POWER UNIT

Abstract

The invention relates to a power unit, in particular for a hybrid vehicle, comprising a reciprocating piston engine and comprising a generator which can be in driving engagement therewith, wherein the reciprocating piston engine has at least two pistons, which are guided in at least two cylinders in tandem arrangement, and two counter-rotating crankshafts, which are connected to the pistons by connecting rods and which are mechanically coupled so as to be in phase, wherein a first generator can be driven by the first crankshaft and a second generator can be driven by the second crankshaft.

Claims

1. A power unit, in particular for a hybrid vehicle, comprising a reciprocating piston engine and comprising a generator which can be in driving engagement therewith, wherein the reciprocating piston engine has at least two pistons, which are guided in at least two cylinders in tandem arrangement, and two counter-rotating crankshafts, which are connected to the pistons by connecting rods and which are mechanically coupled so as to be in phase, characterized in that a first generator is driven by the first crankshaft and a second generator is driven by the second crankshaft, wherein the generators are connected to the respective crankshafts by a toothed gear mechanism or by a traction means, wherein the first generator and the second crankshaft as well as the second generator and the first crankshaft in each case rotate in opposing directions at a rotational speed ratio of 2:1, and wherein the generators in each case comprise at least one imbalance and act as balancing shafts.

2. (canceled)

3. (canceled)

4. The power unit according to claim 1, characterized in that the toothed gear mechanism comprises a toothed crank web, which is coupled to a drive pinion of the relevant generator.

5. The power unit according to claim 1, characterized in that the toothed gear mechanism comprises at least one toothed gear, which is connected, for conjoint rotation, to a shaft pin of the corresponding crankshaft, said shaft pin protruding over the main bearing, and which is coupled to a drive pinion of the relevant generator.

6. The power unit according to claim 1, characterized in that the traction means comprises a chain or a toothed chain or a toothed belt.

7. The power unit according to claim 6, characterized in that a first traction means connects the first generator to the first crankshaft and a second traction means connects the second generator to the second crankshaft.

8. The power unit according to claim 1, characterized in that the generators are arranged on either side adjacent to the crankshafts, the crankshaft axes span a virtual reference plane through the main bearing, and the generator axes are arranged in the reference plane or above the reference plane between the crankshafts and the upper dead centre of the pistons.

9. The power unit according to claim 1, characterized in that the cylinders are offset on the anti-thrust side and the crankshafts have counterweights, which are arranged to as to be phase-shifted.

10. The power unit according to claim 1, characterized in that the firing interval is a 0° crank angle, in particular in 4-stroke operation.

11. The power unit according to claim 1, characterized in that the crankshafts have toothed crank webs, which are in engagement with one another for coupling the crankshafts.

12. The power unit according to any one of the preceding claims, characterized in that the crankshafts have toothed gears which are in engagement with one another for coupling the crankshafts, wherein the toothed gears are arranged between the main bearings of the crankshafts or on the shaft pins of the crankshafts, said shaft pins protruding over the respective main bearings.

13. The power unit according to claim 1, characterized in that four pistons are guided in four cylinders in a square-four arrangement, two pistons thereof being connected in each case to the same crankshaft by connecting rods, wherein the crank pin offset is 270° and pistons arranged diagonally opposite reach the dead centre point simultaneously.

14. The power unit according to claim 1, characterized in that each cylinder is in fluidic connection with an outlet channel, wherein the outlet channels of the cylinders open into a common central exhaust gas channel.

15. The power unit according to claim 14, characterized in that a turbocharger is connected, in particular directly, to the exhaust gas channel.

16. The power unit according to claim 4, characterized in that the crankshafts have toothed gears or toothed crank webs, which are connected to one another in terms of rotation via a toothed belt which comprises teeth on either side for coupling the crankshafts, wherein the toothed belt is wrapped around one of the toothed gears or one of the crank webs.

17. The power unit according to claim 16, characterized in that the toothed belt which comprises teeth on either side has 2 to 4 teeth more than the toothing of the toothed gear or the crank web of the second crankshaft.

18. A vehicle, in particular hybrid vehicle, comprising a power unit according to claim 1.

Description

[0022] In the drawings

[0023] FIG. 1 shows a front view of a power unit with generators arranged in a V shape;

[0024] FIG. 2 shows a front view of a power unit in accordance with an exemplary embodiment according to the invention with horizontally arranged generators;

[0025] FIG. 3 shows a sectional view of the cylinder head of the power unit according to FIG. 1 or FIG. 2 with a turbocharger;

[0026] FIG. 4 shows a schematic illustration of the low-noise crankshafts coupled via a toothed belt which comprises teeth on either side.

[0027] The schematically illustrated power unit in accordance with the exemplary embodiments according to the invention according to FIGS. 1 and 2 has two cylinders 1 and 2 arranged in tandem form (see FIG. 1), in which pistons are guided and which each drive a crankshaft 7 and 8 for example in four-stroke operation via connecting rods 5 and 6. Toothed gears 9 and 10 (see FIG. 2) are arranged on the crankshafts 7, 8 and are in engagement with each other and thus ensure a counter-rotation of the crankshafts 7 and 8 mechanically coupled to one another so as to be in phase. The toothed gears 9 and 10 are preferably arranged between the main bearings of the crankshafts (main bearings not illustrated) or on shaft pins (likewise not illustrated in the drawing) of the crankshaft, said shaft pins protruding over the respective main bearings. The toothed gears can be embodied as spur gears having straight teeth or helical teeth, or can also be embodied as tensioned toothed gears.

[0028] Alternatively, the drive coupling of the crankshafts 7 and 8 can also be provided via toothed crank webs, which are directly engaged with one another for coupling of the crankshafts 7 and 8. A further alternative schematically illustrated in FIG. 4 is that of coupling of the crankshafts via a toothed belt 33 which comprises teeth on either side, wherein it is particularly advantageous, for wear reduction and for smooth running, to provide the toothing of the toothed belt 33 with a different number of teeth compared with the toothing of the toothed gears 9, 10. In particular, the toothed belt 33 can have 1 to 5, preferably 4, teeth more on either side than the toothed gears 9 and 10 of the crankshafts 7 and 8. As a result, different teeth of the toothed belt 33 are in engagement with the teeth of the toothed gears 9 and 10 of the crankshafts 7 and 8 in each of the dead centres of the course of the piston. Gas exchange forces are thus prevented from always acting on the same tooth pairing. It is also possible to use the toothed belt 33 which comprises teeth on either side in conjunction with toothed crank webs 34, 35 for low-noise coupling of the crankshafts 7, 8.

[0029] The drawing, however, does not show that the cylinders arranged with axes parallel to one another according to FIG. 1 have an inwardly directed offset, such that the distance between the cylinder axes is slightly smaller than the distance between the axes of the two crankshafts 7 and 8, however this is readily comprehensible for a person skilled in the art. With this arrangement of the cylinders offset on the anti-thrust side, not only is a compact design achieved, but in particular there is also a smaller introduction of force into the pistons and therefore an easier and wear-reducing movement of the pistons in the cylinders via the connecting rods 5 and 6 and different or smaller inclined position thereof during operation on account of the offset.

[0030] The exemplary embodiments according to FIGS. 1 and 2 differ in the arrangement of the two generators. According to FIG. 1, the generators 11, 12 are arranged in a V shape together with the corresponding crankshafts 7, 8, wherein the distance between the central axes of the generators 11, 12 is greater than the distance between the axes of the crankshafts 7, 8. In FIG. 2 the generators 11, 12 are arranged in the same horizontal plane as the crankshafts 7, 8. The explanations above and hereinafter with regard to the structure of the reciprocating piston engine apply to both embodiments.

[0031] The generators 11, 12 are each characterised in that they have balancing weights 13, 14. The balancing weights 13, 14 are arranged at the same angle, i.e. not rotated relative to one another, in the upper dead centre position of the pistons 3, 4, as can be seen in the drawings. The balancing weights 13, 14 are integrated in the driveshafts or the drive pinions 15, 16 of the two generators 11, 12. By way of example, this can be implemented by eccentrically arranged weights, which are connected to the corresponding drive pinion 15, 16 or the driveshaft. Not illustrated in the drawings are counterweights arranged in a complementary manner on the other generator side, which serve to balance moments about the transverse axis of the reciprocating piston engine. The balancing weights 13, 14 balance the second-order mass forces, whereby the smoothness of the reciprocating piston engine is significantly improved. The drive of the two generators 11, 12 is provided by toothed belts or generally traction means 17, 18, which are in engagement either with a crank web in the corresponding crankshaft 7, 8 on the one hand and with the drive pinion 15, 16 of the corresponding generator 11, 12 on the other hand. Instead of the toothed crank webs, sprockets can also be connected to the crankshafts for conjoint rotation and ensure a transfer of the moments to the traction means.

[0032] The drive of the camshafts illustrated in FIG. 1 is provided by an output gear connected to the second crankshaft 8, which output gear is connected via a traction means to the two camshafts. Furthermore, an oil pump is provided, which is driven by the other crankshaft, i.e. the first crankshaft 7, more specifically by a traction means.

[0033] The above comments apply accordingly to the exemplary embodiment according to FIG. 2.

[0034] Both power units formed in accordance with the exemplary embodiments shown in FIGS. 1 and 2 can have outlet channels 19, 20 in the region of cylinder heads of the reciprocating piston engine, which outlet channels are in fluid connection with the cylinders 1, 2. The outlet channels 19, 20 can open into a common exhaust gas channel 21. The exemplary arrangement of the outlet channels 19, 20 and of the exhaust gas channel 21 is illustrated in FIG. 3.

[0035] The outlet channels 19, 20 each have identical lengths, such that the exhaust gas channel 21 is arranged substantially centrally between the cylinders 1, 2 or centrally between cylinder heads of the cylinders 1, 2. Inlet valves 23, 24 are arranged in each cylinder head and control the inflow of a fuel mixture from inlet channels 25, 26 into the cylinders 1, 2. Outlet valves 27, 28 are associated with the outlet channels 19, 20 and control the outflow of a combustion gas mixture from the cylinders 1, 2 into the outlet channels 19, 20 and thus further on into the exhaust gas channel. The exhaust gas channel 21 ends at a channel exit 22.

[0036] A turbocharger 29 can be connected to the channel exit 22. The turbocharger is preferably flange-mounted directly onto the channel exit 22. A turbine 30 of the turbocharger 29 here lies in the outlet flow of the combustion gas flowing out from the exhaust gas channel 21 and drives a compressor 31, which is arranged in an air-guiding channel 32 of the reciprocating piston engine.

LIST OF REFERENCE SIGNS

[0037] 1, 2 cylinders [0038] 3, 4 pistons [0039] 5, 6 connecting rods [0040] 7, 8 crankshafts [0041] 9, 10 toothed gears [0042] 11, 12 generators [0043] 13, 14 balancing weights [0044] 15, 16 drive pinions [0045] 17, 18 traction means [0046] 19, 20 outlet channels [0047] 21 exhaust gas channel [0048] 22 channel exit [0049] 23, 24 inlet valves [0050] 25, 26 inlet channels [0051] 27, 28 outlet valves [0052] 29 turbocharger [0053] 30 turbine [0054] 31 compressor [0055] 32 air-guiding channel [0056] 33 toothed belt [0057] 34, 35 crank webs