KR20100120620A - Hydrostatic drive system and method for operating of a hydrostatic drive system - Google Patents

Hydrostatic drive system and method for operating of a hydrostatic drive system Download PDF

Info

Publication number
KR20100120620A
KR20100120620A KR1020100041840A KR20100041840A KR20100120620A KR 20100120620 A KR20100120620 A KR 20100120620A KR 1020100041840 A KR1020100041840 A KR 1020100041840A KR 20100041840 A KR20100041840 A KR 20100041840A KR 20100120620 A KR20100120620 A KR 20100120620A
Authority
KR
South Korea
Prior art keywords
pressure
pump
sensor
drive system
delivery
Prior art date
Application number
KR1020100041840A
Other languages
Korean (ko)
Other versions
KR101639981B1 (en
Inventor
볼프강 크래프트
Original Assignee
린데 머티어리얼 핸들링 게엠베하
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 린데 머티어리얼 핸들링 게엠베하 filed Critical 린데 머티어리얼 핸들링 게엠베하
Publication of KR20100120620A publication Critical patent/KR20100120620A/en
Application granted granted Critical
Publication of KR101639981B1 publication Critical patent/KR101639981B1/en

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • 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
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle

Abstract

PURPOSE: A hydrostatic drive system and a method for operating of a hydrostatic drive system are provided to the gating accuracy of a sensor by making a sensor signal in relation to the transmission rate standard. CONSTITUTION: A hydrostatic drive system comprises a load - sensing control pump and at least one power consumption apparatuses. The load-sensing control pump controls transmission volume. An electrical pressure difference controlling unit controls the transmission volume of the pump and includes a sensor and an electronic control unit(7). The electronic control unit establishes a pump.

Description

HYDROSTATIC DRIVE SYSTEM AND METHOD FOR OPERATING OF A HYDROSTATIC DRIVE SYSTEM}

The invention comprises a load-sensing control pump capable of regulating delivery volume and at least one power consuming device, said power consuming device being controllable by a control valve, in particular a directional control valve. A hydrostatic drive system for a mobile working machine, in which case an electric pressure differential regulator is provided for adjusting the delivery volume of the pump, the electric pressure differential regulator providing a load pressure, in particular of the power consuming device. And a sensor device and an electronic control device for detecting a pressure difference formed due to the maximum load pressure of the plurality of power consuming devices and the delivery pressure of the pump, wherein the electronic control device is adapted to match the pressure difference to a preset adjustment pressure difference. Set up the pump.

In addition, the present invention provides a fluid pump for a mobile work machine having a load-sensing control pump capable of adjusting the delivery volume and at least one power consuming device, said power consuming device being controlled by a control valve, in particular a directional valve. A method for operating a mechanical drive system, in which case the delivery volume of the pump is regulated by an electric pressure differential regulator, in which case the load pressure of the power consuming device, in particular the maximum load pressure of a plurality of power consuming devices. And a sensor device is used to detect the pressure difference formed due to the delivery pressure of the pump, wherein the sensor device controls the delivery volume of the pump such that the pressure difference determined by it corresponds to a preset adjustment pressure difference. Functionally connected with a rotary device, in particular a rotary pressure regulator, A pre-rotating device is assigned to the delivery line of the pump and is contacted by the spring and in the locking position direction by the maximum load pressure of the power consuming devices and by the delivery pressure of the pump.

Such load-sensing control drive systems are inserted into mobile work machines, for example, as excavators, construction machines, forest machines, agricultural machines, forklifts or utility trucks (for road cleaning, etc.).

In this type of load-sensing-drive systems, the delivery volume of the pump is controlled by the maximum load pressure and the regulating pressure differential of the driven power consuming devices. One particular opening cross section is set in each of the control valves when driving one or more control valves. The pump is adjusted by the set maximum load pressure of the driven power consuming devices in the increasing direction of the delivery volume until the discharge pressure of the pump is larger by a control pressure difference than the maximum load pressure of the driven power consuming devices. For this reason, by the corresponding opening cross-sections of the control valves, the very same volumetric flow required by the driven power consuming devices can be supplied from the pump.

In order to shut off the hydraulic load-sensing-line to the delivery volume control device of the pump, it is already known to drive the pump by electricity, in which case the delivery volume control device of the pump is driven by an electronic control device, The electronic control device uses corresponding pressure sensors to detect the pressure difference formed due to the maximum load pressure of the power consuming devices and the delivery pressure of the pump or the maximum load pressure of the power consuming devices and the delivery pressure of the pump. Electrohydraulic load-sensing-drive systems of this type are known from US Pat. No. 5,638,677. In the case of the drive system known from US Pat. No. 5,638,677 there is provided a sensor device formed as a pressure differential sensor, the sensor device detecting the pressure difference formed due to the maximum load pressure of the power consuming devices and the delivery pressure of the pump and Connected to the electronic control unit. The pump is adjusted in the direction of increasing the discharge amount until the pressure difference measured by the pressure difference sensor in the driven power consuming devices coincides with the adjustment pressure difference stored in the electronic control device.

The nature and quality of such electrohydraulic load-sensing-adjustment of the pump in relation to the pump's delivery flow regulation is usually dependent on the measured values of the sensor device. Over time of operation and over time, the sensor device becomes inaccurate when detecting measured values due to the aging process due to temperature and pressure effects. This may change the settings of the machine, thereby impairing the drive system and the functioning of the working machine. In order to prevent this result, it is necessary to standardize or calibrate the sensor device at specific service intervals and with it. In order to calibrate or replace the sensor device with one new and suitable sensor device, it is known to detach the sensor device from the working machine and disassemble it with it.

However, calibrating or replacing the sensor device in this manner leads to downtime of the working machine and furthermore high maintenance costs.

The problem underlying the present invention is to provide a hydrostatic drive system and a method for operating a hydrostatic drive system of the kind mentioned in the introduction with low maintenance costs.

According to the present invention, the above object in the drive system is achieved by the standardization of the sensor device can be carried out by the electronic control device without disassembly of the sensor device. Thus, the concept according to the invention is that in the case of the built-in sensor device, the reference and verification of the sensor device for electrohydraulic load-sensing-control of the pump is carried out by the electronic control device. Therefore, the maintenance cost can be reduced by omitting the disassembly of the corresponding sensor device, which may be required for the calibration of the sensor device, and the downtime of the machine caused by the calibration of the sensor device can be avoided. In addition, the reference according to the invention of the sensor device can be carried out in a simple manner for a defined operating period of the drive system, whereby the high quality and characteristics of the volumetric flow control of the pump can be ensured for the entire lifetime.

According to one embodiment of the invention the drive device has a rotating device formed as a pressure limiting valve, the rotating device being assigned to the delivery line of the pump, in the locking position direction by a spring and the discharge position direction by the delivery pressure of the pump. In this case the electronic control device has a reference program, in which the pump is set to a fixed delivery volume if the load pressure is known and the sensor signal provided from the sensor device is stored in the valve characteristics of the rotating device. Adjusted with reference to the curve. In this case, the present invention does not change the set value of the rotating device during the operating time and life of the spring of the rotating device, so that the valve characteristic curve of the rotating device defined by the spring characteristic curve becomes the operating time and the driving time. It is advantageously used to recognize that it has a specific valve characteristic curve that does not change during the lifetime of time. In this case, the valve characteristic curve shows the correlation between the volume flow through the rotary device and the pressure difference in the rotary device or the discharge pressure in the rotary device. This valve characteristic curve remains unchanged for the duration and lifetime of the drive system, so that the sensor device can be gauged to one pressure or one pressure differential by one device of the drive system present. have.

When the rotating device is formed as a pressure limiting valve, the pump is determined by the electronic control device and set with one delivery volume known to the control device when the load pressure is known to the electronic control device in the reference program. It is kept constant in the delivery volume. In this case, the known delivery volume flow of the pump flows through a rotating device formed as a pressure limiting valve, which is brought into contact with the discharge position, ie in the direction of the storage container, due to the delivery pressure of the pump, thereby dispensing the pump. The opening cross section of the pressure limiting valve and the specific valve position of the pressure limiting valve are set in relation to the volume flow. For this valve position, the pressure drop in the rotating device or the sending pressure in contact with the rotating device is assigned with reference to the valve characteristic curve stored in the control device, and the sending pressure is adjusted to the same level as the signal of the sensor device provided from the sensor device. Can be. In this way, the sensor device can be referenced in a simple manner in an embedded state.

According to one preferred embodiment of the present invention, the rotary device is formed as a rotary pressure regulator, which is assigned to the delivery line of the pump and is contacted by the spring and in the locking position direction by the maximum load pressure of the power consuming devices. Can likewise be contacted in the discharge position direction by the discharge pressure of the pump, in which case the electronic control device has a reference program, in which the pump has a control valve of the power consuming device in a neutral position. If present, it is set to a fixed delivery volume and the signal provided from the sensor device is adjusted with reference to the stored valve characteristic curve of the rotating device. A rotary device of this type, formed as a rotary pressure regulator, allows an excess volume of delivery volume flow carried from the pump to flow out into the storage vessel. In this case a rotary pressure regulator can be used to adjust the delivery volume of the pump. In this case, the present invention does not change the set value of the rotary pressure regulator during the operation and life of the spring of the rotary pressure regulator, so that the valve characteristic curve of the rotary pressure regulator defined by the spring characteristic curve is driven by the drive system. It is advantageously used to recognize that it has a constant valve characteristic curve without modifications during the operation and lifetime of. In this case, the valve characteristic curve shows the correlation between the volume flow through the rotary pressure regulator and the pressure difference at the rotary pressure regulator or the discharge pressure or load pressure at the rotary pressure regulator. This valve characteristic curve remains the same without variation during the operation and lifetime of the drive system, whereby the sensor device can be gauged to one pressure or one pressure differential by one device of the drive system present.

When the rotating device is formed as a rotary pressure regulator, the pump is determined by the electronic control device and set to one delivery volume known to the control device when the control valve of the power consuming device is in the neutral position in the reference program. And the volume remains constant. When the control valves are closed, the known delivery volume flow of the pump flows completely through the rotating device formed as a rotary pressure regulator into the storage container, whereby the specific opening cross section associated with the delivery volume flow of the pump and with it the In relation to the delivery volume flow, one valve position of the rotary pressure regulator is set. For this valve position of the rotary pressure regulator a pressure drop in the rotary device can be assigned and detected with reference to the valve characteristic curve stored in the control device, the pressure drop being adjusted to the same level as the signal of the sensor device provided from the sensor device. Can be. In this way, the sensor device can be referenced in a simple manner in an embedded state.

According to one preferred refinement of the invention, reference is made of the sensor signal to the delivery volume of the differently defined pumps. Thus, for different delivery volume flows of the pump, the standardization of the sensor signal supplied from the sensor device can be carried out, whereby the accuracy of gauging of the sensor device can be improved.

The electronic control device also includes an adjustment program for reference of the sensor device, in which case the pump has a maximum pressure regulating device, the maximum pressure regulating device including a pressure shut-off valve for adjusting the delivery volume of the pump and In this case, in the adjustment program, the pump is operated in the pressure shutoff mode by the defined delivery volume, and the sensor signal provided from the sensor device is adjusted by referring to the stored valve characteristic curve of the pressure shutoff valve. Thus, the adjustment or standardization inspection of the sensor device can be carried out when the delivery pressure of the pump is different in the pressure interruption mode. Likewise the setting of the pressure shutoff valve and the valve characteristic curve can be stored in a simple manner in the electronic control device, so that the known delivery volume of the pump in the pressure shutoff mode is referred to as the sensor signal provided from the sensor device with reference to the valve characteristic curve of the pressure shutoff operation. Can be adjusted and checked in the same manner as

According to one preferred embodiment of the present invention, the sensor device is provided with one or more first sensors for detecting the load pressure of the power consuming device, in particular the first sensor and the pump for detecting the maximum load pressure of the plurality of power consuming devices. It may include a second sensor for detecting the pressure. Electrohydraulic load-sensing-control of the pump can be achieved in a simple manner by one sensor that detects the delivery pressure of the pump and one sensor that detects the maximum pressure of the driven power consuming devices. In this case, the pressure difference formed by the load pressure and the delivery pressure of the power consuming device, detected by the two sensors, can be calculated and determined in a simple manner in the electronic control device.

According to an alternative embodiment of the invention, the sensor device likewise uses a pressure differential detection sensor for detecting a pressure difference formed due to the load pressure of the power consuming device, in particular the maximum load pressure of the plurality of power consuming devices and the delivery pressure of the pump. It can be formed as.

In particular, the object of the invention mentioned in the method mentioned in the introduction with respect to a drive system with a rotating device formed as a rotary pressure regulator is that the pump is known for the reference of the sensor device, in particular when the load pressure is known. When the control valve is in the neutral position, it is set by the electronic control device to a constant fixed delivery volume, and the sensor signal provided from the sensor device is achieved in the manner according to the present invention by adjusting with reference to the stored valve characteristic curve of the rotating device. . During standardization, the delivery volume of the pump as well as the delivery volume flow and load pressure are known to the electronic control device, so that the pressure drop associated with the delivery volume flow of the pump or the pump delivery to reference the sensor signal of the sensor device in the embedded state The pressure may be assigned to a sensor signal provided from the sensor device with reference to the valve characteristic curve of the rotating device stored in the electronic control device.

In order to improve the quality of the reference of the sensor device, the reference of the sensor device to the delivery volume of differently defined pumps can be carried out.

In this case, the valve characteristic curve of the rotating device can be detected and stored in the electronic control device at the start of the drive system, in particular at the first start. The valve characteristic curve at the first start of the drive device on the test stand can be detected in a simple manner and stored in the electronic control device.

One or more first sensors for the sensor device to detect the load pressure of the power consuming device, in particular one sensor for detecting the maximum load pressure of the driven power consuming devices and one second sensor for detecting the delivery pressure of the pump In the case according to the present invention, in the method according to the present invention, the signal of the first sensor is set and stored at a stored tangential pressure level when the sensor device is referenced, and the signal of the second sensor is stored in the stored valve of the rotating device. The characteristic curve is adjusted and stored as a reference. In the method according to the invention reference of the sensor device is carried out when the control valves of the power consuming devices are in a neutral position, in which the load pressure signal of the power consuming devices can be stored in the electronic control device in a simple manner. Coincides with the tangential pressure level. The stored tangential pressure level can be adjusted to the same level as the signal of the first sensor that detects the load pressure in the electronic control device during the reference, so that the signal of the first sensor can be referenced in the end. When the control valves are closed, the delivery volume flow of the pump flows completely through the rotary pressure regulator into the storage vessel, which takes one valve position with respect to the delivery flow that fits the valve characteristic curve. As a result, the delivery pressure of the pump has one value that is suitable for the valve characteristic curve of the rotary pressure regulator because the delivery volume of the pump flows completely through the rotating device into the storage container. Thus, with reference to the stored valve characteristic curve of the rotating device, the delivery pressure is assigned to the sensor signal for the delivery pressure of the pump, which is provided from the second sensor device by means of the delivery volume flow notice, together with the delivery volume of the pump, thereby resulting in a second Sensors can also be referenced.

If the pump has a maximum pressure control device (the maximum pressure control device includes a pressure shut-off valve for controlling the delivery volume of the pump), the adjustment or standardization inspection of the sensor device according to one preferred refinement of the invention is carried out. The pump may be operated in pressure shut off mode.

In the pressure shutoff mode of the above manner, the prescribed load pressure regulation is sent to the rotary device for the pressure shutoff operation, and the pump is set to a constant fixed delivery volume, in which case the sensor signal of the sensor device is stored in the pressure shutoff valve. The characteristic curve is adjusted and stored as a reference. By operating the pump at different delivery pressures in the pressure shutoff mode, the reference of the second sensor for detecting the delivery pressure of the pump can be adjusted and inspected in a simple manner.

The valve characteristic curve of the pressure shut-off valve is preferably detected and stored in the electronic control device at the start of the drive system, in particular at the first start-up, whereby the valve characteristic curve of the pressure shut-off valve can be detected in a simple manner.

The adjustment of the reference and / or the reference of the sensor device is carried out in accordance with the defined operating duration of the drive system. With the method according to the invention, in order to ensure a high control quality of the electro-hydraulic load-sensing-control of the pump during the lifetime of the drive system, the reference of the sensor device depends on the pre-given duration of operation of the drive system. And it can be automatically implemented in a simple manner at the desired service interval.

Further advantages and details of the invention are described in detail with reference to the embodiments shown schematically.

1 is a hydrostatic drive system according to the invention,
2 is a valve characteristic curve of a rotating device.

1 shows a circuit diagram of an electro-hydraulic, load-sensing control drive system 1 according to the invention, which drive system, for example, for controlling the power consuming devices of a mobile work machine, in particular a construction machine formed of an excavator. Or to control the working hydraulic pressure of the forklift.

The drive system 1 comprises a pump 2 which is adjustable in the delivery volume and is driven by a drive motor, for example an internal combustion engine, which pumps pressurized medium from the storage vessel 3 to the delivery line 4. ). The delivery line 4 is connected with control valves 5a and 5b formed as directional control valves for driving power consumption devices not shown. In this case, pressure regulators not shown are assigned to the power consuming devices or control valves 5a and 5b to operate the power consuming devices regardless of the load. The control valves 5a, 5b have a spring-centered neutral position shown, in which the delivery line 4 is blocked.

The delivery volume of the pump 2 can be electrically driven using the delivery volume adjusting device 6 of the pump 2, for example, a rotary swash plate. An electronic control device 7 is provided for this purpose, which is functionally connected to the actuating device 11 of the delivery volume control device 6, for example an electrically driven essential flow control valve, on the output side.

On the input side, the electronic control device 7 is connected with a sensor device for detecting the pressure difference formed due to the maximum load pressure of the power consuming devices and the delivery pressure of the pump 2. The sensor device comprises a first sensor 8 for detecting the maximum load pressure of the power consuming devices in the embodiment shown. In this case, the sensor 8 detects the maximum load pressure of the driven power consuming devices generated in the load pressure transmission line 10, the maximum load pressure being a shuttle valve not shown in many power consuming devices. It can be detected by a shuttle valve train. The sensor device comprises a second sensor 9, which is functionally connected with the delivery line 4 of the pump 2 to detect the delivery pressure of the pump 2. In this case, the delivery volume regulating device 6 of the pump 2 using the electronic control device 7 adjusts the pressure rather than the maximum pressure of the driven power consuming devices generated in the load pressure transmission line 10. A discharge pressure as large as a difference is driven to be formed in the delivery line 4. Thus, the electronic control device 7 and the sensor device form an electric pressure differential regulating device of the pump 2.

Also provided is a rotary device 15 arranged in the connecting line 16 which connects the delivery line 4 to the storage container 3. The rotary device 15 is formed as a rotary pressure regulator 17, which has a locking position 17a and a discharge position 17b. The pressure regulator 17 is contacted in the discharge position 17b direction by the discharge pressure of the pump generated in the discharge line 4. For this purpose, a control line 18 is connected to one control surface of the pressure regulator 17 which acts in the discharge position 17b direction, connected to a connecting line 16 upstream of the rotary pressure regulator 17. The pressure regulator 17 is contacted in the direction of the locking position 17a by the spring 19 and by the maximum pressure of the power consuming devices. To this end, a control line 20 connected to the load pressure transmission line 10 is connected to one control surface of the rotary pressure regulator 17 which acts in the locking position 17a direction. Preferably the initial stress of the spring 19 coincides with the adjustment pressure difference.

The control valves 5a, 5b can be operated electrically or electro-hydraulic. For this purpose, target value defining devices 21a, 21b, for example a joystick, are provided, which are connected to the electronic control device 7. In this case, the control device 7 forms control signals corresponding to the operation of the control valves 5a, 5b.

2 shows the valve characteristic curve K of the rotating device 15 formed as the rotary pressure regulator 17, which is stored and accumulated in a corresponding reservoir in the electronic control device 7.

In FIG. 2 the volumetric flow Q passing through the rotary pressure regulator 17 is shown on the abscissa, and the pressure loss ΔP for the pressure regulator 17 is shown on the longitudinal coordinates, the pressure loss being the rotational pressure. When the regulator 17 is contacted in the discharge direction, it is determined by the force of the spring 19 and by the characteristic curve of the spring. Since the spring 19 of the rotary pressure regulator 17 does not change the set value of the rotary pressure regulator for the entire lifespan, the volumetric flow through the valve characteristic curve K and, in addition, the rotary pressure regulator 17. The correlation between Q and the pressure difference DELTA P in the rotary pressure regulator 17 remains the same unchanged for the life of the drive system.

In the drive system according to the invention, when the sensors 8, 9 are formed inside the system, the reference and verification of the sensors 8, 9 can be carried out by the electronic control device 7.

The electronic control device 7 provides a reference program for the reference of the sensors 8, 9, in which the control valves 5a, 5b of the power consuming devices are all in a neutral position in the first stage of the standardization program. Is checked or whether all of the control valves 5a, 5b of the control valves are in a neutral position in which the delivery line 4 of the pump 2 is blocked. In a subsequent step, the pump 2 is set to a specific delivery volume fixedly input to the control device 7 via the control device 7 by correspondingly driving the operating device 11 of the delivery volume control device 6. The pump 2 is kept constant at the set delivery volume. For this reason the constant delivery volume flow Q1 of the pump 2 given is stored in the control device 7 or determined in the control device 7.

A rotational speed detection device (not shown) in the pump 2 or the main engine is used to determine the delivery volume flow of the pump 2 given when the delivery volume of the pump 2 is determined, The rotational speed detection device is functionally connected with the electronic control device 7. The method according to the invention can likewise be carried out when the rotational speed of the pump 2 or the main engine, for example the no-load rotational speed of the main engine, formed as an internal combustion engine, is known, so that the pump 7 in the control device 7 From the delivery volume of (2) the associated delivery volume flow of the pump 2 can be determined.

Accordingly, the pump 2 is set to be constant so that the delivery volume flow Q1 known to the control device 7 is directed toward the closed control valves 5a and 5b, so that the rotary pressure regulator 17 is connected to the pump ( In order to guide the entire delivery volume flow Q1 of 2) into the storage container 3, the delivery pressure generated in the control line 18 is connected in the discharge position 17b direction as opposed to the spring 19.

In this case, the rotary pressure regulator 17 takes a position which corresponds exactly to the characteristic curve K exactly to the delivery volume flow Q1 of the pump 2. Since the delivery volume of the pump 2 and the delivery volume flow Q1 are preset and fixedly input to the electronic control device 7, and the valve characteristic curve K of the rotary pressure regulator 17 is stored, In a further step, when the delivery volume flow Q1 of the pump 2 is delivered and set, the electronic control unit 7 refers to the stored valve characteristic curve K, and the pressure difference in the rotary pressure regulator 17. The pressure value P1 for (ΔP) can be determined.

Since the pump 2 pumps toward the control valves 5a and 5b in the neutral position in the standardization program, the load pressure generated in the load pressure line 10 is likewise stored in the electronic control device 7 as a pressure value. Match the tangential pressure level.

In a further step, the control device 7 detects the load pressure generated in the load pressure line 10 and assigns a pressure value corresponding to the tangential pressure level to the electrical voltage signal provided from the sensor 8. The sensor 8 is then referenced and gauged by detecting a signal from the sensor 8 which stores the pressure value as a new reference value of the sensor 8.

In a further step, the control device 7 detects a signal from the sensor 9 which detects the delivery pressure of the pump 2 generated in the delivery line 4. Since the delivery pressure of the pump 2 corresponds to the pressure drop P1 in the rotary pressure regulator 2, the control device 7 refers to the valve characteristic curve K of the rotary pressure regulator 17. The determined pressure value P1 is assigned to the electric voltage signal provided from the sensor 9, and the pressure value P1 is stored as a new reference value of the sensor 9, so that the sensor 9 is standardized and gauged.

In order to check the adjustment of the sensors 8, 9 and the reference, a constant fluctuating delivery volume flow Q2 is determined in the pump 2 according to FIG. 2, so that the pump is in the further stage of the reference program. The method described for the additional delivery pressure in (2) is carried out.

In addition, the adjustment or inspection of the sensors 8, 9 can be carried out in a further adjustment program of the control device 7. In this case, the pressure shut-off valve of the operating device 11 of the delivery volume adjusting device 6 of the pump 2 returns the pump 2 in the direction of reducing the delivery volume, so that the pump 2 is operated in, for example, the pressure blocking mode. Can be. If the valve characteristic curve of the pressure shut-off valve is known and the delivery pressure of the pump 2 is different, the sensors 8, 9 are defined by the specification of the delivery volume and the load pressure of the pump 2 determined by the control device 7. Adjustment or inspection can be achieved.

The method according to the invention is also used in the sensor device, which is formed as a pressure difference sensor and determines the pressure difference formed due to the load pressure of the power consuming devices and the delivery pressure of the pump. The pressure value P1 determined by the stored valve characteristic curve K is adjusted to the same level as the signal of this type of pressure differential sensor when the delivery volume flow Q1 is determined and used as a new reference value of the pressure differential sensor. .

The valve characteristic curve K of the rotary pressure regulator 17 and optionally the valve characteristic curve of the pressure differential valve present are determined in a simple manner before the first startup of the drive system or during the first startup, for example on a test stand, so that the control device (7) can be stored.

By the method according to the invention, the aging phenomenon, temperature fluctuations or other effects, without incurring the disassembly and switch-off and maintenance costs of the sensors 8, 9 in the drive system according to the invention inserted in a mobile working machine Inaccurate measurement and measurement error of the sensors 8, 9 caused by it can be adjusted and offset, and new reference values for adjusting the electrical delivery volume of the electronic control device 7 can be determined.

Another method according to the invention can be carried out automatically at specific service intervals by the control device 7, in which case it takes only a few seconds to inspect and standardize the sensor device.

Claims (15)

A hydrostatic drive system for a mobile work machine having a load-sensing control pump capable of adjusting the delivery volume and at least one power consuming device, said power consuming device being controllable by a control valve, in particular a directional valve.
At this time, in order to adjust the delivery volume of the pump, an electric pressure difference adjusting device is provided, the electric pressure difference adjusting device is a load pressure of the power consumption device, in particular the maximum pressure of a plurality of power consumption device and the discharge of the pump And a sensor device and an electronic control device for detecting a pressure difference formed due to pressure, wherein the electronic control device sets the pump so that the pressure difference matches a preset adjustment pressure difference,
The reference of the sensor device can be implemented by the electronic control device 7 without disassembling the sensor device.
Hydrostatic Drive System.
The method of claim 1,
A rotating device 15 formed as a pressure limiting valve is provided, which is assigned to the delivery line 4 of the pump 2 and by the spring in the locking position direction and by the delivery pressure of the pump 2. It is possible to contact in the discharge position direction, wherein the electronic control device 7 includes a reference program, in which the pump 2 is set to a predetermined delivery volume when the load pressure is known, and the sensor The sensor signal provided from the device is adjusted with reference to the stored valve characteristic curve of the rotating device.
Hydrostatic Drive System.
The method of claim 1,
The rotary device 15 is formed as a rotary pressure regulator 17, which is assigned to the delivery line 4 of the pump 2, by means of a spring 19 and the maximum pressure of the power consuming devices. Contact with the locking position 17a direction, and contact with the discharge position 17b direction by the discharge pressure of the pump 2, wherein the electronic control device 7 includes a reference program, In the reference program, the pump 2 is set to a predetermined delivery volume Q1 when the control valves 5a and 5b of the power consuming device are in the neutral position, and the signal provided from the sensor device is supplied to the rotary device 17. Adjusted with reference to the stored valve characteristic curve (K)
Hydrostatic Drive System.
The method according to any one of claims 1 to 3,
The reference of the sensor signal to the differently defined delivery volume Q1; Q2 of the pump 2 is performed.
Hydrostatic Drive System.
The method according to any one of claims 1 to 4,
The electronic control device 7 comprises an adjustment program for the standardization of the sensor device, wherein the pump 2 has a maximum pressure control device, and the maximum pressure control device has a delivery volume of the pump 2. A pressure shutoff valve for regulating the pressure relief valve, in which case the pump (2) in the adjustment program is operated in a pressure shutoff mode with a defined delivery volume, and the sensor signal provided from the sensor device is stored in the pressure shutoff valve. Adjusted with reference to the characteristic curve
Hydrostatic Drive System.
6. The method according to any one of claims 1 to 5,
One or more first sensors 8 for the sensor device to detect the load pressure of the power consuming device, in particular the first sensor for detecting the maximum load pressure of a plurality of power consuming devices and the delivery pressure of the pump 2 One or more second sensors 9 for detecting
Hydrostatic Drive System.
6. The method according to any one of claims 1 to 5,
The sensor device is presented as a pressure differential detection sensor for detecting a pressure difference formed due to the load pressure of the power consuming device, in particular the maximum load pressure of the plurality of power consuming devices and the delivery pressure of the pump 2.
Hydrostatic Drive System.
A hydrostatic drive system for a mobile work machine having a load-sensing control pump capable of adjusting the delivery volume and at least one power consuming device, said power consuming device being controlled by a control valve, in particular a directional valve.
At this time, the delivery volume of the pump is controlled by an electric pressure differential adjusting device, and detecting the pressure difference formed due to the load pressure of the power consuming device, in particular the maximum load pressure of the plurality of power consuming devices and the delivery pressure of the pump. A sensor device is used for this purpose, the sensor device being functionally connected with an electronic control device for controlling the delivery volume of the pump such that the pressure difference determined by it corresponds to a preset adjustment pressure difference, and a rotary device, in particular a rotary pressure regulator, is provided. The rotary device is assigned to the delivery line of the pump, is contacted in the locking direction by a spring and by the maximum load pressure of the power consuming device, and in the discharge direction by the delivery pressure of the pump,
For reference of the sensor device, the pump 2 is kept constant by the electronic control device 7 when the load pressure is known, in particular when the control valves 5a and 5b of the power consuming device are in a neutral position. Characterized in that it is adjusted to a given delivery volume Q1 and the signal provided from the sensor device is adjusted with reference to the stored valve characteristic curve K of the rotary device 15.
How a hydrostatic drive system works.
The method of claim 8,
The sensor device is characterized in that reference is made to differently defined delivery volumes Q1 and Q2 of the pump 2.
How a hydrostatic drive system works.
The method according to claim 8 or 9,
The valve characteristic curve K of the rotary device 15 is detected at the start of the drive system 1, in particular at the first start, and is stored in the electronic control device 7.
How a Hydrostatic Drive System Works
The method according to any one of claims 8 to 10,
One or more first sensors 8 for detecting the load pressure of the power consuming device, in particular one sensor for detecting the maximum load pressure of the driven power consuming devices and detecting the delivery pressure of the pump One or more second sensors 9 for which the signal of the first sensor 8 in the reference of the sensor device is set and stored at a stored tangential pressure level and the signal of the second sensor 9. Is adjusted and stored with reference to the stored valve characteristic curve (K) of the rotating device (15)
How a hydrostatic drive system works.
The method according to any one of claims 8 to 11,
The pump 2 provides a maximum pressure regulating device, the maximum pressure regulating device comprising a pressure shut-off valve for adjusting the delivery volume of the pump 2, wherein the pump is used for adjusting the reference of the sensor device. Is operated in a pressure shutoff mode
Method for operating a hydrostatic drive system.
The method of claim 12,
In the pressure shutoff mode, a defined load pressure regulation is sent to the rotary device for the pressure shutoff mode, and the pump 2 is set to a constant fixed delivery volume, wherein the signal of the sensor device is a stored valve characteristic of the pressure shutoff valve. It is characterized by being adjusted by referring to the curve
How a hydrostatic drive system works.
The method according to claim 12 or 13,
The valve characteristic curve of the pressure shut-off valve is detected at the start of the drive system, in particular at the first start, and stored in the electronic control device.
How a hydrostatic drive system works.
The method according to claim 8, wherein
The reference of the sensor device and / or adjustment of the reference of the sensor device is carried out in accordance with a predetermined operating duration of the drive system.
How a hydrostatic drive system works.
KR1020100041840A 2009-05-06 2010-05-04 Hydrostatic drive system and method for operating of a hydrostatic drive system KR101639981B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910020111 DE102009020111A1 (en) 2009-05-06 2009-05-06 Hydrostatic drive system i.e. electrohydraulical load sensing regulated drive system, for use in e.g. construction machine, has pump including electronic control device, where referencing of sensor device is implemented by control device
DE102009020111.4 2009-05-06

Publications (2)

Publication Number Publication Date
KR20100120620A true KR20100120620A (en) 2010-11-16
KR101639981B1 KR101639981B1 (en) 2016-07-15

Family

ID=42932404

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020100041840A KR101639981B1 (en) 2009-05-06 2010-05-04 Hydrostatic drive system and method for operating of a hydrostatic drive system

Country Status (2)

Country Link
KR (1) KR101639981B1 (en)
DE (1) DE102009020111A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012221943A1 (en) * 2012-11-30 2014-06-05 Zf Friedrichshafen Ag Apparatus for adjusting hydrostatic drive of construction/agricultural machine, has detecting unit for setting of output speed of hydraulic motor, and adjusting device to adjust speed of hydrostatic drive based on set output speed
DE102012221944A1 (en) * 2012-11-30 2014-06-05 Zf Friedrichshafen Ag Apparatus for adjusting control pressure of hydrostatic drive for construction or agricultural machine, has unit for load measuring of hydrostatic drive and unit for adjusting control pressure based on detected load of drive
DE102021104398A1 (en) 2021-02-24 2022-08-25 Arburg Gmbh + Co Kg Hydraulic device and method for controlling a hydraulic device
GB202117529D0 (en) * 2021-12-03 2022-01-19 Agco Int Gmbh Mobile machine and method

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0925652A (en) * 1995-07-11 1997-01-28 Hitachi Constr Mach Co Ltd Control circuit of construction machinery
JP2007162690A (en) * 2005-12-12 2007-06-28 Linde Material Handling Gmbh & Co Kg Hydrostatic driving system
JP2008241445A (en) * 2007-03-27 2008-10-09 Kayaba Ind Co Ltd Pressure controller

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5638677A (en) 1991-03-29 1997-06-17 Hitachi Construction Machinery Co., Ltd. Control device for hydraulically propelled work vehicle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0925652A (en) * 1995-07-11 1997-01-28 Hitachi Constr Mach Co Ltd Control circuit of construction machinery
JP2007162690A (en) * 2005-12-12 2007-06-28 Linde Material Handling Gmbh & Co Kg Hydrostatic driving system
JP2008241445A (en) * 2007-03-27 2008-10-09 Kayaba Ind Co Ltd Pressure controller

Also Published As

Publication number Publication date
KR101639981B1 (en) 2016-07-15
DE102009020111A1 (en) 2010-11-11

Similar Documents

Publication Publication Date Title
US8321114B2 (en) Work vehicle and work vehicle control method
US7997117B2 (en) Electrically controlled hydraulic valve calibration method and system
JP4606425B2 (en) Pump system control method and demand flow system
KR100481935B1 (en) Pump trouble diagnosing device for hydraulic drive device and display device of the diagnosing device
JP5769725B2 (en) Recalibration of out-of-range sensors
US8387755B2 (en) Lubrication system and method of control
US20020069916A1 (en) Method and apparatus for determining a valve status
EP2980326B1 (en) Device and method for controlling hydraulic pump in construction machine
JP2008303813A (en) Variable displacement pump control device
KR20100120620A (en) Hydrostatic drive system and method for operating of a hydrostatic drive system
US20190063404A1 (en) Method and system for diagnosing wind turbine power generating apparatus
US20240011478A1 (en) Test device
KR20210144592A (en) Process for calibrating an electro-proportional adjustable proportional valve
CN112368452B (en) Construction machine
JP2019020132A (en) Durability test apparatus of engine
KR20210066311A (en) Testing apparatus for control valve of fuel injection valve
US20220298755A1 (en) Construction Machine
CN114402141A (en) Hydraulic unit
WO2009132180A2 (en) Method of controlling a hydraulic system
US20230296171A1 (en) Method for Calibrating a Pivot Angle Sensor, Control Means, and Propulsion or Working Machine
JP5515375B2 (en) Construction equipment filter clogging detection device
US20140147293A1 (en) Hydraulic machine with electronically controlled valves
EP3252237B1 (en) Hydraulic control system
CN111173808A (en) Hydraulic machine, control assembly, hydraulic system and method
US20240068492A1 (en) Calibration system and calibration method in hydraulic system

Legal Events

Date Code Title Description
N231 Notification of change of applicant
A201 Request for examination
E902 Notification of reason for refusal
E90F Notification of reason for final refusal
E701 Decision to grant or registration of patent right
GRNT Written decision to grant