WO2016060605A1 - Combustion engine as well as method for engine braking using such a combustion engine - Google Patents

Combustion engine as well as method for engine braking using such a combustion engine Download PDF

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Publication number
WO2016060605A1
WO2016060605A1 PCT/SE2015/051083 SE2015051083W WO2016060605A1 WO 2016060605 A1 WO2016060605 A1 WO 2016060605A1 SE 2015051083 W SE2015051083 W SE 2015051083W WO 2016060605 A1 WO2016060605 A1 WO 2016060605A1
Authority
WO
WIPO (PCT)
Prior art keywords
dead centre
storage reservoir
air channel
cylinder volume
piston
Prior art date
Application number
PCT/SE2015/051083
Other languages
French (fr)
Inventor
Anders HÖGLUND
Urban Carlson
Original Assignee
Freevalve Ab
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 Freevalve Ab filed Critical Freevalve Ab
Priority to RU2017116521A priority Critical patent/RU2017116521A/en
Priority to KR1020177012856A priority patent/KR20170066640A/en
Priority to BR112017007539A priority patent/BR112017007539A2/en
Priority to US15/518,304 priority patent/US10344683B2/en
Priority to CN201580055738.0A priority patent/CN107076036B/en
Priority to EP15850606.3A priority patent/EP3207236B1/en
Priority to JP2017520896A priority patent/JP2017534796A/en
Publication of WO2016060605A1 publication Critical patent/WO2016060605A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/04—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation using engine as brake
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B21/00—Engines characterised by air-storage chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B21/00—Engines characterised by air-storage chambers
    • F02B21/02—Chamber shapes or constructions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0203—Variable control of intake and exhaust valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0276—Actuation of an additional valve for a special application, e.g. for decompression, exhaust gas recirculation or cylinder scavenging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/028—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation for two-stroke 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0253—Fully variable control of valve lift and timing using camless actuation systems such as hydraulic, pneumatic or electromagnetic actuators, e.g. solenoid valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0257—Independent control of two or more intake or exhaust valves respectively, i.e. one of two intake valves remains closed or is opened partially while the other is fully opened
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/02—Cutting-out
    • F02D17/023—Cutting-out the inactive cylinders acting as compressor other than for pumping air into the exhaust system

Definitions

  • COMBUSTION ENGINE AS WELL AS METHOD FOR ENGINE BRAKING USING SUCH A COMBUSTION ENGINE
  • the present invention relates in general to a
  • combustion engine as well as a method for engine braking using such a combustion engine, typically being arranged in a so-called heavy vehicle.
  • the combustion engines concerned are above all camshaft free piston engines, which are also known under the term " “engines having free valves”.
  • the present invention relates specifically to a method for engine braking in a combustion engine comprising at least one cylinder having a cylinder volume and a piston
  • an intake air channel having a first pressure PI
  • a first inlet valve arranged between the intake air channel and the cylinder volume
  • an exhaust air channel having a second pressure P2
  • a first outlet valve arranged between the cylinder volume and the exhaust air channel
  • a storage reservoir having a third pressure P3 that is higher than said first pressure PI and said second pressure P2, the storage reservoir being arranged in controllable fluid communication with the cylinder volume.
  • engine braking is realized by closing the exhaust air channel/exhaust gas channel by means of a valve, whereby the combustion engine continues to operate in four-stroke cycle, and when the outlet valves of the cylinder are opened, in order to evacuate exhaust gases during normal operation, a back pressure is generated downstream the cylinder. The back pressure is used to counteract the displacement of the piston from the lower dead centre to the upper dead centre when the outlet valves are open.
  • this engine braking effect only
  • Engine braking according to conventional type entail that the combustion engine must have engine valve springs having high permanent spring force, which is not a problem in connection with conventional camshaft actuated engine valves since the high spring force is recovered on the back side of the cam, however it is devastating for an engine valve control without force recovery.
  • US 7,946,269 to Gerum disclose a combustion engine comprising a cylinder having a cylinder volume and a piston displaceable in said cylinder volume, and a storage volume that is arranged in controllable fluid communication with the cylinder volume via the inlet valves of the cylinders.
  • the combustion engine is driven in four-stroke cycle during the engine braking and when the piston is displaced from the upper dead centre to the lower dead centre and the inlet valves are open, the fluid communication between the storage volume and the cylinder volume is opened. I.e. air having high pressure is provided during the intake stroke,
  • a primary object of the present invention is to provide an improved engine braking method of the initially defined type, which generates at least as high engine braking effect as the drive effect of the combustion engine during four-stroke cycle operation.
  • Another object of the present invention is to provide an engine braking method that prevents unwanted/harmful heating of the components of the combustion engine during engine breaking.
  • Yet another object of the present invention is to provide an engine braking method that allows the size of the engine valve springs of the combustion engine to be reduced, resulting in reduced energy consumption during normal operation.
  • a method of the initially defined type which is characterized by taking place during two-stroke cycle and comprises the steps of displacing the piston from the upper dead centre towards the lower dead centre, keeping the first inlet valve open during at least a part of the time the piston is displaced from the upper dead centre to the lower dead centre, opening the fluid communication between the storage reservoir and the cylinder volume, in connection with the piston being located at the lower dead centre and when the first inlet valve is closed, displace the piston from the lower dead centre towards the upper dead centre, and keeping the fluid communication between the storage reservoir and the cylinder volume open during at least a part of the time the piston is displaced from the lower dead centre to the upper dead centre.
  • a combustion engine that is configured to be driven in accordance with the above mentioned method.
  • the present invention is based on the
  • the present invention also entails that air having high pressure is provided into the cylinder volume at an early stage during the compression stroke of the two-stroke cycle, and thereby generating a great contribution to the engine braking effect.
  • the storage reservoir is connected to the exhaust air channel via a controllable valve, the method comprising the step of ventilating the cylinder volume by means of a short opening of the first outlet valve, in connection with the piston being located at the upper dead centre and when the fluid communication between the storage reservoir and the cylinder volume is closed.
  • Fig. 1 is a schematic cross sectional view of a part of a combustion engine
  • Fig. 2 is a schematic illustration of a combustion engine according to the overall inventive concept
  • Fig. 3 is a schematic illustration of a P/V-diagram for a break cycle
  • Fig. 4 is a schematic illustration of the combustion engine according to a first alternative of a first embodiment
  • Fig. 5 is a schematic illustration of the combustion
  • Fig. 6 is a schematic illustration of the combustion
  • Fig. 7 is a schematic illustration of the combustion
  • Fig. 8 is a schematic illustration of the combustion
  • Fig. 9 is a schematic illustration of the combustion
  • Fig. 10 is a schematic illustration of the combustion
  • FIG. 1 a combustion engine, generally designated 1, as well as to a method for engine braking in such a combustion engine 1. It shall be pointed out that energy recovery is not central, nor desirable, in applications in which the inventive combustion engine 1 and method are intended to be used, on the contrary it is instead central to maximize the energy consumptio .
  • the combustion engine 1 comprises a cylinder block having at least one cylinder 2. Usually said cylinder block comprises three or four cylinders 2. In the disclosed embodiment one cylinder 2 is described, however it shall be realized that the equipment described herein below in connection with the disclosed cylinder 2 is preferably applied to all cylinders of the combustion engine 1, in the case the combustion engine comprises a plurality of
  • the combustion engine 1 is preferably a diesel engine in a vehicle, such as a bus or a truck.
  • the combustion engine 1 comprises a piston 3 axially displaceable in said cylinder 2.
  • the movement of the piston 3, axial displacement back and forth, is transmitted in a conventional way to a piston rod 4 connected to the piston 3, the piston rod 4 in its turn being connected to and drives a crankshaft (not disclosed) in rotation.
  • the combustion engine 1 also comprises a cylinder head 5 that together with said cylinder 2 and said piston 3 delimits a cylinder volume 6, or combustion chamber.
  • ignition of a mixture of fuel and air takes place in a conventional way during normal operation of the combustion engine, and is not described more herein.
  • the combustion engine 1 is preferably driven in four-stroke cycle operation, but it shall be realized that also two-stroke cycle operation is possible.
  • the combustion engine 1 further comprises a first inlet valve 7 and a first outlet valve 8, which preferably are constituted by traditional gas exchange valves.
  • Said first inlet valve 7 is an intake air valve that is configured to optionally open/close the supply of air to the combustion chamber 6 during normal operation.
  • the first outlet valve 8 is an exhaust air valve, or exhaust gas valve, that is configured to optionally open/close for evacuation of
  • the first inlet valve 7 is arranged between the cylinder volume 6 and an intake air channel 9, in which there is a first pressure PI.
  • the first outlet valve 8 is arranged between the cylinder volume 6 and an exhaust air channel 10, in which there is a second pressure P2.
  • first pressure PI and the second pressure P2 is preferably in the range 1-5 bar absolute.
  • the combustion engine 1 further comprises a storage reservoir 11, in which there is a third pressure P3.
  • the third pressure P3 is strictly greater than each of the first pressure PI and the second pressure P2, and is preferably in the range 15-20 bar absolute.
  • the storage reservoir 11 is arranged for controllable fluid communication with the cylinder volume 6. In the embodiment according to figure 2 the storage reservoir 11 is connected to the cylinder volume 6 via a controllable storage reservoir valve 12.
  • the combustion engine 1 comprises a valve actuator 13 that is operatively connected to said first inlet valve 7. Only the valve actuator 13 that is connected to the first inlet valve 7 will be described herein, however it shall be realized that also the first outlet valve 8, and other possible inlet valves and outlet valves, is operatively connected to such a valve actuator.
  • the disclosed, preferred valve actuator 13 comprises at least one inlet opening 14 for pressure fluid and at least one outlet opening 15 for pressure fluid.
  • the pressure fluid is a gas or gas mixture, preferably air or nitrogen. Air has the advantage that it is easy to exchange the pressure fluid or add more pressure fluid if the pressure fluid leak, and nitrogen has the advantage that it is free from oxygen and thereby prevents oxidation of other components. It shall be pointed out that also other types of valve actuators are conceivable.
  • each valve actuator can be operatively connected to one or more gas exchange valves, for instance the combustion engine 1 may comprise two inlet valves which are jointly driven by one and the same valve actuator 13. However it is preferred that each valve actuator drive one gas exchange valve each in order to obtain best possible controllability of the operation of the combustion engine 1.
  • the disclosed valve actuator 13 comprises an actuator piston disc 16 and an actuator cylinder 17 delimiting a cylinder volume.
  • the actuator piston disc 16 separate said cylinder volume in an upper part 18 and a lower part 19 and is axially displaceabie in said actuator cylinder 17.
  • the actuator piston disc 16 form part of an actuator piston or pusher, generally designated 20, that is configured to abut and drive the first inlet valve 7.
  • the valve actuator 13 comprises a controllable inlet valve 21 that is arranged to open/close the inlet opening 14, a controllable outlet valve 22 that is arranged to open/close the outlet opening 15, a hydraulic circuit, generally designated 23, that in its turn comprises a check valve 24 arranged to allow filling of hydraulic circuit 23 and a controllable emptying valve 25 arranged to control the emptying of the hydraulic circuit 23. It shall be pointed out that the valves disclosed in this document are
  • valves may for instance be constituted by slide valves, seat valves, etc.
  • controllable valves may be constituted by a single body.
  • Each valve may be directly or indirectly electrically controlled.
  • electrically controlled is meant that the position of the valve is directly controlled by for instance an electro magnet device, and by indirectly electrically controlled is meant that the position of the valve is controlled by a pressure fluid that in its turn is controlled by for instance an electromagnetic device.
  • the inlet valve 21 is open to allow filling of pressure fluid having high pressure into the upper part 18 of the cylinder volume.
  • the check valve 24 of the hydraulic circuit 23 is opened, whereupon hydraulic liquid is sucked in and replace the volume that the actuator piston 20 leave.
  • the inlet valve 21 is closed and the pressure fluid that has entered the upper part 18 of the cylinder volume is allowed to expand whereupon the actuator piston disc 16 continues its movement downwards.
  • the pressure fluid in the upper part 18 of the cylinder volume does not manage to displace the actuator piston disc 16 any more, i.e.
  • the actuator piston disc 16 stop.
  • the actuator piston disc 16 is kept (locked) in the lower position a required time by holding the emptying valve 25 of the hydraulic circuit 23 closed at the same time as the check valve 24 of the hydraulic circuit 23 is automatically closed.
  • the outlet valve 22 is opened in order to allow evacuation of pressure fluid from the upper part 18 of the cylinder volume, and thereto the emptying valve 25 of the hydraulic circuit 23 is opened whereupon the actuator piston disc 16 is displaced upwards when the hydraulic liquid is evacuated from the hydraulic circuit 23, and at the same time the pressure fluid is evacuated from the upper part 18 of the cylinder volume via the outlet opening 15.
  • the combustion engine 1 comprises a turbine
  • the turbine 27 is preferably part of a conventional super charger unit. It shall be pointed out that in this document the intake air channel 9 extend to the first inlet valve 7 in the direction from the air compressor 28, and the exhaust air channel 10 extend from the first outlet valve 8 in the direction towards the turbine 27.
  • combustion engine 1 is driven in two-stroke cycle
  • FIG 3 is shown a schematic illustration of a braking cycle in a so-called P/V-diagram, wherein P stands for existing pressure in the cylinder volume 6 and V stands for existing volume of the cylinder volume 6 by indicating the location of the piston 3 between the upper dead centre UDC and lower dead centre LDC.
  • the method comprises the steps of displacing the piston 3 from the upper dead centre UDC towards the lower dead centre LDC, keeping the first inlet valve 7 open during at least a part of the time the piston 3 is displaced from the upper dead centre to the lower dead centre, displacing the piston 3 from the lower dead centre towards the upper dead centre, and keeping the fluid communication between the storage reservoir 11 and the cylinder volume 6 open during at least a part of the time the piston 3 is displaced from the lower dead centre to the upper dead centre.
  • the third pressure P3 exist in the cylinder volume 6, acting braking to the piston 3 when it is displaced in the direction from the lower dead centre to the upper dead centre.
  • the first inlet valve 7 When the first inlet valve 7 is open the existing pressure in the cylinder volume 6 is equal to the first pressure PI, and the cylinder volume 6 is ventilated.
  • the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the storage reservoir valve 12.
  • the method comprises the step of opening the fluid communication between the storage reservoir 11 and the cylinder volume 6, in connection with the piston 3 being located at the lower dead centre and when the first inlet valve 7 is closed.
  • This entail that the third pressure P3 starts to act against the piston 3 as early as possible during the compression stroke.
  • the method comprises the step of securing that the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed, in connection with the piston 3 being located in the upper dead centre, in order not to provide the third pressure P3 from the storage reservoir 11 to the cylinder volume 6 during the piston being displaced from the upper dead centre to the lower dead centre.
  • the fluid communication between the storage reservoir 11 and the cylinder volume 6 is open during the entire displacement of the piston 3 from the lower dead centre to the upper dead centre. This result in that the third pressure P3 exists in the cylinder volume 6 during the entire compression stroke, which provide good engine braking effect (according to figure 3) .
  • the fluid communication between the storage reservoir 11 and the cylinder volume 6 is opened and closed a plurality of times during the displacement of the piston 3 from the lower dead centre to the upper dead centre. This result in that each time the fluid
  • the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first inlet valve 8 and/or the first outlet valve 7, in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed (according to figure 3).
  • the combustion engine 1 comprises a controllable valve 29 arranged in the exhaust air channel 10, the storage
  • the storage reservoir 11 being arranged between the first outlet valve 8 and the controllable valve 29. In other words, the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the first outlet valve 8.
  • the storage reservoir 11 may be constituted by a part of the actual exhaust air channel 11, or alternatively may be constituted by a separate tank arranged in, or connected to, the exhaust air channel 10.
  • the combustion engine also comprises a second outlet valve 30, that is arranged in parallel with the first outlet valve 8.
  • a second exhaust air channel 31 extends from the second outlet valve 30 and is connected to the exhaust air channel 10 upstream the controllable valve 29.
  • the second exhaust air channel 31 is connected to the exhaust air channel 10 directly or indirectly via the storage reservoir 11.
  • the storage reservoir 11 is also arranged between the second outlet valve 30 and the controllable valve 29.
  • the combustion engine comprises a second inlet valve 32, which is arranged in parallel with the first inlet valve 7.
  • a second intake air channel 33 is connected to the intake air channel 9 and extends to the second inlet valve 32.
  • the second inlet valve 32 may be controlled jointly with the first inlet valve 7, and the second outlet valve 30 may optionally be controlled jointly with the first outlet valve 8, alternatively the second inlet valve 32 and/or the second outlet valve 30 may be kept closed during the entire engine braking, if nothing else is stated.
  • the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first inlet valve 7, in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed.
  • the pressure in the cylinder volume 6 is decreased from the prevailing pressure, which is at least as high as the third pressure P3, to become equal to the first pressure PI existing in the intake air channel 9.
  • the first inlet valve 7 is closed and when the piston 3 is displaced in the direction from the upper dead centre to the lower dead centre the existing pressure in the cylinder volume 6 decreases to a level below the first pressure PI that provide a braking effect to the piston 3, and thus generates engine braking effect.
  • first inlet valve 7 may be opened at least one more time during the displacement of the piston 3 in the direction from the upper dead centre to the lower dead centre, when the existing/prevailing pressure in the cylinder volume 6 is lower than the first pressure PI, in order to provide fresh air to the cylinder volume in order to cool down the cylinder 2.
  • fresh air is provided to the cylinder volume 6 via the first inlet valve 7, the
  • controllable valve 29 in the exhaust air channel 10 may be opened whereby the pressurized gas in the storage reservoir 11 drives the turbine 27 that drives the air compressor 28 that secure good supply of fresh air.
  • the first inlet valve 1 is closed at the latest when the piston 3 is located at the lower dead centre.
  • controllable valve 29 may alternatively be constituted by an over pressure valve that opens at a predetermined pressure, however it is mentioned as being the controllable valve 29 for sake of clarity.
  • the storage reservoir 11 is connected to the exhaust air channel 10, the controllable valve 29 of the combustion engine 1 being arranged between the storage reservoir 11 and the exhaust air channel 10.
  • the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second outlet valve 30, whereupon the controllable valve 29 and the storage reservoir 11 are arranged in the second exhaust air channel 31.
  • the storage reservoir 11 may be constituted by a part of the second exhaust air channel 31, or alternatively may be constituted by a separate tank arranged in, or connected to, the second exhaust air channel 31.
  • the second outlet valve 30 is not
  • the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first outlet valve 8 , in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed.
  • the pressure in the cylinder volume 6 decreases from the prevailing pressure, which is at least as high as the third pressure P3, to a level equal to the second pressure P2 existing in the exhaust air channel 10.
  • the first cutlet valve 8 is closed and when the piston 3 is displaced in the direction from the upper dead centre to the lower dead centre the prevailing pressure in the cylinder volume 6 decreases to a level below the second pressure P2 that provide a braking effect to the piston 3, and thus generates engine braking effect.
  • the ventilation of the cylinder volume 6, as a complement to or as an alternative to the short opening of the first outlet valve 8, may take place by means of short opening of the first inlet valve 7, in accordance with the first embodiment described above .
  • the method may comprise the step of keeping the controllable valve 29 open whereby the storage reservoir 11 is in fluid communication with the turbine 27, in connection with the step of keeping the first inlet valve 7 open during at least a part of the time of the displacement of the piston 3 in the direction from the upper dead centre to the lower dead centre.
  • This preferably take place when the existing pressure in the cylinder volume 6 is lower than the first pressure PI, in order to provide fresh air to the cylinder volume in order to cool down the cylinder 2.
  • the controllable valve 29 may be opened whereupon the pressurized gas in the storage reservoir 11 drives the turbine 27 that drives the air compressor 28 that secure good supply of fresh air.
  • the storage reservoir 11 is connected to the intake air channel 9 via a check valve 34, which allow fluid flow from the intake air channel 9 to the storage reservoir 11.
  • the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the
  • the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second inlet valve 32, whereupon the check valve 34 and the storage reservoir 11 are arranged in the second intake air channel 33.
  • the storage reservoir 11 may be constituted by a part of the second intake air channel 33, or alternatively may be constituted by a separate tank arranged in, or connected to, the second intake air channel 33.
  • the second inlet valve 32 is not controlled jointly with the first inlet valve 7 during engine braking in this second alternative of the third embodiment.
  • the second inlet valve 32 and the first inlet valve 7 may be controlled jointly.
  • the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first outlet valve 8, in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed, in accordance with the second embodiment described above.
  • the method may comprise the step of keeping the storage reservoir 11 in fluid communication with the cylinder volume 6, in connection with the step of ventilating the cylinder volume 6 by means of short opening of the first outlet valve 8. This results in a great cross-flow of air through the cylinder volume 6 in order to cool down the cylinder 2.
  • controllable valve 29 may be constituted by an over pressure valve that opens at a predetermined pressure, however it is mentioned as being the controllable valve 29 for sake of clarity.
  • the forth embodiment may be described as a combination of the second alternative of the third embodiment (figure 9) and the first alternative of the second embodiment (figure 6) , in which the controllable storage reservoir valve 12 is removed.
  • the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second inlet valve 32.
  • the storage reservoir 11 is part of the exhaust air channel 10 and where the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second cutlet valve 30, priming of the storage reservoir 11 takes place in the beginning of each engine braking occasion.
  • the storage reservoir 11 preferably remains primed between the engine braking occasions.
  • priming of the storage reservoir 11 may take place in the beginning of each engine braking occasion or the storage reservoir 11 may remain primed between the engine braking occasions.
  • the cylinder 2 and the piston 3 are used as a piston compressor.
  • valve actuators may be exchanged with other actuators without deviating from the present
  • the combustion engine may comprise a first and a second inlet valve and a first and a second outlet valve, respectively, in spite of the fact that it has not been expressly disclosed in the detailed description above.

Abstract

The present invention relates to a combustion engine as well as a method for engine braking in such a combustion engine comprising at least one cylinder (2) having a cylinder volume (6) and a piston displaceable in said cylinder (6), an intake air channel (9) having a first pressure PI, a first inlet valve (7) arranged between the intake air channel (9) and the cylinder volume (6), an exhaust air channel (10) having a second pressure P2, a first outlet valve (8) arranged between the cylinder volume (6) and the exhaust air channel (10), and a storage reservoir (11) having a third pressure P3 that is higher than said first pressure PI and said second pressure P2, the storage reservoir (11) being arranged in controllable fluid communication with the cylinder volume (6). The method being characterized by taking place during two-stroke cycle and comprises the steps of, displacing the piston from the upper dead centre towards the lower dead centre, keeping the first inlet valve (7) open during at least a part of the time the piston is displaced from the upper dead centre to the lower dead centre, displace the piston from the lower dead centre towards the upper dead centre, and keeping the fluid communication between the storage reservoir (11) and the cylinder volume (6) open during at least a part of the time the piston is displaced from the lower dead centre to the upper dead centre.

Description

COMBUSTION ENGINE AS WELL AS METHOD FOR ENGINE BRAKING USING SUCH A COMBUSTION ENGINE
Technical field of the Invention
The present invention relates in general to a
combustion engine as well as a method for engine braking using such a combustion engine, typically being arranged in a so-called heavy vehicle. The combustion engines concerned are above all camshaft free piston engines, which are also known under the term ""engines having free valves". The present invention relates specifically to a method for engine braking in a combustion engine comprising at least one cylinder having a cylinder volume and a piston
displaceable in said cylinder, an intake air channel having a first pressure PI, a first inlet valve arranged between the intake air channel and the cylinder volume, an exhaust air channel having a second pressure P2, a first outlet valve arranged between the cylinder volume and the exhaust air channel, and a storage reservoir having a third pressure P3 that is higher than said first pressure PI and said second pressure P2, the storage reservoir being arranged in controllable fluid communication with the cylinder volume.
Background of the Invention and prior art
Today there are several known ways of executing engine braking using a combustion engine, which methods are especially used for engine braking in combustion engines of heavy vehicles, such as diesel engines of buses and trucks. Engine braking is used in these types of vehicles for instance in long downhill slopes in order to avoid the risk of overheating the mechanical wheel braking devices of the vehicle which may lead to wholly or partial loss of braking effect.
One example of engine braking is realized by closing the exhaust air channel/exhaust gas channel by means of a valve, whereby the combustion engine continues to operate in four-stroke cycle, and when the outlet valves of the cylinder are opened, in order to evacuate exhaust gases during normal operation, a back pressure is generated downstream the cylinder. The back pressure is used to counteract the displacement of the piston from the lower dead centre to the upper dead centre when the outlet valves are open. However, this engine braking effect only
corresponds to a part of the drive effect of the combustion engine, at the same time as this type of engine braking above all result in unwanted heating of the components of the combustion engine.
Engine braking according to conventional type entail that the combustion engine must have engine valve springs having high permanent spring force, which is not a problem in connection with conventional camshaft actuated engine valves since the high spring force is recovered on the back side of the cam, however it is devastating for an engine valve control without force recovery.
US 7,946,269 to Gerum, disclose a combustion engine comprising a cylinder having a cylinder volume and a piston displaceable in said cylinder volume, and a storage volume that is arranged in controllable fluid communication with the cylinder volume via the inlet valves of the cylinders. The combustion engine is driven in four-stroke cycle during the engine braking and when the piston is displaced from the upper dead centre to the lower dead centre and the inlet valves are open, the fluid communication between the storage volume and the cylinder volume is opened. I.e. air having high pressure is provided during the intake stroke,
whereupon engine braking takes place during the compression stroke. Thus, no engine braking takes place during the intake stroke, instead air having high pressure is provided that de facto counteract engine braking. Objects of the Invention
The present invention aims at obviating the aforementioned disadvantages and failings of previously known methods for engine braking in combustion engines and at providing an improved engine braking method. A primary object of the present invention is to provide an improved engine braking method of the initially defined type, which generates at least as high engine braking effect as the drive effect of the combustion engine during four-stroke cycle operation.
Another object of the present invention is to provide an engine braking method that prevents unwanted/harmful heating of the components of the combustion engine during engine breaking.
Yet another object of the present invention is to provide an engine braking method that allows the size of the engine valve springs of the combustion engine to be reduced, resulting in reduced energy consumption during normal operation.
Summary of the Invention
According to the invention at least the primary object is attained by means of the initially defined method and combustion engine having the features defined in the independent claims. Preferred embodiments of the present invention are further defined in the dependent claims.
According to a first aspect of the present invention there is provided a method of the initially defined type, which is characterized by taking place during two-stroke cycle and comprises the steps of displacing the piston from the upper dead centre towards the lower dead centre, keeping the first inlet valve open during at least a part of the time the piston is displaced from the upper dead centre to the lower dead centre, opening the fluid communication between the storage reservoir and the cylinder volume, in connection with the piston being located at the lower dead centre and when the first inlet valve is closed, displace the piston from the lower dead centre towards the upper dead centre, and keeping the fluid communication between the storage reservoir and the cylinder volume open during at least a part of the time the piston is displaced from the lower dead centre to the upper dead centre.
According to a second aspect of the present invention there is provided a combustion engine that is configured to be driven in accordance with the above mentioned method.
Thus, the present invention is based on the
understanding that by operating the combustion engine in two-stroke cycle during engine braking and in each
compression stroke fill the cylinder volume with air having high pressure, an engine braking effect exceeding the drive effect of the combustion engine during four-stroke cycle operation is obtained. The present invention also entails that air having high pressure is provided into the cylinder volume at an early stage during the compression stroke of the two-stroke cycle, and thereby generating a great contribution to the engine braking effect.
According to a preferred embodiment the fluid
communication between the storage reservoir and the cylinder volume are opened and closed a plurality of times during the displacement of the piston from the lower dead centre to the upper dead centre. This entail that each time the fluid communication between the storage reservoir and the cylinder volume is closed during the displacement of the piston from the lower dead centre to the upper dead centre, the pressure in the cylinder volume will increase above the existing pressure in the storage reservoir and thereby an extra contribution to the engine braking effect is obtained in relation to the case when the fluid communication between the storage reservoir and the cylinder volume is open.
According to a preferred embodiment the storage reservoir is connected to the exhaust air channel via a controllable valve, the method comprising the step of ventilating the cylinder volume by means of a short opening of the first outlet valve, in connection with the piston being located at the upper dead centre and when the fluid communication between the storage reservoir and the cylinder volume is closed. This entail that the pressure in the cylinder volume is drastically reduced at the same time as heat is released via the exhaust gas system of the vehicle.
In yet another preferred embodiment the method
comprises the step of keeping the controllable valve open in order to have the storage reservoir in fluid communication with the turbine, in connection with the step of keeping the first inlet valve open during at least a part of the time the piston is displaced from the upper dead centre to the lower dead centre. This entail that it is secured that fresh air is provided into the cylinder volume by means of the compressor that is driven by the turbine, leading to cooling down of the components of the combustion engine.
Further advantages with and features of the invention will be apparent from the other dependent claims as well as from the following detailed description of preferred embodiments .
Brief description of the drawings
A more complete understanding of the abovementioned and other features and advantages of the present invention will be apparent from the following detailed description of preferred embodiments in conjunction with the appended drawings, wherein:
Fig. 1 is a schematic cross sectional view of a part of a combustion engine,
Fig. 2 is a schematic illustration of a combustion engine according to the overall inventive concept, Fig. 3 is a schematic illustration of a P/V-diagram for a break cycle, Fig. 4 is a schematic illustration of the combustion engine according to a first alternative of a first embodiment,
Fig. 5 is a schematic illustration of the combustion
engine according to a second alternative of the first embodiment,
Fig. 6 is a schematic illustration of the combustion
engine according to a first alternative of a second embodiment,
Fig. 7 is a schematic illustration of the combustion
engine according to a second alternative of the second embodiment,
Fig. 8 is a schematic illustration of the combustion
engine according to a first alternative of a third embodiment,
Fig. 9 is a schematic illustration of the combustion
engine according to a second alternative of the third embodiment, and
Fig. 10 is a schematic illustration of the combustion
engine according to a fourth embodiment.
Detailed description of preferred embodiments of the invention
Reference is initially made to figures 1 and 2, wherein the overall inventive concept will be described with reference thereto. The present invention relates to a combustion engine, generally designated 1, as well as to a method for engine braking in such a combustion engine 1. It shall be pointed out that energy recovery is not central, nor desirable, in applications in which the inventive combustion engine 1 and method are intended to be used, on the contrary it is instead central to maximize the energy consumptio .
The combustion engine 1 comprises a cylinder block having at least one cylinder 2. Usually said cylinder block comprises three or four cylinders 2. In the disclosed embodiment one cylinder 2 is described, however it shall be realized that the equipment described herein below in connection with the disclosed cylinder 2 is preferably applied to all cylinders of the combustion engine 1, in the case the combustion engine comprises a plurality of
cylinders. The combustion engine 1 is preferably a diesel engine in a vehicle, such as a bus or a truck.
Thereto the combustion engine 1 comprises a piston 3 axially displaceable in said cylinder 2. The movement of the piston 3, axial displacement back and forth, is transmitted in a conventional way to a piston rod 4 connected to the piston 3, the piston rod 4 in its turn being connected to and drives a crankshaft (not disclosed) in rotation.
The combustion engine 1 also comprises a cylinder head 5 that together with said cylinder 2 and said piston 3 delimits a cylinder volume 6, or combustion chamber. In the cylinder volume 6 ignition of a mixture of fuel and air takes place in a conventional way during normal operation of the combustion engine, and is not described more herein. During normal operation the combustion engine 1 is preferably driven in four-stroke cycle operation, but it shall be realized that also two-stroke cycle operation is possible.
The combustion engine 1 further comprises a first inlet valve 7 and a first outlet valve 8, which preferably are constituted by traditional gas exchange valves. Said first inlet valve 7 is an intake air valve that is configured to optionally open/close the supply of air to the combustion chamber 6 during normal operation. The first outlet valve 8 is an exhaust air valve, or exhaust gas valve, that is configured to optionally open/close for evacuation of
exhaust gases from the combustion chamber 6 during normal operation.
The first inlet valve 7 is arranged between the cylinder volume 6 and an intake air channel 9, in which there is a first pressure PI. The first outlet valve 8 is arranged between the cylinder volume 6 and an exhaust air channel 10, in which there is a second pressure P2. Each of first pressure PI and the second pressure P2 is preferably in the range 1-5 bar absolute.
The combustion engine 1 further comprises a storage reservoir 11, in which there is a third pressure P3. The third pressure P3 is strictly greater than each of the first pressure PI and the second pressure P2, and is preferably in the range 15-20 bar absolute. The storage reservoir 11 is arranged for controllable fluid communication with the cylinder volume 6. In the embodiment according to figure 2 the storage reservoir 11 is connected to the cylinder volume 6 via a controllable storage reservoir valve 12.
Furthermore in the preferred embodiment, the combustion engine 1 comprises a valve actuator 13 that is operatively connected to said first inlet valve 7. Only the valve actuator 13 that is connected to the first inlet valve 7 will be described herein, however it shall be realized that also the first outlet valve 8, and other possible inlet valves and outlet valves, is operatively connected to such a valve actuator. The disclosed, preferred valve actuator 13 comprises at least one inlet opening 14 for pressure fluid and at least one outlet opening 15 for pressure fluid. The pressure fluid is a gas or gas mixture, preferably air or nitrogen. Air has the advantage that it is easy to exchange the pressure fluid or add more pressure fluid if the pressure fluid leak, and nitrogen has the advantage that it is free from oxygen and thereby prevents oxidation of other components. It shall be pointed out that also other types of valve actuators are conceivable.
Thereto it shall be pointed out that each valve actuator can be operatively connected to one or more gas exchange valves, for instance the combustion engine 1 may comprise two inlet valves which are jointly driven by one and the same valve actuator 13. However it is preferred that each valve actuator drive one gas exchange valve each in order to obtain best possible controllability of the operation of the combustion engine 1.
The disclosed valve actuator 13 comprises an actuator piston disc 16 and an actuator cylinder 17 delimiting a cylinder volume. The actuator piston disc 16 separate said cylinder volume in an upper part 18 and a lower part 19 and is axially displaceabie in said actuator cylinder 17. The actuator piston disc 16 form part of an actuator piston or pusher, generally designated 20, that is configured to abut and drive the first inlet valve 7.
The valve actuator 13 comprises a controllable inlet valve 21 that is arranged to open/close the inlet opening 14, a controllable outlet valve 22 that is arranged to open/close the outlet opening 15, a hydraulic circuit, generally designated 23, that in its turn comprises a check valve 24 arranged to allow filling of hydraulic circuit 23 and a controllable emptying valve 25 arranged to control the emptying of the hydraulic circuit 23. It shall be pointed out that the valves disclosed in this document are
schematically presented and may for instance be constituted by slide valves, seat valves, etc. Thereto several of the above mentioned controllable valves may be constituted by a single body. Each valve may be directly or indirectly electrically controlled. By electrically controlled is meant that the position of the valve is directly controlled by for instance an electro magnet device, and by indirectly electrically controlled is meant that the position of the valve is controlled by a pressure fluid that in its turn is controlled by for instance an electromagnetic device.
In order to obtain a displacement of the actuator piston disc 16 downwards, in order to open the first inlet valve 7, the inlet valve 21 is open to allow filling of pressure fluid having high pressure into the upper part 18 of the cylinder volume. When the actuator piston 20 is displaced downwards the check valve 24 of the hydraulic circuit 23 is opened, whereupon hydraulic liquid is sucked in and replace the volume that the actuator piston 20 leave. Thereafter the inlet valve 21 is closed and the pressure fluid that has entered the upper part 18 of the cylinder volume is allowed to expand whereupon the actuator piston disc 16 continues its movement downwards. When the pressure fluid in the upper part 18 of the cylinder volume does not manage to displace the actuator piston disc 16 any more, i.e. when the pressure from lower side of the actuator piston disc 26 and the return spring 26 of the first inlet valve 7 is equal to the pressure on the upper side of the actuator piston disc 16, the actuator piston disc 16 stop. The actuator piston disc 16 is kept (locked) in the lower position a required time by holding the emptying valve 25 of the hydraulic circuit 23 closed at the same time as the check valve 24 of the hydraulic circuit 23 is automatically closed. In order to accomplish a return movement the outlet valve 22 is opened in order to allow evacuation of pressure fluid from the upper part 18 of the cylinder volume, and thereto the emptying valve 25 of the hydraulic circuit 23 is opened whereupon the actuator piston disc 16 is displaced upwards when the hydraulic liquid is evacuated from the hydraulic circuit 23, and at the same time the pressure fluid is evacuated from the upper part 18 of the cylinder volume via the outlet opening 15.
Preferably, the combustion engine 1 comprises a turbine
27, connected to and arranged downstream the exhaust air channel 10, and an air compressor 28, connected to and arranged upstream the intake air channel 9, the turbine 27 being arranged to drive the air compressor 28. The air passing through the turbine 27 from the exhaust air channel 10 generates a rotation of a turbine impeller, which is connected to and configured to drive a compressor impeller in the air compressor 28. The compressor impeller such in ambient air and press the air, preferably cooled, into the intake air channel 9. The turbine 27 and the air compressor 28 are preferably part of a conventional super charger unit. It shall be pointed out that in this document the intake air channel 9 extend to the first inlet valve 7 in the direction from the air compressor 28, and the exhaust air channel 10 extend from the first outlet valve 8 in the direction towards the turbine 27.
The inventive method and combustion engine will be described herein below according to different alternative embodiments, which all belong to the one and same inventive concept/inventive idea that will be described with reference to figure 2 , but is also valid for all disclosed embodiments and equivalent embodiments. Thus, the described embodiments are only alternative realizations of the invention.
During the inventive engine braking method the
combustion engine 1 is driven in two-stroke cycle,
independent from the combustion engine 1 being driven in four-stroke cycle or two-stroke cycle during normal
operation. In figure 3 is shown a schematic illustration of a braking cycle in a so-called P/V-diagram, wherein P stands for existing pressure in the cylinder volume 6 and V stands for existing volume of the cylinder volume 6 by indicating the location of the piston 3 between the upper dead centre UDC and lower dead centre LDC.
The method comprises the steps of displacing the piston 3 from the upper dead centre UDC towards the lower dead centre LDC, keeping the first inlet valve 7 open during at least a part of the time the piston 3 is displaced from the upper dead centre to the lower dead centre, displacing the piston 3 from the lower dead centre towards the upper dead centre, and keeping the fluid communication between the storage reservoir 11 and the cylinder volume 6 open during at least a part of the time the piston 3 is displaced from the lower dead centre to the upper dead centre.
When the fluid communication between the storage reservoir 11 and the cylinder volume 6 is open, the third pressure P3 exist in the cylinder volume 6, acting braking to the piston 3 when it is displaced in the direction from the lower dead centre to the upper dead centre. When the first inlet valve 7 is open the existing pressure in the cylinder volume 6 is equal to the first pressure PI, and the cylinder volume 6 is ventilated. The fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the storage reservoir valve 12.
Preferably the method comprises the step of opening the fluid communication between the storage reservoir 11 and the cylinder volume 6, in connection with the piston 3 being located at the lower dead centre and when the first inlet valve 7 is closed. This entail that the third pressure P3 starts to act against the piston 3 as early as possible during the compression stroke.
Preferably the method comprises the step of securing that the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed, in connection with the piston 3 being located in the upper dead centre, in order not to provide the third pressure P3 from the storage reservoir 11 to the cylinder volume 6 during the piston being displaced from the upper dead centre to the lower dead centre.
According to one embodiment of the fundamental
inventive concept the fluid communication between the storage reservoir 11 and the cylinder volume 6 is open during the entire displacement of the piston 3 from the lower dead centre to the upper dead centre. This result in that the third pressure P3 exists in the cylinder volume 6 during the entire compression stroke, which provide good engine braking effect (according to figure 3) . According to an alternative embodiment the fluid communication between the storage reservoir 11 and the cylinder volume 6 is opened and closed a plurality of times during the displacement of the piston 3 from the lower dead centre to the upper dead centre. This result in that each time the fluid
communication is open the third pressure P3 exists in the cylinder volume 6, which provide good engine braking effect, and each time the fluid communication is closed during the displacement of the piston in the direction from the lower dead centre to the upper dead centre the pressure in the cylinder volume 6 increase, which provide extra engine braking effect. During the displacement of the piston 3 from the lower dead centre to the upper dead centre the fluid communication between the storage reservoir 11 and the cylinder volume 6 may be kept closed, subsequent it has been open, as long as the pressure in the cylinder volume 6 does not obstruct the valves that are facing the cylinder volume 6 to be opened as intended to. The pressure in the cylinder volume 6 should not exceed a pressure of about 30 bar absolute, even thus a pressure of about 200 bar is possible from a physical properties point of view.
Preferably the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first inlet valve 8 and/or the first outlet valve 7, in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed (according to figure 3).
Reference is now also made to figures 4 and 5, which disclose two alternatives of a first embodiment of the invention. First of all only additions in relation to the above will be described, everything else is the same if nothing else is stated.
According to this first embodiment of the invention the combustion engine 1 comprises a controllable valve 29 arranged in the exhaust air channel 10, the storage
reservoir 11 being arranged between the first outlet valve 8 and the controllable valve 29. In other words, the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the first outlet valve 8. The storage reservoir 11 may be constituted by a part of the actual exhaust air channel 11, or alternatively may be constituted by a separate tank arranged in, or connected to, the exhaust air channel 10.
In the second alternative of the first embodiment (figure 5), the combustion engine also comprises a second outlet valve 30, that is arranged in parallel with the first outlet valve 8. A second exhaust air channel 31 extends from the second outlet valve 30 and is connected to the exhaust air channel 10 upstream the controllable valve 29. The second exhaust air channel 31 is connected to the exhaust air channel 10 directly or indirectly via the storage reservoir 11. In other words, the storage reservoir 11 is also arranged between the second outlet valve 30 and the controllable valve 29. Thereto the combustion engine comprises a second inlet valve 32, which is arranged in parallel with the first inlet valve 7. A second intake air channel 33 is connected to the intake air channel 9 and extends to the second inlet valve 32.
It shall be realized that in the description herein below the second inlet valve 32 may be controlled jointly with the first inlet valve 7, and the second outlet valve 30 may optionally be controlled jointly with the first outlet valve 8, alternatively the second inlet valve 32 and/or the second outlet valve 30 may be kept closed during the entire engine braking, if nothing else is stated.
In this first embodiment of the invention the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first inlet valve 7, in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed. Thereby the pressure in the cylinder volume 6 is decreased from the prevailing pressure, which is at least as high as the third pressure P3, to become equal to the first pressure PI existing in the intake air channel 9. Thereafter the first inlet valve 7 is closed and when the piston 3 is displaced in the direction from the upper dead centre to the lower dead centre the existing pressure in the cylinder volume 6 decreases to a level below the first pressure PI that provide a braking effect to the piston 3, and thus generates engine braking effect.
Thereto the first inlet valve 7 may be opened at least one more time during the displacement of the piston 3 in the direction from the upper dead centre to the lower dead centre, when the existing/prevailing pressure in the cylinder volume 6 is lower than the first pressure PI, in order to provide fresh air to the cylinder volume in order to cool down the cylinder 2. In connection with, i.e.
jointly or just before, fresh air is provided to the cylinder volume 6 via the first inlet valve 7, the
controllable valve 29 in the exhaust air channel 10 may be opened whereby the pressurized gas in the storage reservoir 11 drives the turbine 27 that drives the air compressor 28 that secure good supply of fresh air.
The point of time fresh air is supplied to the cylinder volume 6, e.g. when the first inlet valve 7 is opened, shall preferably take place during the second half of the
displacement of the piston 3 in the direction from the upper dead centre to the lower dead centre, most preferably during the last quarter of the displacement of the piston 3 in the direction from the upper dead centre to the lower dead centre. The first inlet valve 1 is closed at the latest when the piston 3 is located at the lower dead centre.
Reference is now made to figures 6 and 7, which disclose two alternatives of a second embodiment of the invention. First of all only differences and additions in relation to the above will be described, everything else is the same if nothing else is stated. It shall be pointed out that in these embodiments the controllable valve 29 may alternatively be constituted by an over pressure valve that opens at a predetermined pressure, however it is mentioned as being the controllable valve 29 for sake of clarity. According to this second embodiment of the invention the storage reservoir 11 is connected to the exhaust air channel 10, the controllable valve 29 of the combustion engine 1 being arranged between the storage reservoir 11 and the exhaust air channel 10. According to the first
alternative of the second embodiment (figure 6) the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the controllable storage reservoir valve 12.
According to the second alternative of the second embodiment (figure 7) the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second outlet valve 30, whereupon the controllable valve 29 and the storage reservoir 11 are arranged in the second exhaust air channel 31. The storage reservoir 11 may be constituted by a part of the second exhaust air channel 31, or alternatively may be constituted by a separate tank arranged in, or connected to, the second exhaust air channel 31. For sake of clarity it shall be pointed out that the second outlet valve 30 is not
controlled jointly with the first outlet valve 9 during engine braking in this second alternative of the second embodiment.
In this second embodiment of the invention the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first outlet valve 8 , in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed. Thereby the pressure in the cylinder volume 6 decreases from the prevailing pressure, which is at least as high as the third pressure P3, to a level equal to the second pressure P2 existing in the exhaust air channel 10. Thereafter the first cutlet valve 8 is closed and when the piston 3 is displaced in the direction from the upper dead centre to the lower dead centre the prevailing pressure in the cylinder volume 6 decreases to a level below the second pressure P2 that provide a braking effect to the piston 3, and thus generates engine braking effect. It shall be pointed out that the ventilation of the cylinder volume 6, as a complement to or as an alternative to the short opening of the first outlet valve 8, may take place by means of short opening of the first inlet valve 7, in accordance with the first embodiment described above .
Furthermore the method may comprise the step of keeping the controllable valve 29 open whereby the storage reservoir 11 is in fluid communication with the turbine 27, in connection with the step of keeping the first inlet valve 7 open during at least a part of the time of the displacement of the piston 3 in the direction from the upper dead centre to the lower dead centre. This preferably take place when the existing pressure in the cylinder volume 6 is lower than the first pressure PI, in order to provide fresh air to the cylinder volume in order to cool down the cylinder 2. In connection with, e.g. jointly or before, fresh air is supplied to the cylinder volume 6 via the first inlet valve 7 the controllable valve 29 may be opened whereupon the pressurized gas in the storage reservoir 11 drives the turbine 27 that drives the air compressor 28 that secure good supply of fresh air.
Reference is now made to figures 8 and 9, which disclose two alternatives of a third embodiment of the invention. First of all only differences and additions in relation to the above will be described, everything else is the same if nothing else is stated.
According to this third embodiment of the invention the storage reservoir 11 is connected to the intake air channel 9 via a check valve 34, which allow fluid flow from the intake air channel 9 to the storage reservoir 11. According to the first alternative of the third embodiment (figure 8) the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the
controllable storage reservoir valve 12.
According to the second alternative of the third embodiment (figure 9) the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second inlet valve 32, whereupon the check valve 34 and the storage reservoir 11 are arranged in the second intake air channel 33. The storage reservoir 11 may be constituted by a part of the second intake air channel 33, or alternatively may be constituted by a separate tank arranged in, or connected to, the second intake air channel 33. For sake of clarity it shall be pointed out that the second inlet valve 32 is not controlled jointly with the first inlet valve 7 during engine braking in this second alternative of the third embodiment. During normal operation of the combustion engine, e.g. during propulsion of the vehicle and not during braking, the second inlet valve 32 and the first inlet valve 7 may be controlled jointly.
In this third embodiment of the invention the method comprises the step of ventilating the cylinder volume 6 by means of short opening of the first outlet valve 8, in connection with the piston 3 being located at the upper dead centre and when the fluid communication between the storage reservoir 11 and the cylinder volume 6 is closed, in accordance with the second embodiment described above.
Furthermore the method may comprise the step of keeping the storage reservoir 11 in fluid communication with the cylinder volume 6, in connection with the step of ventilating the cylinder volume 6 by means of short opening of the first outlet valve 8. This results in a great cross-flow of air through the cylinder volume 6 in order to cool down the cylinder 2.
Reference is now made to figure 10 that disclose a forth embodiment of the invention. First of all only differences and additions in relation to the above will be described, everything else is the same if nothing else is stated. It shall be pointed out that in this embodiment the controllable valve 29 may be constituted by an over pressure valve that opens at a predetermined pressure, however it is mentioned as being the controllable valve 29 for sake of clarity.
The forth embodiment (figure 10) may be described as a combination of the second alternative of the third embodiment (figure 9) and the first alternative of the second embodiment (figure 6) , in which the controllable storage reservoir valve 12 is removed.
According to the forth embodiment (figure 10) the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second inlet valve 32.
In the embodiments where the storage reservoir 11 is part of the exhaust air channel 10 and where the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second cutlet valve 30, priming of the storage reservoir 11 takes place in the beginning of each engine braking occasion. In the embodiments where the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the storage reservoir valve 12, the storage reservoir 11 preferably remains primed between the engine braking occasions. In the embodiments where the storage reservoir 11 is part of the second exhaust air channel 31 or part of the second intake air channel 33 and where the fluid communication between the storage reservoir 11 and the cylinder volume 6 is controlled by means of the second cutlet valve 30 and the second inlet valve 32, respectively, priming of the storage reservoir 11 may take place in the beginning of each engine braking occasion or the storage reservoir 11 may remain primed between the engine braking occasions. During priming the cylinder 2 and the piston 3 are used as a piston compressor. Feasible modifications of the Invention
The invention is not limited only to the embodiments described above and shown in the drawings, which primarily have an illustrative and exemplifying purpose. This patent application is intended to cover all adjustments and variants of the preferred embodiments described herein, thus the present invention is defined by the wording of the appended claims and thus, the equipment may be modified in all kinds of ways within the scope of the appended claims.
The disclosed valve actuators may be exchanged with other actuators without deviating from the present
invention.
It shall be pointed out that the term "in connection with..' as have been used in the claims as well as in the description, is meant an interval extending from just before to just after the concerned activity.
It shall also be pointed out that in all alternatives/ embodiments of the present invention the combustion engine may comprise a first and a second inlet valve and a first and a second outlet valve, respectively, in spite of the fact that it has not been expressly disclosed in the detailed description above.
It shall also be pointed out that all information about/concerning terms such as above, under, upper, lower, etc., shall be interpreted/read having the equipment oriented according to the figures, having the drawings oriented such that the references can be properly read.
Thus, such terms only indicates mutual relations in the shown embodiments, which relations may be changed if the inventive equipment is provided with another
structure/design .
It shall also be pointed out that even thus it is not explicitly stated that features from a specific embodiment may be combined with features from another embodiment, the combination shall be considered obvious, if the combination is possible.

Claims

Claims
1. A method for engine braking in a combustion engine comprising at least one cylinder (2) having a cylinder volume (6) and a piston (3) displaceable in said cylinder (2), an intake air channel (9) having a first pressure (PI), a first inlet valve (7) arranged between the intake air channel (9) and the cylinder volume (6), an exhaust air channel (10) having a second pressure (P2), a first outlet valve (8) arranged between the cylinder volume (6) and the exhaust air channel (10), and a storage reservoir (11) having a third pressure (P3) that is higher than said first pressure (Pi) and said second pressure (P2) , the storage reservoir (11) being arranged in controllable fluid
communication with the cylinder volume (6), the method being characterized by taking place during two-stroke cycle and comprises the steps of:
- displacing the piston (3) from the upper dead centre towards the lower dead centre,
- keeping the first inlet valve (7) open during at least a part of the time the piston (3) is displaced from the upper dead centre to the lower dead centre,
- opening the fluid communication between the storage reservoir (11) and the cylinder volume (6), in connection with the piston (3) being located at the lower dead centre and when the first inlet valve (7) is closed,
- displace the piston (3) from the lower dead centre towards the upper dead centre, and
- keeping the fluid communication between the storage reservoir (11) and the cylinder volume (6) open during at least a part of the time the piston (3) is displaced from the lower dead centre to the upper dead centre.
2. The method according to claim 1, wherein the method comprises the steps of: closing the fluid communication between the storage reservoir (11) and the cylinder volume (6), in connection with the piston (3) being located at the upper dead centre.
3. The method according to claim 1 or 2, wherein the fluid communication between the storage reservoir (11) and the cylinder volume (6) is kept open during the entire
displacement of the piston (3) from the lower dead centre to the upper dead centre.
4. The method according to claim 1 or 2, wherein the fluid communication between the storage reservoir (11) and the cylinder volume (6) is opened and closed a plurality of times during the displacement of the piston (3) from the lower dead centre to the upper dead centre.
5. The method according to any of claims 1-4, wherein the combustion engine comprises a turbine (27) arranged
downstream the exhaust air channel (10), and an air
compressor (28) arranged upstream the intake air channel (9), the turbine (27) being configured to drive the air compressor (28) , wherein the combustion engine comprises a controllable valve (29) arranged in the exhaust air channel (10), the storage reservoir (11) being arranged between the first outlet valve (8) and the controllable valve (29), wherein the method comprises the step of ventilating the cylinder volume (6) by means of a short opening of the first inlet valve (7) , in connection with the piston (3) being located at the upper dead centre and when the fluid
communication between the storage reservoir (11) and the cylinder volume (6) is closed.
6. The method according to any of claims 1-4, wherein the combustion engine comprises a turbine (27) arranged
downstream the exhaust air channel (10), and an air
compressor (28) arranged upstream the intake air channel (9), the turbine (27) being configured to drive the air compressor (28), wherein the storage reservoir (11) is connected to the exhaust air channel (10) via a controllable valve (29) , wherein the method comprises the step of ventilating the cylinder volume (6) by means of a short opening of the first outlet valve (7) , in connection with the piston (3) being located at the upper dead centre and when the fluid communication between the storage reservoir (11) and the cylinder volume (6) is closed.
7. The method according to claim 6, wherein the method in connection with the step of keeping the first inlet valve (7) open during at least a part of the time the piston (3) is displaced from the upper dead centre to the lower dead centre, comprises the step of keeping the controllable valve (29) open in order to have the storage reservoir (11) in fluid communication with the turbine (27) .
8. The method according to any of claims 1-4, wherein the combustion engine comprises a turbine (27) arranged
downstream the exhaust air channel (10), and an air
compressor (28) arranged upstream the intake air channel (9), the turbine (27) being configured to drive the air compressor (28), wherein the storage reservoir (11) is connected to the exhaust air channel (10) via a controllable valve (29) , wherein the method in connection with the step of keeping the first inlet valve (7) open during at least a part of the time the piston (3) is displaced from the upper dead centre to the lower dead centre, comprises the steps keeping the controllable valve (29) open in order to have the storage reservoir (11) in fluid communication with the turbine (27) .
9. The method according to claim 5 or 6, wherein the storage reservoir (11) is connected to the intake air channel (9) via a check valve (34), allowing fluid flow from the intake air channel (9) to the storage reservoir (11), wherein the method comprises the step of ventilating the cylinder volume (6) by means of a short opening of the first outlet valve (8) , in connection with the piston (3) being located at the upper dead centre and when the fluid communication between the storage reservoir (1!) and the cylinder volume (6) is closed.
10. A combustion engine comprising at least one cylinder (2) having a cylinder volume (6) and a piston (3) displaceable in said cylinder (2), an intake air channel (9) having a first pressure (PI), a first inlet valve (7) arranged between the intake air channel (9) and the cylinder volume (6), an exhaust air channel (10) having a second pressure (P2), a first outlet valve (8) arranged between the cylinder volume (6) and the exhaust air channel (10), and a storage reservoir (11) having a third pressure (P3) that is higher than said first pressure (Pi) and said second pressure (P2), the storage reservoir (11) being arranged in controllable fluid communication with the cylinder volume (6), the combustion engine (1) being characterized in that it is configured to be driven in two-stroke cycle during engine braking, in that the first inlet valve (7) is configured to be open during at least a part of the time the piston (3) is displaced from the upper dead centre to the lower dead centre, in that the combustion engine is configured to open the fluid communication between the storage reservoir (11) and the cylinder volume (6) in connection with the piston (3) being located at the lower dead centre and when the first inlet valve (7) is closed, and in that the storage reservoir (11) is configured to be in fluid communication with the cylinder volume (6) during at least a part of the time the piston (3) is displaced from the lower dead centre to the upper dead centre.
11. The combustion engine according to claim 10, wherein the combustion engine comprises a turbine (27) arranged downstream the exhaust air channel (10), and an air
compressor (28) arranged upstream the intake air channel (9), the turbine (27) being configured to drive the air compressor (28) .
12. The combustion engine according to claim 11, wherein the combustion engine comprises a controllable valve (29) arranged in the exhaust air channel (10), the storage reservoir (11) being arranged between the first outlet valve (8) and the controllable valve (29).
13. The combustion engine according to claim 11, wherein the storage reservoir (11) is connected to the exhaust air channel (10) via a controllable valve (29).
14. The combustion engine according to claim 11, wherein the storage reservoir (11) is connected to the intake air channel (9) via a check valve (34), allowing fluid flow from the intake air channel (9) to the storage reservoir (11) .
PCT/SE2015/051083 2014-10-15 2015-10-12 Combustion engine as well as method for engine braking using such a combustion engine WO2016060605A1 (en)

Priority Applications (7)

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RU2017116521A RU2017116521A (en) 2014-10-15 2015-10-12 INTERNAL COMBUSTION ENGINE, AND ALSO THE METHOD OF BRAKING THE ENGINE USING SUCH ENGINE
KR1020177012856A KR20170066640A (en) 2014-10-15 2015-10-12 Combustion engine as well as method for engine braking using such a combustion engine
BR112017007539A BR112017007539A2 (en) 2014-10-15 2015-10-12 combustion engine and as well as method for engine braking using such a combustion engine
US15/518,304 US10344683B2 (en) 2014-10-15 2015-10-12 Combustion engine as well as method for engine braking using such a combustion engine
CN201580055738.0A CN107076036B (en) 2014-10-15 2015-10-12 Combustion engine and method for engine braking using such a combustion engine
EP15850606.3A EP3207236B1 (en) 2014-10-15 2015-10-12 Combustion engine as well as method for engine braking using such a combustion engine
JP2017520896A JP2017534796A (en) 2014-10-15 2015-10-12 Combustion engine and method for engine braking using the combustion engine

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SE1451234A SE538553C2 (en) 2014-10-15 2014-10-15 Internal combustion engine and method of engine braking of such an internal combustion engine
SE1451234-7 2014-10-15

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BR112017007539A2 (en) 2018-01-30
EP3207236A4 (en) 2018-11-21
JP2017534796A (en) 2017-11-24
US10344683B2 (en) 2019-07-09
CN107076036A (en) 2017-08-18
SE538553C2 (en) 2016-09-13
RU2017116521A (en) 2018-11-15
CN107076036B (en) 2020-07-31
EP3207236A1 (en) 2017-08-23
US20170306860A1 (en) 2017-10-26
EP3207236B1 (en) 2021-04-28
SE1451234A1 (en) 2016-04-16

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