EP3406866A1 - Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement - Google Patents

Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement Download PDF

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Publication number
EP3406866A1
EP3406866A1 EP17172231.7A EP17172231A EP3406866A1 EP 3406866 A1 EP3406866 A1 EP 3406866A1 EP 17172231 A EP17172231 A EP 17172231A EP 3406866 A1 EP3406866 A1 EP 3406866A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
gas exchange
pressure reservoir
hydraulic drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP17172231.7A
Other languages
German (de)
English (en)
Inventor
Wolfgang Schneider
Patrik Soltic
Andyn OMANOVIC
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wolfgang Schneider Ingenieurbuero
Eidgenoessische Materialprufungs und Forschungsanstalt EMPA
Original Assignee
Wolfgang Schneider Ingenieurbuero
Eidgenoessische Materialprufungs und Forschungsanstalt EMPA
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 Wolfgang Schneider Ingenieurbuero, Eidgenoessische Materialprufungs und Forschungsanstalt EMPA filed Critical Wolfgang Schneider Ingenieurbuero
Priority to EP17172231.7A priority Critical patent/EP3406866A1/fr
Priority to EP18724261.5A priority patent/EP3631174A1/fr
Priority to US16/615,175 priority patent/US11156134B2/en
Priority to CN201880033996.2A priority patent/CN111212961B/zh
Priority to PCT/EP2018/063075 priority patent/WO2018215335A1/fr
Publication of EP3406866A1 publication Critical patent/EP3406866A1/fr
Priority to US17/510,645 priority patent/US20220042428A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L1/462—Valve return spring arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L1/462—Valve return spring arrangements
    • F01L1/465—Pneumatic arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/105—Hydraulic motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/02—Formulas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/033—Hydraulic engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L33/00—Rotary or oscillatory slide valve-gear or valve arrangements, specially adapted for machines or engines with variable fluid distribution
    • F01L33/02—Rotary or oscillatory slide valve-gear or valve arrangements, specially adapted for machines or engines with variable fluid distribution rotary

Definitions

  • the invention relates to a hydraulic drive for accelerating and decelerating dynamically moving components, in particular of valves in gas exchange controls of internal combustion engines and other piston engines.
  • Variable valve timing on internal combustion engines is known as a suitable means of both improving torque versus speed performance, as well as improving overall engine efficiency and reducing emissions.
  • the variety of optimization possibilities is described in the literature.
  • Hydraulic valve actuators in particular for gas exchange valves in the working space of an internal combustion engine, are known per se for a long time, for example from the German Offenlegungsschrift 1'940'177 A. They were used as a replacement for the camshaft-controlled opening of a gas exchange valve, while the Close the valve was still provided by a spring mechanism.
  • the provision of the gas exchange valves by means of spring means, usually in the form of helical compression springs, is still by far the most widely used closing method, since it ensures safe closure.
  • the controlling valve In order to avoid high throttle losses in this situation, the controlling valve must be very fast. Likewise, in the opening endpoint of the gas exchange valve movement, for example, it must switch precisely and reliably, so that the kinetic energy can be captured to the full extent and retained in the spring. These requirements thus require very expensive, high-speed control valves and a complex control electronics.
  • a main spool is acted upon by a precisely defined volume flow of a pilot valve.
  • the pilot valve is fed by a separate constant pressure system to provide the defined volume flow for controlling the main valve. Deviations of the pilot volumetric flow due to wear or clogging of the pilot valve ports, however, have an effect on the speed of the main valve and thus on the quality of the time coordination with the drive piston or the gas valve movement.
  • US 4 009 695 A shows, among other things, the construction of a hydraulic valve drive by means of rotary valve control valves.
  • the spool shafts run continuously with camshaft speed (half engine speed) in rotary valve sleeves;
  • the phase angles are adjusted with simple, comparatively slow worm drives in the angular phase, while the fast processes are automatically clocked by means of the rotating slide shaft.
  • the motor can be operated in stationary operating points completely without control intervention; Adjustments are only displayed when changing an operating point. Such simple adjustment mechanisms can be carried out in principle even without control electronics.
  • Unfortunately allows US 4 009 695 A No control of the Gas litventilhubs and does not recognize any possibility of recovery of hydraulically fed energy.
  • the object of the invention is thus to provide a hydraulic drive for accelerating and decelerating dynamically moving components available, in which the above-mentioned disadvantages of the prior art need not be taken into account.
  • the invention solves this problem by means of a hydraulic drive according to claim 1. It is clear that the present invention is particularly applicable to gas exchange controls of internal combustion engines and other piston engines. However, it results from the elements used that the drive according to the invention is quite generally advantageous, ie also in other applications in which highly dynamic masses have to be moved.
  • the invention presented here works - like the other aforementioned "asymmetric pendulum systems” - also with simple, one-sided restoring energy storage or spring means and with the described energy conversions.
  • the control is designed so advantageous that scatters in speed, precision and uniformity of the control valves hardly affect the hydraulic losses of the drive, so that it can be constructed in return of simple and robust elements. Therefore, a true fully variable hydraulic drive system for gas exchange valves or other highly dynamically moving masses is shown, which keeps the own energy consumption minimal and yet simple and reliable.
  • the invention is also well suited for triggering with rotary valves US 4 009 695 A ,
  • the full variability of the opening and closing times of the gas exchange valves is maintained, a stroke control is possible via pressure level and the own energy consumption is minimized due to energy recovery.
  • a gas exchange valve 20 for a motor both for opening and closing by means of a hydraulic drive 10 with a working cylinder 22 and a drive piston 23 and a force acting against the force of the drive piston spring 25 operated.
  • the hydraulic drive 10 may be divided into a core part 11 and a supply part 90 for ease of understanding.
  • the pressure supply for the proposed pressure reservoir in a conventional manner preferably with controllable pumps 91, 92, which can adjust the flow rate to the flow and pressure requirements.
  • the control takes place in this example via pressure sensors 96 and control electronics 97.
  • the control electronics also takes over the control of the actively electrically switching valves 46, 56 and 66.
  • the supply unit also includes a pressure limiting valve 99, which protects the system against overpressure and at the same time, as explained below, ensures that the gas exchange stroke does not reach a critical value.
  • a slightly raised base pressure p 0 was selected, for which reason a small pump 95 from a collecting tank 98 recirculates the leakage quantities of the pressure medium 30 fed into the self-contained system via a leak collecting line 94 from the spring chamber 93.
  • An embodiment of the base pressure reservoir as a normal, ambient-ventilated tank is basically also possible, but the slightly elevated pressure has various advantages. For example, no pressure spring is required to bring the working piston in contact with the gas exchange valve 20. So you have an inherent valve clearance compensation.
  • the hydraulic pressure force here from a first pressure reservoir with the pressure p 1 , via a first 2/2-way valve 46 and a first check valve 47, the drive piston 23 and its Druckwirk Structure 24 of the surface A acted upon .
  • the gas exchange valve 20 begins to open as soon as the hydraulic pressure force p 1 x A exceeds the biasing spring force F Fv of the spring 25.
  • F Fv biasing spring force
  • an effective pressure is set, which is not exactly the Pressure p 1 corresponds. This too can be taken into account by correction values.
  • the spring 25 used as energy storage is designed with a high spring constant c, so that a rapid movement of the mass is achieved.
  • the high spring constant c causes the spring force F F increases markedly with increasing opening stroke h.
  • a desired stroke h max can also be controlled via the magnitude of the pressure p 1 via the magnitude of the force F Fv . So even a stroke control is possible in two ways.
  • the gas exchange valve 20 now remains in its open position, even if the 2/2-way valve has not yet closed. This starts the holding phase (phase II) of the gas exchange valve. Only a minimal backward movement (closing movement) of the gas exchange valve due to the compression of the pressure medium itself - caused mainly by its low compressibility - will be observed. Thus, the gas exchange of the engine can now continue with the desired stroke. As a precaution, it should be noted that any other flow branches or leakage paths must be prohibited or closed on the flow path between the working cylinder 22 and the check valve since these would impair the holding function.
  • FIG. 4 shows three exemplary for the valve opening 49 Cross-sectional curves of the valve opening 49: A 1a , A 1b and A 1c , which are all possible in the embodiment.
  • the opening of the flow cross-section of the switching valve 46 must only take place about as fast as the movement of the gas exchange valve expires. So no expensive and expensive valve principle is needed.
  • the check valve 47 automatically ensures that the kinetic energy of the moving mass is almost completely converted into spring energy and also cached in the spring 25 - which would be achievable both with an active control intervention of valve 46 only at great expense. It should be noted that in this phase in the working cylinder 22 sets a pressure which - is higher than the pressure p 1 - as a result of the overshoot and the stored spring energy - usually
  • Fig. 1 also the closing process of the gas exchange valve 20, phase 3, by means of another part of the hydraulic drive can be seen.
  • the second 2/2-way valve 56 is opened. It should be pointed out to those skilled in the art that this second 2/2-way valve has hitherto been closed (in phases I and II) ( Fig. 4 , Course A 2 ).
  • Valve 56 is connected to a second pressure reservoir 42 with a pressure p 2 , which is generally lower than the pressure p 1 , but higher than p 0 .
  • a hydraulic flow takes place in the pressure reservoir 42, while the drive piston 23 performs the closing movement ( Fig. 4 , Lift diagram, phase III).
  • the hydraulic reflux is terminated, by the second check valve 57, which is of course arranged in the other direction as the first check valve and a return flow from the pressure reservoir 42 into the working cylinder prevented. It thereby causes - similar to the check valve 47 when opening the gas exchange valve - that the gas exchange valve stops in the reached position, and that the 2/2-way valve must be closed later and at any time before the next gas exchange valve opening cycle ( Fig. 4 , A 2a , A 2b ). Above all, this automatism recuperates a maximum of energy.
  • valve 56 Due to the lack of a need for a precise closure, the valve 56 can be easily constructed and the cost of the electronic control is reduced considerably. Also, the control valve 56 may in turn turn comparatively slowly, which can be dispensed with in many cases to elaborate design using eg vortex current-inhibiting magnet special materials. Finally, it should be mentioned that the late closing of the use of rotary vane technology is very accommodating, since a different length of open the cross section is not disturbing.
  • the placement of the gas exchange valve 20 - ie the closing of the "stop" from the valve seat (phase V) - is in the in Fig. 1 illustrated embodiment, in that a third 2/2-way valve 66 opens a flow path from the working cylinder 22 to the base pressure reservoir by means of a connecting line 68 out.
  • a brake throttle 67 In series with this is a brake throttle 67, by means of which the speed of Aufsetzvorgangs can be controlled.
  • the force for the safe closing and placing the gas exchange valve is obtained from the remaining energy of the spring 25, which is designed so that the closing force at the touchdown point, which is equal to the spring biasing force F Fv is greater than the product of the pressure p 0 x A and other opening forces, as described above.
  • the switching time of the third 2/2-way valve 66 determines the residence time in the holding phase near the valve seat (phase IV). Often, in internal combustion engines and other piston engines here no lingering desired; The closing process of a gas exchange valve should be completed quickly. Since the system represents a vibration system, the time duration of phase III (beginning of the closing movement of the gas exchange valve to the stop point) corresponds to approximately half the period T 1/2 of the spring-mass oscillator according to equation 1.
  • the electronic control can now be programmed so that the start of opening of 2/2-way valve 66 by T 1/2 is later than the beginning of opening of the 2/2 way valve 56. In many cases, the person skilled in the art will choose the duration slightly longer in order to be on the safe side with regard to maximum energy recovery.
  • the embodiment according to Fig. 1 can be equipped with a travel-controlled braking device, such as cut-out in FIG. 5 shown.
  • the transitional cross-section can be suitably shaped, for example with a notch-like contouring in the wall of the working cylinder, or as a bore or groove in the drive piston.
  • FIG. 6 is shown in detail how the soft braking can be performed agruatively.
  • the connecting line 68 is divided into two ports 62 and 63, wherein the first port 62 is shut off at the latest in the vicinity of stroke zero, so shortly before placing the gas exchange valve 20 on the valve seat 18 by the control edge 26 of the drive piston 23, so that the Pressure medium only via port 63 and the throttle 64 can flow.
  • This can also be arranged in the working piston.
  • the embodiment according to Fig. 1 advantageous to be performed with rotary valves.
  • the 2/2-way valves 46, 56 and 66 are replaced by one rotary valve each.
  • the adjustment takes place by means of the adjustment of the phase angle. Since, in the control of the flow paths 49 and 59, due to the inventive automatic holding function of the check valves 47 and 57 for each direction of movement in each case mainly arrives only at the opening time, while the closing time may be in a relatively wide range, it plays - at least within a certain limits - No matter if the closing time is also shifted as a result of the phase rotation.
  • the invention allows to build a fully variable and energy-efficient hydraulic gas exchange valve drive with - the internal combustion engine - cycle synchronously running rotary valves.
  • the 4/2-way valve 86 is used. This is suitable for the use of two high-pressure levels.
  • the third valve 66 is arranged in pressure-controlled design 80 in the connecting line 68 between the working cylinder and the base pressure reservoir.
  • the valve 80 uses the effect that the gas exchange valve 20 during the transition from phase III to phase IV similar to the transition from phase I to II springs back slightly, that tries to reopen, whereby in the working cylinder 22, a negative pressure is generated. This opens the pressure-controlled valve 80 and establishes the desired connection to the base pressure reservoir via the throttle 67 integrated in the cross-section 69.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP17172231.7A 2017-05-22 2017-05-22 Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement Withdrawn EP3406866A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP17172231.7A EP3406866A1 (fr) 2017-05-22 2017-05-22 Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement
EP18724261.5A EP3631174A1 (fr) 2017-05-22 2018-05-18 Entraînement hydraulique permettant d'accélérer et de décélérer des composants à déplacer de manière dynamique
US16/615,175 US11156134B2 (en) 2017-05-22 2018-05-18 Hydraulic drive for accelerating and braking dynamically moving components
CN201880033996.2A CN111212961B (zh) 2017-05-22 2018-05-18 用于对动态运动的构件进行加速和制动的液压驱动装置
PCT/EP2018/063075 WO2018215335A1 (fr) 2017-05-22 2018-05-18 Entraînement hydraulique permettant d'accélérer et de décélérer des composants à déplacer de manière dynamique
US17/510,645 US20220042428A1 (en) 2017-05-22 2021-10-26 Hydraulic Drive for Accelerating and Braking Dynamically Moving Components

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17172231.7A EP3406866A1 (fr) 2017-05-22 2017-05-22 Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement

Publications (1)

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EP3406866A1 true EP3406866A1 (fr) 2018-11-28

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EP17172231.7A Withdrawn EP3406866A1 (fr) 2017-05-22 2017-05-22 Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement
EP18724261.5A Pending EP3631174A1 (fr) 2017-05-22 2018-05-18 Entraînement hydraulique permettant d'accélérer et de décélérer des composants à déplacer de manière dynamique

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP18724261.5A Pending EP3631174A1 (fr) 2017-05-22 2018-05-18 Entraînement hydraulique permettant d'accélérer et de décélérer des composants à déplacer de manière dynamique

Country Status (4)

Country Link
US (2) US11156134B2 (fr)
EP (2) EP3406866A1 (fr)
CN (1) CN111212961B (fr)
WO (1) WO2018215335A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
WO2021121639A1 (fr) * 2019-12-20 2021-06-24 Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt Entraînement hydraulique pour des constituants d'accélération et de freinage qui doivent être déplacés de manière dynamique

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CN114396329B (zh) * 2021-12-21 2023-01-03 哈尔滨工程大学 一种实现低速机排气分级分离的缸头分离阀结构

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DE1940177A1 (de) 1968-08-08 1970-02-19 Kaiser Aluminium Chem Corp Verfahren zur Gewinnung von Aluminium
US4009695A (en) 1972-11-14 1977-03-01 Ule Louis A Programmed valve system for internal combustion engine
JPS5872606A (ja) * 1981-10-24 1983-04-30 Hitachi Zosen Corp ピストン制御孔型排気制御装置
DE3836725C1 (fr) 1988-10-28 1989-12-21 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
WO1993001399A1 (fr) 1991-07-12 1993-01-21 Caterpillar Inc. Systeme de soupape de moteur a recuperation et son procede de fonctionnement
US5562070A (en) * 1995-07-05 1996-10-08 Ford Motor Company Electrohydraulic camless valvetrain with rotary hydraulic actuator
DE10024268A1 (de) * 2000-05-17 2001-11-22 Bosch Gmbh Robert Vorrichtung zur Benzindirekteinspritzung in einer Kolbenbrennkraftmaschine
WO2002029216A1 (fr) * 2000-10-05 2002-04-11 Renault Sport Dispositif d'actionnement de soupapes, et procede de commande pour un tel dispositif
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WO2006138368A2 (fr) * 2005-06-16 2006-12-28 Lgd Technology, Llc Actionneur de soupape variable
WO2007138057A1 (fr) * 2006-05-26 2007-12-06 Robert Bosch Gmbh Procédé de commande de l'échange gazeux d'un moteur à combustion interne
JP2009150296A (ja) * 2007-12-20 2009-07-09 The Ship Machinery Manufacturers Association Of Japan 吸排気弁駆動装置
WO2014179906A1 (fr) * 2013-05-07 2014-11-13 江苏公大动力技术有限公司 Commande à levée variable

Cited By (1)

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WO2021121639A1 (fr) * 2019-12-20 2021-06-24 Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt Entraînement hydraulique pour des constituants d'accélération et de freinage qui doivent être déplacés de manière dynamique

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WO2018215335A1 (fr) 2018-11-29
US20210003045A1 (en) 2021-01-07
CN111212961A (zh) 2020-05-29
EP3631174A1 (fr) 2020-04-08
US20220042428A1 (en) 2022-02-10
US11156134B2 (en) 2021-10-26

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