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.
• 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.
• compressed air which is regulated by pressure regulating means at low pressure level, in the
• Motor brake control cylinder introduced to move the inner piston only against the internal compression spring and stop where a slider is brought into contact with a spring support surface. In this position, the connected engine brake valve is closed, so that only a part of the exhaust gas can pass through this.
• Compression springs due to regulated at a high pressure level compressed air and stops at a position where a guard comes into contact with the slider to fully close the connected engine brake valve.
• 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 back 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. It is therefore an object of the present invention to provide means for generating a springback between the piston rod of the control cylinder and the engine brake valve, which consist of a few individual parts and are designed small-sized.
• the object is based on a control cylinder according to the preamble of
• the invention includes the technical teaching that special means for generating the
• compositions according to the invention for generating the springback can according to
• the elastic spacers are dimensioned so that the relative movement between piston rod and piston only at undesirably high pressure, i. If too much force of the throttle valve is created. This relative movement between piston rod and piston allows for a limited travel
• 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 by way of a pressure limiting valve in order to prevent the
• 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.
• 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 according to another measure improving the invention are sealed with a seal, wherein in the cylinder cover an outwardly leading check valve is arranged to pressure from the spring chamber to the
• 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.
• Figure 1 is a schematic representation of a turbocharger arrangement of a
• FIG. 2 is a perspective view of throttle means of the
• 3 a to 3c show a first embodiment of the means for generating the springback within a control cylinder at different positions of the piston rod
• Figure 4 shows a further embodiment of the means for generating the
• Figure 5 shows a third embodiment of the means for generating the
• Figure 6 shows a modification of the embodiment of Figure 5 with respect to valve technology, which cooperate with the means for generating the springback, and
• FIG. 7 shows a further modification of an embodiment according to FIG. 5
• 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 a rotation of the drive shaft 5 to the
• 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.
• Rotational movement for actuating the engine brake valve 11 is connected.
• 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 control cylinder 12 comprises a cylindrical housing 13 for accommodating a piston 14 with the piston rod 15 therefrom.
• 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 a Operating force by the piston 14 by compressed air.
• the throttle valve of the engine brake valve arranged therein is loaded by the pressure with a torque in the opening direction and the piston rod 15 is loaded with an increased restoring axial force. If this axial force is greater than the force of
• 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 means for generating the springback arranged between the piston 14 and the piston rod 15 comprise one
• Compressed air spring which consists of a piston rod 15 attached to the end of 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 return opening force of 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 an actuation pressure is secured via a pressure limiting valve 29.
• the pressure relief valve 29 can a sufficient pressure
• the pressure limiting valve 29 serves to ventilate the cylindrical pressure
• Working space 26 of the air spring and is arranged in the piston 14 of the control cylinder 12 '.
• the pressure relief valve 29 is adjusted so that in the working space 26 a
• Actuating pressure is ensured, 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 provides e.g. a check valve with an elevated
• Drain 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 relative 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, 6bar -.
• 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)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (1)

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ID=46319757

Family Applications (1)

Country Status (6)

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Citations (5)

Family Cites Families (3)

• 2011
  • 2011-06-17 DE DE102011106629A patent/DE102011106629A1/de not_active Ceased
• 2012
  • 2012-06-15 WO PCT/EP2012/061456 patent/WO2012172056A1/de active Application Filing
  • 2012-06-15 RU RU2014101356/06A patent/RU2597738C2/ru active
  • 2012-06-15 BR BR112013032371-0A patent/BR112013032371B1/pt active IP Right Grant
  • 2012-06-15 CN CN201280029680.9A patent/CN103620189B/zh active Active
  • 2012-06-15 EP EP12728255.6A patent/EP2721274B1/de active Active

Patent Citations (5)

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