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EP0141301B1 - Circuit hydraulique pour un moteur entraînant une charge - Google Patents

Circuit hydraulique pour un moteur entraînant une charge Download PDF

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Publication number
EP0141301B1
EP0141301B1 EP84112058A EP84112058A EP0141301B1 EP 0141301 B1 EP0141301 B1 EP 0141301B1 EP 84112058 A EP84112058 A EP 84112058A EP 84112058 A EP84112058 A EP 84112058A EP 0141301 B1 EP0141301 B1 EP 0141301B1
Authority
EP
European Patent Office
Prior art keywords
valve
line
load
pressure
control valve
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
EP84112058A
Other languages
German (de)
English (en)
Other versions
EP0141301A1 (fr
Inventor
Gary Thompson Barker
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
Application filed by Deere and Co filed Critical Deere and Co
Priority to AT84112058T priority Critical patent/ATE28233T1/de
Publication of EP0141301A1 publication Critical patent/EP0141301A1/fr
Application granted granted Critical
Publication of EP0141301B1 publication Critical patent/EP0141301B1/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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8636—Circuit failure, e.g. valve or hose failure

Definitions

  • the invention relates to a hydraulic circuit for a double-acting cylinder with a piston that divides the cylinder into a lifting side and a lowering side for lifting and lowering a load, engine with a pump for pressurized liquid, a control valve and two lines connect the control valve to the motor, depending on the position of the control valve, serve as a feed or return line and each have a hydraulically controlled valve, both of which can be controlled against the force of a spring by the pressure prevailing in the line between the control valve and valve in the lower side.
  • valves are designed such that they open at the same time.
  • two springs of equal strength are provided, which act on pilot-controlled pistons. These are provided with conical surfaces that connect the corresponding inlets and outlets.
  • bypass channels with check valves are also installed in the pistons, which are used in such a way that they prevent or at least greatly delay a reduction in the pilot pressure when the control valve is in the neutral position, so that the corresponding lines are exposed to large loads.
  • the motor which is preferably used for lifting and lowering loads, comes to a standstill immediately or moves in a controlled manner without external influence and abruptly Movements are excluded.
  • both valves can immediately go into their closed position, with the valve that opens first, which is provided for lowering the load in the return line, relieving the relevant end of the valve at an early stage Cylinder enters before the other 'end of the cylinder is pressurized.
  • control valve is designed as a valve with inlet metering and releases the return before the inlet opens, it is achieved that a connection of a line, i. H. which then acts as a return line with a collecting container before a valve can be adjusted from its closed position to its open position via the common pressure.
  • a connection of a line i. H. which then acts as a return line with a collecting container before a valve can be adjusted from its closed position to its open position via the common pressure.
  • an anti-cavitation line is connected to the associated line between the control valve and the valve that opens first, to the lower side of the cylinder into which the other Line opens, is connected and has a check valve.
  • the check valve in the cavitation line should of course be provided in such a way that it only allows an inlet to the end of the cylinder which tends to cavitate.
  • the invention provides that a bypass throttle line with a throttle bridges the valve provided in the line from which the pilot pressures are branched off.
  • a check valve that allows the fluid to flow to the control valve can be provided in said line.
  • a load control system is designated 10. It has a hydraulic cylinder 12 with a displaceable piston 14, which divides the cylinder into a lower side 16 and a lifting side 18.
  • a piston rod 20 is connected to the piston 14 and led out of the cylinder to move a load 22.
  • the load control system 10 is also equipped with a pump 24 which is connected to a collecting container 26 and conveys pressurized liquid to one end of the hydraulic cylinder 12.
  • a manually operable control valve 28 is connected to the pressure side of the pump 24 and is connected via lines 30 and 32 to the lower side 16 and the lifting side 18 of the hydraulic cylinder 12, respectively.
  • the control valve 28 which is preferably designed as a four-way three-position valve with inlet metering, liquid can be supplied in each case to one side of the cylinder, the other side of the cylinder then being connected to the collecting container 26 in order to ensure a return flow Allow liquid.
  • a hydraulically controlled valve 34 is connected between the control valve 28 and the lower side 16 of the cylinder 12 and is normally held in a closed position by a spring 36, in which the flow of the liquid through this valve is interrupted.
  • a bypass line 38 bridges the valve 34 and is equipped with a check valve 40, which is arranged so that the liquid flow from the lower side 16 of the hydraulic cylinder 12 is possible and a liquid flow in the opposite direction is prevented.
  • a pilot line 42 branches off from the line 30 and is connected to the valve 34 in such a way that the area of the valve 34 which is opposite the spring 36 can be acted upon by pressurized liquid. As soon as the pressure in the pilot line 42 overcomes the force of the spring 36, the valve 34 will move into its open position, in which there is a fluid connection between the control valve 28 and the lower side 16 of the hydraulic cylinder 12.
  • a bypass throttle line 44 is connected in parallel to the bypass line 38 and bridges the valve 34. It is provided with an orifice 46, the function of which will be explained below.
  • the load control system 10 is also equipped with a hydraulically controlled valve 48 which holds the load and is provided in the line 32.
  • This valve 48 is also pressed by a spring 50 towards its closed position, in which a liquid flow from the stroke side 18 of the hydraulic cylinder 12 is normally prevented.
  • a pilot line 52 Via the pressure in a pilot line 52, the valve 48 can be adjusted into its open position against the force of the spring 50.
  • the pilot line 52 connects the valve 48 to the line 30 at a location that is between the control valve 28 and the valve 34. As soon as the pressure in the pilot line 52 rises and the force of the spring 50 overcomes, the valve 48 will shift into its open position, in which a fluid flow from the stroke side 18 of the hydraulic cylinder 12 via the control valve 28 to the collecting container 26 is possible.
  • a second check valve 54 is provided in the line 32, which allows a liquid flow from the valve 48 to the control valve 28, but prevents liquid flow in the opposite direction.
  • a bypass line 56 is also provided which bridges the valve 48 and the second check valve 54 and has a third check valve 58 which is arranged such that it prevents the flow of liquid from the stroke side 18 to the control valve 28 past the valve 48.
  • An anti-cavitation line 60 is also provided and connected at one end to the line 32 between the second check valve 54 and the valve 48 and at the other end to the line 30 between the valve 34 and the cylinder 12.
  • the anti-cavitation line 60 is designed such that liquid passing through the valve 48 can reach the lower side 16 of the hydraulic cylinder 12, so that no cavitation can occur. Reverse liquid flow is prevented by a fourth check valve 62 provided in the anti-cavitation line 60.
  • control valve 28 preferably has an inlet metering. This is intended to express that the line 32 is already open to the collecting container 26 before a pressure channel in the control valve 28 opens in order to allow liquid to flow into the line 30. As a result, the pressure in the line 32 will be considerably lower than the pressure in the line 30 when the lower side 16 of the cylinder 12 is pressurized with liquid under pressure and the load 22 is lowered in accordance with the arrangement according to FIG. 1. Since the pressure in line 32 is always low under these conditions, the pressure between valve 48 and control valve 28 will not change significantly if line 32 would fail. On the other hand, the opening times of the valve 34 and the valve 48 would not change significantly in such a case either. Since the amount by which the piston rod 20 slides out of the cylinder 12 also depends on the opening times of the valve 34 and the valve 48, the amount of displacement would not change particularly if the line 32 were to be defective.
  • the load control system 10 is furthermore provided with two sensor lines 64 and 66, which branch off from the anti-cavitation line 60 and are connected at the other ends to the valve 34 and to the load-holding valve 48, specifically on the engagement sides of the springs 36 and 50, see above that the pressure in the sensor lines 64 and 66 tends to move the valves 34 and 48 towards their closed positions, whereby an additional common pressure is present at each of the two valves so that both adjust proportionally.
  • the piston 14 can move gradually or gradually in contrast to abruptly, which is considered to be particularly advantageous.
  • the valve 48 is designed in such a way that it adjusts itself in the direction of its open position in front of the valve 34 when the pressure in the pilot line 52 is present.
  • the outlet for the liquid located on the stroke side 18 of the cylinder 12 is already free before additional liquid, which is under pressure, reaches the lower side 16 of the cylinder 12.
  • This also helps the piston 14 to move gradually and prevent it from moving an additional pressure builds up on the lower side 16 of the cylinder 12.
  • This feature also allows the load 22 to jump slightly without affecting the pressure in line 30 and pilot lines 42 and 52.
  • the open position of the valve 48 remains unaffected if the load jumps, which leads to a uniform operation.
  • Valve 34 and load-holding valve 48 operate proportionally in that they are both adjusted to their open position by a common fluid pressure against the action of springs 36 and 50 and another common pressure that deviates from the foregoing. This second common pressure therefore tends to adjust the valve 34 and the valve 48 in the direction of their closed positions.
  • the valve 34 is designed or adjusted so that with respect to the load-holding valve 48 at no operating speed, the liquid flowing through the valve 34 is sufficient to fill up the volume on the lower side 16 of the cylinder 12, which is in the downward movement of the Piston 14 arises as a result of the liquid flowing out of the stroke side 18 and through the valve 48. As a result, there will always be a pressure on the lower side 16 which is lower than the pressure in the line 30.
  • the proportionality of the valves 34 and 38 helps to ensure that both open in a uniform and controlled manner.
  • a pressure line 68 may also be provided in the system such that it bridges the load holding valve 48.
  • a pressure valve 70 is then to be arranged, which is normally held in its closed position by a spring and is adjusted so that it opens at a predetermined pressure, so that pressurized liquid can flow out from the stroke side 18 when the pressure between the stroke side 18 and the valve 48 should exceed the predetermined pressure.
  • This valve need not necessarily be reconnected to line 32. It can also, as shown in FIG. 2, branch off from the line 32 via a line 69 and be connected to the collecting container 26.
  • the load control system shown in FIG. 2 is designated 11. It differs from the system in FIG. 1 essentially in that the load 22 rests on the piston rod 20 and in that the pressure relief valve 70 is connected to the collecting container 26 via the line 69, which branches off from the line 32. This is important in this case because, in this constellation, the larger liquid volume that is dispensed from the lifting side 18 cannot be absorbed on the lower side 16. This arrangement allows liquid to flow out of the system before the pressure rises above a predetermined value, so that no damage occurs in the system.
  • This pressure is lower than the pressure in pilot lines 42 and 52, can range from 0.7 kg / cm 2 to 7 kg / cm 2 (10 to 100 psi) and tends to move valves 34 and 48 towards to move to their closed positions.
  • the valves 34 and 38 can adjust proportionally, and when the valve 48 moves a fixed amount in the direction of its closed position, the valve 34 moves a certain amount, which need not necessarily correspond to the fixed amount.
  • the ratio of the adjustment is essentially linear.
  • the jumping mentioned above can occur under certain operating conditions, that is to say that when the load is lowered, different speeds occur instead of the lowering speed desired by the operator.
  • valve 34 would cause an oscillating pressure on the lower side 16 of the cylinder 12, whereby the valve 48 would open and close and the jumping would be increased.
  • the springs 36 and 50 are selected so that the valve 48 measures the liquid from the stroke side 18, that is, it can always move in an opening and closing sense. This is of course influenced by the pressures applied to both valves on their sides. If the load should drop at a desired speed, the operator can intervene in a controlling manner by actuating the control valve 28. Depending on the amount by which the control valve 28 is adjusted, the pressure in the line 30 will also change and, since the valve 34 serves to build up a pressure upstream of the valve 34, this pressure is used to adjust the valve 48.
  • valves 34 and 38 are designed such that the load-holding valve 48 allows a larger amount of liquid to flow from the stroke side 18 of the cylinder 12 than is supplied to the lower side 16. This can of course lead to cavitation on the lower side 16, but this can be compensated for by the anti-cavitation line 60 and the fourth check valve 62 provided therein, since liquid is thus sucked from the line via the anti-cavitation line 60 into the lower side 16. This ensures that no cavitation occurs. Any slight fluctuation on the lower side 16 is also perceived by the sensor lines 64 and 66 and the pilot lines 42 and 52. This results in the same pressure changes on the valves 34 and 48, so that both valves are not impaired in their functions under dynamic load conditions.
  • the pressure in the pilot lines 42 and 52 also depends on the pressure between the control valve 28 and the valve 48 when the valve 34 is in a metering position, ie it is neither closed nor completely open. In this position, the pressure in the pilot lines 42 and 52 is determined by the pressure in the sensor lines, the forces of the springs 36 and 50 and the flow rate through the valve 34.
  • the control valve 28 After the load 22 has been lowered by a desired amount, the control valve 28 is returned to its neutral position. So that no more liquid can get into line 30 and the pressure in line 30 will decrease via the orifice 46, so that both valves 34 and 48 are returned to their closed positions under the influence of the forces of the springs 36 and 50th and the common pressure in the sensor lines 64 and 66. Liquid will still reach the lower side 16 via the orifice 46. The pressure upstream of the sequence valve 34 will drop to an amount which is no longer sufficient to hold or adjust the valves 34 and 48 in their open positions.
  • control valve To raise the load 22, the control valve is moved upward into a position in which liquid under pressure is passed from the pump 24 through the line 32 and the bypass line 56 to the stroke side 18 of the cylinder 12. The liquid located on the lower side 16 in the cylinder 12 will then reach the collecting container 26 through the bypass line 38, the check valve 40 and the line 30.
  • the operation of the system according to FIG. 2 corresponds essentially to the function described above.
  • the load 22 is raised when the stroke side 18 of the cylinder 12 is filled with liquid. Accordingly, the load 22 is lowered when the lower side 16 is connected to the pump 24.
  • valves 34 and 48 shift to their closed positions and load 22 to their respective positions is held.
  • the valve 34 would not be directly attached to the cylinder 12, and a breakage would occur in the line 30 behind the valve 34 when the lower side 16 of the cylinder according to FIG. 1 was loaded with liquid, the load 22 would only increase Move down in a controlled manner as long as valve 48 does not close. The same would apply under the aforementioned conditions if a break in the line 32 in front of the valve 48 would occur.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Vehicle Body Suspensions (AREA)
  • Control Of Eletrric Generators (AREA)
  • Selective Calling Equipment (AREA)
  • Component Parts Of Construction Machinery (AREA)

Claims (6)

1. Circuit hydraulique pour un moteur réalisé sous la forme d'un cylindre ou vérin à double effet (12) comportant un piston (14) subdivisant le cylindre en un côté d'élévation (18) et un côté d'abaissement (16) pour élever et abaisser une charge (22), comportant une pompe (24) pour du liquide sous pression, une valve de commande (28) et deux conduits (30, 32) qui relient la valve de commande au moteur (12), servent de conduit d'amenée ou de retour selon la position de la valve de commande et comportent chacun une valve pilotée hydrauliquement (34 et 48), ces deux valves pouvant être pilotées par la pression régnant dans le conduit (30) correspondant au côté d'abaissement (16) entre la valve de commande (28) et la valve (34) contre l'action d'un ressort (36, 50) caractérisé en ce que, lorsque la charge s'abaisse, la valve (34) correspondant au côté d'abaissement (16) du cylindre hydraulique (12) s'ouvre un certain temps après la valve (48) correspondant au côté d'élévation (18).
2. Circuit hydraulique selon la revendication 1, caractérisé en ce que la valve de commande (28) est réalisée sous la forme d'une valve à dosage de l'admission et ouvre l'orifice de retour avant l'ouverture d'admission.
3. Circuit hydraulique selon la revendication 1 ou 2, une seconde pression de liquide commune, pouvant s'opposer à la pression pivotant les valves (34, 48), pression qui est toujours présente et est prélevée sur le circuit hydraulique, caractérisé en ce que la seconde pression de liquide commune dérive de l'autre conduit (32) entre la valve de commande (28) et la valve (48) appartenant à l'autre conduit (32).
4. Circuit hydraulique selon une ou plusieurs des revendications précédentes, caractérisé en ce qu'un conduit d'anticavitation (60) est raccordé au conduit (32) correspondant entre la valve de commande (28) et la valve (48) s'ouvrant en premier, ce conduit étant raccordé au côté d'abaissement (16) du cylindre (12) dans lequel débouche l'autre conduit (30) et comportant un clapet de retenue (62).
5. Circuit hydraulique selon une ou plusieurs des revendications précédentes, caractérisé en ce qu'un conduit d'étranglement en dérivation (44) comportant un étranglement (46) court-cir- cuite la valve (34) qui est prévue dans le conduit (30) à partir duquel la pression pilotant les valves (34, 48) est dérivée.
6. Circuit hydraulique selon la revendication 4, caractérisé en ce qu'il est prévu, entre le point de raccordement du conduit d'anticavitation (60) au conduit (32) comportant la valve (48) s'ouvrant en premier et la valve de commande (28), un clapet de retenue (54) permettant l'écoulement du liquide vers la valve de commande (28) dans le conduit (32) précité.
EP84112058A 1983-10-26 1984-10-09 Circuit hydraulique pour un moteur entraînant une charge Expired EP0141301B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84112058T ATE28233T1 (de) 1983-10-26 1984-10-09 Hydraulischer kreislauf fuer einen eine last bewegenden motor.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US545567 1983-10-26
US06/545,567 US4610193A (en) 1983-10-26 1983-10-26 Load control system

Publications (2)

Publication Number Publication Date
EP0141301A1 EP0141301A1 (fr) 1985-05-15
EP0141301B1 true EP0141301B1 (fr) 1987-07-08

Family

ID=24176741

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84112058A Expired EP0141301B1 (fr) 1983-10-26 1984-10-09 Circuit hydraulique pour un moteur entraînant une charge

Country Status (12)

Country Link
US (1) US4610193A (fr)
EP (1) EP0141301B1 (fr)
JP (1) JPS6098203A (fr)
AT (1) ATE28233T1 (fr)
AU (1) AU565152B2 (fr)
BR (1) BR8405420A (fr)
CA (1) CA1227725A (fr)
DE (1) DE3464646D1 (fr)
DK (1) DK512884A (fr)
ES (1) ES8601411A1 (fr)
IE (1) IE55694B1 (fr)
ZA (1) ZA848299B (fr)

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JPS622805U (fr) * 1985-06-20 1987-01-09
US5046309A (en) * 1990-01-22 1991-09-10 Shin Caterpillar Mitsubishi Ltd. Energy regenerative circuit in a hydraulic apparatus
DE4107776A1 (de) * 1991-03-11 1992-09-17 Heilmeier & Weinlein Hydraulische steuervorrichtung
US5220862A (en) * 1992-05-15 1993-06-22 Caterpillar Inc. Fluid regeneration circuit
ATE150536T1 (de) * 1993-02-02 1997-04-15 Putzmeister Maschf Verfahren zum fördern von vorzerkleinerten metallschrott oder dergleichen festkörper enthaltenden dickstoffen
JP2992434B2 (ja) * 1993-12-02 1999-12-20 日立建機株式会社 建設機械の油圧制御装置
US5579676A (en) * 1995-07-13 1996-12-03 Husco International, Inc. Hydraulic valve to maintain control in fluid-loss condition
DE10006908A1 (de) * 2000-02-16 2001-08-23 Caterpillar Sarl Genf Geneva Hydraulische Kolbenzylindereinheit für landwirtschaftliche Arbeitsmaschinen
KR100430398B1 (ko) * 2000-12-26 2004-05-04 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 건설기계용 낙하방지장치
US6701822B2 (en) 2001-10-12 2004-03-09 Caterpillar Inc Independent and regenerative mode fluid control system
US6715403B2 (en) 2001-10-12 2004-04-06 Caterpillar Inc Independent and regenerative mode fluid control system
AT412810B (de) * 2003-05-28 2005-07-25 Hoerbiger Automatisierungstech Bremsventil, insbesonders für hydraulische betätigungsanordnungen für bewegbare teile an fahrzeugen
DE102005043367B4 (de) * 2005-09-12 2016-09-08 Laeis Gmbh Steuervorrichtung und Steuerverfahren für eine Kolben-Zylinder-Anordnung
SE531754C2 (sv) * 2007-05-11 2009-07-28 Nordhydraulic Ab Hydraulisk lastkontrollventilanordning
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Also Published As

Publication number Publication date
AU565152B2 (en) 1987-09-03
DK512884A (da) 1985-04-27
JPS6098203A (ja) 1985-06-01
EP0141301A1 (fr) 1985-05-15
IE842750L (en) 1985-04-26
US4610193A (en) 1986-09-09
ES537050A0 (es) 1985-10-16
ZA848299B (en) 1986-06-25
DK512884D0 (da) 1984-10-26
DE3464646D1 (en) 1987-08-13
IE55694B1 (en) 1990-12-19
AU3191184A (en) 1985-05-02
ES8601411A1 (es) 1985-10-16
BR8405420A (pt) 1985-09-03
CA1227725A (fr) 1987-10-06
ATE28233T1 (de) 1987-07-15

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