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
  • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
  • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
  • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/20—Drives; Control devices
  • E02F9/22—Hydraulic or pneumatic drives
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/20—Drives; Control devices
  • E02F9/22—Hydraulic or pneumatic drives
  • E02F9/2221—Control of flow rate; Load sensing arrangements
  • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/20—Drives; Control devices
  • E02F9/22—Hydraulic or pneumatic drives
  • E02F9/2221—Control of flow rate; Load sensing arrangements
  • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
  • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
  • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
  • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
  • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
  • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
  • F15B13/0401—Valve members; Fluid interconnections therefor
  • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
  • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
  • F15B2211/205—Systems with pumps
  • F15B2211/20576—Systems with pumps with multiple pumps
• • 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
  • F15B2211/265—Control of multiple pressure sources
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/60—Circuit components or control therefor
  • F15B2211/605—Load sensing circuits

Definitions

• the invention relates to a hydraulic dual-circuit system for controlling consumers of a mobile device, in particular a tracked device according to the preamble of patent claim 1, and a Verschschaltventilan extract for such a dual-circuit system.
• No. 6,170,261 B1 discloses a hydraulic two-circuit system of a mobile device, for example a chain or tracked device.
• the chassis has two chains, which are each controlled separately via one of the hydraulic circuits.
• To the two hydraulic circuits of the chain unit are also still a slewing gear and units of equipment, such as the boom, the dipper and the spoon connected.
• Each of the two hydraulic circuits is fed by a variable displacement pump with pressure medium, which are controlled depending on the highest load pressure of the consumer in each associated circle.
• Interconnecting valve assembly is carried out with two pressure compensators, one of which is assigned to each of the circles and via which the connection to the other circuit can be opened in dependence on the load pressure and the pump pressure in the associated circuit.
• a disadvantage of this solution is that the Verschschaltventilan Aunt has a relatively complex structure.
• the present invention seeks to provide a hydraulic dual-circuit system and a suitable Verschoppelventilan extract with a simple structure.
• connection valve which is designed with at least four control surfaces, wherein two acting in one direction control surfaces of the highest load pressure in a first circle and the pump pressure in the second circle and acting in the other direction control surfaces of the highest Load pressure in this circuit and the pump pressure in the former circle are acted upon.
• two pressure ports and one LS circuit associated with the first circuit may then be connected to an LS output port associated with the second circuit for summing, thereby preventing a higher load pressure acting in one of the circuits from occurring at low pressure medium demand the other circuit is reported with lower load pressure and high pressure medium requirement.
• a valve body of the interconnection valve is biased via a centering spring arrangement into a blocking position.
• check valves are provided in the load pressure lines.
• an LS line of a circle is in each case connected to an LS line assigned to the other circle.
• control surfaces of the valve body acted upon by the pump pressure and the load pressure are of equal size.
• connection valve is particularly simple in construction, when the pump pressure and the load pressure of a circle each act on a spring chamber defining a rear end face and the pump pressure and the load pressure of the other circle on annular end faces of the valve body.
• a valve body of the Verschaltungsventils is preferably carried out with a central control collar on which two control edges are designed to control the connection between the two pressure ports.
• the valve body further has two outer LS control coils, on each of which a control edge for auf mortn the connection between the LS input terminal of the one circuit and the LS output terminal of the other circuit is formed.
• the spring-chamber-side rear surfaces of the two control collars form the above-mentioned rear end faces.
• Such a structure makes it possible to form the valve body symmetrical, so that the manufacture and assembly is particularly simple.
• connection valve is further simplified when the above-described check valves are integrated into the valve housing of the connection valve.
• Figure 1 is a circuit diagram of a control block for controlling a
• Figure 2 is a circuit symbol of a Verschschaltventilaniser a
• FIG. 3 shows a concrete embodiment of the interconnecting valve arrangement from FIG. 1.
• FIG. 1 shows a circuit diagram of a hydraulic excavator control 1. This is constructed as a two-circuit system with two hydraulic circuits 2, 4, which are each supplied via a variable displacement pump, not shown, with pressure medium.
• the excavator provided with the control shown in Figure 1 has a chassis with two chains whose traction drives are supplied via the two circuits 2, 4 independently with pressure medium.
• other consumers of the excavator such as a slewing gear, a stick, a spoon or a boom, are controlled via the two-circuit system.
• the control block which implements the excavator control according to FIG. 1 is designed as a disk, with the two variable-displacement pumps (not shown) connected to pressure connections P
• This also has a tank connection T and working connections A-
• the other consumers of the excavator such as the drive of the slewing gear, the hydraulic cylinder for actuating the stem, the spoon or the boom are connected. In the illustrated embodiment, it is assumed that are connected to the terminals A2, B2 of the boom and the port A4, B4 of the spoon.
• the illustrated control block also has two Load pressure connections, in the following LS-
• the control of the aforementioned consumer takes place in each case via a proportionally adjustable directional control valve 6, which in each case a pressure compensator 8 is connected downstream.
• the directional control valve 6 has a variable measuring orifice forming a speed part and a directional part, wherein the measuring orifice of the pressure compensator. 8 upstream and the directional part downstream of the pressure compensator 8 is arranged.
• Each pressure compensator 8 is beauf beat in the closing direction of the load pressure and in the opening direction of the pressure downstream of the orifice of the directional control valve 6 beiller.
• the pressure compensator piston adjusts itself in dependence on the applied control pressures in a control position in which the pressure drop across the orifice plate of the proportionally adjustable directional control valve 6 is kept contant, so that a load pressure independent flow control is possible.
• Such LS controls are well known, so that can be dispensed with a detailed description of the structure of the directional control valve 6 and the downstream pressure compensator 8.
• the control of the directional control valve 6 takes place in each case via pilot valves 10, 12, via which a control pressure is applied to the frontal control surfaces of a slide of the directional control valve 6. These pilot valves are actuated, for example, as a function of the actuating movement of a joystick.
• each directional valve has two working ports, which are each connected via a working line 18 and 20 with the associated load ports A, B.
• an output connection of the directional control valve 6 is connected via a tank line 22 to the tank connection T of the control block.
• each still pressure relief valves are provided, wherein the pressure at the working ports A2, B2, B- and B3 and A4 (not shown) limiting pressure relief valves are designed with Nachsaugfunktion, so that at Advance of the consumer (negative load) pressure medium from the tank can be sucked to avoid cavitation phenomena.
• a respective connected to the load pressure port LS of the two circuits 2, 4 load pressure signaling line 28, 30 is connected via an LS flow control valve 32 and 34 to the common tank line 22.
• the pressure compensators 8 are designed so that they report in their fully open end position at its input pressure (downstream pressure of the orifice plate) in the load pressure line 28 and 30, so that in this is always the highest load pressure in the respective circuit 2 or 4 ,
• the above-described directional valves with the associated pressure compensator 8, the pilot valves 10, 12 and the pressure relief valves 24, 25 may each be received in a disk or in a common control block.
• an interconnecting valve arrangement 38 is provided in an intermediate disc 36, via which the pressure lines 14, 16 of the two hydraulic circuits 2, 4 can be interconnected in certain operating states, so that the actuated consumers of both variable displacement pumps are connected together Pressure medium to be supplied.
• this has a connecting valve 40 constructed as a pressure compensator, whose pressure compensator valve, hereinafter called valve body 42, has four control surfaces A1, A2, A3, A4 is executed, wherein two acting in one direction control surfaces
• control surfaces A3, A4 are connected via a further pressure control line 48 to the pressure line 14 and another LS control line 50 to the load pressure signaling line 30 of the second circle.
• A1, A2, A4 and A3 are the same.
• the valve body 42 is biased via a Zentrierfederan Aunt 51 in a middle blocking position, in the two connected to the pressure lines 14, 16 pressure ports P1 and P2 and two the first circuit 2 associated ports LS1 and LS1 'and two the second circuit 4 associated ports LS2, LS2 'are shut off.
• the LS input port LS1 is connected via an LS channel 52 and via a check valve 54, which opens in the direction of the port LS1, to the load pressure signaling line 28 of the first circuit 2, to which the LS output port LS1 'is also connected via an LS branch channel 56 ,
• the load pressure signaling line 30 of the second circuit 4 is connected via a further LS channel 58 and a further check valve 60 to the LS input connection LS2 and via a further LS channel 62 to the LS output connection LS2 '.
• the valve body 42 of the interconnection valve 40 can be displaced upward (view according to FIG. 2) into one of the control positions marked b or downwards to one of the control positions identified by a.
• control positions a, b the summed from the circle with the higher pressure level to the other circle Pressure fluid flow rate throttled via the Zuschaltventil 40 to the lower pressure level.
• the control position is established when the pressure difference between the pump pressure and the load pressure in the first circuit is approximately equal to that in the second circuit.
• a pressure medium from the second circle 4 is summed to the pressure medium flow rate of the first circle 2, wherein the LS-LS1 and LS2 'are connected to each other, while the two other LS-LS2, LS1' are locked against each other.
• the check valve 54 prevents that at a lower load pressure in the first circuit 2, the higher load pressure of the second circuit 4 is reported in the first circle, so that in accordance with the first circle associated variable displacement pump is not raised in this case. In the case in which the higher load pressure in the first circuit 2 is applied, it is reported via the opening check valve 54 and the two connected LS connections LS1 and LS2 'to the variable displacement pump of the second circuit and this raised accordingly.
• the pressure ports P1 and P2 are connected to one another so that pressure medium from the first circuit is summed to the pressure medium volume flow of the second circuit and the LS ports LS2 and LS1 'are connected to one another, wherein the non-return valve 60 prevents a lower load pressure in the first circuit 2 (in the load pressure signaling line 28) is reported to the load pressure signaling line 30 of the second circuit 4.
• FIG 3 shows a concrete embodiment of a Verschschaltventilan extract 38 shown in FIG 2.
• Figure 3 shows a longitudinal section through the valve disc 36 or through a
• valve bore 64 is formed, in the pressure compensator valve or valve body 42 is guided axially displaceable.
• the valve bore 64 is extended in its central region to two pressure chambers 66, 68, which are separated from one another by a housing web 70.
• the pressure chamber 66 is connected to the pressure port P1 and the pressure chamber 68 to the pressure port P2.
• the valve bore is widened in the radial direction in each case to LS annular spaces 70, 72 and 74, 76, wherein the outer annular spaces 70, 76 are connected to the load pressure signaling channel 30 and thus the highest load pressure of the second circle 4 is applied in these spaces.
• the two inner annular spaces 72, 74 are acted upon in accordance with the load pressure signaling line 28 and thus with the highest load pressure of the first circuit 2.
• the load pressure signaling lines 28, leading to the annulus 72 LS channel 52 and arranged therein check valve 54 and the annular space 74 leading LS branch channel 56 are shown.
• the connection of the other two annular spaces 70, 76 to the load pressure signaling line 30 via corresponding channels with integrated check valve 60 (not shown in Fig. 3).
• the valve body 42 has a middle one
• Control edges 80, 82 are formed. With axial displacement of the
• Valve body 42 via one of the control edges 80, 82 the
• the valve body 42 has on both sides two collars 84, 86 which are each connected via a radially recessed piston neck to an external control collar 88 or 90.
• Each control collar 88, 90 is in one Reduction sleeve 92 and 94 out, respectively, which are inserted into an end-side, step-shaped enlarged end portion of the valve bore 64 and thus reduce the effective guide diameter for the valve body 42 and create a surface difference.
• an annular end face is provided in each case, which form the control surfaces A2 and A3.
• the control surface A3 limited with the adjacent end face of the Reduzierbuchse 92 a space 96 in which the pressure of the pressure line 14 and thus at the pressure port P1 is applied.
• the annular end face A2 of the collar 86 delimits with the adjacent end face of the reducing bushing 94 a further space 98, in which, correspondingly, the pressure in the pressure line 16 and thus the pressure at the pressure port P2 are present.
• the two outer control collars 88, 90 are each slightly downgraded by a piston neck 100, 102 in the middle, so that in each case a control edge 104, 106 is formed.
• the two end surfaces of the valve body 42 form the control surfaces A1 and A1 (see Figure 2), which are acted upon by the pressure in the pressure line 16 of the second circle or with the highest load pressure of the second circle.
• end surfaces A1, A4 and the annular end faces A2, A3 are each designed with the same area.
• the valve body 42 is biased by the Zentrierfederan kann 51 in its illustrated mid-position.
• This Zentrierfederan effet 51 also acts as a control spring arrangement, and is the concrete Embodiment with two control springs 108, 110 executed, the spring constant is designed so that it is slightly below the pump Ap.
• the spring force of a control spring 108, 110 corresponds approximately to a pressure of delta-p difference: 3 to 6 bar (determined from experiment).
• the two control springs 108, 110 are each supported on a spring bushing 112, 114 screwed into the valve bore 64 and each engage via a spring plate 116, 118 on the end faces A1, A4 of the valve body 42.
• the the control springs 108, 110 assigning, radially enlarged Ringstim lake the Reduzierbuchsen 92, 94 serve as an end stop for the spring plates 1 16, 118. Through these two end stops and the illustrated center position of the valve body 42 is determined.
• the energy saving for this case is calculated as follows:
• the solution according to the invention is characterized by an extremely compact design, which can be realized with little device complexity.
• the interposing valve arrangement has a connection valve with two pressure connections, two LS input and two LS output connections, wherein a valve body of the interposing valve is designed with four control surfaces, of which two unidirectional control surfaces have the highest load pressure in the first circuit and the pump pressure in the first second circuit and acting in the other direction control surfaces of the highest load pressure in the second circuit and the pump pressure in the first circuit are acted upon.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Mechanical Engineering (AREA)
• Mining & Mineral Resources (AREA)
• Civil Engineering (AREA)
• Structural Engineering (AREA)
• Fluid-Pressure Circuits (AREA)
• Operation Control Of Excavators (AREA)

Applications Claiming Priority (2)

Publications (2)

Family

ID=38791990

Family Applications (1)

Country Status (8)

Families Citing this family (10)

Family Cites Families (9)

• 2006
  • 2006-11-15 DE DE102006053897A patent/DE102006053897A1/de not_active Withdrawn
• 2007
  • 2007-09-13 EP EP07802290A patent/EP2092200B1/fr not_active Not-in-force
  • 2007-09-13 JP JP2009536612A patent/JP5156754B2/ja not_active Expired - Fee Related
  • 2007-09-13 KR KR1020097009848A patent/KR101432564B1/ko not_active Expired - Fee Related
  • 2007-09-13 CN CN200780042638XA patent/CN101542133B/zh not_active Expired - Fee Related
  • 2007-09-13 WO PCT/EP2007/007962 patent/WO2008058584A1/fr not_active Ceased
  • 2007-09-13 US US12/513,961 patent/US8347617B2/en not_active Expired - Fee Related
  • 2007-09-13 AT AT07802290T patent/ATE532968T1/de active

Non-Patent Citations (1)

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