 26 acting on the end of the rod 16 opposite to that secured to the compensator drawer 5 .
  • the core of the electromagnet is immersed in the fluid supplied by the conduit 27 , which allows balancing of the forces due to the pressure.
  • Each distributor element can have a correcting device defined as a function of the receiver which it supplies.
  • the invention brings a great improvement to the existing technique by providing a proportional distributor of simple design and making it possible to benefit from a simultaneity of movements in different receivers whatever the relative loads thereof. .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Coating Apparatus (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

This directional valve, comprising means (16, 17) reducing the output of the receiver or receivers (4) least loaded as a function of the load of the receiver or receivers (24) most highly loaded, is characterised in that these means employ the pressure of the receiver or receivers (24) most highly loaded, which is applied directly to each compensator slide (5) supplying the receivers (4, 24), which acts counter to the action of the spring (6). Application to the simultaneous control of a plurality of hydraulic receivers. <IMAGE>

Description

La présente invention a pour objet un distributeur proportionnel pour la commande de récepteurs hydrauliques.The present invention relates to a proportional distributor for controlling hydraulic receivers.

Il est connu d'utiliser des distributeurs proportionnels pour la commande de récepteurs hydrauliques. Un avantage du distributeur proportionnel est qu'il permet une indépendance des mouvements simultanés dans les différents récepteurs. Cependant, ce type d'appareil connaît des limites, puisque cette indépendance des mouvements n'existe plus lorsque la somme des débits des récepteurs utilisés simultanément est supérieure au débit de la pompe.It is known to use proportional distributors for controlling hydraulic receivers. An advantage of the proportional distributor is that it allows independence of simultaneous movements in the different receivers. However, this type of device has limits, since this independence of movement no longer exists when the sum of the flow rates of the receivers used simultaneously is greater than the flow rate of the pump.

Dans un tel cas, on retrouve un fonctionnement en parallèle, le débit allant préférentiellement vers le récepteur le moins chargé.In such a case, there is a parallel operation, the flow preferably going to the least loaded receiver.

La figure 1 du dessin schématique annexé représente une vue partielle et en coupe d'un distributeur proportionnel.Figure 1 of the accompanying schematic drawing shows a partial view in section of a proportional distributor.

Pour ce qui concerne le tiroir principal 2 et la partie correspon­dante du corps 3, le distributeur est agencé de façon symétrique par rapport à l'axe Y′Y. Le tiroir principal du distributeur est monté dans un alésage ménagé dans le corps 3, cet alésage comportant un certain nombre de gorges annulaires, tandis que le tiroir 2 comporte également des gorges annulaires débouchant dans sa paroi.With regard to the main drawer 2 and the corresponding part of the body 3 , the distributor is arranged symmetrically with respect to the axis Y′Y. The main drawer of the distributor is mounted in a bore formed in the body 3 , this bore comprising a certain number of annular grooves, while the drawer 2 also comprises annular grooves opening into its wall.

Comme montré au dessin, ce distributeur est destiné à alimenter un récepteur désigné par la référence générale 4, qui peut être constitué par exemple par un vérin.As shown in the drawing, this distributor is intended to supply a receiver designated by the general reference 4 , which can be constituted for example by a jack.

Le corps 3 comporte un second alésage à l'intérieur duquel est monté coulissant un tiroir de compensateur 5 soumis à la charge d'un ressort 6. Le fluide hydraulique est véhiculé par une pompe 7 à partir d'un réservoir 8.The body 3 has a second bore inside which a compensator slide 5 is slidably mounted subject to the load of a spring 6 . The hydraulic fluid is conveyed by a pump 7 from a reservoir 8 .

Lorsque le tiroir 2 est déplacé dans le sens de la flèche F, il se produit successivement les événements suivants :
- Interruption de la liaison entre la gorge 9 d'alimentation en fluide sous pression et la gorge de retour 10 ;
- Ouverture de la liaison de la gorge 9 avec une gorge 12 du tiroir 2, puis, par le canal 13, mise en communication avec une gorge 14 ménagée dans le corps, elle-même reliée avec une chambre du récepteur. La gorge symétrique de la gorge 14 est reliée à l'autre orifice de ce récepteur en raison de la symétrie par rapport à l'axe Y′Y ;
- Ouverture de l'encoche 15 d'alimentation progressive du tiroir 2. A partir du début de cette ouverture, la pompe 7 est en liaison avec le récepteur 4 et commence à lui fournir de l'énergie motrice.
- Le tiroir de compensateur 5, taré par le ressort 6, entre immédiatement en action et maintient un écart de pression constant entre l'amont et l'aval des encoches d'alimentation 15 du tiroir 2.When drawer 2 is moved in the direction of arrow F, the following events occur successively:
- Interruption of the connection between the groove 9 for supplying pressurized fluid and the return groove 10 ;
- Opening of the connection of the groove 9 with a groove 12 of the drawer 2 , then, by the channel 13 , placed in communication with a groove 14 formed in the body, itself connected with a chamber of the receiver. The symmetrical groove of the groove 14 is connected to the other orifice of this receiver due to the symmetry with respect to the axis Y′Y;
- Opening of the progressive feed notch 15 of the drawer 2 . From the start of this opening, the pump 7 is connected to the receiver 4 and begins to supply it with motive energy.
- The compensator drawer 5 , calibrated by the spring 6 , immediately comes into action and maintains a constant pressure difference between the upstream and downstream of the feed slots 15 of the drawer 2 .

Cet écart de pression a la valeur suivante :
Δ P = To S

Figure imgb0001
où To représente l'effort du ressort 6, et S est la section du tiroir de compensateur 5.This pressure difference has the following value:
Δ P = To S
Figure imgb0001
 where To represents the force of the spring 6 , and S is the section of the compensator slide 5 .

Pour réaliser les commandes simultanées de n récepteurs avec un distributeur proportionnel de ce type, il convient, afin de conserver l'effet proportionnel, que le débit Q fourni par la pompe soit supérieur ou, éventuellement, égal à la somme des débits Q1 + Q2 + ... + Qn nécessaires à l'alimentation simultanée des n récepteurs inégalement chargés.To carry out the simultaneous orders of n receivers with a proportional distributor of this type, it is advisable, in order to maintain the proportional effect, that the flow Q supplied by the pump is greater or, possibly, equal to the sum of the flows Q1 + Q2 + ... + Qn necessary for the simultaneous supply of n unevenly charged receptors.

Pour la suite des explications, et pour des raisons de simplicité du raisonnement, le nombre n de récepteurs est égal à 2.For the following explanations, and for reasons of simplicity of reasoning, the number n of receivers is equal to 2.

Si le débit Q de la pompe devient inférieur à la somme des débits Q1 + Q2, le récepteur le moins chargé recevant un débit Q1, recevra la totalité du débit qui lui est nécessaire.If the flow rate Q of the pump becomes lower than the sum of the flow rates Q1 + Q2, the least loaded receiver receiving a flow rate Q1, will receive the entire flow rate necessary for it.

Par contre, le récepteur le plus chargé recevra un débit d'une valeur Q - Q1, qui est inférieur à Q2, débit théorique nécessaire pour ce second récepteur.On the other hand, the most loaded receiver will receive a flow of a value Q - Q1, which is less than Q2, the theoretical flow required for this second receiver.

Dans le cas d'utilisation d'une pompe à régulation de couple ou de puissance, il se peut que le débit de la pompe soit inférieur au débit Q1 du récepteur le moins chargé. Il n'y a alors plus de mouvement simultané car, seul le récepteur le moins chargé fonctionne. Le document FR. A. 2 587 419, concerne un dispositif permettant la réduction du débit du ou des récepteurs les moins chargés, par réduction du tarage de la balance des pressions des compensateurs. Cette réduction du tarage est obtenue par mise en oeuvre d'une pression de correction, de valeur inférieure à la pression de l'utilisateur le plus chargé, engendrée par une valve qu'il convient de piloter, en fonction du sens de variation recherché pour la pression de correction. Il s'agit d'une solution complexe et coûteuse, ne pouvant pas se monter sur des installations existantes.When using a torque or power regulated pump, the pump flow rate may be lower than the flow rate Q1 of the least loaded receiver. There is then no more simultaneous movement because, only the least loaded receiver works. The document FR. A. 2,587,419, relates to a device allowing the reduction of the flow rate of the least loaded receptor (s), by reducing the calibration of the pressure balance of the compensators. This reduction in the calibration is obtained by implementing a correction pressure, of value less than the pressure of the busiest user, generated by a valve which should be controlled, depending on the direction of variation sought for correction pressure. It is a complex and expensive solution, which cannot be mounted on existing facilities.

Le but de l'invention est de fournir un distributeur proportionnel avec lequel on puisse disposer de la simultanéité des mouvements, quelles que soient les charges relatives des récepteurs.The object of the invention is to provide a proportional distributor with which it is possible to have simultaneity of movements, whatever the relative loads of the receivers.

A cet effet, le distributeur proportionnel qu'elle concerne comportant des moyens réduisant le débit du ou des récepteurs les moins chargés en fonction de la charge du ou des récepteurs les plus chargés, est caractérisé en ce que ces moyens mettent en oeuvre la pression du ou des récepteurs 24 les plus chargés, qui est appliquée directement sur chaque tiroir 5 de compensateur alimentant les récepteurs 4, 24, et qui agit à l'encontre de l'action du ressort 6.To this end, the proportional distributor which it concerns comprising means reducing the flow rate of the least loaded receiver (s) as a function of the load of the most loaded receiver (s), is characterized in that these means use the pressure of the or the most loaded receivers 24, which is applied directly to each compensator slide 5 supplying the receivers 4, 24, and which acts against the action of the spring 6.

Conformément à une possibilité, les moyens agissant sur chaque tiroir de compensateur sont constitués par une tige coaxiale à ce tiroir et prenant appui sur la face de celui-ci opposée à celle sur laquelle agit le ressort de tarage, et dont l'extrémité libre est équipée d'un piston sur lequel s'applique la pression du fluide alimentant le récepteur le plus chargé.According to one possibility, the means acting on each compensator drawer consist of a rod coaxial with this drawer and bearing on the face thereof opposite to that on which the calibration spring acts, and whose free end is equipped with a piston on which the pressure of the fluid supplying the most loaded receiver is applied.

Ainsi, il est possible de corriger la différence de pression au niveau des encoches du tiroir du distributeur du récepteur le moins chargé.Thus, it is possible to correct the pressure difference at the notches of the drawer of the distributor of the least loaded receiver.

Selon une forme d'exécution de ce distributeur, la tige agissant sur le tiroir de compensateur est entourée par un ressort prenant appui, d'une part, dans un alésage ménagé dans le corps et, d'autre part, sur la face du piston opposée à celle sur laquelle agit la pression du fluide alimentant le récepteur le plus chargé. La présence de ce ressort antagoniste permet de modifier la loi de correction introduite par la pression de fluide agissant sur ledit piston.According to one embodiment of this distributor, the rod acting on the compensator slide is surrounded by a spring bearing, on the one hand, in a bore formed in the body and, on the other hand, on the face of the piston opposite to that on which the pressure of the fluid supplying the most loaded receiver acts. The presence of this opposing spring makes it possible to modify the correction law introduced by the fluid pressure acting on said piston.

Selon une autre forme d'exécution, la tige agissant sur le tiroir de compensateur est entourée par un ressort prenant appui, d'une part, dans le fond d'un alésage ménagé dans le corps et, d'autre part, sur une rondelle disposée à l'intérieur de cet alésage, traversée par la tige et dont le mouvement en direction du piston est limité par une butée, la distance entre la rondelle et la butée étant telle qu'au cours du déplacement du piston et de la tige, le piston vienne d'abord en appui contre la rondelle et avant de déplacer éventuellement axialement celle-ci à l'encontre de l'action du ressort.According to another embodiment, the rod acting on the compensator slide is surrounded by a spring bearing, on the one hand, in the bottom of a bore formed in the body and, on the other hand, on a washer disposed inside this bore, traversed by the rod and whose movement towards the piston is limited by a stop, the distance between the washer and the stop being such that during the displacement of the piston and the rod, the piston first comes to bear against the washer and before possibly moving the latter axially against the action of the spring.

Il est ainsi possible de définir un seuil pour la mise en action de la correction, ce seuil correspondant à la mise en appui du piston contre la rondelle actionnée par le ressort.It is thus possible to define a threshold for the actuation of the correction, this threshold corresponding to the abutment of the piston against the washer actuated by the spring.

Conformément à une autre forme d'exécution, les moyens destinés à limiter l'action de la pression de fluide sur la tige sont constitués par un piston mû hydrauliquement.In accordance with another embodiment, the means intended to limit the action of the fluid pressure on the rod consist of a hydraulically driven piston.

Selon une autre forme d'exécution encore, le tiroir de compen­sateur est équipé, sur sa face opposée à celle associée à un ressort de tarage, d'une tige sur laquelle est susceptible d'agir à l'encontre de l'action du ressort de tarage le noyau d'un électro-aimant.According to yet another embodiment, the compensator drawer is equipped, on its face opposite to that associated with a calibration spring, with a rod on which is capable of acting against the action of the spring taring the core of an electromagnet.

Dans la mesure où l'action exercée sur le tiroir de compensateur pour réduire le débit du récepteur le moins chargé est hydraulique, il est prévu au moins un élément à fonction "ou" permettant de réaliser l'alimen­tation sur le piston placé en bout de la tige à partir du circuit de fluide le plus chargé. Si le nombre de récepteurs est de n, le nombre d'éléments à fonction "ou", est de n - 1. Il s'agit dans tous les cas d'une installation simple, fiable et peu coûteuse, pouvant également être montée sur des appareils existants.Insofar as the action exerted on the compensator slide to reduce the flow rate of the least loaded receiver is hydraulic, there is provided at least one element with a "or" function for supplying power to the piston placed at the end of the rod from the busiest fluid circuit. If the number of receivers is n, the number of elements with "or" function is n - 1. In all cases, this is a simple, reliable and inexpensive installation, which can also be mounted on existing devices.

De toute façon, l'invention sera bien comprise à l'aide de la description qui suit, en référence au dessin schématique annexé représentant, à titre d'exemples non limitatifs, plusieurs formes d'exécution de ce distri­buteur proportionnel :

  • Figure 2 est une vue d'un distributeur proportionnel à deux récepteurs;
  • Figures 3 à 6 sont quatre vues à échelle agrandie correspondant à quatre systèmes permettant d'établir un effort antagoniste sur un tiroir de compensateur.
In any case, the invention will be clearly understood with the aid of the description which follows, with reference to the appended schematic drawing representing, by way of nonlimiting examples, several embodiments of this proportional distributor:
  • Figure 2 is a view of a proportional distributor to two receivers;
  • Figures 3 to 6 are four views on an enlarged scale corresponding to four systems making it possible to establish an opposing force on a compensator drawer.

La figure 2 représente un système similaire à celui de figure 1 dans lequel les mêmes éléments sont désignés par les mêmes références que précédemment.FIG. 2 represents a system similar to that of FIG. 1 in which the same elements are designated by the same references as above.

Dans le cas présent, le système comprend un premier récepteur 4 qui peut être considéré comme le moins chargé. Il est alimenté en fluide par un débit Q1 fourni sous une pression P1. Le deuxième récepteur 24 est le récepteur le plus chargé ; la pompe lui fournit un débit Q2 sous une pression P2.In the present case, the system comprises a first receiver 4 which can be considered to be the least loaded. It is supplied with fluid by a flow Q1 supplied under a pressure P1. The second receiver 24 is the busiest receiver; the pump supplies it with a flow rate Q2 under a pressure P2.

Comme montré au dessin, sur la face en bout de chaque tiroir de compensateur 5 prend appui, coaxialement à celui-ci, une tige 16 dont la face en bout forme un piston 17 de section s, sur lequel vient s'appliquer la pression P2 du récepteur 24 le plus chargé. La sélection de cette pression est réalisée par l'intermédiaire d'un organe 18 à fonction "ou".As shown in the drawing, on the end face of each compensator drawer 5 is supported, coaxially with the latter, a rod 16 whose end face forms a piston 17 of section s, on which the pressure P2 is applied of the busiest receiver 24 . The selection of this pressure is carried out by means of a member 18 with "or" function.

Du fait de l'exercice de la pression P2 sur le piston 17 est obtenue une correction de la différence de pression ΔP aux encoches 15 du tiroir 2 du distributeur le moins chargé dont la pression est P1. L'écart de pression aux encoches du récepteur 4 le moins chargé a pour valeur :
ΔP = To S

Figure imgb0002
- (P2 - P1) s S
Figure imgb0003
où :
P2 est la pression du récepteur le plus chargé
P1 est la pression du récepteur le moins chargé
s est la section du piston 17
To est l'effort du ressort 6 et,
S est la section du tiroir 5.Due to the exercise of the pressure P2 on the piston 17 is obtained a correction of the pressure difference ΔP at the notches 15 of the spool 2 of the least loaded distributor whose pressure is P1. The pressure difference at the slots of the least loaded receiver 4 has the following value:
ΔP = To S
Figure imgb0002
 - (P2 - P1) s S
Figure imgb0003
or :
P2 is the pressure of the most loaded receiver
P1 is the pressure of the least loaded receiver
s is the section of the piston 17
To is the force of spring 6 and,
S is the section of drawer 5 .

Le choix de la section s permet de régler le niveau de correction.Selecting section s allows you to adjust the level of correction.

La figure 3 représente une variante d'exécution dans laquelle un ressort 19 entourant coaxialement la tige 16 et logé à l'intérieur d'un alésage 20 prend appui, d'une part, sur le fond de l'alésage et, d'autre part, contre la face du piston 17 opposée à celle contre laquelle s'exerce la pression de fluide.FIG. 3 represents an alternative embodiment in which a spring 19 coaxially surrounding the rod 16 and housed inside a bore 20 bears, on the one hand, on the bottom of the bore and, on the other hand part, against the face of the piston 17 opposite to that against which the fluid pressure is exerted.

L'effort antagoniste du ressort 19 permet de modifier la loi de correction résultant de la pression P2 sur le piston 17.The opposing force of the spring 19 makes it possible to modify the correction law resulting from the pressure P2 on the piston 17 .

Dans la forme d'exécution représentée à la figure 4, le ressort 19, logé à l'intérieur de l'alésage 20, prend appui non pas directement contre le piston 17, mais contre une rondelle 21 traversée librement par la tige 16 et dont le mouvement, en direction du piston 17, est limité par un circlips 22. Lorsque le piston 17 arrive en contact avec la rondelle 21, il rencontre un effort antagoniste supplémentaire égal à la valeur de précontrainte du ressort 19. La tige 16 ne peut continuer sa course que si la pression qui s'applique sur le piston 17 croît à la valeur :
Po = Fo s

Figure imgb0004

où Fo est la précontrainte du ressort et s est la section du piston 17.In the embodiment shown in Figure 4, the spring 19 , housed inside the bore 20 , bears not directly against the piston 17 , but against a washer 21 freely traversed by the rod 16 and whose the movement towards the piston 17 is limited by a circlip 22 . When the piston 17 comes into contact with the washer 21 , it encounters an additional opposing force equal to the preload value of the spring 19 . The rod 16 can only continue its stroke if the pressure which applies to the piston 17 increases to the value:
Po = Fo s
Figure imgb0004
where Fo is the spring preload and s is the cross section of the piston 17 .

La figure 5 représente une variante d'exécution dans laquelle à mi-longueur de la tige 16 est disposé un piston 23 monté à l'intérieur d'une chambre 25 à l'intérieur de laquelle est établie une pression de fluide Pc. Cette pression de fluide génère un effort antagoniste à celui exercé par le fluide sous une pression P2 sur le piston 17.FIG. 5 represents an alternative embodiment in which at mid-length of the rod 16 is disposed a piston 23 mounted inside a chamber 25 inside which a fluid pressure Pc is established. This fluid pressure generates a force antagonistic to that exerted by the fluid under a pressure P2 on the piston 17 .

La figure 6 représente une variante d'exécution dans laquelle l'effort antagoniste au ressort de tarage est fourni par un électro-aimant 26 agissant sur l'extrémité de la tige 16 opposée à celle solidaire du tiroir de compensateur 5. Le noyau de l'électro-aimant est immergé dans du fluide amené par le conduit 27, ce qui permet un équilibrage des efforts dus à la pression.FIG. 6 represents an alternative embodiment in which the force opposing the calibration spring is provided by an electromagnet 26 acting on the end of the rod 16 opposite to that secured to the compensator drawer 5 . The core of the electromagnet is immersed in the fluid supplied by the conduit 27 , which allows balancing of the forces due to the pressure.

Chaque élément de distributeur peut avoir un dispositif correcteur défini en fonction du récepteur qu'il alimente.Each distributor element can have a correcting device defined as a function of the receiver which it supplies.

Comme il ressort de ce qui précède, l'invention apporte une grande amélioration à la technique existante en fournissant un distributeur propor­tionnel de conception simple et permettant de bénéficier d'une simultanéité des mouvements dans différents récepteurs quelles que soient les charges relatives de ceux-ci.As is apparent from the above, the invention brings a great improvement to the existing technique by providing a proportional distributor of simple design and making it possible to benefit from a simultaneity of movements in different receivers whatever the relative loads thereof. .

Comme il va de soi, l'invention ne se limite pas aux seules formes d'exécution de ce distributeur, décrites ci-dessus à titre d'exemples ; elle en embrasse, au contraire, toutes les variantes d'exécution.It goes without saying that the invention is not limited to the sole embodiments of this dispenser, described above by way of examples; on the contrary, it embraces all variants of execution.

Claims (7)

1- Distributeur proportionnel pour la commande de récepteurs hydrauliques, comportant des moyens (16,17) réduisant le débit du ou des récepteurs (4), les moins chargés en fonction de la charge du ou des récepteurs (24) les plus chargés, caractérisé en ce que ces moyens mettent en oeuvre la pression du ou des récepteurs (24) les plus chargés, qui est appliquée directement sur chaque tiroir (5) de compensateur alimentant les récepteurs (4, 24), et qui agit à l'encontre de l'action du ressort (6) 1 - Proportional distributor for controlling hydraulic receivers, comprising means (16,17) reducing the flow rate of the receiver (s) (4), the least loaded depending on the load of the most loaded receiver (s) (24), characterized in that these means use the pressure of the most loaded receptor (s) (24), which is applied directly to each drawer (5) of compensator supplying the receivers (4, 24), and which acts against spring action (6) 2- Distributeur selon la revendication 1, caractérisé en ce que les moyens agissant sur chaque tiroir (5) de compensateur sont constitués par une tige (16) coaxiale à ce tiroir et prenant appui sur la face de celui-ci opposée à celle sur laquelle agit le ressort de tarage (6), et dont l'extrémité libre est équipée d'un piston (17) sur lequel s'applique la pression (P2) du fluide alimentant le récepteur (24) le plus chargé. 2 - Distributor according to claim 1, characterized in that the means acting on each drawer (5) of compensator consist of a rod (16) coaxial with this drawer and bearing on the face thereof opposite to that on which the calibration spring (6) acts, and the free end of which is fitted with a piston (17) on which the pressure (P2) of the fluid supplying the most loaded receiver (24) is applied. 3- Distributeur selon la revendication 2, caractérisé en ce que la tige (16) agissant sur le tiroir (5) de compensateur est entourée par un ressort (19) prenant appui, d'une part, dans un alésage (20) ménagé dans le corps et, d'autre part, sur la face du piston (17) opposée à celle sur laquelle agit la pression (P2) du fluide alimentant le récepteur (24) le plus chargé. 3 - Distributor according to claim 2, characterized in that the rod (16) acting on the slide valve (5) is surrounded by a spring (19) bearing, on the one hand, in a bore (20) formed in the body and, on the other hand, on the face of the piston (17) opposite to that on which acts the pressure (P2) of the fluid supplying the receiver (24) most loaded. 4- Distributeur selon la revendication 2, caractérisé en ce que la tige (16) agissant sur le tiroir (5) de compensateur est entourée par un ressort (19) prenant appui, d'une part, dans le fond d'un alésage (20) ménagé dans le corps et, d'autre part, sur une rondelle (21) disposée à l'intérieur de cet alésage, traversée par la tige (16) et dont le mouvement en direction du piston est limité par une butée (22), la distance entre la rondelle et la butée étant telle qu'au cours du déplacement du piston (17) et de la tige, le piston vienne d'abord en appui contre la rondelle et avant de déplacer éventuellement axialement celle-ci à l'encontre de l'action du ressort (19). 4 - Distributor according to claim 2, characterized in that the rod (16) acting on the slide valve (5) is surrounded by a spring (19) bearing, on the one hand, in the bottom of a bore ( 20) formed in the body and, on the other hand, on a washer (21) disposed inside this bore, traversed by the rod (16) and whose movement towards the piston is limited by a stop (22 ), the distance between the washer and the stop being such that during the displacement of the piston (17) and of the rod, the piston first comes to bear against the washer and before possibly moving the latter axially to the against the action of the spring (19). 5- Distributeur selon la revendication 2, caractérisé en ce que les moyens destinés à limiter l'action de la pression de fluide sur la tige (16) sont constitués par un piston (23) mû hydrauliquement. 5 - Distributor according to claim 2, characterized in that the means intended to limit the action of the fluid pressure on the rod (16) consist of a piston (23) hydraulically driven. 6- Distributeur selon l'une quelconque des revendications 2 à 5, caractérisé en ce qu'il comprend au moins un élément (18) à fonction "ou" permettant de réaliser l'alimentation sur le piston (17) placé en bout de la tige (16) à partir du circuit de fluide le plus chargé. 6 - Distributor according to any one of claims 2 to 5, characterized in that it comprises at least one element (18) with function "or" allowing to carry out the supply on the piston (17) placed at the end of the rod (16) from the most charged fluid circuit. 7- Distributeur selon la revendication 1, caractérisé en ce que le tiroir de compensateur (5) est équipé, sur sa face opposée à celle associée à un ressort de tarage, d'une tige (16) sur laquelle est susceptible d'agir à l'encontre de l'action du ressort de tarage le noyau d'un électro-aimant (26). 7 - Distributor according to claim 1, characterized in that the compensator drawer (5) is equipped, on its face opposite to that associated with a calibration spring, a rod (16) on which is capable of acting against the action of the calibration spring the core of an electromagnet (26).
EP90420007A 1989-01-06 1990-01-04 Proportional directional valve for controlling hydraulic actuators Withdrawn EP0377544A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8900566A FR2641583A1 (en) 1989-01-06 1989-01-06 PROPORTIONAL DISTRIBUTOR FOR CONTROLLING HYDRAULIC RECEIVERS
FR8900566 1989-01-06

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EP0377544A1 true EP0377544A1 (en) 1990-07-11

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2672944A1 (en) * 1991-02-15 1992-08-21 Bennes Marrel PROPORTIONAL DISTRIBUTOR AND CONTROL ARRANGEMENT OF A PLURALITY OF HYDRAULIC RECEIVERS COMPRISING FOR EACH RECEIVER SUCH A DISTRIBUTOR.
EP0638730A1 (en) * 1993-06-24 1995-02-15 Voac Hydraulics Boras Ab Control means for a hydraulic motor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2548290A1 (en) * 1983-06-14 1985-01-04 Linde Ag HYDRAULIC INSTALLATION COMPRISING A PUMP AND AT LEAST TWO HYDRAULIC POWER UTILIZATION EQUIPMENT POWERED BY THIS PUMP
DE3522450A1 (en) * 1985-06-22 1987-01-02 Bosch Gmbh Robert Hydraulic device for actuating an adjusting part
FR2587419A1 (en) * 1985-09-13 1987-03-20 Rexroth Mannesmann Gmbh CONTROL DEVICE FOR AT LEAST TWO HYDRAULIC FLUID CONSUMERS SUPPLIED BY AT LEAST ONE PUMP
DE3713824A1 (en) * 1987-04-24 1988-11-03 Rexroth Mannesmann Gmbh Valve arrangement

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2548290A1 (en) * 1983-06-14 1985-01-04 Linde Ag HYDRAULIC INSTALLATION COMPRISING A PUMP AND AT LEAST TWO HYDRAULIC POWER UTILIZATION EQUIPMENT POWERED BY THIS PUMP
DE3522450A1 (en) * 1985-06-22 1987-01-02 Bosch Gmbh Robert Hydraulic device for actuating an adjusting part
FR2587419A1 (en) * 1985-09-13 1987-03-20 Rexroth Mannesmann Gmbh CONTROL DEVICE FOR AT LEAST TWO HYDRAULIC FLUID CONSUMERS SUPPLIED BY AT LEAST ONE PUMP
DE3713824A1 (en) * 1987-04-24 1988-11-03 Rexroth Mannesmann Gmbh Valve arrangement

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2672944A1 (en) * 1991-02-15 1992-08-21 Bennes Marrel PROPORTIONAL DISTRIBUTOR AND CONTROL ARRANGEMENT OF A PLURALITY OF HYDRAULIC RECEIVERS COMPRISING FOR EACH RECEIVER SUCH A DISTRIBUTOR.
EP0500419A1 (en) * 1991-02-15 1992-08-26 Marrel Proportional valve and control system with a plurality of actuators having each such a valve
US5222426A (en) * 1991-02-15 1993-06-29 Marrel Proportional distributor and control system for a plurality of hydraulic receivers incorporating a distributor of this kind for each receiver
EP0638730A1 (en) * 1993-06-24 1995-02-15 Voac Hydraulics Boras Ab Control means for a hydraulic motor
US5501136A (en) * 1993-06-24 1996-03-26 Voac Hydraulics Boras Ab Control system for a hydraulic motor

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FR2641583A1 (en) 1990-07-13

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