EP2721274B1 - Cylindre de commande pour un frein de moteur comprenant des moyens pour générer un retour élastique - Google Patents

Cylindre de commande pour un frein de moteur comprenant des moyens pour générer un retour élastique Download PDF

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Publication number
EP2721274B1
EP2721274B1 EP12728255.6A EP12728255A EP2721274B1 EP 2721274 B1 EP2721274 B1 EP 2721274B1 EP 12728255 A EP12728255 A EP 12728255A EP 2721274 B1 EP2721274 B1 EP 2721274B1
Authority
EP
European Patent Office
Prior art keywords
piston
spring
control cylinder
pressure
valve
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.)
Active
Application number
EP12728255.6A
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German (de)
English (en)
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EP2721274A1 (fr
Inventor
Andras Voith
Janos Toth
Attila Mihalyi
Kornel Kantor
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Publication date
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Publication of EP2721274A1 publication Critical patent/EP2721274A1/fr
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Publication of EP2721274B1 publication Critical patent/EP2721274B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/226—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having elastic elements, e.g. springs, rubber pads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/04—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning exhaust conduits
    • F02D9/06—Exhaust brakes
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/148—Lost-motion means between the piston and the output

Definitions

  • the invention relates to a control cylinder for an engine brake for generating a deceleration function by throttling the exhaust gas flow outlet side of a turbocharger in a vehicle engine, comprising a cylindrical housing for housing a piston with piston rod, which the cylindrical housing in a spring chamber for accommodating a return spring for the piston rod and a Pressure chamber for generating an actuating force for the piston divided by compressed air, wherein the piston cooperates with means for generating a springback.
  • Pneumatic cylinders of this type are used, for example, in commercial vehicle technology to actuate valves arranged on the outlet side of a turbocharger of diesel engines.
  • the engine brake control cylinder generates a linear closing and opening force for an operating lever of the valve that is inserted into the exhaust gas exhaust passage of the turbocharger.
  • the control cylinder of the engine brake generates the closing force for the valve by compressed air provided by the vehicle.
  • the return spring and exhaust back pressure defines the opening force for the valve.
  • the publication JP 08261021 A discloses a control cylinder for an engine brake, which is designed as a single-acting pneumatic cylinder of the type described above.
  • a warm-up switch in which a warm-up switch is turned on, compressed air regulated by pressure regulating means at a low pressure level is introduced into the control cylinder of the engine brake to move the inner piston only against the internal compression spring and stop where a slider comes in contact is brought with a spring support surface.
  • the connected engine brake valve is closed, so that only a part of the exhaust gas can pass through this.
  • an intermediate element with a prestressed spring and axial return spring means is used in the power flow between the piston rod of the control cylinder and a lever actuating the engine brake valve.
  • the intermediate element allows a limited return opening of a throttle valve of the engine brake valve by way of a limited springback at undesirably high pressure in the exhaust pipe.
  • this additional intermediate element requires a correspondingly large installation space and increased parts and assembly costs.
  • the control cylinder comprises a cylindrical housing for accommodating a piston with a piston rod.
  • the piston divides the housing into a spring chamber for accommodating a spring for the piston rod, and a pressure chamber for generating an actuating force by the piston by means of compressed air.
  • the piston rod is guided longitudinally displaceable relative to the piston.
  • a balancing device is housed in the control cylinder, and disposed between the movable piston and the rod of the piston.
  • the balancing device comprises a biased spring disposed within the cylindrical housing, which acts on the one hand on the piston rod and on the other hand on the piston.
  • WO 2009/103561 A1 an exhaust gas control system having an exhaust throttle valve in an exhaust passage, an actuator of the exhaust throttle valve with an actuating linkage and an exhaust pressure control device of the exhaust gas pressure occurring upstream of the exhaust throttle valve in the exhaust passage.
  • the actuating linkage has a Regelaktuatorik which cooperates with a pressure compensation volume, wherein the pressure compensation volume is pneumatically connected to a throttle opening upstream of the exhaust throttle valve.
  • the EP 0 872 646 A1 discloses a compressed air cylinder for actuating the exhaust flap of an engine brake, the first end face is fixed and pivotally mounted. Furthermore, a piston rod of a piston displaceable in a cylinder housing exits from its opposite second end face. The piston rod is connected to an actuating mechanism, preferably an axis of an exhaust flap of an engine brake via a flap lever. An outer channel is provided for supplying and discharging compressed air, wherein this via a connecting channel with the cylinder housing connected is. A retainer is provided for the piston in the retracted position and a retraction means is provided for the piston from the extended to the retracted position.
  • the retractor consists of a pressure chamber, with a feed channel and a discharge channel having an inlet valve and a discharge valve, respectively, which communicate with the outer channel.
  • the pressure chamber can be filled via the supply channel and the inlet valve simultaneously with the cylinder housing with compressed air. Further, the pressure chamber after the pressure relief of the cylinder housing on the outer end face of the piston exert pressure such that it is pressed in retracted position.
  • the invention includes the technical teaching that special means for generating the springback within the cylindrical housing of the control cylinder are arranged.
  • the inventive means for generating the springback can be realized according to different - described in detail below - embodiments, in principle, the function of the aforementioned intermediate element is realized within the control cylinder, in which a mutually relative movement of the piston rod and the piston takes place and between the two components elastic spacers are formed of different types.
  • the elastic spacers are dimensioned so that the relative movement between piston rod and piston arises only at undesirably high pressure, ie at too high a force of the throttle.
  • This relative movement between the piston rod and piston allows for a limited travel rear opening of the throttle valve, whereby the pressure in the exhaust pipe is reduced so far that the engine braking effect is still sufficient, but the reduced pressure can no longer lead to engine damage.
  • the means for generating the springback comprise a prestressed spring arranged within the cylindrical housing, which acts on the one hand on the piston rod and on the other hand on the piston.
  • the spring may be formed as a compression spring made of spring steel, which is coupled via a mounted on the piston rod disc side of the piston rod. On the other side, the spring can come coaxially on the piston end face to the plant.
  • the spring travel of the spring is adjustable by means of an adjusting screw acting thereon.
  • the piston rod should be longitudinally slidably guided relative to the piston, for example, be plugged end into a corresponding coaxial recess of the piston.
  • the means for generating the springback comprise a compressed air spring housed within the cylindrical housing, which acts on the one hand on the piston rod and on the other hand on the piston.
  • a pneumatic spring for example, consist of a piston integrated in the cylindrical working space, which cooperates with a piston arranged therein, on which the piston rod is mounted.
  • the cylindrical working space can be ventilated via a pressure limiting valve in order to maintain the return opening force of a throttle valve provided for engine braking at a constant tolerance range for all actual actuating pressures.
  • cylindrical working space can also be connected via a discharge valve to the environment in order to limit the pressure in the working space to a maximum value.
  • the control cylinder according to the invention should be protected on the part of the spring chamber against contamination to a long service life, in particular the above-described Valve technology, to ensure.
  • the piston rod relative to the cylinder cover of the cylindrical housing can be sealed with a seal according to another measure improving the invention, wherein in the cylinder cover an outwardly leading check valve is arranged to dissipate excess pressure from the spring chamber to the environment.
  • a refill valve can be integrated, which is arranged between the spring chamber and the pressure chamber. The refill valve prevents low pressure in the spring chamber, which would cause, inter alia, a suction effect for impurities from the outside.
  • a vehicle engine 1 is equipped with a turbocharger 2.
  • the turbocharger 2 comprises a turbine part 3, which is mechanically connected to a compressor part 4 via an intermediate drive shaft 5.
  • the exhaust gas from the vehicle engine 1 is passed through an exhaust pipe 6 to the turbine part 3 of the turbocharger 2 via an inlet 7.
  • the exhaust gas flow causes rotation of the drive shaft 5 to drive the compressor part 4.
  • the compressor part 4 sucks fresh air from the atmosphere through an air inlet 8 in order to make it available to the vehicle engine 1 via an inlet pipe 9 on the air inlet side.
  • engine braking means are arranged in the region of an exhaust gas outlet 10 of the turbocharger 2, which comprises an exhaust gas brake valve 11, which is designed in the manner of a flap valve.
  • the exhaust brake valve 11 is controlled by a control cylinder 12 of the engine brake actuated to bring about a deceleration function by throttling the exhaust gas flow on the exhaust side of the turbocharger 2 in the region of the exhaust gas outlet 10.
  • the engine brake valve 11 is connected in the exhaust outlet 10 by a lever for implementing the linear movement of the control cylinder 12 of the engine brake in a rotational movement for actuating the engine brake valve 11.
  • the control cylinder 12 of the engine brake is pivotally mounted on a support frame, which is arranged to one end of the control cylinder 12 of the engine brake.
  • the piston 14 divides the housing 13 into a spring chamber 16 for accommodating a return spring 17 for the piston rod 15 and a pressure chamber 18 for generating an actuating force by the piston 14 by compressed air.
  • the piston 14 moves from the illustrated basic position together with the displaceable piston rod 15 up to the full stroke, as in FIG. 3b shown.
  • the relative position of the piston rod 15 to the piston 14 is determined by a spring housing 20, attached to the piston rod 15 disc 21 and by a prestressed spring 22.
  • the spring travel of the means for generating the springback via an adjusting screw 23 is adjustable.
  • the adjusting screw 23 is screwed on the front side of the piston rod 15.
  • the head of the adjusting screw 23 forms an end stop with a shoulder formed on the piston 14 within a coaxial recess.
  • the adjusting screw 23 is to be adjusted during assembly of the control cylinder 13 and should be secured with adhesive or the like.
  • the required by screwing the adjusting screw 23 in the piston 14 mounting hole is closed with a sealing washer 24.
  • the other embodiment shown arranged between the piston 14 and the piston rod 15 means for generating the springback comprises a pneumatic spring which consists of a piston rod 15 fixed to the piston 25 and a side of the piston 14 of the control cylinder 12 'cylindrical working space 26.
  • the working space 26 is in pneumatic communication with the pressure chamber 18 of the control cylinder 12 'through an opening 27 in a disk 28 which is firmly inserted in the piston 14.
  • On the working surfaces of the piston 14 and the inner piston 25 thus acts the same within the pressure chamber 18 applied pressure.
  • the diameter of the piston 14 is to be dimensioned so that the force exerted by pressurization force is greater than the spring force of the return spring 17 and the actuating force of the - not shown here - throttle valve of the engine brake valve.
  • the diameter of the inner piston 25 is to be dimensioned such that the force exerted due to pressurization is equal to the remindöffhungskraft the throttle valve of the engine brake valve.
  • the operating pressure of the control piston 12 In order to keep the return force of the piston rod 15 to almost constant value, the operating pressure of the control piston 12 'must be kept within narrow limits. Since the Actuating pressure between cut-in pressure and cut-off pressure of the air supply system can change, even in special cases can fall to a backup pressure, it is advantageous if the actuation pressure is below the operating pressure range.
  • Such actuation pressure is secured via a pressure relief valve 29.
  • the pressure limiting valve 29 serves to ventilate the cylindrical working space 26 of the pneumatic spring and is arranged in the piston 14 of the control cylinder 12 '.
  • the pressure relief valve 29 is adjusted so that an operating pressure is ensured in the working space 26, which is below the real operating pressures.
  • the cylindrical working space 26 is connected via a built-in piston 25 in the discharge valve 30 with the environment to limit the pressure in the working space 26 to a maximum value.
  • the drain valve 30 represents, for example, a check valve with an increased opening pressure to drain the excess pressure from the working space 26 of the air spring in the spring chamber 16. In this case, the diameter of the working space 26 must be dimensioned so that the desired rearward opening force of the throttle valve is not exceeded at the opening pressure of the blow-off valve 30.
  • the piston rod 15 is sealed with respect to a cylinder cover 31 of the cylindrical housing 13 with a seal 32.
  • an outwardly leading check valve 33 is arranged to remove excess pressure from the spring chamber 16 to the environment. As a result, the spring chamber 16 is protected against contamination from the outside.
  • a refill valve 34 is further integrated, which is arranged between the spring chamber 16 and the pressure chamber 18.
  • the refill valve 34 is the Working chamber 18 is only connected to the spring chamber 16 when the pressure difference is below a limit - for example, 1.6 bar -.
  • the refill valve 34 may be performed by the valve body as Elastomerbauteil.
  • the refill valve 34 prevents dirt from being sucked into the spring chamber 16 from the outside, since during return movement of the piston 14 the spring chamber volume becomes larger, which leads to a low pressure below the atmospheric pressure in the spring chamber 16. The low pressure prevents the return movement of the piston 14 and a suction effect, whereby dirt can be sucked from the outside. This is no longer to be feared due to the pressure compensation brought about by the refill valve 34.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Supercharger (AREA)
  • Safety Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Actuator (AREA)

Claims (6)

  1. Cylindre (12) de commande d'un frein moteur pour procurer une fonction de décélération par étranglement du courant de gaz d'échappement du côté de la sortie d'un turbocompresseur (2), d'un moteur (1) de véhicule, comprenant une enveloppe (13) cylindrique pour loger un piston (14) ayant une tige (15) de piston, afin de subdiviser l'enveloppe (13) en
    - une chambre (16) de ressort pour loger un ressort (17) pour la tige (15) du piston et
    - une chambre (18) sous pression pour produire une force d'actionnement par le piston (14) par de l'air comprimé, dans lequel
    - le piston (14) coopère avec des moyens de production d'un retour élastique, la tige (15) de piston étant guidée de manière à pouvoir coulisser longitudinalement par rapport au piston (14),
    caractérisé en ce que les moyens de production du retour élastique comprennent un ressort à air comprimé, qui est logé dans l'enveloppe (13) cylindrique et qui agit d'une part sur la tige (15) du piston et d'autre part sur le piston (14).
  2. Cylindre de commande suivant la revendication 1,
    caractérisé en ce que le ressort à air comprimé est constitué d'une chambre (26) de travail cylindrique, qui est intégrée au piston (14) et qui coopère avec un piston (25), qui y est disposé et sur lequel la tige (15) de piston est montée.
  3. Cylindre de commande suivant la revendication 2,
    caractérisé en ce que l'espace (26) de travail cylindrique peut être alimenté en air par une soupape (29) de limitation de la pression, afin de maintenir, dans une plage de tolérance constante à toutes les pressions réelles d'actionnement, la force d'ouverture de rappel d'un volet (11) d'étranglement prévu pour le freinage-moteur.
  4. Cylindre de commande suivant la revendication 3,
    caractérisé en ce que la chambre (26) de travail cylindrique communique avec l'atmosphère ambiante par une soupape (30) de décharge, afin de limiter à une valeur maximum la pression dans la chambre (26) de travail.
  5. Cylindre de commande suivant la revendication 1,
    caractérisé en ce que la tige (15) de piston est rendue étanche, par rapport à un couvercle (31) de cylindre de l'enveloppe (13) cylindrique, par un joint (32), dans lequel un clapet anti-retour (13), conduisant vers l'extérieur, est monté dans le couvercle (31) de cylindre pour évacuer une surpression de la chambre (16) de ressort à l'atmosphère.
  6. Cylindre de commande suivant la revendication 1,
    caractérisé en ce que, dans le piston (14), est intégrée une soupape (34) de post-remplissage, qui est montée entre la chambre (16) de ressort et la chambre (18) sous pression.
EP12728255.6A 2011-06-17 2012-06-15 Cylindre de commande pour un frein de moteur comprenant des moyens pour générer un retour élastique Active EP2721274B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011106629A DE102011106629A1 (de) 2011-06-17 2011-06-17 Steuerzylinder für eine Motorbremse mit Mitteln zur Erzeugung einer Rückfederung
PCT/EP2012/061456 WO2012172056A1 (fr) 2011-06-17 2012-06-15 Cylindre de commande pour un frein de moteur comprenant des moyens pour générer un retour élastique

Publications (2)

Publication Number Publication Date
EP2721274A1 EP2721274A1 (fr) 2014-04-23
EP2721274B1 true EP2721274B1 (fr) 2018-05-02

Family

ID=46319757

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12728255.6A Active EP2721274B1 (fr) 2011-06-17 2012-06-15 Cylindre de commande pour un frein de moteur comprenant des moyens pour générer un retour élastique

Country Status (6)

Country Link
EP (1) EP2721274B1 (fr)
CN (1) CN103620189B (fr)
BR (1) BR112013032371B1 (fr)
DE (1) DE102011106629A1 (fr)
RU (1) RU2597738C2 (fr)
WO (1) WO2012172056A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105757050B (zh) * 2016-05-01 2018-01-05 张述成 具有缓冲制动功能的储能式阀缸结构
US10364912B2 (en) 2016-08-15 2019-07-30 Emerson Process Management Valve Automation, Inc. Thermal volume control for an actuator assembly

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1116823A (fr) * 1953-11-28 1956-05-14 Installation de freinage au moteur mise automatiquement en et hors d'action, applicable aux véhicules comportant un moteur à combustion interne
JPH03237230A (ja) * 1990-02-14 1991-10-23 Toyota Motor Corp ディーゼル機関の排気ブレーキ装置
JP2816460B2 (ja) * 1992-07-31 1998-10-27 三菱自動車工業株式会社 自動車のブレ−キ装置
JPH08261021A (ja) 1995-03-24 1996-10-08 Jidosha Kiki Co Ltd 排気ブレーキ装置用シリンダ
DE19716564A1 (de) * 1997-04-19 1998-10-22 Technomatik Maschinenelemente Druckluftzylinder
FR2777945B1 (fr) * 1998-04-22 2000-06-16 Fowa Dispositif ralentiseur monte dans le circuit d'echappement des gaz d'un vehicule equipe d'un moteur a combustion
EP1404952B1 (fr) * 2001-06-26 2007-06-13 Volvo Lastvagnar AB Appareil de turbine d'echappement
DE102008010658B4 (de) * 2008-02-22 2010-08-19 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Abgasregelsystem und Abgasregelverfahren

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2012172056A1 (fr) 2012-12-20
RU2597738C2 (ru) 2016-09-20
CN103620189B (zh) 2016-03-30
DE102011106629A1 (de) 2012-12-20
EP2721274A1 (fr) 2014-04-23
CN103620189A (zh) 2014-03-05
BR112013032371B1 (pt) 2021-04-20
RU2014101356A (ru) 2015-07-27

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