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EP2674626B1 - Circuit hydraulique - Google Patents

Circuit hydraulique Download PDF

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Publication number
EP2674626B1
EP2674626B1 EP12171621.1A EP12171621A EP2674626B1 EP 2674626 B1 EP2674626 B1 EP 2674626B1 EP 12171621 A EP12171621 A EP 12171621A EP 2674626 B1 EP2674626 B1 EP 2674626B1
Authority
EP
European Patent Office
Prior art keywords
pressure
chamber
pump
hydraulic control
line
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.)
Not-in-force
Application number
EP12171621.1A
Other languages
German (de)
English (en)
Other versions
EP2674626A1 (fr
Inventor
Georg Neumair
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
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Filing date
Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP12171621.1A priority Critical patent/EP2674626B1/fr
Publication of EP2674626A1 publication Critical patent/EP2674626A1/fr
Application granted granted Critical
Publication of EP2674626B1 publication Critical patent/EP2674626B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating 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
    • F15B2211/40—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
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow 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
    • F15B2211/505—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

Definitions

  • the invention relates to a hydraulic circuit specified in the preamble of claim 1. Art.
  • an internal combustion engine (favorable for its independence from supply in a portable device) or an AC motor (convenient supply from the AC mains, and light weight in a portable device) often has problems starting up against rapidly building up pressure.
  • EP 2 241 763 A2 CN 102 042 274 A and EP 1 832 686 A1 ,
  • the invention has the object of providing a hydraulic circuit with pressure switch in such a way that it is ensured that the pressure switch only independent of external influences in the blocking position switches when the drive of the pump has started properly, or has come to a sufficient speed or easily generates sufficient torque.
  • the at the locking side of the 2/2-way seat valve associated with the closing member chamber is filled when starting the drive only from the control line with low volume flow flowing control hydraulic medium before the pressure switch can switch to the blocking position, even if at the pressure switches Function diaphragm generated pressure difference, eg due to cold hydraulic fluid, would be sufficient to switch the pressure switch in the locked position.
  • a fixed or selectable period of time as a time buffer for the proper starting of the drive will thus elapse until sufficient speed is reached with the hydraulic circuit. In this way, the reliability of the hydraulic circuit or a device equipped with it without increasing the safety function of the pressure switch is increased.
  • the chamber has a pressure-dependent variable volume for filling with the hydraulic medium.
  • the variability of the volume ensures that a sufficient portion of the energy of the pressure from the control line is consumed in filling the chamber to achieve the desired period of time.
  • the chamber contains a pressurizable by the hydraulic medium boundary wall which is displaceable in the chamber under pressure of the hydraulic medium against a resilient force storage, preferably up to a maximum filling volume defining boundary position of the boundary wall.
  • the yielding force accumulator not only consumes pressure energy in the hydraulic medium to produce a sufficiently long delay period, but returns in pressure-free state of the hydraulic circuit, the boundary wall back to the starting position, so that the usable volume for filling at each startup is filled again energieaufzehrend.
  • the boundary wall is expediently formed by a sealed against the bias of a spring displaceable piston, which is preferably relieved of pressure on its side facing away from the pressure.
  • the piston When the chamber is filled, the piston first absorbs pressure energy from the hydraulic medium entering the chamber, thanks to its resistance to movement and the force of the spring, to ensure that the pressure switch does not come too early into the blocking position. Furthermore, the piston is a simple structural means to set the desired time span by hydraulic means at each start-up process substantially similar.
  • a diaphragm in the control line, which can set the period of time precisely reproducible in cooperation with the piston and the energy storage, within which the pressure switch can not switch to the blocking position.
  • the 2/2-way poppet valve which is leak-tight in the locked position, and includes a closing member and a stationary valve seat, wherein the closing member on an opening side of the pressure switch from a tapped from the supply line control pressure and a spring and the locking side of Pressure is applied in the control line, it is important that the force of the spring on the opening side is greater than the force of the spring of the energy accumulator of the chamber, so that the pressure switch in the pressureless state of the hydraulic circuit reliably switches to the passage position and fulfills its Ablassfunktion.
  • the chamber is integrated into the pressure switch forming 2/2-way seat valve. This measure also saves installation space.
  • closure member and the piston are arranged coaxially in a common pressure switch housing, preferably on opposite sides of an axially continuous threaded insert, which forms a stationary boundary wall of the directly connected to the control line chamber.
  • the housing is expedient part of an internal flow channels containing valve block, preferably made of steel, which contains adjacent to the pressure switch the function panel.
  • valve block preferably made of steel, which contains adjacent to the pressure switch the function panel.
  • all the functional components of the hydraulic circuit are combined in the smallest space in the valve block, i. with short connecting flow channels and low flow losses.
  • the piston In terms of assembly technology, it is expedient for the piston to be arranged with the spring of the energy accumulator in a screw plug which is externally bored out into a mounting bore, preferably in the valve block, for the pressure switch. In this way, no additional space for the chamber is needed because the screw is required anyway for mounting the pressure switch in the mounting hole, and then additionally receives the piston and / or even the chamber.
  • a further supply line of at least one further pump is connected to the supply line downstream of the pressure-sensitive function shutter and upstream of the pressure switch via a branch line. From the further supply line leads a drain line to the return.
  • the discharge line contains a spring-loaded, pressure-controlled in the opening direction drain valve.
  • a blocking in the direction of the drain line check valve is arranged.
  • a control line preferably with an aperture disposed therein, leads to the drain valve.
  • the hydraulic circuit is structurally simple expanded for a dual-circuit function to summarily feed streams of several pumps at least until setting a predetermined pressure levels in the supply line, and after exceeding this pressure level nurrang the flow rate of a pump, suitably with higher delivery pressure and lower flow rate, feed, for example, first to adjust a tool in rapid traverse, before working with high working pressure.
  • a common drive may be provided for the pumps, or separate drives are provided.
  • the further pump is designed so that it generates a lower delivery pressure than the delivery pressure of a pump, and delivers a larger flow than the flow rate of a pump.
  • very high working pressures can build up to 800 bar from the pump with the higher discharge pressure after using the other pump with the larger flow rate, the predetermined pressure level has been reached.
  • the drain valve, the diaphragm and the check valve also this extended embodiment of the hydraulic circuit also housed in the valve block containing the pressure switch with its components.
  • the valve block is internally mounted in a pump chamber of a dual-circuit motor pump unit, arranged in the at least one high-pressure pump element with low flow rate and high delivery pressure and at least one low-pressure pump element with high flow rate and low discharge pressure and via the supply lines to terminals of the Valve block are connected. Since the valve block is housed in the interior of the motor pump unit, space is saved on the outside of the motor pump unit, since in the pump chamber usually a space is available, which uses the valve block.
  • Such two-circuit motor pump units are used, for example, in portable tools such as torque wrenches, scissors or lifting devices, in which savings in space and weight are an important factor, and improve the performance characteristics of the device.
  • the hydraulic circuit is particularly useful when the pumps can be driven by a common AC motor or separate AC motors, because AC motors can start only with difficulty against pressure.
  • the chamber optionally with the action of the associated aperture in the control line to a start-fill period of about 500 ms to about one second designed. This period is sufficient even under unfavorable conditions (cold hydraulic medium, cold drive, adverse weather conditions and the like.) To ensure the drive trouble-free start.
  • a hydraulic circuit H in FIG Fig. 1 For example, the delivery rate of a pump 4 conveying with a delivery pressure P1 is fed into a supply line 18 to a supply port 19 when a drive 6 of the pump 4 is switched on.
  • the drive 6 may be, for example, an electric motor or an internal combustion engine. As an electric motor, an AC motor can be used, which receives electrical power from the normal power grid.
  • the hydraulic circuit H is designed so that the drive 6 is facilitated by using a pressure switch 22, the start in which the flow is first low loss to a return R is discharged until the drive has come to sufficient speed or sufficient torque. When the drive 6 is switched off, the system pressure from the supply line 18 via the pressure switch 22 in the return R is relieved.
  • the hydraulic circuit H in Fig. 1 can be incorporated into a valve block 1, although alternatively also a block structure of the hydraulic components or a connection of the hydraulic components via connecting lines are possible.
  • a pressure switch function panel 8 is arranged in the supply line 7.
  • the pressure switch 22 is arranged, which is designed as a 2/2-way valve seat with a relative to a seat adjustable closing member 28.
  • the closing member 28 is acted upon by a control spring 25 and with a control pressure from a control line 24, which here from the drain line 21, e.g. between the node 20 and the pressure switch 22, branches off.
  • a control line 27 which leads to a blocking side 26 of the 2/2-way seat valve and the closing member 28 is able to act with control pressure in the direction of the blocking position of the pressure switch 22.
  • an aperture 27 ' can be arranged in the control line 27 if the control line 27 should not produce a sufficient throttle effect on account of its relatively small cross-section anyway.
  • the locking side 26 and the closing member 28 is associated with a chamber 29, which provides a predetermined or adjustable, fillable with hydraulic fluid volume.
  • a chamber 29 which provides a predetermined or adjustable, fillable with hydraulic fluid volume.
  • the energy accumulator 31 is, for example, a spring, while the boundary wall 30 can be formed by a piston 30 'which can be displaced in a sealed manner.
  • the chamber 29 could alternatively be designed in the manner of a pressure accumulator with a variable receiving volume. The chamber 29 is relieved of pressure on the side of the energy accumulator 31, for example, to the return R.
  • the purpose of the chamber 29 is to ensure in the start-up phase of the drive 6 a fixed or selectable period of time, which initially elapses before the pressure switch 22 switches to its blocking position to facilitate the drive 6, the start-up phase.
  • This time span elapses in that the chamber 29 from the control line first has to be filled with control hydraulic medium before the pressure on the blocking side 26 rises to such an extent that the pressure switch 22 switches into the blocking position.
  • the pump 4 After switching on the drive 6, the pump 4 performs hydraulic medium via the supply line 7 in the hydraulic circuit H. Thanks to the spring 25, the pressure switch 22 is initially in the passage position shown to the return R. The boundary wall 30 of the chamber 29 is placed by the energy storage 31 so that the volume of the chamber 29 is a minimum. The flow rate of the pump 4 flows with low loss through the pressure switch 22 to the return R. About the pressure switch function panel 8, a pressure difference builds up, with the ratio of the force of the spring 25 plus the pressure in the control line 24 to the higher pressure in the control line 27th the pressure switch 22 initially still remains in the passage position shown.
  • the force of the spring 25 is greater than the force of the force accumulator 31, so that first the chamber 29 is completely filled before the then increasing pressure on the locking side 26, the closing member 28 is in the blocking position. From this time, the flow of the pump 4 is brought via the supply line 18 to the supply port 19 (pressure level P).
  • the force of the energy accumulator 31 only needs to be so great that after removal of the working pressure in the supply line 18 via the pressure switch 22, the boundary wall 30 is moved back into the starting position.
  • hydraulic circuit H is often used in high-pressure hydraulics, when two different flow rates with different delivery pressures, here P1 and P3, are summarized summed until reaching a first pressure level, and from exceeding the predetermined pressure levels only one of the flow rates, namely the higher delivery pressure to feed is.
  • An application of such hydraulic circuits are, for example, portable hydraulically operated tools or devices that run as quickly as possible after a start-up a kind of rapid traverse, and then work at high pressure.
  • the hydraulic circuit H in Fig. 2 is for example with a motor pump unit 2 combined, which contains at least two pumps 4, 5 in a pump chamber 3, which are driven either by a common drive 6 or by separate drives 6 and 6 ', usually eg an electric motor or an internal combustion engine.
  • an electric motor an AC motor can be used.
  • the hydraulic circuit H can also be useful for other applications.
  • the hydraulic circuit H is incorporated in the motor pump unit 2 inside to save space outside the motor pump unit 2 and to ensure short flow paths with few flow losses.
  • the hydraulic circuit H is designed so that it facilitates the start-up phase of the respective drive by the combined flow rates of the pumps 4, 5 are first discharged to the return R loss, until the drive sufficient has come to speed.
  • the hydraulic circuit H in Fig. 2 is contained in a valve block 1, which contains all hydraulic components in the embodiment shown.
  • a construction is conceivable in which the individual hydraulic components are arranged for example in a block structure and / or with connecting lines.
  • the hydraulic medium is fed into the supply line 7 and a corresponding flow channel in the valve block 1, wherein in the supply line 7, the pressure switch function panel 8 is arranged.
  • the flow rate of the pump 5 (delivery pressure P3) is fed via a separate further supply line 9 and a corresponding flow channel in the valve block 1.
  • From the supply line 9 branches off a discharge line 10 to the return line R, in which a discharge valve 11 is arranged, which is loaded in the closing direction by a spring 12, and is acted upon in the opening direction from a control line 13 via a diaphragm 14.
  • the supply line 9 is connected to the supply line 7 via a branch line 15 at a node 17.
  • a check valve 16 is arranged, which blocks in the direction of the drain line 10.
  • a supply line 18 extends, for example, to the supply terminal 19, e.g. on the housing of the motor pump unit. 2
  • the further discharge line 21 branches off to the return R.
  • the pressure switch 22 is arranged, which is designed as a 2/2-way seat valve with the adjustable relative to a seat closing member 28.
  • the closing member 28 of the spring 25 and with Control pressure from the control line 24 is applied, which branches off from the further discharge line 21, for example between the node 20 and the pressure switch 22.
  • Upstream of the function panel 8 branches off from the supply line 7 from the control line 27, which leads to the blocking side 26 of the pressure switch 22 and the closing member 28 is able to act with control pressure in the reverse direction.
  • the aperture 27 ' can optionally be arranged.
  • the control line 27 leads not only to the blocking side 26 of the pressure switch 22, but also to the closing member 28 on the locking side 26 associated chamber 29, which provides a predetermined or adjustable, fillable with hydraulic fluid volume.
  • the boundary wall 30 against the force of the energy accumulator 31, for example from the position shown in which the volume is a minimum, against the force of the energy accumulator 31 under pressure applied to increase the volume and optionally when filling to produce a negligible backpressure.
  • the energy accumulator 31 is, for example, a spring, while the boundary wall 30 can be formed by the piston 30 'which can be displaced in a sealed manner.
  • the chamber 29 could alternatively be designed in the manner of a pressure accumulator with a variable receiving volume.
  • the chamber 29 is relieved of pressure on the side of the energy accumulator 31, for example, to the return R.
  • the energy accumulator 31 only needs to be so strong that the chamber 29 again offers its minimum volume after the working pressure has been reduced, or the hydraulic medium is expelled from the chamber 29.
  • the purpose of the chamber 29 is to ensure in the start-up phase a fixed or selectable period of time before the pressure switch 22 switches to its blocking position to the drive 6, 6 'to facilitate the start-up phase. This period is achieved in that the chamber 29 from the control line 27 must first be filled with hydraulic fluid before the pressure on the locking side 26 rises so much that the pressure switch 22 switches to the blocking position.
  • both pumps 4, 5 have a common drive motor 6, for example an AC motor
  • both pumps 4, 5, after switching on the drive 6, convey hydraulic medium via the supply lines 7, 9 into the hydraulic circuit H.
  • the drain valve 11 is initially in the shut-off position shown, while the pressure switch 22 is initially in the passage position shown by the return spring R thanks to the spring 25.
  • the boundary wall 30 of the chamber 29 is adjusted by the energy storage 31 so that the fillable volume is a minimum.
  • the force of the spring 25 is greater than the force of the energy accumulator 31.
  • the chamber 29 is filled before the then increased pressure on the locking side 26, the closing member 28 is in the blocking position. From this point on, the delivery flows of both pumps 4, 5 are brought via the supply line 18 to the supply port 19 until a predetermined pressure level P is reached there. About the aperture 14 and the control line 13, the drain valve 11 is then turned on. At the same time, the check valve 16 is in the blocking position. The flow of the pump 5 with the delivery pressure P3 is funded via the supply line 9 and the discharge line 10 through the drain valve 11 from now on loss return to R, while the supply line 18 only with the flow of the pump 4 (delivery pressure P1) is fed.
  • Fig. 3 to 6 is a non-limiting example of a concrete embodiment of the hydraulic circuit H of Fig. 2 explained with their hydraulic components.
  • Fig. 3 shows a side view of the valve block 1, which has an approximately trapezoidal outline in this view, for example, and consists for example of steel.
  • the outline shape in Fig. 2 is only a non-limiting example and has the purpose, for example, the hydraulic circuit H in the valve block 1 to save space, for example in the interior of a motor pump unit 2, as in Fig. 2 shown to be able to accommodate.
  • valve block 1 in Fig. 3 next to each other the pressure-sensitive function panel 8, the pressure switch 22, the drain valve 11 and the check valve 16 are housed, and interconnected, for example via internal flow channels accordingly.
  • the outside of the valve block 1 in Fig. 2 are provided holes 32 for mounting screws, and connections 33, 34, 35 for the pump 4, 5 and the supply port 19, as well as connections to the return R, which may be open holes in the embodiment shown.
  • the function panel 8 contains in Fig. 4 in a housing bore in the supply line 7, a diaphragm plate 43, to which the delivery pressure P1 of the pump 4 is brought from below.
  • Below the diaphragm disc 43 branches off the control line 27, in which the optional aperture 27 'is placed, and which leads to a further housing bore in which the pressure switch 22 and the chamber 29 are arranged.
  • the control line 27 opens here directly in the chamber 29, which is defined above a screw plug 39, in which the boundary wall 30 forming piston 30 'and the energy storage 31 (a compression spring) are housed.
  • the housing bore 38 (see also Fig. 4 ) is seated for mounting the pressure switch 22 provided threaded insert 41 which is continuous (bore 42) and defines a stop for the piston 30 '.
  • Fig. 5 is a sectional view in the section plane IV - IV in Fig. 2 and illustrates the internal structure of the pressure switch 22 and the chamber 29.
  • the closing member 28 is, for example, a valve cone with a sealing surface 37 which cooperates with a stationary seat 36 in the housing bore 38, and of the spring 25 down, ie in the opening direction of the seat 36th gone, is charged.
  • the further drain line 21 is recognizable as a bore, from which the control line 24 leads to the spring chamber above the closing member 28, and lead from the passages to a chamber below the seat 36. Another space above the seat 36 is in communication with the return R.
  • the piston 30 ' is sealed in the locking screw 39 against the force accumulator 31 forming spring 30 slidably.
  • the spring chamber is relieved of pressure, for example through a bore 40 to the return R.
  • Fig. 6 is a sectional view in the sectional plane V - V in Fig. 2 and shows the check valve 16, which is arranged between the node 17 and the stub 15, which leads in the valve block 1 to the drain valve 11.
  • Fig. 7 is a sectional view in the section plane VI - VI in Fig. 2 and shows the internal structure of the drain valve 11.
  • a slide 44 is sealingly displaceable in a bore in the valve block 1, which is acted upon at the lower end of the control line 13 and the diaphragm 14 with the pressure in the supply line 18, and is loaded from above by the spring 12.
  • the drain line 10 opens approximately in the middle, where in the position shown, the slider 44 are placed on this control edges 45, 46. If the slide 44 is moved upwards against the spring 12, then it establishes a connection of the drain line 10 with the return line R, which has a bore mouth at the top on one side of the valve block 1.
  • the hydraulic components of the hydraulic circuit H could also be combined in a block design, either with separate valve blocks placed directly next to one another, or valve blocks which are connected via lines or piping (not shown).
  • the motor pump unit 2 shown only schematically several high-pressure pump elements and a plurality of low-pressure pump elements, for example distributed around a drive shaft of the drive motor 6, may be mounted in the pump chamber 3, which define the pumps 4, 5.
  • the delivery flows of the pumps 4, 5 could be led out of the housing of the motor pump assembly 2 to the outside and fed there into the externally mounted hydraulic circuit H (not shown).
  • the period of time that facilitates the start-up phase for the respective drive 6, 6 'and is created by the filling of the chamber 29 can be selected as required by coordination between, for example, the optional diaphragm 27' and the loading surface of the boundary wall 30 and the force of the energy accumulator 31 , so that even under unfavorable circumstances (tough, very cold hydraulic medium), the pressure switch 22 switches only in the blocking position when the drive has already come to a sufficient speed or is able to generate sufficient torque. This is particularly useful when using an AC motor that starts against pressure only reluctant or then absorbs too much power and can be overloaded.
  • the diaphragm 14 serves for damping during the control of the drain valve 11, which can be designed for a response pressure (pressure level) between approximately 10 and 150 bar.
  • a response pressure pressure level
  • the aperture 27 '(as an option) and especially the chamber 29, for example, a period of 500 ms to 1.0 seconds for the start-up phase of Set drive that elapses in each case until the switching of the pressure switch 22 in the locked position.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (16)

  1. Circuit hydraulique (H) comprenant un aiguillage de pression (22) pour envoyer du fluide hydraulique refoulé par au moins une pompe (4) reliée à un moyen d'entraînement (6), dans une conduite d'alimentation (18), circuit
    dans lequel l'aiguillage de pression (22) est agencé entre la conduite d'alimentation (18) et un retour (R), et est soumis, sur des côtés d'obturation et d'ouverture (26, 23), à une commande pilote en pression en direction de la position de commutation respective, soit pour alimenter la conduite d'alimentation (18), soit pour décharger la conduite d'alimentation (18) vers le retour (R), et
    dans lequel l'aiguillage de pression (22) est une vanne à siège 2/2 voies avec un organe de fermeture (28) et un siège stationnaire (36), dans une conduite d'amenée (7) reliée à la pompe (4) est agencé un diaphragme fonctionnel d'aiguillage de pression (8), en amont du diaphragme fonctionnel d'aiguillage de pression (8) une conduite de commande (27) est dérivée vers le côté d'obturation (26) de l'aiguillage de pression (22), l'organe de fermeture (28) peut être sollicité, sur le côté d'ouverture (23), par une pression de commande prélevée de la conduite d'alimentation (18) et par un ressort de réglage (25), et sur le côté d'obturation (26), par la pression dans la conduite de commande (27), caractérisé en ce que sur le côté d'obturation (26), à l'organe de fermeture (28) est associée au moins une chambre (29), qui peut être remplie avec du fluide hydraulique à partir de la conduite de commande (27) pendant un intervalle de temps fixé ou pouvant être sélectionné.
  2. Circuit hydraulique selon la revendication 1, caractérisé en ce que la chambre (29) présente un volume pour le fluide hydraulique, qui est variable en fonction de la pression.
  3. Circuit hydraulique selon la revendication 1, caractérisé en ce que la chambre (29) comporte une paroi de délimitation (30), qui peut être sollicitée en pression par le fluide hydraulique, et peut être déplacée dans la chambre (29), sous pression, à l'encontre d'un accumulateur de force (31) souple, de préférence un piston (30') qui peut coulisser de manière étanche à l'encontre de la précontrainte d'un ressort en guise d'accumulateur de force (31), et qui est de préférence déchargé en pression sur son côté opposé à celui soumis à la pression.
  4. Circuit hydraulique selon la revendication 1, caractérisé en ce qu'à la chambre (29) est associé un diaphragme (27') dans la conduite de commande (27).
  5. Circuit hydraulique selon l'une au moins des revendications précédentes, caractérisé en ce que la force du ressort de réglage (25) sur le côté d'ouverture (23) est supérieure à la force de l'accumulateur de force (31) de la chambre (29).
  6. Circuit hydraulique selon la revendication 1, caractérisé en ce que la chambre (29) est intégrée à la vanne à siège 2/2 voies formant l'aiguillage de pression (22).
  7. Circuit hydraulique selon la revendication 1, caractérisé en ce que l'organe de fermeture (28), le siège de vanne (36) et le piston (30') sont agencés de manière coaxiale dans un carter commun délimitant également la chambre (29), de préférence sur des côtés opposés d'un insert à visser (41), axialement traversant, dans la chambre (29) raccordée directement à la conduite de commande (27).
  8. Circuit hydraulique selon la revendication 7, caractérisé en ce que le carter est une partie d'un bloc de vanne (1), de préférence en acier, renfermant des canaux d'écoulement intérieurs et contenant de manière adjacente à l'aiguillage de pression (22), le diaphragme fonctionnel (8).
  9. Circuit hydraulique selon la revendication 3, caractérisé en ce que le piston en tant que paroi de délimitation (30) avec le ressort de l'accumulateur de force (31) est agencé dans une vis de fermeture (39), ouverte du côté extérieur par perçage (40), et insérée dans un alésage de montage (38), de préférence dans le bloc de vanne (1), pour l'aiguillage de pression (22).
  10. Circuit hydraulique selon l'une au moins des revendications 1 à 9, caractérisé en ce qu'à la conduite d'alimentation (18), en aval du diaphragme fonctionnel d'aiguillage de pression (8) et en amont de l'aiguillage de pression (22), est raccordée, par l'intermédiaire d'une conduite de dérivation (15), au moins une conduite d'amenée (9) en provenance d'une autre pompe (5), en ce que de la conduite d'amenée (9) de ladite autre pompe (5), une conduite d'évacuation (10) mène au retour (R) et renferme une vanne d'évacuation (11) chargée par ressort et commandée en pression en direction de l'ouverture, en ce que dans la conduite de dérivation (15) est agencé un clapet anti-retour (16) obturant en direction de la conduite d'évacuation (16), et en ce qu'à partir de la conduite d'alimentation (18), une conduite de commande (13), de préférence avec un diaphragme (14), mène à la vanne d'évacuation (11).
  11. Circuit hydraulique selon la revendication 10, caractérisé en ce que pour les pompes (4, 5) sont prévus un entraînement commun (6) ou des entraînements séparés (6, 6').
  12. Circuit hydraulique selon la revendication 10, caractérisé en ce que ladite autre pompe (5) est configurée pour une pression de refoulement (P3) plus basse que la pression de refoulement (P1), et un débit volume plus grand que le débit volume de la pompe (4).
  13. Circuit hydraulique selon les revendications 8 et 10, caractérisé en ce que la vanne d'évacuation (11), le diaphragme (14) et le clapet anti-retour (16) sont agencés dans le bloc de vanne (1).
  14. Circuit hydraulique selon l'une au moins des revendications précédentes, caractérisé en ce que le bloc de vanne (1) est monté à l'intérieur dans une chambre de pompe (3) d'un groupe moteur-pompe (2) dans lequel sont agencés au moins un élément de pompe haute-pression (4) à faible débit et au moins un élément de pompe basse-pression (5) à débit élevé.
  15. Circuit hydraulique selon l'une au moins des revendications précédentes, caractérisé en ce que les pompes (4, 5) comportent en guise du ou des entraînements (6, 6'), un moteur à courant alternatif commun ou des moteurs à courant alternatif séparés.
  16. Circuit hydraulique selon la revendication 1, caractérisé en ce que la chambre (29), le cas échéant avec l'action du diaphragme (27') associé, est configurée pour un intervalle de temps de remplissage de démarrage d'environ 500 ms jusqu'à environ 1 seconde.
EP12171621.1A 2012-06-12 2012-06-12 Circuit hydraulique Not-in-force EP2674626B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12171621.1A EP2674626B1 (fr) 2012-06-12 2012-06-12 Circuit hydraulique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12171621.1A EP2674626B1 (fr) 2012-06-12 2012-06-12 Circuit hydraulique

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EP2674626A1 EP2674626A1 (fr) 2013-12-18
EP2674626B1 true EP2674626B1 (fr) 2015-09-30

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017200212B4 (de) 2017-01-09 2021-12-16 Hawe Hydraulik Se Zweistufenpumpe mit Umschaltventil

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1832686A1 (fr) * 2006-03-06 2007-09-12 Qinghua He Dispositif de verrouillage hydraulique.
ES2471920T3 (es) * 2009-04-17 2014-06-27 Hawe Hydraulik Se Dispositivo de control hidráulico y válvula compensadora de presión para ello
CN102042274B (zh) * 2010-08-19 2013-03-27 中联重科股份有限公司 液压控制回路和液压马达控制系统

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