WO2010123378A1 - Recyclage d'énergie - Google Patents

Recyclage d'énergie Download PDF

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Publication number
WO2010123378A1
WO2010123378A1 PCT/NO2010/000148 NO2010000148W WO2010123378A1 WO 2010123378 A1 WO2010123378 A1 WO 2010123378A1 NO 2010000148 W NO2010000148 W NO 2010000148W WO 2010123378 A1 WO2010123378 A1 WO 2010123378A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
load
motor
pressure
hydraulic
Prior art date
Application number
PCT/NO2010/000148
Other languages
English (en)
Inventor
Tor Henrik Vik
Original Assignee
Tor Henrik Vik
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 Tor Henrik Vik filed Critical Tor Henrik Vik
Publication of WO2010123378A1 publication Critical patent/WO2010123378A1/fr

Links

Classifications

    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • 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
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the present invention relates to hydraulic systems, especially for cranes and winches, and in particular a system for conserving energy in open and closed loop hydraulic systems using load holding valves (balance valves) or other types of valves for converting potential energy and positional energy to heat.
  • load holding valves balance valves
  • other types of valves for converting potential energy and positional energy to heat.
  • Hydraulic systems are classified in open and closed loop types (with open and closed circuits). Closed loop systems are often used in larger and more complicated constructions.
  • the hydraulic circuit forms a closed loop with a pump unit and powered components connected in series. For example, if the system is to lift a load with a winch, the pump will pump the oil through the winch motor and back to the other side of the pump, further again to the winch motor, etc., until the load has reached the desired height and the brake in the gear box is activated (the winch drum is driven by a winch motor through a gear drive and the gear drive is equipped with a parking brake). Supplied energy is stored as potential energy and positional energy in the load.
  • the brake in the gear box is de-activated and the load is "hanging" on the pump. Then, the pump is angled opposite way and releases the oil the other way around. Thus, the position of the load is controlled directly by the angling position of the pump.
  • the potential energy may power the pump as a motor and this energy may be recovered.
  • closed systems may only recover energy from hydraulic motors. Energy from cylinders may not be recovered as load holding valves are used on cylinders in order to lock the cylinders when they are holding load. This is also affected by the difference in volume between the piston side and the rod side. Thus, cylinders must be handled by a separate embedded open subsystem, see below.
  • a benefit of open systems is that all lifting components may be equipped with load holding valves. This is valves which prevent the load from sagging/dropping (by oil leaking back through control valves/check valves, hose ruptures, etc.) and allow us to lower the load in a controlled way by controlling the amount of oil and pressure supplied to the opposite side of the lifting component. This is important from a safety view.
  • the benefits of a system according to the invention are a lower energy demand, less positional and potential energy that is converted to heat, which means less need for cooling the system and less costly cooling gear, safety may be provided by having no critical hoses past load holding valves, the pilot ratio on the load holding valves may preferably be lower in order to improve stability, the system may be controlled purely by hydraulics without any control system, the motor recovering the energy may also be used for heating the oil reservoir at a small cost, the system may have different volumes on supplied and recycled oil, which is advantageous when driving cylinders (this advantage is not present in any of the prior art systems), energy is also recovered from cylinders.
  • FIG. 1 is a schematic circuit drawing of an open hydraulic system without energy recovery (prior art) when lifting a load
  • Fig. 2 shows the system in Fig. 1 when lowering the load
  • Fig. 3 shows an open system according to the invention, in a situation corresponding to that in Fig. 2, i.e. when the load is lowered,
  • Fig. 4 is a schematic drawing of a corresponding system involving a winch.
  • Fig. 1 shows a common open system when lifting a load.
  • the load is lifted by a cylinder 6, and the pressure necessary for lifting the load is 200 bar.
  • This pressure is generated by a pump 2 which retrieves oil from the tank 3.
  • the pump is driven by an electric drive motor 1.
  • the oil passes from the pump 2 via a control valve 4 to the cylinder 6.
  • a commonly known load holding valve 5 is placed across the cylinder preventing the load from dropping if the motor power cuts out, for example.
  • Fig. 2 shows the same system when the load is lowered.
  • the control valve is shifted such that the pump delivers a pressure on port B, here 50 bar, to trigger the load holding valve 5.
  • the oil on the lower side of the piston in the load carrying cylinder 6 will then pass through the load holding valve to port A on the control valve 4, pass the valve to port T and further to the tank 3.
  • This results in a total pressure drop of 225 bar 200 bar from the load on the lifting cylinder + 25 bar from the trigger pressure from the pump at an area ratio of 1 :2 in the cylinder), most of which is lost across the load holding valve 5.
  • the energy from the load (and the pump) is then lost as heat in the oil across the load holding valve.
  • Fig. 3 a corresponding open hydraulic system modified with an energy recovering setup according to the present invention.
  • the system in Fig. 3 is shown when the load is to be lowered.
  • the system includes a cylinder 36 which is supplied with oil from a pump 31 via a control valve 34 and with a load holding valve 35 across the cylinder 36.
  • the energy recovering setup includes a hydraulic recovery motor 310 connected to the same shaft as the drive motor 31 and pump 32. This may be a variable axial motor or the like.
  • the recovery motor 310 is connected directly to the load holding valve 35 avoiding the control valve 34, and delivers the oil to the tank 33.
  • first and second check valves 31 1 and 312 in the line from the control valve port A to the load holder valve 35 and in the line from the load holder valve to the recovery motor, respectively.
  • a third pilot controlled check valve 313 in series with the second check valve 312 is used, but oriented in the opposite direction.
  • the last valve is controlled by the pressure on the control valve port B.
  • it may be used a pilot controlled 2-2 valve to prevent pilot ratios.
  • the system may serve several driven components, shown at ports 314 and 315. The driven components must not necessarily be cylinders as shown in the figure, but may be winch motor, for example.
  • the load on the cylinder 36 in Fig. 3 is also here 200 bar.
  • the load holding valve 35 is again triggered with a pressure of 50 bar delivered on the control valve port B. Due to the area ratio of the cylinder, this contributes an additional pressure of 25 bar on the cylinder output.
  • the trigger pressure has also triggered the third check valve 313 such that the oil is passing through the second and third check valves 312 and 313 to the recovery motor 310 and drives this.
  • the recovery motor 310 in its turn drives the drive motor 31, i.e. that it now operates as an electrical generator and delivers power.
  • the first check valve 31 1 prevents the oil from the load holding valve from entering the tank 33 directly without passing through the recovery motor 310.
  • a fourth check valve 316 in order to avoid cavitations when the system is "idling". This may for example have a spring of 0.1 bar.
  • the load holding valve has a pilot ratio, i.e. a ratio between internal pilot and external pilot on the pressure needed for opening the valve.
  • a ratio of 1 :3 means that the external pilot needs 1 x the pressure (set spring force) for opening it, while the internal pilot needs 3x the pressure to open it.
  • both pilots contribute in opening the valve.
  • the spring is set stronger than the pressure that may be obtained in the external pilot alone at maximal load on the system.
  • the load holding valves which are employed in this system must have external drainage of the spring chamber to prevent the back pressure from acting on the valve.
  • the spring chamber may also be ventilated to the atmosphere.
  • pilot ratio of the load holding valves may be changed, e.g. to 1 : 10. Then, experience has shown that the system becomes instable, and easily breaks into oscillations. Pilot ratios of 1 :2 and 1 :3 provide greater stability and control of the position energy.
  • the recovery motor may be a variable axial piston motor for different pressures and volumes according to the position energy that is to be recovered. This is achieved with a regulator on the motor controlling the displacement volume according to desired pressure in the recovery port (the port allowing the hydraulic motor to run in the same direction as the pump and electric motor).
  • the regulator is set so the motor lies with a small displacement volume (nearly zero) when "idling", and when the pressure from the position energy increases to desired recovery pressure the regulator (the pressure cut off) will control the displacement volume of the recovery motor in order to control the recovery pressure.
  • cut off' means the pressure in the working ports at which the motor should increase the displacement volume, i.e. at which loads loading a motor the moment should increase.
  • the cut off is used to determine the pressure drop across the recovery motor by varying the displacement volume.
  • the system may be secured with a safety valve adapted to pass the oil to the tank.
  • the cut off of the recovery motor may be varied according to the pressure across the load holding valves by means of a PLC and pressure sensors (not shown). Then, the pressure sensors sense the pressure on each side of the load holding valves and transmit measured values to a PLC, which in its turn controls the cut off of the recovery motor.
  • the cut off should be somewhat lower than the pressure generated by the potential energy so the load holding valves still may control the load adequately. With this solution the system will be more optimal and achieve approximately the same "reverse power" potential as a closed system when lowering a load with a winch. Also when the positional energy on the cylinders varies, the cut off may be controlled to recover as much potential energy as possible.
  • Fig. 4 shows an embodiment of an open system with energy recoverage according to the invention and where the load is lifted with a winch motor.
  • the load 46.5 is hanging from a winch drum 46.4 in a wire, and is the potential energy of the system.
  • the winch drum 46.4 is driven by a hydraulic motor 46.1 via a gear box 46.2 which reduces the number of revolutions per minute from the hydraulic motor 46.1 and increases the torque of the winch.
  • the gear box includes a parking brake 46.3. This is spring loaded towards “on”, and is lifted by means of pressure (approximately 15-20 bar).
  • the braking system includes a sprag clutch so that the brake only operates down. This means that for safety reasons the brake may only be released when lowering a load, and is activated when lifting.
  • the hydraulic motor 46.1 is a variable axial piston motor for different speeds and moments according to the load on the winch, as explained above.
  • the load holding valve 45 controls the oil pressure which the positional energy produces at the port of the winch motor 46.1 and prevents the load from rushing back, e.g. when operating the control valve 44.
  • This is a similar task as for the parking brake 46.3. But it is not used as a parking brake as there normally will be a certain internal leakage in the hydraulic motor meaning that the load could sag slowly until the motor goes empty of oil and then cavitates. This will mean that the load could fall freely.
  • first 411 and second 412 check valves or mono-direction valves are also first 411 and second 412 check valves or mono-direction valves, as well as a third pilot operated check valve 413.
  • the latter is installed to close the recovery motor 410 during lifting and open it when lowering.
  • the recovery motor is initially (idle) set to minimum displacement volume.
  • the pressure will increase until the motor enters cut off and recovers the energy that the load holding valve normally would convert to heat.
  • the pressure difference across the recovery motor is adjusted with the cut off.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Transportation (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Cette invention concerne un système hydraulique ouvert (ou un système ouvert intégré dans un système clos) spécialement conçu pour les grues et les treuils mécaniques. Le système comprend un réservoir d'huile (33), une pompe hydraulique (32) actionnée par un moteur d'entraînement (31) via un arbre de transmission, une soupape de commande (34), un composant mené (36) conçu pour mouvoir une charge, et une soupape de retenue de charge (35) qui est raccordée via le composant mené (36). De plus, le système comprend un moteur hydraulique de récupération (310) monté sur l'arbre sortant du moteur à entraînement (31) et de la pompe (32). Quand la charge est libérée, l'énergie potentielle et l'énergie positionnelle libérées par la charge entraîneront le moteur de récupération (310) qui, à son tour, entraînera le moteur d'entraînement (31) comme un générateur. L'énergie potentielle contenue dans la charge peut ainsi être récupérée.
PCT/NO2010/000148 2009-04-22 2010-04-22 Recyclage d'énergie WO2010123378A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20091602 2009-04-22
NO20091602A NO330016B1 (no) 2009-04-22 2009-04-22 Energigjenvinning

Publications (1)

Publication Number Publication Date
WO2010123378A1 true WO2010123378A1 (fr) 2010-10-28

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PCT/NO2010/000148 WO2010123378A1 (fr) 2009-04-22 2010-04-22 Recyclage d'énergie

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NO (1) NO330016B1 (fr)
WO (1) WO2010123378A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2354564A1 (fr) * 2010-01-30 2011-08-10 Seal Concept GmbH Sécurité anti-rupture de tuyau pour engins de levage actionnés de manière hydraulique
CN104791310A (zh) * 2015-02-06 2015-07-22 湘潭大学 流量回收节能型管片拼装机水平移动液压控制系统
EP2794457A4 (fr) * 2011-12-20 2015-07-29 Daniel Andrew Hawkins Palan pour déplacer une charge
CN107620701A (zh) * 2017-09-18 2018-01-23 北京航空航天大学 基于功率回馈的高速恒压变量柱塞泵驱动及变载荷试验装置
CN108439274A (zh) * 2018-04-08 2018-08-24 杭叉集团股份有限公司 电控压力控制进气切断装置及其操作方法、叉车

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6460332B1 (en) * 1998-11-04 2002-10-08 Komatsu Ltd. Pressure oil energy recover/regenation apparatus
US7249457B2 (en) * 2005-02-18 2007-07-31 Timberjack Inc. Hydraulic gravitational load energy recuperation
US20080152513A1 (en) * 2006-12-20 2008-06-26 Hans Esders Hydraulic circuit arrangement with recovery of energy

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6460332B1 (en) * 1998-11-04 2002-10-08 Komatsu Ltd. Pressure oil energy recover/regenation apparatus
US7249457B2 (en) * 2005-02-18 2007-07-31 Timberjack Inc. Hydraulic gravitational load energy recuperation
US20080152513A1 (en) * 2006-12-20 2008-06-26 Hans Esders Hydraulic circuit arrangement with recovery of energy

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2354564A1 (fr) * 2010-01-30 2011-08-10 Seal Concept GmbH Sécurité anti-rupture de tuyau pour engins de levage actionnés de manière hydraulique
EP2794457A4 (fr) * 2011-12-20 2015-07-29 Daniel Andrew Hawkins Palan pour déplacer une charge
CN104791310A (zh) * 2015-02-06 2015-07-22 湘潭大学 流量回收节能型管片拼装机水平移动液压控制系统
CN107620701A (zh) * 2017-09-18 2018-01-23 北京航空航天大学 基于功率回馈的高速恒压变量柱塞泵驱动及变载荷试验装置
CN108439274A (zh) * 2018-04-08 2018-08-24 杭叉集团股份有限公司 电控压力控制进气切断装置及其操作方法、叉车

Also Published As

Publication number Publication date
NO330016B1 (no) 2011-02-07
NO20091602L (no) 2010-10-25

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