• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Multi-control hydraulic circuit for supplying receivers with hydraulic fluid supplied by a pressure control pump (PLS) of the control line (LS) depending on the load pressure of the receivers (Ri) and delivering the hydraulic fluid at the set pressure. The circuit being composed of hydraulic modules (Mi) each associated with a receiver having a distributor that adjusts the variable flow supplying the receiver (Ri) through a pressure compensator (15), connected at the input (U) to the output of the variable throttle (20) of the distributor (11) and output (V). The plunger (150) manages the communication between its input (U) and its output (V). The pressure compensator (15) has a fluidic connection (31, 32) provided with a constriction (33, 33a) and connecting the outlet (V) to the line (LS), irrespective of the position of the plunger (150) .
    公开号:FR3057309A1
    申请号:FR1659756
    申请日:2016-10-10
    公开日:2018-04-13
    发明作者:Emmanuel Richer
    申请人:Robert Bosch GmbH；
    IPC主号:
    专利说明:

    057 309
    59756 ® FRENCH REPUBLIC
    NATIONAL INSTITUTE OF INDUSTRIAL PROPERTY © Publication number:
    (to be used only for reproduction orders)
    ©) National registration number
    COURBEVOIE © IntCI 8 : F15 B 11/05 (2017.01)
    PATENT INVENTION APPLICATION
    A1
    ©) Date of filing: 10.10.16.(© Priority: © Applicant (s): ROBERT BOSCH GMBH— DE. @ Inventor (s): RICHER EMMANUEL. ©) Date of public availability of the request: 04/13/18 Bulletin 18/15. ©) List of documents cited in the preliminary search report: See the end of this booklet(© References to other related national documents: ® Holder (s): ROBERT BOSCH GMBH. ©) Extension request (s): © Agent (s): CABINET HERRBURGER.
    MULTIPLE CONTROL HYDRAULIC CIRCUIT.
    FR 3 057 309 - A1
    Multiple control hydraulic circuit for supplying receivers with hydraulic fluid supplied by a pressure-controlled flow pump (PLS) of the control line (LS) depending on the load pressure of the receivers (Ri) and supplying the hydraulic fluid at the set pressure. The circuit being composed of hydraulic modules (Mi) each associated with a receiver having a distributor which regulates the variable flow supplying the receiver (Ri) through a pressure compensator (15), connected at the inlet (U) to the outlet of the variable throttle (20) of the distributor (11) and at the outlet (V). The plunger (150) manages the communication between its inlet (U) and its outlet (V).
    The pressure compensator (15) has a fluid connection (31,32) provided with a throttle (33,33a) and connecting the outlet (V) to the line (LS), whatever the position of the plunger (150) .
    i
    Field of the invention
    The present invention relates to a multiple control hydraulic circuit for supplying receivers with hydraulic fluid supplied by a flow pump controlled by the pressure of the control line dependent on the load pressure of the receivers and supplying the hydraulic fluid to the regulated pressure, the circuit being composed of hydraulic modules each associated with a receiver having a distributor whose drawer actuated by the operator regulates the variable flow supplying the receiver through a pressure compensator, connected at the inlet to the outlet of the throttle variable from the distributor and at the output, to the supply of the associated receiver, via a non-return valve, the pressure compensator having a plunger managing the communication between its input and its output, and of which:
    * one side is exposed to the control pressure of the control line and the other side transmits this pressure to the outlet of the distributor to subject it to a fixed pressure difference corresponding to the difference between the control pressure and the pump pressure, * the diver having a side passage communicating his line of entry and exit depending on the position of the diver.
    State of the art
    Such a multiple control hydraulic circuit is already known, in particular in document EP 0 566 449 B1 which describes a hydraulic distributor combining pressure compensation and selection of maximum pressure.
    This state of the art which is a reference in this field is interesting but it would be desirable to improve the operation of the hydraulic distributor, in particular for the transient phases, to give the hydraulic circuit thus controlled more flexibility and efficiency.
    Presentation and advantages of the invention
    To this end, the subject of the invention is a hydraulic multiple control circuit of the type defined above characterized in that the pressure compensator has a fluid connection provided with a throttle and connecting the outlet to the control line, whatever whatever the position of the diver.
    The pressure compensator, thanks to this fluidic connection, gives the hydraulic multiple control circuit a certain flexibility of operation since the control pressure is not limited to the maximum pressure imposed on the control line by the receiver having the charge the higher.
    Thanks to the exchange of fluid between the circuits of the receivers via pressure compensators, a pressure is established at an evolving level, and not blocked on a fixed value.
    According to another advantageous characteristic, the fluid connection crosses the plunger by connecting one side of the plunger still facing the outlet of the compensator and the top of the plunger opening into the control line.
    This realization of the fluidic connection which is a permanent connection in the general sense, constitutes a technically very interesting solution because simple to realize.
    According to another characteristic, the compensator has: a lateral passage starting from the inlet and the outlet of which opens laterally into the outlet in a variable section depending on the equilibrium position of the plunger as a function of the flow rate arriving from the distributor, a zone of separation which closes the outlet for the side passage in the depressed position of the plunger when the outlet pressure of the distributor is lower than the control pressure, the fluid connection opening into the outlet beyond the separation zone to remain open when the plunger is in the depressed position.
    According to another advantageous characteristic, the fluid connection is composed of a transverse passage opening into the outlet beyond the separation zone which separates the transverse passage from the outlet from the lateral passage and from a longitudinal passage opening into the top of the plunger .
    According to the invention, the constriction of the fluid connection is preferably carried out in the longitudinal passage, which simplifies its realization, preferably at a constriction which would be carried out in the transverse passage; in fact, it opens on both sides of the plunger to guarantee communication with the compensator outlet.
    According to another advantageous characteristic, the fluidic connection is formed of a transverse passage opening into the outlet beyond the separation zone between the outlet of the lateral passage and a longitudinal passage opening into a transverse passage high open laterally under the above, a constriction connecting the high transverse passage above the plunger, opening into the line.
    This alternative embodiment has the advantage of modifying the section of the throttle connecting the plunger of the dominant circuit to the connecting pipe with respect to the section of passage of the throttles in the other fluid connections by which the hydraulic fluid of the line control escapes to the plungers and circuits of the other receivers.
    In general, the permanent fluid connection between the control pipe and the outlet of the compensator makes it possible to give the operation an extremely advantageous flexibility for controlling the circuit.
    Drawings
    The present invention will be described below in more detail with the aid of examples of a multiple control hydraulic circuit represented in the appended drawings in which:
    FIG. 1 is a diagram of a hydraulic multiple control circuit with two modules, FIG. IA is a detail on an enlarged and schematic scale of an example of a module of the circuit of FIG. 1, FIGS. 2A, 2C are views in schematic section of a known pressure compensator represented in three positions, the stopped position (FIG. 2A), the equilibrium position (FIG. 2A) and the end position (FIG. 2C), FIGS. 3A-3C show a first embodiment of a pressure compensator according to the invention, in the three characteristic positions, the stopped position (FIG. 3A), the equilibrium position (FIG. 3B) and the end of travel position (FIG. 3C) , Figures 4A, 4C show a second embodiment of a pressure compensator according to the invention, in the three characteristic positions, the stopped position (Figure 4A) the equilibrium position (Figure 4B) and the end position racing (Figure 4C), Figure 5 shows very schematically nt an example of a multiple control hydraulic circuit composed of two modules.
    In the description of the figures, the expressions lower upper correspond to the orientation of the figures.
    Description of embodiments of the invention
    FIG. 1 shows a multiple control hydraulic circuit 100 supplying receivers RI, Ri (i = 1-2 ...) with hydraulic liquid under controlled pressure, supplied by an adjustable pump 1 withdrawing the liquid from a tank 2.
    The Ri receivers, the number of which depends on the equipment controlled by the hydraulic circuit 100, are for example double-acting cylinders, single-acting cylinders, but also actuators or rotary motors. At the outlet of the receivers, the hydraulic fluid returns to the reservoir 2 through the circuit.
    The multiple control hydraulic circuit 100 is made up of modules, Mi (i = 1-2 ...) each associated with a receiver Ri and connected in parallel to the supply line P of hydraulic fluid at a regulated pressure Pr and to the return line T to the tank 2. The supply line P has a pressure limiter 3 which limits the pressure to a maximum level P m ; its output is connected to tank 2.
    The pump 1 is controlled by the control pressure line LS connected to the modules Mi and transmitting the control pressure Pc supplied by the modules as a function of the load pressure of the receivers Ri.
    The pipes also called lines P, LS, T are produced by holes passing through the modules Mi in the form of stacked plates. The stack of Mi modules is fitted with an Mo input module for connection to pump 1 and tank 2 and a Mex end module which closes the pipes.
    The Mi modules have the same general structure, so their description will be limited to a Mi module and its receiver Ri (i = l ...).
    Each module Mi comprises a distributor 11, the drawer 12 of which is actuated by the operator according to the maneuver to be carried out with the receiver Ri which he controls. It regulates the flow of liquid to be supplied to the receiver Ri supplied as a function of the single operation of the drawer 12 (its throttle 20) by means of the pressure compensator 15 combined with the distributor 11. The pressure compensator 15 whose general operation is known will be discussed below.
    Each module Mi thus has an active output 16, an input 17 (output) of control pressure Pc (line LS), an input 18 of hydraulic fluid under pressure 18 (line P) and an output 19 (line T) to the reservoir. 2.
    By convention, the two return / return connections of the hydraulic fluid from the receiver Ri are considered to be an active output since only the direction "go" matters and that, depending on the commanded direction of the receiver Ri, the two pipes are reversed.
    The hydraulic fluid supply input 18 is connected through the distributor 11 by the line U to the input of the pressure compensator 15 whose output V feeds the receiver Ri by returning through the distributor 11 then playing the role of 'switch to supply one or the other chamber of the receiver Ri if the latter has a double effect; in the case of a single-acting receiver, only the hydraulic chamber will be supplied directly and the distributor will not have this switching function. The referral function is performed by the drawer 12.
    According to the conventional representation used here, the slide 12 has an intermediate segment SI for the neutral position, blocking the entry and exit of the receiver Ri. This segment SI is bordered on each side by a segment S2, S3 with a passage (throttle 20) of variable section according to the positioning of the drawer 12 to connect either directly the chambers A and B of the receiver (supply and return to the tank) or by reversing this supply to chambers A and B. The reversing segment S3 is not intended for a single-acting receiver.
    The hydraulic circuit of the module Mi is that of the LUDV mode, with the compensator 15 downstream of the throttle 20 of the distributor 11 as opposed to the LS mode according to which the pressure compensator 15 would be installed upstream of the throttle 20. But in in both mounting cases, the pressure control line is conventionally designated by "LS control pressure line".
    FIG. 1A shows, in a simplified manner, a single module Mi on an enlarged scale. In this module Mi, the route of the lines between the lines P, LS, T and the distributor 11 as well as the compensator 15 leaves only the active lines, those of a liquid circulation and those of a pressure transmission. Thus, in the drawing of the distributor 11, only the line of variable section (throttle 20) of the slide 12 remains connected downstream by the line U to the input U1 of the compensator 15 and by the link U2 to its face 151 for transmission. pressure. Line V is the link connected at the output of the compensator 15 to the receiver Ri. The line LS is connected by its branch LS2 to the face 152 of the plunger 150 to transmit its pressure Pc and to the inlet LSI for the passage of hydraulic fluid. The face 152 can also be subjected to the action of a calibrated spring 153.
    The pressure Pu of the line U acting on the face 151 of the plunger 150 exerts a thrust in the direction of the opening opposite to that exerted on the face 152 which acts in the direction of closing the passage between the lines U and V.
    The simplified layout thus shows the direct connection from the output of the compensator 15 to the active output 16 without going back into the distributor 11 which is perfectly transparent, the connection through the distributor is only necessary to reverse the supply of the chambers of the receiver .
    The liquid return from the receiver Ri has been suppressed since it is a pressureless liquid returning to the tank 2, for example directly.
    In this simplified diagram, the plunger 150 of the compensator 15 is the plunger of a compensator of the invention, respectively represented in three positions in FIGS. 3A-3C; 4A-4C.
    The module Mi is the representative of the modules (Mi = l-2 ... n) of the hydraulic multiple control circuit 100 (FIG. 1) controlling the receivers Ri (i = l-2 ... n). The receivers Ri necessarily have a charge (pressure) different from each other and according to the known operation, the module Mj of which, at a given moment, the receiver Rj having the highest charge, imposes this as the control pressure Pls to pump 1 which, depending on this pressure, feeds the various Mi modules.
    In this organization, the control pressure Pls imposed by the module Mj is reflected at the level of the other modules Mi, active (that is to say whose distributor actively controls the receiver associated with this module) by an identical pressure difference at the terminals of each distributor 11 so that the distributors distribute the flow rate supplied by the pump 1 to the line P as a function of the single passage section (throttle 20) adjusted by the drawer 12 of the distributor 11 of each module Mi. This distribution is not fixed because in a multiple control hydraulic circuit 100, the Mi modules have variable operation since some modules will be stopped and others, activated; each time the dominant module for which the receiver has the greatest load, imposes its pressure to control pump 1, the flow of which will then be distributed under the same conditions as above according to the new surface of the passage section of each drawer 12 of the modules activated.
    The changes of state of the various Mi modules induce pressure variations resulting in an operation with abrupt variations of each Mi module which the invention remedies by fluidizing the operation of the multiple control hydraulic circuit 100 by softening the rigid connection according to the state of the art between the load of the dominant module and the other modules.
    To explain this situation, a pressure compensator will be presented below in general (Figures 2A-2C) in comparison with pressure compensators according to the invention (Figures 3A-3C; 4A-4C).
    Thus, FIGS. 2A-2C show a module Mi with a known pressure compensator, in its initial position (FIG. 2A), in its equilibrium position (FIG. 2B) and in its end-of-travel position (FIG. 2C).
    The compensator 25 has a bore 254 housing the plunger 250. The line LS crosses the top of the bore 254; the outlet pipe V comes from the side of the bore 254 and the inlet pipe U opens into the lower part of the bore 254. The pipe U is connected to the outlet of the passage 20 of the drawer 12 of the distributor 11. Line V is the compensator output line 25 connected to the active output 16 of the module Mi and to the receiver Ri.
    The diver 250 includes:
    a lateral passage 230 (or a set of passages distributed around the periphery), a longitudinal passage 231 provided with a throttle 233 and opening into a transverse conduit 232 in the top of the plunger under the upper face 252 of the plunger 250,
    The lateral passage 230 communicates, along a surface of variable section, the pipes U and V as a function of the position of the plunger 250 in the bore 254.
    The known compensator 25, operating in LUDV mode, will be described below.
    Initially, at start-up (FIG. 2A) the plunger 250 is in the low position; there is no pressure, neither in the LS control line, nor in the pump line P and the line U, the pump being stopped.
    Switching on the pump 1 produces an output at the pressure APo; this pressure is transmitted by at least one compensator 25 (it is assumed that a distributor of the circuit is actuated) and therefore in the control line LS whose control pressure Pls will be: Pls = APo and arrives on the face 252 of the plunger 250 ; gradually, the control pressure of the pump 1 increases to finally arrive at the pressure requested by the distributor.
    In normal operation (FIG. 2B), the compensator 25 is at equilibrium, which means that the two faces 251, 252 are at the same pressure (the active surfaces of the faces being assumed to be equal). Thus, the outlet of the distributor 11 is at the pressure Pls imposed by the plunger 250 transmitting to its lower face 251 the pressure Pls applied to its upper face 252 and its inlet is at the outlet pressure Pp from the pump 1.
    However, the pump 1, controlled at the pressure Pls delivers at the pressure Pp = Pls + ΔΡο; ΔΡο is the pressure difference that the pump adds to the control pressure to output the pressure Pp.
    Thus, the distributor 11 is subjected to a constant pressure difference ΔΡι = ΔΡο so that its flow rate Qi only depends on the opening section (variable) 20, controlled by the operator operating the distributor 11.
    The communication between the input U and the output V of the compensator 25 is exposed to a pressure difference ΔΡ2 = Ρν-Ρυ (= Pls) which thus gives ΔΡ2 = ΔΡο. This pressure difference is constant.
    The passage section between U and V in the compensator 25 at equilibrium is thus adjusted automatically since the flow rate Ql is imposed on it by the distributor 11.
    If the compensator 25 has a calibrated spring acting in addition to the pressure Pls, the situation is slightly modified but the operating principle described above remains the same.
    Operation assumes that the outlet pressure Pv is not less than the charge pressure otherwise the non-return valve 155 cannot open to supply the receiver Ri. This case is equivalent to a start of operation of the hydraulic system, when the control pressure Pls = 0 and that the pump 1 starts to flow at the pressure ΔΡο and then gradually, the control pressure Pls reaches the highest charge pressure activated receptors.
    If the thrust generated by the pressure Pu and applied to the face 251 exceeds that exerted on the other face 252, the plunger 250 arrives at the end of the stroke, completely opening the inlet of the pipe V and making the pipe U communicate with the line LS by transmitting to it the pressure Pu decreased by the throttle 233 (FIG. 2C).
    ίο
    The plunger 250 imposes its pressure as the control pressure in the line LS controlling the pump 1 and then operates as a pressure selector of the module Mi of which the receiver Ri has the highest load. In the other active Mi modules, the compensators function as pressure regulating valves. The situation evolves as a function of that of the Mi modules which, at a given instant, feeds the highest load.
    This distribution of flow, advantageous in itself, nevertheless has drawbacks of operating rigidity when a module is stopped or another module is activated as has already been described above.
    The pressure compensator 15, 15a according to the invention makes it possible to reduce or avoid this difficulty.
    FIGS. 3A-3C show a first embodiment of a pressure compensator 15 according to the invention, installed in the bore 154 of the module Mi with its lines LS, U, V. The calibrated spring 153 has not been represented.
    Thus, FIGS. 3A-3C show the module Mi with a pressure compensator 15 in its initial position (FIG. 2A), in its equilibrium position (FIG. 2B) and in its end-of-travel position (FIG. 2C).
    The compensator 15 has a bore 154 housing the plunger 150. The line LS crosses the top of the bore 154; the outlet pipe V comes from the side of the bore 154 and the inlet pipe U opens into the lower part of the bore 154. The pipe U is connected to the outlet of the passage 20 of the drawer 12 of the distributor 11. Line V is the compensator output line 15 connected to the active output 16 of the module Mi and to the receiver Ri.
    According to the diagramming convention of FIG. IA, the plunger 150 comprises:
    a lateral passage 30 (or a set of passages distributed around the periphery), a longitudinal passage 31 provided with a throttle 33 and opening onto the top face 152 of the plunger 150, a connecting passage 32 connected to the longitudinal passage 31 and opening into the outlet pipe V, whatever the position of rotation of the plunger in the bore 154 and whatever its longitudinal position.
    The lateral passage 30 communicates, along a surface of variable section, the pipes U and V as a function of the position of the plunger 150 in the bore 154.
    According to the comparison of FIGS. 3A, 3B and of FIG. IA, the liquid passage pipe U1 is constituted by the lateral passage 30; the pressure line U2 is the outlet of the line U under the plunger 150. The liquid line LSI is the communication by the longitudinal passage 31 and the connection passage 32; the pressure line LS2 is the outlet of the line LS in bore 134.
    The longitudinal passage 31 with a throttle 33 opens on the one hand, into the top 152 and on the other hand, into a connecting passage 32 passing through the lower part of the plunger 150, above its lateral passage 30 without communicating with that -this. There remains a separation zone 34 between the outlet of the connecting passage 32 and the lateral passage (s) 30. The lower part 35 of the plunger 150 forms a driving stop.
    A push on the face (bottom) 152 of plunger 150 goes in the direction of closing the U / V communication between the inlet pipe U and the outlet pipe V and an opposite push, generated by the pressure Pu s' exerting on the other face (above) 151 goes in the direction of the opening of the U / V communication.
    Under normal conditions (FIG. 3B), the plunger 150 goes into equilibrium position according to the pressure Pls applied to its face 152 and transmitted to its face 151 to arrive at the distributor 11 whose flow rate Q1 will be regulated by the throttle 20 .
    In all the positions of the plunger 150, including the end position of FIG. 3C, the line LS communicates with the pipe V by the longitudinal passage 31 with its throttle 33 and the transverse passage 32 so that if the pressure Pls in the line LS is higher than the pressure in the line, there will be passage of liquid from the line LS to the lines V, U. It is only in the extreme posi3057309 tion of the absence of pressure in the line U that the plunger 150 will be pushed in so much that the separation zone 34 will cut the communication between the lines U and V and will only leave the connection between the line LS and the line V.
    However, according to a variant, there is no separation zone 34.
    In all the variable, equilibrium positions of the plunger 150, there is floating communication between the lines V and U with a positive or negative leak with the line LS through the passage 31 and the connection passage 32.
    As a variant of the embodiment described and shown, the permanent communication between the lines V and LS can take place in the body of the compensator 15 and not in the plunger 150. This solution is advantageous but that of the plunger 150 provided with this communication (31 -32) has the advantage of greater flexibility and simplicity of manufacture, because according to demand, it will be possible to equip the same module, with a plunger with or without communication 31-32.
    In the compensators 15 according to the invention, the line LS which connects the different modules Mi carries out an exchange of liquid through the “leakage” paths in the plungers 150 so that the pressure Pls of the line LS controlling the operation of the pump 1 will be lower than the pressure imposed by the module associated with the regulator Ri with the highest charge pressure.
    This “fuzzy” control pressure Pls is less than the maximum control pressure which would be imposed in an installation operating in LUDV mode, and allows, according to the invention, much more flexible operation of the hydraulic installation, in particular during stops / starts of the different Mi modules.
    In this example of compensator 15 according to the invention, the lower face 151 is generally and substantially the apparent surface from below of the plunger 150; the situation is similar for the upper face 152. The effective hydraulic surfaces of these faces 151, 152 are reduced in a variable manner due to the communication by the passages 31, 32, 33.
    Figures 4A-4C show a variant of the pressure compensator 15a according to the invention. This variant differs from the embodiment of FIGS. 3A-3C by the top 152a of the plunger 150a.
    The plunger 150a has a longitudinal passage 31a 5 without constriction, opening at the bottom in the transverse passage 32a like the plunger 150, with a separation zone 34a and below this, a lateral passage 30a.
    In the upper part, the longitudinal passage 31a arrives in a high transverse passage 35a opening on the sides and connected to the face 152a of the top of the plunger 150a by a constriction 33a.
    The operation of the pressure compensator 15a is generally the same as that of the plunger 15, as long as the top transverse passage 35a is covered by the bore 154 since at this time, the throttle 33a of the plunger 150a is the equivalent of 1 constriction 33 of the plunger 150. It is only when the top of the plunger 150a opens into the line LS that the constriction 33a no longer intervenes since communication is released through the plunger 150. This means that at this time , the same pressure prevails in the line LS and in the lines V and U. Thus, the module Mj associated with the receiver Rj having the greatest load, will impose on the line LS this load and not a pressure reduced by the reduction in pressure generated by the throttle 33a.
    The difference between the section SI of the constriction 33a and that S2 of the transverse passage 35a accentuates the blurring effect.
    In the high position of the plunger 150a associated with the receiver
    Ri having the greatest load, the communication between the pipe U and the line LS takes place in the outgoing direction by the transverse passage 35a while the compensators of the other active Mi modules will be assumed to be at equilibrium. This means that the transver30 sal 35a passage of these divers 150a will be cut and the communication between the LS line and the V or U line will be through throttle 33a.
    FIG. 5 shows an example of a multiple control circuit 100-1 with several modules Mi of which two modules Ml, M2 are shown.
    They correspond to the structure of FIG. 1 and the receivers RI, R2 have respectively as load, a pressure of 100 bar and 200 bar. The pressure relief valve 3 has a threshold which is fixed at 250 bar.
    It is assumed that the receiver R2 is stopped, its piston being at the end of its travel. The module M2 therefore transmits the inlet pressure P = Pls + APo, supplied by the pump 1, to the line P towards the line LS through the compensator 15-2 with a pressure drop ΔΡ2.
    By assumption, as before the R2 receiver stopped, the pressure was 200 bar, we can assume that the pump pressure
    Pp (= Pls + APo) is greater than the charge pressure Pi of the receiver Ri.
    The receiver RI being active, its compensator 15-1 balances and transmits the control pressure Pls which thus applies to the outlet of the distributor 11-1.
    Modules that have a charge pressure higher than the pump pressure will stop and the distribution of the pump flow will be more blurred due to the average pressure drop.
    NOMENCLATURE OF MAIN ELEMENTS (without literal suffixes)
    Multiple control hydraulic system
    Distributor
    Drawer
    if ίS2 > Drawer segments S3 - Pressure compensator 150 Diver 151 First side / bottom 152 Second side / top 153 Tared spring 154 Bore 155 Non-return valve Side passage Longitudinal passage Cross passage Choking Separation area High transverse passage
    Pressure compensator
    250 Diver
    251 First side / bottom
    252 Second side / top
    254 Bore
    230 Side passage
    231 Cross passage
    232 Longitudinal passage
    233 Strangulation
    Active pressure output
    Control pressure input
    Hydraulic fluid inlet Outlet to the tank Variable throttle of the drawer
    1
    3
    Mid
    Ri P T LS Pls
    Pp U V
    1
    3
    Mid
    Ri P T LS Pls
    Pp U V
    Feed pump
    Tank
    Pressure limiter
    Distributor module
    Receiver
    Pump line
    Tank return line
    Control pressure line
    Control pressure
    Pump pressure
    Compensator input
    Compensator output
    权利要求:
    Claims (6)
    [1" id="c-fr-0001]
    1 °) Multiple control hydraulic circuit for supplying receivers (Ri) with hydraulic liquid supplied by a pump (1) with a flow controlled by the pressure (Pls) of the control line (LS) depending on the charge pressure of the receivers (Ri) and delivering the hydraulic fluid at the set pressure (Pp), the circuit being composed of hydraulic modules (Mi) each associated with a receiver (Ri) having a distributor (11) including the slide (12) actuated by the operator regulates the variable flow supplying the receiver (Ri) through a pressure compensator (15), connected at the input (U) to the output of the variable throttle (20) of the distributor (11) and at the output (V) , to the supply of the associated receiver (Ri), by means of a non-return valve (155), the pressure compensator (15) having a plunger (150) managing the communication between its input (U) and its output (V), and of which:
    * one side (152) is exposed to the control pressure (Pls) of the control line (LS) and the other side (151) transmits this pressure to the outlet of the distributor (11) to subject it to a difference of fixed pressure corresponding to the difference between the control pressure (Pls) and the pump pressure (Pp), * the plunger (150) having a lateral passage (30) making its inlet line (U) and its outlet (V) communicate according to the position of the plunger (150), circuit characterized in that the pressure compensator (15) has a fluid connection (31, 32) provided with a throttle (33, 33a) and connecting the outlet (V) to the line regardless of the position of the plunger (150).
    [2" id="c-fr-0002]
    2 °) hydraulic circuit according to claim 1, characterized in that the fluid connection (31, 32) passes through the plunger (150) by connecting one side of the plunger still facing the outlet (V) and the top (152) of the plunger (150) opening into the command line (LS).
    [3" id="c-fr-0003]
    3) hydraulic circuit according to claim 1, characterized in that the compensator (15) has a lateral passage (30) starting from the inlet (U) and the outlet of which opens laterally into the outlet (V) in a variable section depending on the equilibrium position of the plunger (150) as a function of the flow rate arriving from the distributor (11), a separation zone (34) which closes the outlet for the lateral passage (30) in the depressed position of the plunger when the pressure of dispenser outlet is lower than the control pressure (Pls), the fluid connection (31, 32) opening into the outlet (V) beyond the separation zone (34) to remain open when the plunger (150) is in the depressed position.
    [4" id="c-fr-0004]
    4) hydraulic circuit according to claims 1 and 3, characterized in that the fluid connection (31, 32) is composed of a transverse passage (32) opening into the outlet (V) beyond the separation zone ( 34) which separates the transverse passage from the outlet from the lateral passage (33) and from a longitudinal passage (31) opening into the top (152) of the plunger (150).
    [5" id="c-fr-0005]
    5 °) Hydraulic circuit according to one of claims 1 and 4, characterized in that the throttle (33) of the connection is made in the longitudinal passage (31).
    [6" id="c-fr-0006]
    6 °) hydraulic circuit according to one of claims 1 and 3, characterized in that the fluid connection (31a, 32a) is formed of a transverse passage (32a) opening into the outlet (V) beyond the area separation (34a) between the outlet of the lateral passage (30) and a longitudinal passage (31a) opening into a high transverse passage (35a) open laterally below the top (152a), a constriction (33a) connecting the transverse passage high (35a) above (152a) of the plunger, opening into the line (LS).
    1/5
    X-X-1
    Ο
    Ό ^ Mi (i = 1) '' Mi (i = 2) 'ΜθΧ
    类似技术:
    公开号 | 公开日 | 专利标题
    FR3057309A1|2018-04-13|HYDRAULIC CONTROL CIRCUIT
    EP3527865B1|2021-03-03|Fluid valve
    JP2009174714A|2009-08-06|Hydraulic control valve system with isolated pressure-compensation device
    FR2689575A1|1993-10-08|Hydraulic distributor with pressure compensation and a maximum pressure selection to control a pump and multiple hydraulic control including such distributors.
    CN105570220A|2016-05-11|Multiway valve and hydraulic flow sharing system
    WO2015064025A1|2015-05-07|Hydraulic drive system of construction machine
    WO2003013896A1|2003-02-20|Hydrostatic transmission device of a mobile machine
    EP2491277A1|2012-08-29|Hydrostatic transmission device enabling improved braking
    FR2910566A1|2008-06-27|VALVE ARRANGEMENT WITH HYDRAULIC CONTROL
    WO2014167190A1|2014-10-16|Device for controlling the supply of a fluid to a system allowing fluid consumption to be optimised
    FR2913218A1|2008-09-05|Hydrostatic transmission device for land vehicle, has front and rear motors fixed by series flow-line, and pressure limitation valve connecting flow-line with low pressure circuit, where valve is controlled based on high pressure of pump
    EP0009749B1|1983-10-05|Pressure control valve with 3 or 4 levels
    CN105986595B|2019-10-01|Hydraulic system and machine for machine
    CN202851491U|2013-04-03|Load-sensitive multi-way valve used in loader variable system
    BE898332A|1984-03-16|Method for saving energy when adjusting a cylinder of hydraulic excavator equipment by means of a hydraulic assembly.
    EP0500419B1|1995-11-22|Proportional valve and control system with a plurality of actuators having each such a valve
    FR2964711A1|2012-03-16|IMPROVED BREAKER CIRCUIT BREAKER
    FR2873175A1|2006-01-20|HYDRAULIC CIRCUIT COMPRISING A MULTIFUNCTION SELECTOR
    EP3163076B1|2018-06-13|Hydraulic machine with two displacements and safety valve
    FR2621354A1|1989-04-07|LOAD INDEPENDENT CONTROL DEVICE FOR HYDRAULIC USER DEVICES
    EP1674765B1|2008-02-13|Fluid supply system for a mecanism with a hydraulic control
    FR2691517A1|1993-11-26|Hydrostatic transmission comprising control and braking valves powered by the same control pressure.
    FR2845439A1|2004-04-09|HYDRAULIC VALVE DEVICE
    FR3025853B1|2019-07-19|HYDROSTATIC DRIVE SYSTEM
    KR102125582B1|2020-06-22|Hydraulic systems of construction machinery
    同族专利:
    公开号 | 公开日
    CN107917118A|2018-04-17|
    JP2018063048A|2018-04-19|
    FR3057309B1|2018-11-16|
    US20180100521A1|2018-04-12|
    CN107917118B|2021-04-02|
    JP6961448B2|2021-11-05|
    US10563674B2|2020-02-18|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP0516864A1|1990-11-26|1992-12-09|Hitachi Construction Machinery Co., Ltd.|Hydraulic driving system and direction change-over valves|
    EP0733743A1|1995-03-24|1996-09-25|O&K ORENSTEIN & KOPPEL AG|Flow distribution device, independent of the load pressure, for control valves in mobile working machines|
    EP2871370A1|2013-10-15|2015-05-13|Robert Bosch Gmbh|Valve assembly|CN113775592A|2021-11-11|2021-12-10|太原理工大学|Digital mechanical redundant pressure compensation flow control system|FR2689575B1|1992-04-06|1994-07-08|Rexroth Sigma|HYDRAULIC DISTRIBUTOR WITH PRESSURE COMPENSATION AND A MAXIMUM PRESSURE SELECTION FOR DRIVING A PUMP AND MULTIPLE HYDRAULIC CONTROL INCLUDING SUCH DISTRIBUTORS.|
    US6782697B2|2001-12-28|2004-08-31|Caterpillar Inc.|Pressure-compensating valve with load check|
    CN103174697B|2013-03-22|2015-04-15|江苏恒立高压油缸股份有限公司|Hydraulic valve system with pressure compensation function|
    CN104265715B|2014-10-16|2017-02-15|江苏恒立液压科技有限公司|pressure compensating valve|
    JP6440451B2|2014-10-27|2018-12-19|Ｋｙｂ株式会社|Load sensing valve device|
    CN105782153A|2016-05-04|2016-07-20|宁波市加力特机械有限公司|Pressure compensation valve of hydraulic pressure station of electric platform|CA2960802A1|2014-09-29|2016-04-07|Parker-Hannifin Corporation|Directional control valve|
    CN109114051B|2018-08-28|2019-12-31|武汉船用机械有限责任公司|Variable load tool|
    EP3620582B1|2018-09-10|2022-03-09|Artemis Intelligent Power Limited|Apparatus comprising a hydraulic circuit|
    EP3620583A1|2018-09-10|2020-03-11|Artemis Intelligent Power Limited|Industrial vehicle with hydraulic machine torque control|
    US11178819B2|2019-01-24|2021-11-23|Deere & Company|Modularized hydraulic system for agricultural combine|
    CN113074155A|2021-04-02|2021-07-06|同济大学|Negative pressure opening plug-in mounting type oil replenishing valve|
    法律状态:
    2017-10-23| PLFP| Fee payment|Year of fee payment: 2 |
    2018-04-13| PLSC| Publication of the preliminary search report|Effective date: 20180413 |
    2018-10-22| PLFP| Fee payment|Year of fee payment: 3 |
    2019-10-22| PLFP| Fee payment|Year of fee payment: 4 |
    2020-10-20| PLFP| Fee payment|Year of fee payment: 5 |
    2021-10-18| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1659756|2016-10-10|
    FR1659756A|FR3057309B1|2016-10-10|2016-10-10|HYDRAULIC CONTROL CIRCUIT|FR1659756A| FR3057309B1|2016-10-10|2016-10-10|HYDRAULIC CONTROL CIRCUIT|
    US15/728,136| US10563674B2|2016-10-10|2017-10-09|Multi-hydraulic control circuit|
    CN201710929497.9A| CN107917118B|2016-10-10|2017-10-09|Compound control hydraulic circuit|
    JP2017196883A| JP6961448B2|2016-10-10|2017-10-10|Multiple control type hydraulic circuit|
    [返回顶部]