IndraDyn T MST130A-0250-N parameters .
The goal of this research is to apply direct-driven hydraulics (DDH) to the concept of zonal (i.e., locally and operation-focused) hydraulics, which is an essential step in the hybridization and automation of machines. DDH itself aims to combine the best properties of electric and hydraulic technologies and will lead to increased productivity, minimized energy consumption and higher robust performance in both stationary and mobile machines operating in various environments. In the proposed setup, the speed and position control of a double-acting cylinder is implemented directly with an electric motor drive in a closed-loop system without conventional control valves and an oil tank. The selection of the location of the hydraulic accumulator and connection of the external leakage lines will also be part of this study. Simulations and experimental research to study the details of the hydromechanical and electrical realization of the DDH are performed.
- direct driven hydraulics
- non-road mobile machinery
- energy efficiency
- electric drive
- hybrid topology
- energy regeneration
The climate for industrial and economic growth is changing as resource scarcity pushes up costs, and enterprises are more closely scrutinized because of changing expectations about their public and social responsibilities. Governments have set tight CO2 emission rules  and new exhaust limits have just been implemented, such as Tier Emission Standards. The next known step will be the 2019/2020 Tier V, which is a regulation imposing an ulterior sharp tightening of exhaust limits, especially in terms of particles. Now, there is a four-year time window to prepare engines for the upcoming regulations through solutions for peak power shaving and the downsizing of diesel engines. Electric and hybrid vehicles are a suitable solution for reaching these target environmental requirements; such vehicles have a huge potential for application in the non-road mobile machinery (NRMM) industry, with its market in mining, process and goods manufacturing, forest harvesting and construction work. Figure 1 illustrates typical examples of NRMMs.
The NRMM industry and its customers are traditionally quite conservative in putting new ideas and technologies into use. When they opt for “mild hybridization”, the machine manufacturers do not need to change the construction frame of the whole machine immediately. However, some changes in layout design concepts, machine types and business models should be considered in the long term. Therefore, we address several challenges to improve NRMMs by bringing zonal hydraulics into machines. Combining the best properties of traditional hydraulics and electric intelligence allows the following benefits to be achieved in NRMMs:
easy electrification of NRMMs
higher efficiency compared to conventional machines
electrohydraulic power pack with no tank and pipelines
reduction of potential leakage points
sensorless position control
1.1. State of the art
During recent years, the NRMM industry has had a tendency towards integrated, compact electrohydraulic systems that deliver powerful, linear movement with either valve- or pump-controlled systems. These technological steps are considered important stages towards a solution to commonly identified problems, such as the reduction of CO2 emissions and improved performance, productivity, reliability and controllability [2, 3], as well as good options for forcing a smaller diesel engine to operate within its optimum efficiency area since, in general, the diesel engines of NRMMs operate far from their optimum efficiency range . Restrictive environmental regulations are not the only factor imposing the need for innovation in NRMMs. Today, as the search for natural resources expands to areas previously considered too remote and environmentally hostile to support viable extraction and processing operations, researchers all around the world are facing the challenge of establishing and maintaining industrial activities in extreme environments. In these, components of the drive face thermal issues, primarily at start-up, when everything in the drive has cooled down to low, even Arctic temperatures. Under these conditions, conventional hydraulic fluid in all hydraulic systems solidify, so when the NRMM starts up, there is no fluid circulating to protect the pump and other components from extreme wear. For successful operation, a relevant start-up procedure is crucial, as the risk of equipment failure is unacceptable in remote locations.
Zonal or decentralized hydraulics—as we will call it—is an approach first introduced in the aircraft industry . Adapting this time-proven design from the aircraft industry, simplifying its design as well as broadening its orientation and performance options will support a similar development in NRMMs. In a fully zonal system, the hydraulic pumps are removed from the engine and replaced within hydraulic power packs distributed throughout the NRMM system. In this architecture, multiple hydraulic power sources may be utilized in each zone in order to achieve energy savings and work with a power-on-demand approach.
Figure 2 illustrates the zonal hydraulic architecture applied to NRMMs. A challenge in this is the increasing number of electric components in the limited volume available in the vehicle. On the other hand, the main advantages of this architecture are the reduced hydraulic tubing (tubes are replaced with wiring), the elimination of some hydraulic components and simplified machine assembly.
In this study, an electrohydraulic actuator (EHA) will be used to achieve high power density, low noise and high performance in a compact package in order to take the development of a power unit onto the next level. The electrohydraulic actuator allows decoupling from the main hydraulic system, thus enabling a zonal approach and, at the same time, reducing parasitic losses in order to obtain better fuel efficiency and lower operating costs. The robust, leak-free, one-piece housing design delivers system simplicity and lowers both installation and maintenance costs. The electrohydraulic actuator reduces space and weight demands. It can eliminate hoses, fittings, valves and fixtures and is easy to integrate into larger systems.
Currently, electrohydraulic actuators are mostly installed and developed for aircraft applications [6, 7], where the price level and reliability requirements are very high. Most of the research studies related to electrohydraulic actuators have been conducted to adjust the state of the servo valve [8, 9]. However, this approach results in low energy efficiency because of the flow via the pressure relief valves of the hydraulic pumps and throttle losses at the control valves. Consequently, several techniques have been developed to overcome this drawback in order to achieve higher efficiency. In ref. , the concept of a pump-controlled electrohydraulic actuator is introduced as an advanced hydraulic system where the proposed structure of the electrohydraulic actuator is directly operated by a bidirectional pump. There are already commercially integrated power packages on the market, but they are based on conventional technology and they do not respond to the above-mentioned challenges created by the hybridization problem. Examples of commercial pump-controlled electrohydraulic actuators are, for instance, the mini-motion package from Kayaba Industry Co.  and the intelligent hydraulic servo drive-pack from Yuken Kogyo Co. . The disadvantages of the architecture evidenced in ref.  are the use of complex and expensive pumps and the lower dynamic properties of the system in general. In addition, none of these commercial solutions are designed for power-on-demand control, sensorless positioning or even energy regeneration, all highly desirable improvements in a competitive product.
Some studies have been conducted to introduce the concept of electrohydraulic actuators as zonal hydraulics in NRMM. In ref. , an electrohydraulic actuator is used for the power steering of heavy vehicles. In refs. [14–17], a compact drive for automation of all kinds of linear motions was introduced and investigated from the thermal point of view. In these sources, even if they proposed direct pump control similar to the direct-driven hydraulic approach, a set of valves is used to balance the flow and to ensure the direction of the electrohydraulic actuator motion. In refs. [18, 19], direct-driven hydraulics (DDH), an electrohydraulic actuator, was introduced without conventional directional valves. The DDH drive combines the best properties of electric and hydraulic drive technologies in one:
direct control of flow, as well as the velocity and position of the actuator
high hydraulic efficiency because there are virtually no flow-restricting valves
no need for expensive variable displacement pumps
easier to find the optimum operational point for each of the powertrain components (fewer compromises) since each actuator has two pump units and an electric motor
the pump units and internal combustion motor are disconnected
possibility of realizing efficient energy recovery systems using both hydraulic accumulators and electric batteries
Therefore, the idea of implementing the DDH drive in the powertrain of NRMMs as an application of the zonal hydraulic concept was born. In this research, direct-driven hydraulics (DDH) is seen as a tool to convert existing NRMMs to hybrids combining the best properties of traditional hydraulics and electric intelligence. Figure 3 illustrates the hybrid proposal for NRMMs. With this approach, several challenges that traditionally manifest themselves in the hybridization process will be solved. In the proposed setup, the speed and position control of a double-acting cylinder is implemented directly with a motor drive in a closed-loop system without conventional control valves and an oil tank. The selection of the optimal size and the location of the hydraulic accumulator will also be part of this study. Simulations and experimental research to study the details of the hydro-mechanical and electrical realization of the DDH will be performed.
The next chapter introduces the experimental DDH setup.
2. Description of test setup
The experimental setup uses a speed-controlled electric servo motor drive rotating two hydraulic pumps to directly control the amount of hydraulic oil pumped to the asymmetrical double-acting cylinder MIRO C-10-60/30× 400. The simplified circuit diagram of the experimental test setup is illustrated in Figure 4. The hydraulic pump/motors P1 and P2 create an input and output flow that depends on the rotating speed of the servo motor. The oil pressure rises to the required level as determined by the payload. During lowering motion, the potential energy of the payload creates a flow that rotates the hydraulic machine P1 as a motor and the hydraulic machine P2 as a pump, and the mechanically connected electric motor acts as a generator, which is controlled by the frequency converter. The speed-controlled generator controls the amount of fluid flow and the position of the payload. The program for the electric drive controls both the electrical and hydraulic sides of the system as there is no conventional valve control.
For easier understanding of the real displacements of the pumps, the following ratios
where is the cylinder area from the rod side. The diameter of the cylinder piston head is
As previously stated, the pump/motors P1 and P2 are mounted on the same axis, so their speeds are identical. If the pump leakage is ignored, the ratio of the flow rates
Figure 4 illustrates the first prototype of the DDH setup with and . To test the concept, the components for this prototype were taken off the shelf.
Two XV-2M internal gear pump/motors by Vivoil with displacements of 14.4 and 22.8 cm3/rev were used, P2 and P1, respectively . The position feedback from the motor is given by means of its in-built incremental encoder (4096 pulses per revolution, resolution 14 bits), and read with the Unidrive SP1406 drive software . It converts the AC power supply from the line and allows the speed of the permanent magnet brushless servo motor, Unimotor 115U2C manufactured by Emerson Control Techniques, to be set, taking advantage of the information obtained by the feedback device fitted to ensure the rotor speed is exactly as demanded . This experimental setup was tested with a payload of 150 kg at motor speed ranges from 300 to 500 rpm. Figure 5 shows an example of measured data for a motor speed of 400 rpm and a payload of 150 kg: speed, torque and pressure.
In Figure 5, during the lifting, which lasts from 1 to 7 s, the pressure in the pump/motor P1 is about 2 MPa, which rises by the end to 4 MPa. It is worth remarking that the rise appears to be due to the difference between and . A similar rise also occurs in the pump/motor line P2, from atmospheric pressure to 2.6 MPa.
During the lowering, performed from 7 to 13 s, a drop in the pressure from high pressure to about 1 MPa happens. During the lifting, the motor torque is 7 Nm; during the lowering, the torque is around 1 Nm. The pressure in the tank line is close to atmospheric pressure, as it is supposed to be in an open system.
In order to overcome the rise in pressure at the end of the movement and investigate the tankless approach, a new prototype was designed. Figure 6 illustrates the experimental test setup of the second DDH prototype. The system is closed by giving up the tank completely (compare to Figure 2b) and replacing it with a hydraulic accumulator A.
Within the framework of this work for the second prototype and . It can be seen that the ideal
2.1. Components used
In the second prototype, DDH setup an electric motor, an IndraDyn T MST130A-0250-N torque motor from Bosch Rexroth, is used. The parameters of the electric motor are shown in Table 1.
|1.2 kW||4.5 Nm||13 Nm||2500 rpm||4000 rpm||10||1.3 Nm/A||0.085 V/min-1||5.9 Ohm||17.5 mH|
|m3/rev||25 MPa||0.3 MPa*||500 Nm||3500 rpm|
|m3/rev||25 MPa||0.3 MPa*||500 Nm||4000 rpm|
Two Parker AD100B20T9A1 diaphragm accumulators are utilized as the initial choices. Table 4 shows the parameters of the hydraulic accumulators.
The pressure was measured with Gems 3100R0400S pressure transducers. The velocity of the cylinder piston was measured with an SGW/SGI wire-actuated encoder by SIKO.
According to the manufacturer, the pump/motors used have an external leakage-oil line with a pressure limitation of 0.3 MPa. During the start, the maximum allowed short-term pressure is 1 MPa. Thus, a detailed investigation of the hydraulic connection of the external leakage line is required.
3. Investigation of the hydraulic connections
This chapter introduces calculations for pump/motor leakage flow in order to identify a suitable connection for the external leakage line. The DDH system can be divided into three separated fluid volumes: the piston side of the cylinders A1 and the rod side of the cylinders A3 with the hydraulic accumulator B and the hydraulic accumulator A between the pump/motors. The accumulation of hydraulic fluid in any of these volumes will raise the pressure, as was shown in Figure 5 for the first prototype.
This chapter contains a simple model in which the volumetric efficiency of the pumps
The calculations were performed by determining the change in the volume of fluid during the lifting and lowering with the maximum stroke length of the cylinder
Next, the theoretical flow
The actual flows
During the lifting, the side flow
The cylinder losses are assumed to be negligible, so the required flows
It is assumed that the cylinder is moved at a constant velocity
As was stated earlier, the external leakage line of the pump/motors that are used should be connected to the line under 0.3 MPa. The next section will determine the structure. The least sensitive case will be selected as the system structure. The review will be carried out for a total of four different alternative cases. Figure 7a illustrates Case I, where both the leakage lines are connected to the line with hydraulic accumulator A. In Case II in Figure 7b, both external leakage lines are connected to hydraulic accumulator B. Figure 7c shows Case III, where the external leakage lines of the pump/motors P2 and P1 are connected to the line with hydraulic accumulators A and B, respectively. Figure 7d illustrates Case IV, where the external leakage lines of the pump/motors P1 and P2 are connected to the lines with hydraulic accumulators A and B, respectively.
3.1. Case I
In Case I, during the lifting, the A3 side of the cylinder should remove flow equal to
During the lowering, the A3 chamber of the cylinder should receive the flow of
The entire cycle change of volume Δ
3.2. Case II
Figure 7b illustrates Case II, where both of the leakage lines are connected to the line with hydraulic accumulator B and A3 chamber branch. During the lifting, the chamber A3 should remove the flow
During the lowering, the A1 chamber of the cylinder should remove the flow
The entire cycle change of volume Δ
3.3. Case III
In Case III, the leakage flow of the pump/motor P2 is connected to the hydraulic accumulator A line and the P1 leakage flow to the A3 chamber line of the cylinder, as shown in Figure 7c. During the lifting, the A3 chamber of the cylinder should pump out the flow
During the lowering, the A3 chamber of the cylinder should provide the flow
The entire cycle volume change Δ
3.4. Case IV
In Case IV, the leakage flow from the pump/motor P1 is directed to the hydraulic accumulator A and the leakage flow of the pump/motor P2 is directed to the hydraulic accumulator B. During the lifting, A3 chamber flow of the cylinder
During the lowering, the A3 chamber of the cylinder should pump out the
The entire cycle change in the volume Δ
Four cases of the locations of pump/motor leakages were investigated. The different implementation variants were determined by the changes in the volume of the cylinder as a function of the volumetric efficiency, and the results are shown in Figure 8. As a result, Case IV appears to be the most independent case . However, this method did not investigate the pressure built up with various payloads. Neither did this investigation consider the practical aspects of realizing such a system. Therefore, the system structure will be investigated further in Matlab Simulink.
5. Simulink modeling
Matlab Simulink R2015a and Simscape SimHydraulics and the SimPowerSystems component library were used for creating the simulation model. The following assumptions were made:
The effect of temperature on fluid properties is neglected.
External leakages in the hydraulic pump/motor are neglected. Volumetric efficiency is assumed to be 1.
Losses in the hydraulic accumulator are ignored.
Figure 10 illustrates the simulation results: reference signal, motor speed and cylinder position. A maximum payload of 150 kg was utilized for the simulation.
The movement of the cylinder is smooth and identical to the first prototype demonstrated in Figure 5. The flows in volume A (the line with accumulator A), B (the line with accumulator B) and C (line between the pump/motor P1 and the cylinder) are illustrated in Figure 11.
Flows B and C are mirrors of each other, which corresponds to correct behavior. Conversely, flow A has an initial drop which corresponds to sucking in oil from accumulator A during the initial lifting motion.
Figure 12 illustrates the experimental results for two system configurations with hydraulic accumulators: A and A + B. The pressure with accumulator A (red line) configuration goes up to 2.7 MPa, whereas the proposed combination A + B maintains the pressure in the range of 0.7 MPa.
The system pressure is illustrated in Figure 13, where
6. Experimental investigation
The essential parameters, such as currents, voltage, pressure, flow and height, were measured from the DDH setup. The location of the utilized sensors is illustrated in Figure 4. The experimental efficiencies and energies of the DDH test setup system for lifting movements were calculated as shown below:
The output energy of the hydraulic part
Depending on the operating point of a hydraulic pump/motor unit in its performance curve, the relationship between the flow and hydraulic losses in a system varies significantly. During the lifting, the hydraulic pump/motor unit operates as a pump. The input energy of the pump is mechanical energy and the output is hydraulic energy. Figure 14 presents an example of a Sankey diagram for the measured losses and efficiencies of the DDH system.
In Figure 14, hydro-mechanical losses equal 33.4%. Hydro-mechanical losses include shaft and hydraulic losses. Hydraulic losses in DDH systems are composed of pipe friction losses and other fittings, entrance and exit losses and losses from changes in the pipe size resulting from a reduction in the diameter, pump/motors and cylinder losses. The overall cylinder efficiency is mostly dependent on the frictional losses encountered by the piston and the rod during its stroke. Frictional losses depend on the pressure difference across the seal, sliding velocity, seal material, temperature, time, wear and direction of the movement. Measured electrical machine losses are 20.7%. Electrical machine losses are composed of the following elements: stator and rotor resistive losses, iron losses, additional losses and mechanical losses. Mechanical losses include friction in the motor bearings. Bearing losses depend on the shaft speed, bearing type, properties of the lubricants and the load. The converter losses take place mostly in the semiconductor switches and in the auxiliary power systems. In this study, the losses of the frequency converter are not included.
It was challenging to create the DDH test setup due to the asymmetrical double-acting cylinder used and the difficulty of finding matching displacements of the pump/motors in order to fulfill
This paper described a DDH setup and its potential for applicability to NRMMs. It investigates the compensation of pump/motor displacement for an asymmetrical double-acting cylinder and the location of hydraulic accumulators and external leakage pump/motor lines. The review was carried out for four different alternative cases. The mathematical model used in the review suggested Case IV as the least sensitive case. Further investigations were performed in Matlab Simulink. According to the simulations, Cases II, III and IV did not fulfill the requirements of a leakage line where the maximum allowed constant pressure was 0.3 MPa and, in the short term, it was 1 MPa. Therefore, only Case I can be used for the realization of the DDH setup, in which both external leakage lines are connected to line A (accumulator A).
The experimental tests demonstrated that direct-driven hydraulics (DDH) has the advantage of a fully self-contained electrohydraulic actuator, which combines the high power density of hydraulics and the accuracy of an electric motor. The measured energy efficiency of the DDH varies by up to 46% with the direction of the motion of the cylinder and the motor speed. As the Sankey diagram showed, the hydro-mechanical losses dominate in the original DDH setup. As expected, with regard to the efficiency of the DDH setup, the weak link in the chain is found in the losses of the hydro-mechanical components of the system. Therefore, further studies are required on the improvement of DDH.
The research was enabled by the financial support of ArcticWell project (Academy of Finland) and internal funding at the Department of Engineering Design and Production at Aalto University.
Tier 4 Emission Standards for Nonroad Diesel Engines, online, https://www.dieselnet.com/standards/us/nonroad.php#tier4.
Liukkonen, M., Lajunen, A., Suomela, J. Comparison of different buffering topologies in FC-hybrid non-road mobile machineries. At the 7th IEEE Vehicle Power and Propulsion Conference, Chicago, September 6–9, 2011. Chicago 2011.
Wang, T. et al. An energy-saving pressure-compensated hydraulic system with electrical approach. ieee/asme transactions on mechatronics, vol. 19, no. 2, april 2014 Mech., 2013.
Bifeng, Y., Tao, G., Shengji, L.,. Investigate on the combustion and emission characteristics of small non-road diesel engine fueled with bio-diesel, In 2012 (ISDEA), 2012, pp. 852–856.
Skinner, J., Smith, A., Frischemeoer, S., Holland, M. Advancements in hydraulic systems for more electric aircraft. Proceedings of MEA 2015 Conference, Toulouse, France, February 2015.
Youzhe, J., Song, P., Li, G., Zhanlin, W., Lihua, Q. Pressure loop control of pump and valve combined EHA based on FFIM. The Ninth International Conference on Electronic Measurement & Instruments, 2009.
Zhang, Q., Li, B. Feedback linearization PID control for electro-hydrostatic actuators, at 2nd International Conference on Artificial Intelligence, Management Science and Electronic Commerce (AIMSEC), 2011, p. 358 - 361, DOI: 10.1109/AIMSEC.2011.6010249
Liang, B., Li, Y., Zhang, Z. Research on Simulation of Aircraft Electro-Hydrostatic Actuator Anti-Skid Braking System (ICMTMA), 2011.
Altare, G., Vacca, A., Richter, C. A novel pump design for an efficient and compact electro-hydraulic actuator. IEEE Aerospace Conference, 2014 IEEE, 2014, pp. 1–12.
Ahn K. K., Nam D.N.C.., Jin M.,. Adaptive backstepping control of an electrohydraulic actuator. IEEE/ASME Transactions on Mechatronics, Vol. 19, No. 3, June 2014.
Mini-Motion Package (MMP), [online] http://www.kybfluidpower.com/Mini_Motion_Package.html.
AC Servo Motor Driven Hydraulic Pump Control System, [online] http://www.yuken.co.uk/long_cat/%5BK%5D/816-817.pdf.
Daher, N., Ivantysynova, M. Electro-hydraulic energy-saving power steering systems of the future. Proceedings of the 7th FPNI PhD Symposium on Fluid Power, 27-30 June 2012, Reggio Emilia, Italy.
Michel, S., Weber, J., Electrohydraulic compact-drives for low power applications considering energy-efficiency and high inertial loads. 2012. Fluid Power and Motion Control FPMC 2012 conference, Bath, UK, p.93-109
Michel, S., et al. Energy-efficiency and thermo energetic behavior of electrohydraulic compact drives, at 9th International Fluid Power Conference (IFK), 24 - 26 March 2014, Aachen, Germany.
Busquets, E., Ivantysynova M. Temperature prediction of displacement controlled multi-actuator machines. Int. J. of Fluid Power, Jan., 2014.
Busquets, E. An investigation of the cooling power requirements for displacement-controlled multi-actuator machines, M.Sc thesis, Purdue university, 2013.
Minav, T., Bonato, C., Sainio, P., Pietola, M. Direct driven hydraulic drive, at 9th International Fluid Power Conference (IFK), 24 - 26 March 2014, Aachen, Germany.
Minav, T.A., Bonato, C., Sainio, P., Pietola, M. Efficiency of direct driven hydraulic drive for non-road mobile working machines, at 2014 International Conference on Electrical Machines (ICEM), 2-5 September 2014, Berlin, Germany, pp. 2431–2435.
Vivoil motor, Data Sheet: reversible motor - series XV, http://www.vivoil.com/files/xm_en/xm201.pdf, visited on September 8, 2013.
Emerson Control Techniques Unidrive SP1406 drive, http://www.emersonindustrial.com, visited on September 8, 2013.
Emerson Control Techniques Unimotor 115U 2C, http://www.emersonindustrial.com/en-en/documentcenter/ControlTechniques/Brochures/unimotor_fm_product_data.pdf, visited on 1 September, 2013.
Bosch Rexroth Indradyn T Torque motors. [online]. http://www.boschrexroth.com/dcc/content/internet/en/pdf/PDF_p146807_en.pdf.
Bosch Rexroth AZMF External gear motors. [online]. www.boschrexroth.com.
Kauranne, H., Kajaste, J., Vilenius, M. Hydraulitekniikka, Helsinki: Sanoma Pro Oy, 2013. 496 p. ISBN 978-962-63-0707-7.
Kiesi, M. Suorasähkökäyttöisen hydraulijärjestelmän paineakun valinta ja mitoitus, Bachelor Thesis, Aalto University, 2014.