EP3201437A1 - Verbrennungsmotor - Google Patents
VerbrennungsmotorInfo
- Publication number
- EP3201437A1 EP3201437A1 EP15771961.8A EP15771961A EP3201437A1 EP 3201437 A1 EP3201437 A1 EP 3201437A1 EP 15771961 A EP15771961 A EP 15771961A EP 3201437 A1 EP3201437 A1 EP 3201437A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- internal combustion
- engine
- combustion engine
- intermediate plate
- crankshaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 51
- 230000005540 biological transmission Effects 0.000 claims abstract description 35
- 238000001816 cooling Methods 0.000 claims description 33
- 230000008878 coupling Effects 0.000 claims description 13
- 238000010168 coupling process Methods 0.000 claims description 13
- 238000005859 coupling reaction Methods 0.000 claims description 13
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 9
- 230000009849 deactivation Effects 0.000 claims description 7
- 238000007789 sealing Methods 0.000 claims description 4
- 239000003921 oil Substances 0.000 description 14
- 238000003860 storage Methods 0.000 description 14
- 210000000078 claw Anatomy 0.000 description 11
- 238000001514 detection method Methods 0.000 description 8
- 239000000498 cooling water Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 239000000446 fuel Substances 0.000 description 4
- 230000035699 permeability Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000005294 ferromagnetic effect Effects 0.000 description 2
- 230000001939 inductive effect Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000005291 magnetic effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000000153 supplemental effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B21/00—Combinations of two or more machines or engines
- F01B21/02—Combinations of two or more machines or engines the machines or engines being all of reciprocating-piston type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
- F01B1/12—Separate cylinder-crankcase elements coupled together to form a unit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
- F01B1/04—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in V-arrangement
-
- 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
- F02B73/00—Combinations of two or more engines, not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F7/0021—Construction
- F02F7/0031—Construction kit principle (modular engines)
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F7/0002—Cylinder arrangements
- F02F7/0012—Crankcases of V-engines
Definitions
- the present invention relates to an internal combustion engine.
- DE 31 32 368 A1 discloses a vehicle engine.
- This vehicle engine comprises at least two engine blocks.
- the two engine blocks each have their own crankshaft.
- One of the crankshafts is connected to an output shaft by means of a closing / free-wheeling clutch.
- a first transmission is provided between the one-way clutch and the output shaft.
- a second transmission is provided, which connects the crankshaft with a transmission shaft part by means of a freewheel.
- the transmission shaft part is part of a transmission shaft that runs parallel to the crankshafts.
- the transmission shaft has a second part. Via the transmission shaft, the output of the engine block is transmitted to the same output shaft to which the power of the second engine block is transmitted.
- DE 27 47 131 A1 a vehicle unit is disclosed.
- This document discloses various engine arrangements or vehicle aggregates in which, for example, two in-line engines are arranged next to one another or are arranged in a V-shape relative to one another and are coupled to one another via a "frame"
- the vehicle assembly may be configured such that two V-shaped engine blocks are arranged in a V-shape relative to each other.
- an output shaft is disclosed, which is arranged below the cylinder heads.
- a stopped second internal combustion engine part is to be accelerated to a rotational speed until the speed difference permissible for the engagement process is reached or undershot.
- the friction clutch should be controlled accordingly and thus the jaw clutch should initially be bridged.
- first end faces of the at least three claws come into sliding contact with a second base. While maintaining a permissible speed difference, the first end faces should slide on the second base.
- An engagement process is to be initiated automatically by the transition of a second base to a second engagement phase and the associated clearance when the required angular position is set and the respective claw can engage in the associated pawl pocket.
- DE 10 2010 005915 A1 discloses a method and a device for operating a multi-cylinder internal combustion engine.
- This document describes a synchronizing clutch required for connecting and disconnecting a sub-cylinder unit on a mass balance shaft of a permanently operated cylinder unit.
- the mass balance shaft and thus the crankshaft of the permanently operated cylinder unit can be connected and disconnected with the crankshaft of the cylinder unit which can be switched on and off.
- no additional shaft is required to actuate the cylinder inlet and cylinder deactivation.
- crankshaft is divided into two sections.
- the ends of the crankshaft sections support bevel gears which cooperate with a multi-plate clutch which is suitably operated to connect the two crankshaft sections or to keep a left-hand cylinder group idle.
- An output shaft is connectable to a right cylinder group, and a bevel gear of an associated crankshaft section also drives, via another bevel gear, an air compressor housed in the cylinder, which communicates with an air intake manifold of the engine via a passage.
- a vehicle engine which is composed of blocks, each of which contains at least one cylinder and which have at their end faces mutually similar fastening means which are arranged symmetrically with respect to a vertical center plane.
- the engine includes a block having an odd number of cylinders and a block having an even number of cylinders, for example, two and three cylinders, respectively, which allow combinations of 2 + 2 and 3 + 3 combinations with an odd total number of cylinders.
- the blocks may be directly interconnected with the housing containing the auxiliaries then connected to the free end of one of the blocks, while a housing for transmission to an output shaft is connected to the free end of the other block.
- the blocks may be interconnected via a housing containing a transmission for an output shaft.
- the transmission housing may then include clutches that selectively connect the crankshafts of the two blocks to the output shaft.
- the vehicle engine comprises a first engine block and a second engine block, which are interconnected via a transmission housing.
- a manual transmission is provided with an output shaft.
- a differential for a front-wheel drive is provided, in which the performance is transmitted via a hollow shaft arrangement.
- the power transmission should be done by means of a chain or belt drive.
- a drive part forms part of the housing for two clutches and freewheel wheels.
- a crankshaft is connected to a central shaft which carries a clutch disc and a freewheel 46a which cooperate with the housing.
- the central shaft is continued by a free-running extension, which protrudes through another coupling housing.
- a crankshaft is connected to a torque converter. Furthermore, the crankshaft has a clutch disc. On the clutch disc, a shaft is fixed, which encloses the shaft. The shaft can interact by means of a freewheel with clutch housings and also interact by means of a clutch disc 53 directly to the clutch housing.
- a microcomputer is disclosed which opens or closes respective clutches when the output varies depending on the traffic or road conditions.
- WO 2012/142993 discloses an internal combustion engine having a main engine with a first crankshaft part rotating about an axis of rotation and a supplemental engine with a second crankshaft part. Between the crankshaft parts a synchronizer clutch is arranged, which is formed of a friction clutch and a form-locking coupling.
- the friction clutch is designed as a multi-plate clutch and serves to equalize the rotational speeds of the two crankshaft parts during their synchronization.
- the form-fitting coupling contains the first crankshaft part associated form-fitting elements and the second crankshaft part associated form-fitting elements, which forms the positive engagement between them during axial operation of the positive locking clutch at a predetermined differential speed between the two crankshaft parts.
- the interlocking elements are formed from trapezoidally aligned in the axial direction claws.
- Object of the present invention is to provide a compact and simple design engine, which ensures high reliability.
- the invention has the features specified in patent claim 1.
- Advantageous embodiments thereof are specified in the subclaims.
- an internal combustion engine is provided with at least two mutually coupled engine blocks each having two cylinders, which are each connected to a transmission and a clutch with a common drive shaft.
- an engine block is understood to be a housing which, in addition to cylinders and corresponding cylinder heads, comprises a crankshaft bearing, a crankcase and a corresponding water or air cooling system.
- both engine blocks are individually decoupled from the drive shaft via the corresponding coupling, the engine is redundant. In this way, both engine blocks can be operated completely independently of each other. This results in a high level of safety when using the engine in airplanes, since if one engine block fails, it can be automatically or manually disengaged and the other engine block continues to run without it being braked or blocked by the failed engine block.
- the two engine blocks can be V-shaped such that the respective cylinder heads are arranged V-shaped and the drive shaft is arranged in the region of the V-recess between the cylinder heads.
- Such an arrangement of the drive shaft allows a compact construction of the engine.
- the two engine blocks can also be designed such that they form a boxer engine.
- the drive shaft can then be arranged corresponding to above or below the cylinder.
- Each engine block can have its own crankshaft.
- the engine according to the invention thus does not have a continuous crankshaft. Therefore, the drive torque does not have to be transmitted from one side of the engine through the crankshaft to the one-sided output.
- the torque is output via output-side or outer ends of the crankshafts.
- an internal crankshaft e) lenwange including storage is only the leadership and balance. This allows a very simple and easy design of the crankshafts, which are inexpensive to manufacture.
- crankshaft can be constructed as a built-up crankshaft, i. be formed as a 15 lightweight assembled crankshaft from individual parts.
- the connecting rods require no Lagerverschraubung and can be easily assembled.
- crankshaft cheeks designed, for example, as fineblanked parts or forged cheek segments.
- Special contour elements such as collars or penetrations, increase the length of the joint for the cheek - bearing connection and ensure the separation of the thermal and geometric notches. This leads to an improvement in the component stiffness.
- a forged or milled from the solid crankshaft requires connecting rods, which must be designed separable at the bearing to the crankshaft for mounting. This requires 30 more weight and higher production costs.
- the transmission could be designed as a belt transmission or as a gear transmission. Furthermore, the two gear can be arranged at the output side ends of the crankshafts, which connect them to the drive shaft.
- the two transmissions can be arranged in the region in which the two motor blocks are connected to one another or coupled to one another.
- the gears are then preferably designed as a gear transmission.
- the gear can be designed such that in each case a arranged on the crankshaft first gear is connected via a second gear with a arranged on the output shaft third gear.
- the transmission can be made smaller with a given transmission ratio.
- a gear arranged on a camshaft to be engaged by way of a fourth gearwheel coupled to the second gearwheel such that the camshaft is driven or driven via the gearwheel pair consisting of fourth and fifth gearwheels.
- the clutches can be designed such that they enable a coupling of the corresponding crankshaft to the drive shaft only in a single angular position.
- This can for example be realized by a dog clutch, in which a claw of one half of the dog clutch has a different geometry than the other claws, so that this claw is engageable only in a corresponding recess of the other half of the dog clutch.
- the two engine blocks of the engine at standstill manually, ie be engaged by hand only in this one position.
- the coupling in only one position has the advantage that the engine blocks are always coupled in the same angular position and so the balance of the engine parts remains the same even when reconnecting the engine parts. A manual adjustment of the engine parts is therefore not necessary.
- the engine may have a lower or upper camshaft.
- An underlying camshaft reduces the space required by the combustion engine.
- a device for, preferably mechanical, decoupling of rocker arms and camshaft be provided such that a cylinder shutdown is possible.
- the push rods are moved in the region of the camshaft so that here the transfer of the lifting movement is disengaged from the camshaft to the push rod.
- An associated cylinder deactivation makes it possible to switch off one of the two engine blocks or its cylinders and in this way continue to operate the other engine block at its optimum operating point in the range between 70% and 80% load.
- the cylinder deactivation is preferably carried out in the lower part load range. In this operating range, the entire engine would reach a poor efficiency.
- these cylinders act as spring accumulators and consume significantly less energy during idling than when corresponding changes in gas occur due to the gas exchange when the valves open.
- the internal combustion engine which would have a poorer efficiency with only 35, in particular 40% of the power across all cylinders of both engine blocks, instead be operated with 70, in particular 80% of the power with only one engine block. This increases the overall efficiency and at the same time reduces fuel consumption.
- the internal combustion engine may have a water cooling device for cooling the cylinder heads, wherein on the drive shaft at least one roller fan is arranged, which is likewise designed to cool the cylinder.
- the roller fan which is arranged on the drive shaft, allows a high volume flow for cooling the cylinder, at the same time low pressure. Cooling air can be selectively supplied via such air cooling in order to support the water cooling device of the cylinder heads.
- the roller fans also ensure that the engine does not have to be supplied externally with a cooling air flow. Due to the roller fans, the cylinders are always forced cooled as long as the drive shaft rotates, ie the engine is running.
- the internal combustion engine according to the invention comprises all components which are necessary for the operation of one of the two engine blocks of the engine in duplicate, only the drive shaft is present only once. There may also be two completely separate power grids, which are connected to the on-board supply via diodes in order to avoid mutual influences of the power grids on each other.
- the engine according to the invention preferably has two separate cooling and oil circuits and correspondingly two cooling water and two oil pumps.
- the second engine block is not loaded by the cooling line to be applied to the first engine block.
- the internal combustion engine according to the invention is preferably intended for use in aircraft, in particular in ultralight aircraft.
- the internal combustion engine also have an electric drive, whereby it is thus designed as a hybrid drive.
- the additional electric motor also serves for short-term performance enhancement, e.g. at take-off, in short-term climb or in aerobatics.
- An advantage of the engine concept is therefore also that the cylinders are air-cooled, but the cylinder head is water-cooled. If the cooling water is lost, the engine can continue to run in emergency mode for a certain amount of time even without cooling water, since the heat can also be dissipated via the forced air-cooled cylinders.
- the internal combustion engine according to the invention is preferably completely redundant. This means that all ancillaries also exist at least twice are. This will be achieved eg two separate lubrication systems, two separate circuits, two generators, two turbochargers, etc.
- an intermediate plate for connecting at least two engine blocks is provided.
- the intermediate plate is a plate-shaped component which has two sealing surfaces, which are designed to seal one side of an engine block, wherein the intermediate plate has at least one bearing bore for receiving at least one bearing of a crankshaft.
- Such an intermediate plate serves both for sealing and for connecting the two engine blocks.
- a storage opening with corresponding storage devices for supporting the two crankshafts is arranged in the intermediate plate.
- the storage opening can be designed for coaxial storage of two crankshafts.
- the two crankshafts are stored in the intermediate plate both in the area of the crank arm and in the middle.
- the center distance of the bearing of each crankshaft part can be designed as large as possible
- a crankshaft at the corresponding end has a pin-shaped portion
- the other crankshaft has a tubular portion at the corresponding end.
- the crankshafts mesh with one another, whereby the bearing distances of each crankshaft are made substantially larger than if a separate bearing were provided for each crankshaft part in the middle of the intermediate plate.
- An engine according to the invention preferably has a displacement of between 1500 and 2000 cc.
- the power of the engine can be in a suction version at about 150 hp and in the turbocharger version at about 200 hp.
- the additional power through the electric motor can be about 30 hp (continuous load) and 50 hp (peak load).
- the combustion engine offers more power in a smaller space compared to comparable comparable four-cylinder aircraft engines available on the market. It is also lighter and easier to set up.
- the internal combustion engine comprises two identical V-engines, one of which is designed as a left-hand rotor and one as a right-handed runner.
- the two crankshafts rotate in the same direction of rotation. Due to the fact that the drive off of the crankshafts takes place on both end sides of the engine, a bearing of the crankshaft ends in itself is possible in the region of the intermediate plate. As a result, the bearing distances of these crankshaft parts can be maximized without lengthening the length of the engine.
- This internal combustion engine also allows due to its construction a simple timing belt replacement, since only the drive shaft and not the entire engine must be removed.
- sensors are provided with which an operating condition of the two engine blocks can be detected independently.
- the operating state sensors may be arranged in both clutches as torque sensors.
- the torque sensors may be designed as electronic sensors for torque detection, for example as piezoelectric sensors or non-contact torque sensors.
- the Fraunhofer ITWM sells an inductive sensor for non-contact detection of torques.
- the measuring concept of the sensor is based on the anisotropic magnetostrictive effect in ferromagnetic wave surfaces.
- This effect causes a different magnetic permeability in the direction of the tensile stresses and compressive stresses as a function of the mechanical torsional stresses at the measuring point.
- this permeability change is measured, which is proportional to the torsional stress on the shaft surface over a wide measuring range.
- Another way to torque detection is to provide a spring-loaded roller on the gear, such as a tension roller adjacent to a run of the belt. Depending on whether the belt drive the drive shaft or the engine block (in case of failure) is driven, one or the other run of the belt is stretched. This tension can be detected with the tension pulley and a corresponding sensor. Additionally and / or alternatively, at least two exhaust gas sensors may be provided, which are correspondingly integrated into the exhaust system of the two engine blocks in such a way that the exhaust gas temperatures of the two engine blocks can be monitored independently of one another.
- the internal combustion engine according to the invention has a control device (not shown) which monitors the torque and / or the exhaust gas temperature of the two engine blocks by means of the sensors.
- FIG. 1 is a perspective view of an internal combustion engine according to the invention
- FIG. 2 shows the internal combustion engine of Figure 1 in a side exploded view
- FIG. 3 shows two V-shaped arranged cylinder blocks with intermediate plate of the inventive internal combustion engine in a perspective exploded view
- FIG. 7 is a further perspective view of the internal combustion engine according to the invention
- Fig. 8 is a perspective view of a turbocharger with intercooler
- Fig. 9 is another perspective view of the turbocharger with intercooler
- FIG. 10 is a perspective view of the internal combustion engine according to the invention with two provided on the intermediate plate gear housings, and
- FIG. 1 shows the transmission of the embodiment shown in Figure 10 with a camshaft control in a perspective view
- FIG. 12 shows a device for decoupling rocker arms in a perspective view
- FIG. 13 shows an alternative embodiment of the device for decoupling
- FIG. 14 shows an alternative embodiment of the device for decoupling rocker arms in a perspective view.
- An embodiment of an internal combustion engine 1 comprises two mutually coupled V-type engines or engine blocks 2, 3, each with two cylinders 4 (FIGS. 1 to 3).
- the V-shaped engine blocks have corresponding V-shaped arranged cylinder or cylinder heads.
- a piston (FIG. 4) is arranged, each of which acts on a crankshaft 5, 6 with a connecting rod.
- the first and second crankshaft 5, 6 of the first and second engine blocks 2, 3 are thus formed separately, i. they are not connected.
- crankshafts 5, 6 are each mounted with their ends on an intermediate plate 11 and on a first or second crankcase 8, 10.
- the intermediate plate 1 1 is arranged between the two crankcases 8.10.
- the crankcase 8,10 are arranged at the from the intermediate plate 1 1 facing away outer sides of the engine blocks 2.3.
- the intermediate plate 1 1 is for sealing and connecting the first and second engine block 2, 3 with first and second crankcase 8, 10 is formed ( Figures 2 to 5).
- the intermediate plate 1 1 is a disc-shaped element on the radially circumferentially equally spaced from each other holes 12 are formed for connection to the two Kur- belgeperusen 8, 10.
- a transverse to the intermediate plate 1 1 extending bearing bore 13 is formed (Fig. 5)
- a storage-side end 18 of the first crankshaft 5 and a storage-side end 19 of the second crankshaft 6 are arranged.
- the storage-side end 18 of the first crankshaft 5 is a tubular portion 20.
- the storage-side end 19 of the second crankshaft 6 is a pin-shaped portion 21.
- the outer diameter of the pin-shaped portion 21 is smaller than the inner diameter of the tubular portion 20. (Is that correct?)
- a bearing device 17 such as a sliding, ball or roller bearing, is provided between the inner surface of the bearing bore and the outer surface of the tubular portion 20.
- a further storage device 17 is arranged in the tubular portion of the pin-shaped portion 21 of the second crankshaft 6 in the bearing bore 13 and the further bearing means 17, the two crankshafts are completely decoupled from each other in their rotational movement.
- the bearing bore 13 is extended on both sides of the intermediate plate by corresponding pipe sections 14 and expanded in diameter.
- the pipe sections 14 are additionally connected via stiffening struts 15 with the intermediate plate 1 1.
- the cavities of the pipe sections 14 form storage openings 16.
- crank webs 36 of the first and second crankshaft 5, 6 are mounted (Fig. 5).
- the two crankshafts 5, 6 are thus stored in the intermediate plate 1 1 both in the region of the crank arm 36 and in the middle of the bearing opening 13 of the intermediate plate 1 1.
- the center distance of the bearings of each crankshaft can be made large.
- the bearing distances of each crankshaft can be made substantially larger than if a separate bearing were provided in the middle of the intermediate plate for each crankshaft part.
- the storage-side end 18 of the first crankshaft 5 and the storage-side end 19 of the second crankshaft 6 are decoupled from one another and stored in their own storage device 17 in the storage opening 16 (not shown).
- camshaft drive 22 and an oil pump drive 23 are provided on the intermediate plate 1 1 (FIGS. 3 to 5).
- the camshaft 22 and oil pump drives 23 are designed as bevel gear wheel and extend from the region of the bearing bore 13 in which they are in engagement with one of the crankshafts 5,6, radially outwardly to camshaft 33 and an oil pump.
- these drives could also be designed as a spur or other gear
- a device 39 for, preferably mechanical, decoupling rocker arms 40 and camshaft 33 is provided (FIGS. 12 to 14).
- the device 39 comprises an eccentric shaft 41 on which the rocker arms 40 are mounted eccentrically such that the pivot point of the rocker arms 40 can be displaced such that the rocker arms 40 can no longer reach the valves 44 due to the displacement of the pivot point in the actuated state.
- valves remain closed even with a lifting movement of the push rod 41, whereby a cylinder deactivation is possible.
- the rotation of the eccentric shaft can take place, for example, by means of a hydraulic cylinder 42.
- This or the hydraulic cylinders are connected via a valve, such. B. a solenoid valve, an electric valve or a mechanical valve can be controlled.
- a valve such. B. a solenoid valve, an electric valve or a mechanical valve can be controlled.
- the engine oil pressure existing from the engine circuit can be used.
- the eccentric shaft 43 can thus be arranged in a rocker arm disengaged position and in a rocker arm engaged position.
- a spring 45 may be provided which presses the rocker arm even with rotated eccentric shaft on the push rod 41, whereby it is held on the camshaft 33.
- the eccentric shaft 43 may also be actuated electromagnetically or mechanically.
- a spring 46 may be provided which pushes up the push rod 41 in the cylinder head.
- the rocker arm 40 also remains on the valve.
- a mechanical decoupling of the rocker arms 40 from the camshafts 33 may be realized by means for displacing the plungers and thereby disengaging the rocker arms so that the plungers are no longer in communication with the rocker arms.
- the push rods are moved in the region of the camshaft so that here the transfer of the lifting movement is disengaged from the camshaft to the push rod.
- the two V-shaped first and second engine blocks 2, 3 form a V-recess 24 in the region between their cylinders.
- a drive shaft 26 is arranged in the area of the V-recess between cylinder heads 25 of the cylinder 4.
- crankcases 8.10 In the au wash matter arranged crankcases 8.10 is in each case a transmission 72 and a clutch 28, which connects the respective output-side end of the first crankshaft 7,9 and 5 of the second crankshaft 6 with the drive shaft 26 (Fig. 6).
- Such an arrangement of the gear 27 is referred to as an external gear assembly.
- the gear 27 are designed as belt transmissions. Alternatively, the gear 27 may also be designed as a gear transmission.
- the two transmissions 27 can, according to an advantageous embodiment, be arranged in the region in which the two engine blocks 2, 3 are connected or coupled with one another. This means that the gear 27 are in the range of intermediate plate 1 1 arranged. Such an arrangement of the gear 27 is referred to as internal gear assembly.
- the gear 27 are then preferably designed as a gear transmission.
- the gear 27 may be formed such that in each case a arranged on the crankshaft first gear 47 is connected via a second gear 48 with a arranged on the output shaft 26 third gear.
- the transmission can be made smaller or formed at a given transmission ratio.
- a fifth gearwheel arranged on a camshaft engages in such a way that the camshaft is driven or driven via this gearwheel pair consisting of fourth and fifth gearwheel 50, 51 becomes.
- the gears are covered by a fixed to the intermediate plate 1 1 housing 52.
- the clutches 28 are designed as jaw clutches.
- the jaw clutches are designed such that a claw of one half of the claw coupling has a different geometry than the other claws, so that this claw can only be engaged in a correspondingly complementary recess of the other half of the claw coupling. This ensures that the two halves of the couplings 28 can be engaged with each other only in a certain rotational position.
- Each of the two engine blocks 2, 3 is provided with a turbocharger 29.
- the internal combustion engine 1 is redundantly formed by the two separate turbocharger systems 29 with respect to the air supply. This means that if one part of the engine fails and the turbocharger gets damaged, this only leads to a 50% loss of power, because then the remaining engine part with turbocharger still reaches its full capacity. Alternatively, a single turbocharger is conceivable.
- Intercoolers for cooling the compressed and heated intake air are integrated in a section of pipe between the turbochargers 29 and the intake bends to the cylinders. These coolers are designed to increase their surface of lamell lenförmigen pipe sections. In the inner part of these pipe sections, the compressed and heated air flows from the turbochargers to the intake pipes and gives off the heat to the corrugated pipe fins. Cooling air flows in the opposite direction around the fins on the outside of the pipe fins and dissipates the heat here. The oppositely directed air flows result in an optimal cooling effect combined with very small installation space and low weight.
- roller fans 31 On the drive shaft 26, two roller fans 31 are provided.
- the roller fans cause that the engine does not have to be supplied with a cooling air flow from the outside.
- the cylinders are always cooled by the roller fans as long as the drive shaft rotates, ie the engine is running.
- a water cooling device 35 with two separate cooling circuits for cooling the two engine blocks 2, 3 is arranged.
- a cooling fan 30 is provided in this area in order to increase the cooling capacity.
- This cooling fan 30 provides an air flow for both the intercooler and the water cooling device 35 ready.
- a fan housing of the cooling fan is designed such that it leads in the upper part of the cooling air flow to the intercoolers. The lower area ensures the supply of the cooling air flow to the water cooling device 35.
- a driven end 32 of the drive shaft are two separate generators 34 to ensure at any time, ie even in case of failure of a generator sufficient power.
- These generators can also be electric drives to form a hybrid drive.
- the above-explained camshaft drive is arranged centrally on the intermediate plate.
- the camshaft and oil pump drives can be arranged on the opposite / outer sides of the housing.
- the internal combustion engine can also have an electric drive (FIGS. 2 and 7), as a result of which the internal combustion engine is designed as a hybrid drive.
- sensors are provided with which an operating state of the two engine blocks can be detected independently of one another.
- These sensors can preferably be designed for the independent detection of the torque of the two engine blocks or also of the exhaust gas temperatures of the two engine blocks or else for the detection of other suitable parameters for determining the operating state. These sensors are therefore subsumed below under the term operating condition sensors.
- the operating state sensors may be arranged in both clutches as torque sensors.
- the torque sensors may be designed as electronic sensors for torque detection, for example as piezoelectric sensors or non-contact torque sensors.
- the Fraunhofer ITWM sells an inductive sensor for non-contact detection of torques.
- the measuring concept of the sensor is based on the anisotropic magnetostrictive effect in ferromagnetic wave surfaces. This effect causes a different magnetic permeability in the direction of the tensile stresses and compressive stresses as a function of the mechanical torsional stresses at the measuring point. With the sensor, this permeability change is measured, which is proportional to the torsional stress on the shaft surface over a wide measuring range.
- Another way of detecting torque is to apply a spring-loaded pulley to the transmission, such as a spring. to provide a tension roller adjacent to a run of the belt. Depending on whether the belt drive the drive shaft or the engine block (in case of failure) is driven, one or the other run of the belt is stretched. This tension can be detected with the tension pulley and a corresponding sensor.
- At least two exhaust gas sensors may be provided, which are correspondingly integrated in the exhaust system of the two engine blocks in such a way that the exhaust gas temperatures of the two engine blocks can be monitored independently of each other.
- the internal combustion engine according to the invention has a control device (not shown) which monitors the torque and / or the exhaust gas temperature of the two engine blocks by means of the sensors. Once the torque of one of the two engine blocks over a longer period, eg. B. greater than 0.5, or 1, or 1, 5, or 2, or 3 or 4 seconds, having a predetermined difference from the other engine block, the control device controls the clutch of the corresponding engine block and disengages this , In this way, the crankshaft of this engine no longer has to be turned and the other engine can continue to work without the frictional resistance of the failed engine block.
- a control device not shown
- a manual disengagement may additionally or alternatively be provided.
- the driver receives this information from the control electronics. This can then Disconnect the engine by manually or electrically actuating the appropriate clutch.
- the internal combustion engine comprises two - except for the mirrored camshaft - completely identical engines or engine blocks, each of which is operable by itself.
- component reduction would be, e.g. Although the cooling water and oil containers and cooler to separate the circuit side, but, for. the double containers or coolers in each case in a double component summarize.
- engagement may be possible during operation as long as a clutch can be provided to ensure the unique angular position during engagement during the run.
- engagement in any angular position of the two engine parts would be conceivable, but then the unbalance of the two engine parts could add up in the worst case and thus double.
- the two gears can also be arranged in the region of the intermediate plate.
- the at least two engine blocks are preferably arranged in a V-shape. But it is also a boxer or a series arrangement of the cylinder possible.
- an engine block may also comprise only one cylinder.
- the engine blocks can also be designed as a series or boxer engines.
- the internal combustion engine according to the invention comprises all components which are necessary for the operation of an engine block of the engine in duplicate, only the drive shaft is present only once. This means that there are two completely separate power grids, which are supplied by two separate generators and which are connected to the on-board supply via diodes for protection.
- the motor according to the invention has two separate cooling and oil circuits and correspondingly two cooling water and two oil pumps. This means that even if an engine block fails, an operation of the second engine block is ensured.
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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PL15771961T PL3201437T3 (pl) | 2014-09-30 | 2015-09-30 | Silnik spalinowy |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014114183.0A DE102014114183A1 (de) | 2014-09-30 | 2014-09-30 | Verbrennungsmotor |
PCT/EP2015/072636 WO2016050885A1 (de) | 2014-09-30 | 2015-09-30 | Verbrennungsmotor |
Publications (2)
Publication Number | Publication Date |
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EP3201437A1 true EP3201437A1 (de) | 2017-08-09 |
EP3201437B1 EP3201437B1 (de) | 2020-04-22 |
Family
ID=54238445
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP15771961.8A Active EP3201437B1 (de) | 2014-09-30 | 2015-09-30 | Verbrennungsmotor |
Country Status (6)
Country | Link |
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US (1) | US10837282B2 (de) |
EP (1) | EP3201437B1 (de) |
CN (1) | CN107250484B (de) |
DE (1) | DE102014114183A1 (de) |
PL (1) | PL3201437T3 (de) |
WO (1) | WO2016050885A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2020234857A1 (en) * | 2019-05-22 | 2020-11-26 | Viveknath Richards | Four stroke internal combustion engine of v-twin layout with innovative arrangement |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102014221293A1 (de) * | 2014-10-21 | 2016-04-21 | Volkswagen Aktiengesellschaft | Verfahren und Steuervorrichtung zum Erkennen eines Verbrennungsvorgangs einer Verbrennungskraftmaschine eines Hybridfahrzeugs |
CN108331663B (zh) * | 2018-02-07 | 2019-08-30 | 广西玉柴机器股份有限公司 | 大功率v型多缸柴油机系统 |
CN108252803B (zh) * | 2018-02-07 | 2022-04-01 | 广西玉柴机器股份有限公司 | V型12缸柴油机 |
WO2019183427A1 (en) * | 2018-03-22 | 2019-09-26 | Continental Motors, Inc. | Engine ignition timing and power supply system |
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SE7611617L (sv) | 1976-10-20 | 1978-04-21 | Kronogard Sven Olof | Fordonsmaskineri |
SE8006807L (sv) * | 1980-09-29 | 1982-03-30 | United Motor & Transmissions A | Fordonsmotor |
SE434972B (sv) | 1981-07-21 | 1984-08-27 | Volvo Ab | Fordonsmotor |
DE3619351C2 (de) * | 1985-06-27 | 1995-04-27 | Kaniut Sen Herbert Dipl Ing | Multi-Split-Motor für Kraftfahrzeuge mit geteilter Kurbelwelle und Motor-Querwelle für Hilfsgeräte-Antriebe |
US5429080A (en) * | 1993-12-13 | 1995-07-04 | Evestar Technologies, Inc. | Compact internal combustion engine |
DE19839231A1 (de) | 1998-08-28 | 2000-03-02 | Peter Pelz | Antriebssystem, insbesondere für ein Kraftfahrzeug, Vorrichtung zur Leistungssteuerung eines Antriebssystems und Verbrennungsmotor |
GB2344378A (en) | 1998-12-05 | 2000-06-07 | Rover Group | Modular i.c. engine |
US6306056B1 (en) * | 1999-12-17 | 2001-10-23 | Daimlerchrysler Corporation | Dual engine hybrid electric vehicle |
US20070079778A1 (en) * | 2005-10-11 | 2007-04-12 | Atkinson Michael K | Cylinder block for integral gas compressor and internal combustion engine |
EP2067961B1 (de) | 2007-12-05 | 2014-11-12 | Volvo Car Corporation | Kupplungsvorrichtung |
JP5014264B2 (ja) | 2008-06-06 | 2012-08-29 | 本田技研工業株式会社 | 空冷式汎用v型エンジンにおける潤滑装置 |
KR101063382B1 (ko) * | 2008-09-04 | 2011-09-07 | 기아자동차주식회사 | 마그네슘 엔진블록 |
DE102010005915B4 (de) * | 2010-01-27 | 2013-01-17 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Vorrichtung zum Betreiben einer mehrzylindrigen Brennkraftmaschine |
DE102011018410A1 (de) | 2010-05-31 | 2012-01-19 | Schaeffler Technologies Gmbh & Co. Kg | Antriebsbaugruppe |
DE102010022544B4 (de) * | 2010-06-02 | 2019-08-22 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Vorrichtung zum Ausgleich der freien Massenkräfte und Massenmomente bei Brennkraftmaschinen mit einem geteilt ausgeführten Kurbeltrieb |
DE102010022674B4 (de) | 2010-06-04 | 2014-09-04 | Audi Ag | Antriebsvorrichtung für ein Kraftfahrzeug |
DE102010036576A1 (de) | 2010-07-22 | 2012-01-26 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Brennkraftmaschine |
DE112012001771A5 (de) | 2011-04-20 | 2014-01-09 | Schaeffler Technologies AG & Co. KG | Verfahren zum Betrieb einer Brennkraftmaschine mit geteilter Kurbelwelle und Synchronkupplung zur Kopplung zweier Kurbelwellenteile einer Brennkraftmaschine |
US8919311B2 (en) * | 2013-03-06 | 2014-12-30 | General Electric Company | Method and systems for variable valve timing for a V-engine with a single central camshaft |
DE102013005652B4 (de) * | 2013-04-04 | 2015-01-08 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Kupplungseinrichtung zum winkelgetreuen und zündfolgerichtigen Verbinden von Brennkraftmaschinenteilen |
CN203685386U (zh) | 2014-01-24 | 2014-07-02 | 长安大学 | 一种最大输出功率可调节式组合发动机 |
-
2014
- 2014-09-30 DE DE102014114183.0A patent/DE102014114183A1/de not_active Withdrawn
-
2015
- 2015-09-30 CN CN201580064334.8A patent/CN107250484B/zh active Active
- 2015-09-30 EP EP15771961.8A patent/EP3201437B1/de active Active
- 2015-09-30 WO PCT/EP2015/072636 patent/WO2016050885A1/de active Application Filing
- 2015-09-30 US US15/515,422 patent/US10837282B2/en active Active
- 2015-09-30 PL PL15771961T patent/PL3201437T3/pl unknown
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2020234857A1 (en) * | 2019-05-22 | 2020-11-26 | Viveknath Richards | Four stroke internal combustion engine of v-twin layout with innovative arrangement |
Also Published As
Publication number | Publication date |
---|---|
DE102014114183A1 (de) | 2016-04-14 |
WO2016050885A1 (de) | 2016-04-07 |
US10837282B2 (en) | 2020-11-17 |
EP3201437B1 (de) | 2020-04-22 |
CN107250484A (zh) | 2017-10-13 |
CN107250484B (zh) | 2020-03-17 |
PL3201437T3 (pl) | 2021-01-11 |
US20180051563A1 (en) | 2018-02-22 |
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