Reciprocating piston engine, in particular internal combustion engine

Abstract

The invention relates to a reciprocating piston engine, in particular an internal combustion engine, comprising at least one length adjustable connecting rod (1) connected to a crankshaft (26), which connecting rod (1) comprises at least one first rod part (2) having a small connecting-rod eye (3) and at least one second rod part (4) having a large connecting-rod eye (5), which two rod parts (2, 4) can be displaced telescopically with respect to and/or into each other by means of a length adjustment device (100), wherein the length adjustment device (100) can be fluidically connected in at least one position of a control valve (15) to at least one oil pressure line (14, 6), and can be separated from the oil pressure line (16) in at least one second position of the control valve (15), wherein the control valve (15) can be electrically switched and inductively actuated. In order to allow the compression ratio to be flexibly changed in a way that is as simple, space-saving and reliable as possible, the control valve (15) can be electrically connected to at least one induction device (21) fixed to the connecting rod, in which an electrical current can be induced in at least one position of the connecting rod (1) by means of at least one magnet device (24) fixed to the crank housing or crankshaft.

Claims

1. A reciprocating piston engine comprising a length-adjustable connecting rod connected to a crankshaft and comprising a first rod part with a small connecting rod eye and a second rod part with a large connecting rod eye, the two rod parts being displaceable with respect to and/or into each other by means of a length adjustment device, wherein the length adjustment device can be fluidly connected to a hydraulic medium line in at least one position of a control valve and can be separated from the hydraulic medium line in a second position of the control valve, wherein the control valve can be inductively actuated, wherein the control valve can be electrically connected to an induction device fixed to the connecting rod in which an electrical current and/or electrical voltage can be induced in at least one position of the connecting rod by means of a magnet device.

2. The reciprocating piston engine according to claim 1, wherein the induction device comprises at least one inductance loop, wherein the inductance loop is formed by at least one conductive path printed on the connecting rod.

3. The reciprocating piston engine according to claim 1, wherein the induction device is arranged on at least a front side of the connecting rod and/or on a side surface of a bearing cap of a connecting rod bearing of the connecting rod.

4. The reciprocating piston engine according to claim 1, wherein an electrical switching apparatus is arranged in a current flow between the induction device and the control valve.

5. The reciprocating piston engine according to claim 4, wherein the electrical switching apparatus is actuatable by a signal receiver fixed to the connecting rod which communicates with a signal transmitter fixed to the casing.

6. The reciprocating piston engine according to claim 1, wherein the magnet device comprises pole segments of different magnetic polarity which are arranged as a magnetic ring of multiple consecutive pole segments of different magnetic polarity.

7. The reciprocating piston engine according to claim 1, wherein the magnet device is arranged on or in at least one crank arm of the crankshaft.

8. The reciprocating piston engine according to claim 1, wherein the magnet device is arranged in a crankcase or in a hydraulic medium sump.

9. The reciprocating piston engine according to claim 1, wherein the magnet device comprises at least one permanent magnet.

10. The reciprocating piston engine according to claim 1, wherein the magnet device is of a switchable design.

11. The reciprocating piston engine according to claim 10, wherein the magnet device comprises at least one stator coil, wherein a coil current of the at least one stator coil is switchable.

12. The reciprocating piston engine according to claim 10, wherein the magnet device is position-adjustable, and wherein the magnet device is mounted displaceable or pivotable in a crankcase or in a hydraulic medium sump.

13. The reciprocating piston engine according to claim 1, wherein the control valve is formed by a piezo valve or a magnetic valve.

14. The reciprocating piston engine according to claim 1, wherein the second rod part forms a guide cylinder and the first rod part forms a piston element longitudinally displaceable in the guide cylinder, wherein a high pressure chamber is spanned on at least one side of the piston element between the second rod part and the piston element.

15. The reciprocating piston engine according to claim 1, wherein at least one high pressure chamber is connected to a switchable labyrinth seal.

16. The reciprocating piston engine according to claim 1, wherein the control valve is electrically switchable.

17. The reciprocating piston engine according to claim 1, which comprises two induction devices, each having at least one generator coil, wherein the generator coils of different induction devices are arranged adjacently in relation to a direction of rotation of the connecting rod.

18. The reciprocating piston engine according to claim 17, wherein different generator coils of the same induction devices are arranged one behind the other in relation to the direction of rotation of the connecting rod.

19. The reciprocating piston engine according to claim 17, wherein the generator coils each comprise two pole arms each having a respective pole, wherein the poles are aligned at least substantially outwardly in relation to the connecting rod, in a substantially radial direction in relation to an axis of rotation of the connecting rod.

20. The reciprocating piston engine according to claim 19, wherein the poles of the generator coil are arranged one behind the other in relation to the rotational direction of the connecting rod and/or poles of different induction devices are arranged offset by half a pole.

21. The reciprocating piston engine according to claim 1, wherein the magnet device is displaceable toward an axis of rotation of the connecting rod or a crankshaft axis respectively.

22. The reciprocating piston engine according to claim 17, comprising two magnet devices, wherein one magnet device is in each case arranged opposite one of the two induction devices and comprises at least one stator coil.

23. The reciprocating piston engine according to claim 1, wherein the magnet device exhibits a form of at least one section of a figure-eight path of the connecting rod.

24. The reciprocating piston engine according to claim 1, wherein the magnet device comprises at least one stator coil having a multi-phase winding configured to generate a multi-phase rotating field.

25. The reciprocating piston engine according to claim 24, further comprising a control means arranged to generate the rotating field in an opposite direction to a movement of the connecting rod.

26. The reciprocating piston engine according to claim 25, wherein the control means is further arranged to set a rotational speed of the rotating field subject to a rotational speed of a crankshaft, wherein a relative rotational speed of from approximately 20,000 to approximately 40,000 rpm, is set between the rotating field and crankshaft.

27. A method for operating the reciprocating piston engine according to claim 24, wherein the rotating field is generated in the opposite direction to the movement of the connecting rod.

28. The method according to claim 27, wherein a rotational speed of the rotating field is set subject to the rotational speed of a crankshaft, wherein a relative rotational speed of approximately 30,000 rpm is set between the rotating field and the crankshaft.

29. A method for operating the reciprocating piston engine according to claim 11, wherein the coil current of the stator coil is changed so as to equalize a change in an induced energy due to a change in a rotational speed of a crankshaft.

Description

(1) The invention will be described in greater detail in the following on the basis of a non-limiting example embodiment as depicted in the figures. Shown therein schematically:

(2) FIG. 1 a first embodiment of a connecting rod of an internal combustion engine according to the invention in longitudinal section,

(3) FIG. 2 a detail of the connecting rod in one implementation of said first inventive embodiment,

(4) FIG. 3 a crank throw including connecting rod in a longitudinal section through the crankshaft,

(5) FIG. 4 a detail of the connecting rod including magnet device in a second implementation of the first embodiment,

(6) FIG. 5 a second embodiment of a connecting rod of an internal combustion engine according to the invention,

(7) FIG. 6 a third embodiment of a connecting rod of an internal combustion engine according to the invention,

(8) FIG. 7 a fourth embodiment of a connecting rod of an internal combustion engine according to the invention with deactivated magnet device,

(9) FIG. 8 said connecting rod with activated magnet device,

(10) FIG. 9 an enlarged view of a bearing cap having two induction devices,

(11) FIG. 10 an arrangement of two magnet devices in relation to two induction devices on a bearing cap; and

(12) FIG. 11 a stator coil with a multi-phase winding.

(13) Functionally equivalent parts in the embodiments are provided with the same reference numerals.

(14) FIG. 1 shows a two-part connecting rod 1 of a reciprocating piston engine, in particular an internal combustion engine, having an upper first rod part 2 with the small connecting rod eye 3 for connecting to a not shown piston and a lower second rod part 4 with the large connecting rod eye 5 forming a connecting rod bearing 5a for connecting to a crankshaft 26. The first rod part 2 is displaceable vis--vis the second rod part 4 between an extended position and an inserted position. Apreferably pressurized oil-operatedlength adjustment device 100 as depicted schematically in FIGS. 5 to 8 is provided for the longitudinal adjustment. The length adjustment device 100 can be for example a variant as depicted in FIGS. 1 to 4. Other variants able to provide an oil-controllable longitudinal adjustment are also possible. Since this aspect relates to a peripheral scope of the invention, the following will only describe one possible variant, wherein the use of a different solution is expressly not excluded.

(15) The connecting rod 1 is shown in FIG. 1 divided along the longitudinal axis 1a of the connecting rod 1, wherein it is depicted in its first position of shorter piston rod length and lowered first rod part 2 on the left and in its second position of longer piston rod length and raised second rod part 4 on the right.

(16) A control valve 15 connected to the connecting rod bearing 5a by an oil pressure line 16 is arranged between the length adjustment device 100, which is preferentially arranged in the center region of the connecting rod 1, and the connecting rod bearing 5a of the large connecting rod eye 5. An oil-pressurizable connection likewise exists between the control valve 15 and the length adjustment device 100.

(17) To actuate the control valve 15, the connecting rod 1 inventively comprises an induction device 21 which can be electrically connected to a coil 15a of the control valve 15 by an electrical switching apparatus 23. The electrical switching apparatus 23 is arranged in the electrical connection between the inductance loop 22 and the control valve 15.

(18) According to the first embodiment of the invention, the induction device 21 has at least one inductance loop 22 which in the depicted implementation is formed by at least one conductive path printed on the connecting rod 1 which exhibits a plurality of consecutive induction loops. The induction loop 22 is for example arranged on at least one front side 1b of the connecting rod 1 in the region of the large connecting rod eye 5. However, it can also alternatively or additionally be provided on a side of a bearing cap 17 of the connecting rod bearing 5a. The induction loop 22 ideally extends over at least half the circumference of the large connecting rod eye 5 on the front side 1b. This can thereby be either the upper or the lower circumference half.

(19) The induction device 21 moreover comprises a magnet device 24 arranged on a part adjacent the connecting rod 1. In the example embodiments, the magnet device 24 is arranged on or in a crank arm 25 of the crankshaft 26 adjacent the front side 1b of the connecting rod 1 or the bearing cap 17 respectively. The magnet device 24 thereby faces the inductance loop 22.

(20) The magnet device 24 can be configured as a magnetic ring 27 having a plurality of consecutive pole segments 27a, 27b of different magnetic polarity (see FIG. 4). Alternatively or additionally thereto, the magnetic ring 27 can exhibit individual e.g. cylindrical permanent magnets 28 which are for example arranged in axial bores of the crank arm 25 (axial here means oriented along the longitudinal axis 26a of the crankshaft 26; i.e. normal to the drawing plane of the paper). The position of the individual permanent magnets 28 in the crank arm 25 of the crankshaft 26 is schematically implied in FIG. 2 as an example. Permanent magnets 28 are for example suitable in cases of increased power demand.

(21) During the relative movement of the connecting rod 1 and the crank arm 25, the magnet device 24 sweeps the inductance loops 22 with alternating polarity. A voltage is thus induced in the printed inductance loops 22 as long as the crankshaft 26 rotates. The electrical power generated can be used to continuously operate an electrical circuit able to energize the electrical switching apparatus 23 via a non-contact transmitted signal, whereby the control valve 15 implemented as an electrical switch valve is activated or deactivated.

(22) FIGS. 1 to 4 depict a concrete variant of the length adjustment device 100 in which the first 2 and second rod part 4 of the connecting rod 1 are displaceable in the direction of the longitudinal axis 1a of the connecting rod 1 about an adjustment area limited by an end stop 6. A substantially cylindrical piston element 7 implemented as a differential piston is fixed in the upper first rod part 2.

(23) The first rod part 2 and the second rod part 4 of the connecting rod 1 are hydraulically coupled in the pressure direction and mechanically limited in the opposite direction. Pressure direction here means the direction in which the force of the combustion in the piston chamber acts on a not-shown piston.

(24) The piston element 7 is displaceably guided axially (in the direction of the longitudinal axis 1a of the connecting rod 1) in a guide cylinder 8 of the lower second rod part 3 of the connecting rod 1, whereby in an extended state of the two rod parts 2, 3, a first high pressure chamber 10 stretches between a first face 9 of the piston element 7 facing the large connecting rod eye 5 and the second rod part 4 or the guide cylinder 8 respectively. Furthermore, in a collapsed state of the two rod parts 2, 3, a second high pressure chamber 12 stretches between a second face 11 of the piston element 7 facing the small connecting rod eye 3 and the second rod part 3. The second high pressure chamber 12 is thereby of substantially annular configuration.

(25) The first high pressure chamber 10 and the second high pressure chamber 12 are connected via first or second oil ducts 13 or 14 to a control valve 15 implemented for example as a simple switch valve which optionally establishes the flow connection between an oil pressure line 16 from the connecting rod 5a and the first oil duct 13 or second oil duct 14. The connecting rod bearing 5a is connected to a not-shown oil supply line in the crankshaft 26. A respective check valve 19, 20 opening toward the high pressure chambers 10, 12 is in each case arranged between the control valve 15 of the first high pressure chamber 10 or second high pressure chamber 12 in the first oil duct 13 or second oil duct 14. The control valve 15 can be arranged in the connecting rod 1 or in the bearing cap 17 of the connecting rod bearing 5a.

(26) The first high pressure chamber 10 and the second high pressure chamber 12 can be provided withnot shown to any greater detailend position cushionings so as to minimize impacts and shocks during the switching of the connecting rod 1.

(27) Activating the control valve 15 enables the flow connection between the oil pressure line 16 and one of the two oil ducts, for example first oil duct 13, and blocks the other oil duct, for example second oil duct 14. As a result, it takes for instance the extended length of the connecting rod 1 to achieve a high compression ratio when the first high pressure chamber 10 is filled with oil. The filling is supported by inertial force when the connecting rod 1 is in operation.

(28) When deactivated, the flow connection between the oil pressure line 16 and the one oil duct, for example first oil duct 13, is blocked and the other oil duct, for example second oil duct 14, enabled. It thus takes for instance the shortened length of the connecting rod 1 to achieve a low compression ratio in the combustion chamber. This ensues by the second high pressure chamber 12 filling with oil or respectively the first high pressure chamber 10 being drained (for example by not-shown lines and/or in combination with the switch valve 15).

(29) The control valve 15 thus alternatingly switches the oil pressure supply between the two high pressure chambers 10, 12, whereby there is only comparatively low electrical power requirement.

(30) The electrical switching apparatus 23 is connected to a signal receiver 29 arranged for example in the connecting rod 1 and thus activated by a wirelessly transmitted signal. The signal receiver 29 communicates with a signal transmitter (antenna), not depicted in the figures, arranged for example in the crankcase. Both analog electrical or magnetic fields in the form of proximity sensors as well as digitally processed electromagnetic signal bursts in the form of a telemetric signal transmission unit can be used for the non-contact signal transmission of the control signal for the electrical switching apparatus 23.

(31) As can be seen from FIG. 1, an adjustable or switchable seal, configured here as a labyrinth seal 18, is connected to the second high pressure chamber 12. The upper first rod part 2 and the lower second rod part 4 thereby engage with one another via the adjustable labyrinth seal 18.

(32) The lower first high pressure chamber 10 is filled with oil via the first oil duct 13 in which the first check valve 19 opening toward the first high pressure chamber 10 is arranged. The upper second high pressure chamber 12 is filled with oil via a second oil duct 14 having a second check valve 20 opening toward said second high pressure chamber 12.

(33) The control valve 15 from which the first oil duct 13 and the second oil duct 14 run can be formed for example as an electrically actuated 3/2-way valve. Implementations as a piezo valve or magnetic valve are also possible.

(34) Should the connecting rod 1 adopt a first position of e.g. short rod length, the control valve 15 fills the upper second high pressure chamber 12 with oil. Leakages through the labyrinth seal 18 caused by the inertial force are directly compensated by replenishment from the second oil duct 14.

(35) Should the connecting rod 1 be changed into a second position of e.g. long rod length, the control valve 15 switches. The first check valve 19 lets oil into the first high pressure chamber 10. The oil from the upper second high pressure chamber 12 is forced through the labyrinth seal 18upward in FIG. 1and partly also from the second high pressure chamber 12 past the piston element 7 into the lower first high pressure chamber 10.

(36) When switched from the second position to the first position, oil passes the piston element 7 into the upper second high pressure chamber 12.

(37) This solution allows very simple construction without complicated sealing or circuitry solutions. The labyrinth seal 18 has a relatively long sealing length, which retards leakages or respectively promotes the flow of oil via other routes (for example from the second high pressure chamber 12 into the first high pressure chamber 10). The length adjustments of the connecting rod 1 can be achieved over just a few cycles.

(38) In the second embodiment depicted in FIG. 5, the magnet device 24 comprising permanent magnets 28 is fixedly connected to a crankcase 30. One or more inductance loops are arranged on the connecting rod 1, for example in the bearing cap 17 of the connecting rod bearing 5a. As in the first embodiment, a voltage is induced in the inductance loops 22 as soon as and for as long as the crankshaft 26 rotates. This generated electrical power can also be used here to continuously operate an electrical circuitnot shown in FIG. 5which is capable of energizing an electrical switch via non-contact transmitted signal, whereby the electrically switchable electrical control valve 15 is activated or deactivated. This electrical switch is actuated as described by a signal receiver which wirelessly communicates with a signal transmitter arranged in the crankcase 30. The control valve 15 can be activated as described to fill/drain high pressure chambers 10, 12 when the length adjustment device 100 is realized in accordance with the example embodiment depicted in FIGS. 1 to 4. As the schematic depiction of the length adjustment device 100 in FIGS. 5 to 8 shows, same can also be realized in other ways.

(39) In the third implementation depicted in FIG. 6, the switchable magnet device 24 fixedly connected to the crankcase 30 or an oil pan exhibits at least one stator coil 31, the coil current of which and thus the magnetic field of the induction device 21 can be changed by an electrical switching apparatus 23a disposed external of the connecting rod 1. The induction device 21 can thus be activated/deactivated by switching the coil current of the stator coil 31 on and off. The elements of the electrical switching apparatus 23 and signal receiver 29 in the connecting rod 1 as well as the switching transmitter in the crankcase 30 can thus be omitted since the switching of the control valve 15 ensues directly via the stator coil 31. A reset position of the control valve 15 defined by anot shown in any greater detailreturn spring of the control valve 15 is thereby associated with the de-energized state and an operational position of the control valve 15 associated with the energized state of the stator coil 31. This enables a simple way to provide a fail-safe function.

(40) FIGS. 7 and 8 show a fourth implementation, wherein the magnet device 24similar to as in FIG. 5is formed by permanent magnets 28, although the magnet device 24 here is of switchable design. In contrast to FIG. 6, however, the switching function of the magnet device 24 is achieved here by the magnet device 24 being displaceably or pivotably mounted in the crankcase 30. By the displacing or pivoting motion of the magnet device 24 via an actuating device 32, the minimum distance between the induction loops 22 fixed to the connecting rod and the permanent magnets 28 can be increased or reduced and thus the magnetic field acting on the inductance loops changed. Activating and/or deactivating the induction device 21 thus ensues in simple manner via the actuating device displacing or pivoting the permanent magnets 28.

(41) Here as well, no further electrical elements such as electrical switch, signal receiver or signal transmitter are needed. As can be seen in FIG. 7, the magnet device 24 is far enough away from the connecting rod 1 when the induction device 21 is deactivated that voltage can no longer be induced in the induction loops 22 of the connecting rod 1, whereby the control valve 15 adopts its de-energized reset position. When the induction device 21 is activated, the minimum distance between the connecting rod 1 and magnet device 24 is shortened enough that a voltage is induced into the inductance loops 22 and the control valve 15 thus switched into its operational position (FIG. 8).

(42) FIG. 9 shows a bearing cap 17 with two induction devices 21a, 21b. A first induction device 21a thereby exhibits at least one first generator coil 33 which is preferably configured as a salient pole generator. The coil core is thereby of U-shaped design with two arms 35a, 36a which form the two poles 37a, 38a of the first generator coil 33. The windings of the coil are divided among the two arms 35a, 36a in the depicted implementation.

(43) The second induction device 21b also comprises a second generator coil 34 which is likewise U-shaped and has two arms 35b, 36b ending as two flat poles 37b, 38b of the second generator coil 34.

(44) The poles 35a, 36a; 35b, 36b of each generator coil 33, 34 are arranged one behind the other in relation to the direction of rotation of the connecting rod, as suggested by the double-arrow in the detail of the connecting rod, as well as the connecting rod 1. Further generator coil poles of an induction device 21a, 21b are likewise arranged one behind the other in relation to the rotational direction such that the poles of each induction device 21a, 21b are arranged in a row. The respective pole surfaces of the induction devices 21a, 21b are thereby preferably slightly rounded and correspond to an enveloping at the poles in for instance the form of the connecting rod figure-eight path and/or connecting rod movement as is to be expected in a region in which, as depicted in FIG. 10, a magnet device 24 or multiple magnet devices 24a, 24b of the reciprocating piston engine are arranged. Preferably, the geometry of the magnet devices 24a, 24b also corresponds to the form of the connecting rod figure-eight path in that area of the connecting rod 1 movement in which the magnet devices 24a, 24b are arranged.

(45) The two induction devices 21a, 21b in particular serve to be able to separately control two coils of the control valve 15. Two coils 15a of a control valve 15 can thereby be supplied separately with current and/or voltage and thus a switching of a control valve 15 realized with two or three switching states.

(46) Preferably, as FIG. 10 shows, two magnet devices 24a, 24b are provided, each arranged opposite the respectively associated induction device 21a, 21b. This enables different coils 15a of the control valve 15 to be supplied by means of one or more electrical switching apparatus 23a, as shown in FIG. 6, each activating or able to activate a respective one of the two magnet devices 24a, 24b.

(47) Alternatively, a connecting rod 1 with two induction devices 21a, 21b can also be operated in switchable fashion by a single magnet device 24 when same can displace in at least one substantially axial direction of the crankshaft so that it can be brought into close proximity to both the first induction device 21a as well as close proximity to the second induction device 21b in order to induce a current/voltage in the respective induction device 21a, 21b.

(48) In order to pivot and/or displace such a magnet device 24 toward the crankshaft, an actuating device 32 is preferably provided as is depicted with respect to the implementations of FIGS. 7 and 8. The alternating voltage induced on the generator coils 33, 34 of the first and second induction device 21a, 21b can advantageously be directly conducted to the coils 15a of the control valve via electrical lines without a rectification or any electrical switching element needing to be provided in the connecting rod 1.

(49) Preferably, the coil current of a switchable stator coil 31 can be changed so as to offset a change in induced energy resulting from a change in the rotational speed of the crankshaft of a reciprocating piston engine.

(50) Further preferably, the stator coils 31 of the magnet device 24 or magnet devices 24a, 24b are provided with multi-phase windings A, B, C, as is shown in FIG. 11.

(51) The windings of the respective phase A (circular), B (crossover) and C (point) thereby alternate over the length of the stator coil. In particular, two, three or more phases can be provided.

(52) By means of these phases of the stator coil 31, a rotating field, also called an alternating field or travelling field, can be generated. When such a rotating field acts on the stator coil 31 in opposite direction to the movement of the connecting rod, any relative rotational speed can be set between the connecting rod 1 and the magnet device 24 or static coil 31 respectively. In particular, it can be provided for the relative rotational speed to remain constant as the crankshaft speed changes in order to also keep the transfer of energy between the magnet device and the induction device constant. A high-frequency rotating field is therefore generated in the case of slow engine speeds or crankshaft speeds. As engine speed/crankshaft speed increases, the rotating field frequency is then reduced.

(53) Preferably, a relative rotational speed of approximately 30,000 rpm is set, which corresponds approximately to a transmitted power of 7 W when the poles have an approximate length L of 8 mm and width B of 9 mm, as shown in FIG. 9, and the respective magnet device 24 exhibits dimensioning adapted to that effect. The relative rotational speed of a stator coil 31 with a multi-phase winding can be set in a controller (ECU) of the reciprocating piston engine via software and/or hardware (not depicted). Such a control means is in particular equipped to regulate the power electronics (not depicted) of the reciprocating piston engine for regulating the rotational speed of the rotating field as a function of the rotational speed of the crankshaft.