CN108368816B

CN108368816B - Starting device and method for starting an internal combustion engine equipped with a dual mass flywheel

Info

Publication number: CN108368816B
Application number: CN201680072018.XA
Authority: CN
Inventors: M·博塞克; H·维特
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2015-12-22
Filing date: 2016-11-28
Publication date: 2020-12-08
Anticipated expiration: 2036-11-28
Also published as: CN108368816A; DE102016223519A1; WO2017108038A1; DE112016005904A5

Abstract

The invention relates to a starting device for starting an internal combustion engine (60), comprising: a swingable shaft (24), wherein the swingable shaft (24) is swingable about a shaft (26, 62, 70) by a swing arm (40); at least one engagement pinion (30, 32) arranged on the swingable shaft (24) for engagement into at least one ring gear (16, 34) of a dual mass flywheel (20) for starting the internal combustion engine (60); an adjusting lever (42), wherein the adjusting lever (42) is connected to an actuator and to the swing arm (40) for transmitting a movement of the actuator to the swing arm (40) for swinging the engagement pinion (30, 32) into the gear ring (16, 34), wherein the adjusting lever (42) and the swing arm (40) are connected to the shaft (26, 62, 70). In this way, the starting of the internal combustion engine (60) is further simplified and/or improved.

Description

Starting device and method for starting an internal combustion engine equipped with a dual mass flywheel

Technical Field

The invention relates to a starter device for starting an internal combustion engine, comprising at least one engagement pinion for engaging into at least one ring gear of a dual-mass flywheel. The invention also relates to a method for starting an internal combustion engine by means of such a starting device.

Background

From german laid-open patent application DE 19729421 a1, a flywheel arrangement is known with a first flywheel and a second flywheel, wherein, in the event of a defined relative rotation between the first and second flywheel, a lever mechanism acts on a part of the second flywheel in order to prevent further rotation between the first and second flywheel. German laid-open patent application DE 102011117395 a1 discloses a dual mass flywheel having a multi-part primary flywheel, comprising a first and a second disk, which can be connected to a starter, wherein a locking mechanism is arranged between the first and the second disk, which locking mechanism changes from an open state, in which the first and the second disk are force-free, to a locked state, in which the first and the second disk are force-free, at a critical rotational speed. From german laid-open patent application DE 102010012514 a1, a device for starting an internal combustion engine by means of a preferably electric starter motor, the pinion of which is constantly in engagement with a ring gear arranged on a flanged pulley, is known, wherein a freewheel, which transmits torque only in the drive direction of the starter motor, is provided between the hub of the flanged pulley and a force output shaft of the internal combustion engine, wherein the flanged pulley and the freewheel are arranged between at least one driven flange, which is on the force output shaft, and a clutch element of a downstream-connected transmission, which is in dynamic connection with the driven flange.

Disclosure of Invention

The object of the invention is to further simplify and/or improve the starting of an internal combustion engine.

According to the invention, this object is achieved by a starting device having the features of the invention. Preferred configurations of the invention are given in the description, which can illustrate one aspect of the invention either individually or in combination.

The invention relates to a starting device for starting an internal combustion engine, comprising: a swingable shaft, wherein the swingable shaft is swingable around a shaft via a swing arm; at least one engagement pinion arranged on the pivotable shaft for engagement in at least one ring gear of the dual mass flywheel for starting the internal combustion engine; an adjusting lever, wherein the adjusting lever is connected with the actuator and the swing arm for transmitting the movement of the actuator to the swing arm for swinging the engagement pinion into the gear ring, wherein the adjusting lever and the swing arm are connected with the shaft.

By means of the pivotable shaft, the at least one engagement pinion can be pivoted radially into the at least one ring gear of the dual mass flywheel during a starting process of the internal combustion engine as a result of the pivoting movement of the pivotable shaft.

The starting device can be connected to a starter, in particular an electric motor, by means of a shaft, or can be designed as a separate solution

In this independent solution, the starting device can only view the swing-in device as an independent structural group, comprising: an actuator, an adjustment lever, a swing arm, a swingable shaft, a shaft, and at least one engagement pinion. A separate embodiment of the starting device may be necessary if the internal combustion engine is driven during the starting process, for example by a belt starter motor. Furthermore, such an embodiment may be necessary if starters according to the prior art are used, however, the starter device must be mounted offset in the circumferential direction due to the mounting space.

The shaft can be, for example, a motor shaft, a pin or a pivot shaft, which is fixedly arranged in the housing, wherein the motor shaft is connected to the starter. Furthermore, the shaft can interconnect the adjusting lever and the swing arm such that the at least one engagement pinion can be swingably moved about the shaft. Furthermore, the shaft can be fixedly connected to the adjusting lever and at the same time is rotatably mounted in the housing.

The actuator can be a magnetic switch (Magnetschalter).

When starting the internal combustion engine, the rocker lever can be actuated by the actuator in order to pivot the pivotable shaft in order to pivot the at least one engagement pinion into the at least one ring gear of the dual mass flywheel. Thereafter, a starter (e.g., an electric motor or a belt starter motor) may be supplied with electric current to accelerate the dual mass flywheel. In this case, the primary side of the dual mass flywheel can be accelerated first. If a first ignition of the internal combustion engine can occur, the primary side can be accelerated further, wherein the secondary side can be accelerated by the bow spring. During the subsequent ignition during the engine start, the primary side will again precede the secondary side, thereby further increasing the pretension of the bow spring.

During the starting process, the primary side and the secondary side can already be tensioned against one another by 150Nm, for example. With a ring gear diameter of, for example, 300mm and a meshing angle of, for example, 20 °, a tooth flank normal force of 1064N may be present. In the case of a steel/steel (dry) friction coefficient of μ ═ 0.5, a friction force of 532N would be present.

Due to the radial pivot arrangement of the starting device, there is a radially repelling force due to the tooth engagement angle, which can be directed counter to the friction force and thus compensate for it. Furthermore, it is possible to achieve an immediate radial swinging out of the swingable shaft from the ring gear at any time with minimal effort.

By means of the radially pivoted-in starting device, a significantly greater clearance can be provided for the tooth gap search (Zahnl ü ckenfinedung) than for the axial engagement according to the prior art. This is of great importance primarily in the case of "Change of mind" starting (e.g., it occurs more frequently in vehicles with Start-stop systems). A "change of mind" is present when the internal combustion engine is switched off during a standstill (for example, during a red signal light) and a new start-up procedure is started again during the deceleration operation of the engine, since the signal light is just switched to green. In this case, the ring gear, which is still rotating, is to be coupled to the torsional vibration damper. A larger clearance for the teeth to be found or for the synchronization when swinging in the radial direction can therefore allow a larger relative rotational speed between the ring gear and the pinion.

In particular, the teeth can be embodied as helical teeth, which leads to a significantly quieter tooth engagement, compared to axially engaging starters with straight teeth according to the prior art.

In this way, the starting of the internal combustion engine can be further simplified and/or improved by means of the starting device.

In a preferred embodiment, a first engagement pinion for contacting a primary-side ring gear on a primary side of the dual mass flywheel and a second engagement pinion for contacting a secondary-side ring gear on a secondary side of the dual mass flywheel are arranged on the swingable shaft. In this way, the primary side as well as the secondary side of the dual mass flywheel can be accelerated during the starting process.

Preferably, the first and second engagement pinions are coupled to each other rigidly on the swingable shaft, by a freewheel, by friction means or by a spring element. In the case of a rigid coupling of the two engagement pinions, the teeth for transmitting the ignition torque to the secondary side must be of significantly more robust design. In the case of a connection via a freewheel, the first engagement pinion exceeds the second engagement pinion in terms of rotational speed during the starting process, however, the second engagement pinion is able to accelerate the first engagement pinion. For example, when the starter is energized, the primary side can be accelerated first. In this case, the freewheel can slip, so that the primary side can accelerate the secondary side in a phase-shifted manner by means of the bow spring of the damper. At the time of ignition of the internal combustion engine, the primary side can be further accelerated. In this case, the freewheel can slip again, so that the secondary side can only be accelerated by the bow spring. In this case, the arc springs of the dual mass flywheel can be compressed and kept preloaded, so that the freewheel is locked. The free wheel thus prevents the teeth from having to transmit a large ignition torque, which simplifies the construction of the starting device. In the case of a friction device, the second engagement pinion can be coupled with the first engagement pinion by a defined friction torque. The friction torque of the friction device can advantageously exceed 1Nm, particularly preferably 3Nm, in particular 4 Nm. Furthermore, the friction device can have a free angle range in which the friction device generates no friction torque or only a very small friction torque. By means of the spring element, the two engagement pinions can be coupled to one another with a slight torsion (torsionsweich).

In a preferred embodiment, the swing arm and the adjustment lever are constructed as one component. In this way the starting device can be simplified.

Preferably, the actuator comprises a pull rod for transmitting the movement of the actuator to the adjusting lever, wherein a fixedly arranged slide stop and a movable slide are arranged on the pull rod, wherein the adjusting lever is arranged between the slide stop and the slide for transmitting the movement of the actuator. For example, in one embodiment variant, in which a slide that can be moved on a pull rod of an actuator, in particular a magnetic actuator, is arranged on the pull rod, it is provided to combine the adjusting lever and the pivot arm into one component. The slide can be pressed by a preferably pretensioned spring element, in particular a spring element, against a slide stop arranged opposite the slide, wherein the slide stop is fixedly connected to the pull rod. The function of rapid residual pivoting (Rest-Einschwenken) can be achieved by means of a slide, preferably by means of an additional spring element, for the following situations: at the beginning of the starting process, the teeth of the pinion are not immediately in the tooth gaps of the ring gear, but instead the tooth tips abut the tooth tips. The embodiment described here in which the adjusting lever and the swivel arm are constructed as one component with a slide can be applied to all variants of the starting device, except for the "independent solution" which uses an additional synchronization pinion.

Preferably, the pivot arm and the adjusting lever are coupled to one another by a spring element, in particular by a torsion spring (schenkelfoder), or by a compression spring, in particular a coupling spring. The spring element can preferably withstand pressure. In this way, a quick and simple return of the starting device into the initial position after the engine has started can be achieved.

In particular, the shaft can be connected to a starter. The starter can be in particular an electric motor. By means of the starter, the shaft can transmit torque to the swingable shaft for starting the engine.

Preferably, a pinion is disposed on the shaft, wherein the pinion is in contacting engagement with the pinion. By means of an additional pinion on the shaft, it is possible to transmit torque from the shaft to at least one engaging pinion of the swingable shaft. In particular, the torque of the starter can be transmitted to the ring gear by engaging the pinion. Here, the pinion can always engage the engagement pinion and thus drive the swingable shaft.

In a preferred embodiment, a freewheel is provided on the shaft. By means of the freewheel on the shaft, the latter can accelerate the primary side of the ring gear of the dual-mass flywheel via the pinion and the engaging pinion, which ring gear, however, can exceed the rotational speed of the shaft.

Preferably, the first engaging pinion and the second engaging pinion have the same or different addendum circle diameters, respectively, for engaging into the primary-side ring gear and the secondary-side ring gear having the same or different addendum circle diameters. With the same tip circle diameter, the same transmission ratio can be achieved in the gear pairs each consisting of the engagement pinion and the ring gear. Furthermore, when the engaging pinion and/or the ring gear have different addendum circle diameters, improvement of cogging search at the time of engagement can be facilitated. For example, the first engagement pinion can have a larger tip circle than the second engagement pinion, so that the primary-side gear pair thus formed by the first engagement pinion and the primary-side ring gear is also produced as the first one during the engagement process.

The invention also relates to a method for starting an internal combustion engine by means of a starting device designed or developed as described above, comprising the following steps: swinging at least one engagement pinion from an initial position into at least one toothed ring of the dual mass flywheel; igniting the internal combustion engine by means of a starter or belt starter motor; reaching an idle speed of the internal combustion engine; and the starting device is swung out into the initial position.

By means of the method, the starting of the internal combustion engine can be further simplified and/or improved.

Drawings

The invention is explained below by way of example according to preferred embodiments with reference to the drawing, wherein the features shown below are able to show one aspect of the invention individually or in combination. It shows that:

FIG. 1 is a schematic drawing of a starting device according to the prior art;

FIG. 2 is a schematic illustration of a first embodiment of the starting apparatus;

FIG. 3 is a partial cross-sectional view of the starter device of FIG. 2;

FIG. 4 is a detail view of a portion of the starter device of FIG. 2 in an initial position;

FIGS. 5 to 9 are parts of detailed views of the starting device of FIG. 4 during operation;

FIG. 10 is a schematic view of a second embodiment of the starting device;

FIG. 11 is a schematic view of a third embodiment of the starting apparatus;

FIG. 12 is a partial cross-sectional view of the starting device according to FIG. 10 or FIG. 11;

FIG. 13 is a detail view of a portion of the first embodiment of the starting device of FIG. 12 in an initial position;

14-17 parts of a detail view of the starting device of FIG. 13 when actuated;

fig. 18 and 19 are parts of a detail view of different embodiments of the arrangement of the shaft in the starting device according to fig. 12;

FIG. 20 is a detail view of a portion of the second embodiment of the starting device of FIG. 12 in an initial position;

FIGS. 21 to 24 are parts of detailed views of the starting device of FIG. 20 during operation;

FIG. 25 is a fragmentary, cross-sectional view of a third embodiment of the starting device;

FIG. 26 is a detail view of a portion of the starter device of FIG. 25 in an initial position;

27-32 parts of a detail view of the starting device of FIG. 25 when operated;

FIG. 33 is a portion of a cross-sectional view of a fourth embodiment of the starting device;

FIG. 34 is a detail view of a detail of the starting device of FIG. 33 during operation;

FIG. 35 is a detail view of another embodiment of the starting device in a home position;

FIGS. 36-38 are portions of detailed views of the starting device of FIG. 35 during operation;

FIG. 39 is a detail view of another embodiment of the starting device in a partial detail view in an initial position; and

fig. 40 to 43 are parts of a detail view of the starting device of fig. 39 during actuation.

The same reference numbers will be used for the same components/terms in the following description of the drawings.

Detailed Description

Fig. 1 shows a schematic representation of a starting device 10 according to the prior art. All parts of the starting device 10 are enclosed by a dashed box. The starting apparatus includes a starter engaged in an axial direction. The starter includes a starter 12 connected to a motor shaft 26. A starter pinion 12 is arranged on the motor shaft 26. At the time of engine start, the starter pinion 12 is axially engaged into the ring gear 16. The ring gear 16 is mounted on the primary side 18 of a dual mass flywheel 20. All of the components of the dual mass flywheel 20 are enclosed by a dashed box.

Fig. 2 shows a schematic representation of a first embodiment of a starting device 22 according to the invention. The starter device 22 is therefore provided with a starter 12 which has a starter pinion 14 coupled via a freewheel 24 on its motor shaft 26. The starting device 22 also has an additional swingable shaft 28 on which a first engagement pinion 30 and a second engagement pinion 32 are mounted. The swingable shaft 28 is swingably mounted around the motor shaft 26 of the starter 12. The starter pinion 14 on the motor shaft 26 is always in mesh with the first engagement pinion 30 and thus drives the swingable shaft 28. Here, the first engagement pinion 30 is engaged into the primary-side-mounted ring gear 16 of the dual mass flywheel 20. The second engagement pinion 32 meshes with a secondary-side ring gear 34. The two

engagement pinions

30, 32 mounted on the swingable shaft 28 are coupled to each other via a second freewheel 36.

Fig. 3 shows a detail view of a cross-sectional view of the starting device 22 on the dual mass flywheel 20. The swing arm 40 and the adjustment lever 42 are shown here simply as one component. The starting apparatus 22 includes, in addition to the swing arm 40 and the adjustment lever 42: a starter 12 in the form of an electric motor having a planetary gear set and a motor shaft 26 connected to the starter 12; a freewheel 24 arranged on the motor shaft 26; a starter pinion 14 arranged on the motor shaft; a magnetic switch 44 connected to the adjustment lever 42; a swingable shaft 28 connected to the swing arm 40 and extending parallel to the motor shaft 26 and connected through the starter pinion 14. On the swingable shaft 28, the first engaging pinion 30 and the second engaging pinion 32 are connected to each other through a second free wheel 36. The first engagement pinion 32 meshes with the starter pinion 14 and with the primary-side ring gear 16 of the dual mass flywheel 20. The dual mass flywheel 20 has a primary side 18 and a secondary side 46. The second engagement pinion 32 meshes with the secondary-side ring gear 34.

The freewheel 24 is configured such that the starter 12 can accelerate the primary side 18 via the starter pinion 14 and the first engagement pinion 30, however, the primary side 18 or the starter pinion 14 exceeds the rotational speed of the starter 12.

The second free wheel 36 is configured such that the first engagement pinion 30 can exceed the rotational speed of the second engagement pinion 36, however, the second engagement pinion 32 is able to accelerate the first engagement pinion 30.

Fig. 4 shows a detail of the starter device 22 in the initial position. The adjuster rod 42 and the swing arm 40 are coupled to each other by a pre-tensioned torsion spring 48. The entire end view does not show the freewheel. The first and second engagement pinions 30, 32 and the primary-side ring gear 16 and the secondary-side ring gear 34 are successively superimposed. For this reason, only the first engagement pinion 30 and the primary-side ring gear 16 are shown in fig. 4. In the following, only the swing-in process of the first engagement pinion 30 and the primary-side ring gear 16 will be described. The swing-in of the second engagement pinion 32 and the primary-side ring gear 34 is performed similarly.

In fig. 5 to 9, the starting process is shown in detail by means of a starting device.

Fig. 5 shows how the magnetic switch 44 is energized. The adjusting lever 42 is attracted by the magnetic switch 44, whereby the first coupling pinion 30 swings in until it strikes against the ring gear teeth of the primary ring gear 16. The starter 12 is not yet energized so that the starter pinion 14 can now also be considered stationary.

Due to the oscillating movement of the oscillating arm 40 around the starter pinion 14, the first engagement pinion 30 performs an additional rotation caused by the rolling of the teeth. This is shown by means of arrow 50.

In fig. 6, the magnetic switch 44 further attracts the adjustment lever 42 and the torsion spring 48 is further pretensioned there.

The starter 12 is now energized and begins to rotate. In this case, the starter pinion 14 drives the first engagement pinion 30 until it can find the next tooth gap in the primary-side ring gear 16 and the swing-in process is continued.

Fig. 7 shows how the rotational speed of the starter increases during a further swing-in process. By means of the oscillating movement, the first coupling pinion 30 in turn executes a rotation 52, wherein this rotation is counter to the direction of rotation 54 caused by the starter 12. The superimposed rotation and the driving rotation are thus at least partially offset during the swing-in.

Fig. 8 shows how, after reaching the end stop 38 on the housing 50 and thus ending the opposite rotation 52 of the first engagement pinion 30, the primary ring gear 16 and thus the internal combustion engine, not shown, are driven.

Fig. 9 shows how the current of the starter 22 is interrupted after the internal combustion engine is reliably started. The return spring 56 ensures a quick pivoting-out.

In fig. 10 and 11, the starting device is shown as a separate solution, wherein only the swing-in device is considered as a separate structural group.

Such an embodiment may be necessary if the internal combustion engine 60 is driven by the belt starter motor 58 during starting, as shown in fig. 10.

An embodiment may also be necessary in which, although the starting device 10 according to the prior art is used, the pendulum-in device must be installed offset in the circumferential direction, as shown in fig. 11, for reasons of installation space.

In fig. 10, it can be seen that the pivotable shaft 28 is connected to a housing-fixed pivot shaft 62 by means of the pivot arm 40. The swing arm 40 is connected to a magnetic switch 44. The swingable shaft 28 is connected with the dual mass flywheel 20 through a first engagement pinion 30 and a second engagement pinion 32.

The second free wheel 36 is configured such that the first engagement pinion 30 can exceed the rotational speed of the second engagement pinion 32, however, the second engagement pinion 32 is able to accelerate the first engagement pinion 30.

In contrast to fig. 10, in fig. 11, the internal combustion engine 60 is driven by the starter device 10 according to the prior art instead of the belt starter motor 58.

The swingable shaft 28 is connected to a swing shaft 62 fixed to the housing via a swing arm 40. The swing arm 40 is connected to a magnetic switch 44. The swingable shaft 28 is connected with the dual mass flywheel 20 through a first engagement pinion 30 and a second engagement pinion 32.

Fig. 12 shows a part of a sectional view of the swing unit without the electric motor, for example when using a belt starter motor for the starting of the internal combustion engine 60. The embodiment shown in fig. 12 comprises a second freewheel 36. An embodiment without a freewheel at all is also possible. The swing arm 40 and the adjustment lever 42 are shown here as one component for simplicity. One practical implementation setting: the pivot arm 40 and the adjusting lever 42 are separate components which are coupled to one another by a pretensioned spring element, not shown.

The second freewheel 36 is configured such that the first engagement pinion 30 can be rotated at a rotational speed that exceeds the second engagement pinion 32, however, the second engagement pinion 32 is able to accelerate the first engagement pinion 30.

Fig. 13 shows the starting device of fig. 12 in an initial position. The necessary freewheel is not shown. The adjustment lever 42 and the swing arm 40 are separate members that are coupled to each other by a joint spring 64. The engagement spring 64 is necessary to achieve a quick snap-in into the socket. Furthermore, the swing arm 40 and the adjustment lever are connected by a pin 70 rigidly connected to the housing, about which the adjustment lever 42 and the swing arm 40 can swing. The pivot arm 40 and the adjusting lever 42 come into contact on a stop 66, so that the engaging spring 64 can be mounted with a preload.

Fig. 14 shows how the magnetic switch 44 is energized. Whereby the magnetic switch 44 attracts the adjustment rod 42. Here, the first engagement pinion 30 is tooth-touching with the primary-side ring gear 16 and is therefore not engaged. Here, the first engagement pinion 30 is in contact with a housing-fixed end stop 68. Thereby preventing further movement of the first engagement pinion 30 in the direction to the right of the magnetic switch 44.

In fig. 15, the magnetic switch 44 continues to move to its stop. In this case, the coupling spring 64 is further pretensioned. Thus, the contact of the adjustment lever 42 and the swing arm 40 is released at the stop 66.

Fig. 16 shows how the primary-side ring gear 16 is accelerated by a starter (e.g., a belt starter motor), not shown. This occurs by: the starter is energized and the primary side is thereby accelerated. In the next tooth gap, the preloaded engaging spring 64 ensures a rapid "residual" pivoting-in of the pivot arm 40 into the primary-side toothed ring 16.

In fig. 17, it is shown that the internal combustion engine reaches the idling rotation speed after the ignition of the internal combustion engine. After passing through the resonant speed of the dual mass flywheel, the current to the magnetic switch 44 is interrupted. The return spring 56 swings the first engagement pinion 30 out of the primary-side ring gear 16 again.

A first arrangement of the central axes of the components of the starting device relative to each other is shown in fig. 18. As can be seen from the illustration, the bearing pin 70, the engagement pinion 30 and the ring gear 16 are angled relative to one another in the pivoted-in state. Depending on the direction of rotation of the ring gear 16 and the tension occurring between the primary side and the secondary side of the dual mass flywheel, an undesired swinging out of the force engaging the pinion 16 can occur.

Fig. 19 shows an ideal arrangement of the central axes. Ideally, the arrangement is selected such that the central axes of the ring gears 16, 34 and of the engagement pinions 30, 32 and the bearing pin 70 lie in as much as possible one plane in the swung-in state. This applies both to the embodiment of fig. 10 with a belt starter motor and to the embodiment of fig. 11 with a starter. The radially acting engagement force thus has no or only a very small lever arm in order to cause a roll-out.

Fig. 20 shows an embodiment of the starting device according to fig. 19 in an initial position. The adjusting lever 42 and the pivot arm 40 are coupled by a pretensioned torsion spring 48.

Fig. 21 shows how the magnetic switch 44 is energized. The adjusting lever 42 is attracted by the magnetic switch 44, whereby the first coupling pinion 30 swings in until it strikes against the ring gear teeth of the primary ring gear 16.

In fig. 22 it is shown how the magnetic switch 44 further attracts the adjustment rod. And here further pretensions the torsion spring 48. In addition, a separately mounted starter or belt starter motor, not shown, is supplied with current.

Fig. 23 shows how the primary ring gear 16 is now driven when the first engagement pinion 30 finds the next tooth gap and can continue the swing-in process.

In fig. 24 it is shown how the current to the magnetic switch 44 is interrupted after the start-up procedure is completed. The return spring 56 causes the starter to swing out into the initial position.

Fig. 25 shows a schematic diagram of an extended "stand-alone solution":

in this view, the swing arm 40 and the adjustment lever 42 are shown as simplified as one component.

In order to optimize the pivoting-in behavior still further in relation to the preceding embodiments, it can be advantageous to use an additional synchronization pinion 72, which is coupled to the pivot shaft 62 via the freewheel 24. The pivot shaft 62 is fixedly connected to the adjusting lever 42 and is at the same time rotatably mounted in the housing 50. The mode of action of the synchronization pinion 72 is explained in fig. 26 to 32.

If the magnetic switch 44 attracts the adjustment lever 42, the freewheel 24 switches such that the adjustment lever 42 carries the synchronization pinion 72 and thus also twists the first engagement pinion 30. However, the synchronizing pinion 72 can overrun the adjusting lever 42 in rotation speed when the primary-side ring gear 16 is driven by the internal combustion engine.

The first engagement pinion 30 may be rotationally faster than the second engagement pinion 32, however, the second engagement pinion 32 may be capable of accelerating the first engagement pinion 30.

In principle, the secondary-side toothed ring 34 and the deep-groove ball bearings, not shown, of the dual-mass flywheel are located as far as possible in one plane, so that the tilting moment onto the deep-groove ball bearings can be kept small.

Fig. 26 shows the starting device of fig. 25 in an initial position. The adjuster rod 42 and the swing arm are coupled by a pre-tensioned torsion spring 48. The necessary freewheel is not shown in the figures.

In fig. 27 it is shown how the magnetic switch 44 is energized. The adjusting lever 42 is attracted by the magnetic switch 44, whereby the first coupling pinion 30 swings in until it strikes against the ring gear teeth of the primary ring gear 16.

Fig. 28 shows how the magnetic switch 44 further attracts the adjustment lever 42. In this case, the synchronization pinion 72 and therefore also the first engagement pinion 30 are twisted until they can find the next tooth gap in the primary-side ring gear 16 and can continue the swing-in process.

Fig. 29 shows how the teeth of the first engagement pinion 30 are swung into the tooth grooves of the primary-side ring gear 16.

Fig. 30 shows how the magnetic switch 44 reaches its end position when the synchronization pinion 72 is further twisted. In this case, the first engagement pinion 16 strikes against an end stop 38. In addition, a starter, not shown, is supplied with current. At the same time, the first coupling pinion 30 is completely pivoted in, wherein the pivoting movement causes a rotation of the coupling pinion 30, which is counter to the direction of rotation caused by the synchronization pinion 72. The two rotational movements are thus at least partially offset during the remaining swing-in.

In fig. 31, the starter drives the primary-side ring gear 16. This primary-side ring gear in turn drives the synchronization pinion 72 via the first engagement pinion 30. A freewheel, not shown, arranged on the pivot shaft 62 makes it possible to overrun the synchronization pinion 72 relative to the adjusting lever 42 in terms of rotational speed.

Fig. 32 shows how the current to the magnetic switch 44 is interrupted after a successful start-up procedure. The return spring 56 in turn causes the starter to swing out into the starting position.

Fig. 33 shows another embodiment of the starting device. The starter device comprises only a first engagement pinion 30. Further, to simplify the illustration, the adjuster rod 42 and the swing arm 40 are shown as a one-piece member without spring elements.

Fig. 34 shows a swing-in process of the starter device from fig. 33. The primary side engagement for starting the internal combustion engine is exclusively carried out by means of the advantageous tooth gap search. The pivoting-in process takes place as in fig. 2.

Fig. 35 shows a starting position of a further embodiment of the starting device. The starting device comprises a magnetic switch 44 on which a pull rod 74 is arranged. The pull rod 74 comprises a fixedly arranged slide stop 76 and a movable slide 78. A return spring 56 is arranged between the magnetic switch 44 and the slider stop 76. Furthermore, a pivot-in spring 80 is arranged between the slide 78 and the end of the tension rod 74 which is arranged opposite the magnetic switch 44. Both the return spring 56 and the swing-in spring 80 are preloaded. An adjusting lever 42 is arranged between the slide stop 76 and the slide 78. The preloaded pivot-in spring 80 presses the slide 78 against the adjusting lever 42 and thus the adjusting lever 42 against the slide stop 76.

In fig. 36, the magnetic switch 44 is energized and attracts the pull rod 74. Here, the return spring 56 is increasingly compressed. Due to the preloaded pivot-in spring 80, the slide 78 is pressed against the adjusting lever 42, so that the adjusting lever 42 is pressed against the slide stop 76. In addition, the adjusting lever 42 transmits the movement of the pull rod 74 further to the swing arm 40, so that the first engagement pinion 30 moves in the direction of the primary-side ring gear 16. Here, the first engaging pinion 30 is tooth-touching with the primary-side ring gear 16.

Fig. 37 shows how the magnetic switch 44 further attracts the pull rod 74 until the end position is reached, so that the current circuit for the starter motor, not shown, is closed. Here, both the return spring 56 and the pivot-in spring 80 are prestressed to the greatest possible extent. Ring gear 16 is twisted by the starter motor until the next tooth slot is found.

Fig. 38 shows how the remaining swing-in process is carried out once the next tooth gap is found. In this case, the maximally prestressed pivot-in spring 80 abruptly moves the slide 78 toward the adjusting lever 42. Once the engine, not shown, reaches the ignition speed, the engine is started to the idle speed.

Fig. 39 shows an initial state of another embodiment of the starting device. In contrast to the starting device of fig. 35 to 38, the integrated component comprising the adjusting lever 42 and the swing arm 40 is arranged on the motor shaft with the starter pinion 14. The preloaded pivot-in spring 80 presses the slide 78 against the adjusting lever 42 and thus the adjusting lever 42 against the slide stop 76.

In fig. 40 it is shown how the magnetic switch 44 is energized. Whereby the magnetic switch 44 attracts the pull rod 74. Here, the return spring 56 is increasingly compressed. The engagement pinion 30 is tooth-touching with the ring gear 16.

Fig. 41 shows how the magnetic switch 44 further attracts the pull rod 74 into the end position, where the current circuit for the starter motor, not shown, is now closed. Here, both the return spring 56 and the pivot-in spring 80 are prestressed to the greatest possible extent.

In fig. 42 it is shown how the starter motor establishes the rotational speed. Here, the engagement pinion 16 is also twisted until the next tooth slot is found, so as to be submerged in this tooth slot.

Fig. 43 shows the residual swing-in process. In this case, the maximally prestressed pivot-in spring 80 causes the slide 78 to move abruptly back toward the adjusting lever 42. The engine reaches ignition speed and starts to idle speed.

The possibility of helical teeth is also advantageous.

In order to better find the tooth gaps during engagement, it can be advantageous if the engagement pinion and/or the ring gear have different tip circle diameters. For example, the first engaging pinion has a larger tip circle than the second engaging pinion, so that the primary side gear pair including the engaging pinion and the ring gear is also found as the first one in the engaging process.

Embodiments in which the two engagement pinions are rigidly coupled to one another, i.e. embodiments without a freewheel on the coupling shaft, are also conceivable. However, in order to transmit the ignition torque to the secondary side, the teeth must be of significantly more robust design.

It is also conceivable to combine the adjusting lever and the pivot arm as one component, wherein the spring element is eliminated. In its simplest form, the embodiment of fig. 12 can be formed by a magnetic switch, a pivoting element and a pivotable shaft with two rigidly coupled engagement pinions.

Embodiments are also conceivable in which, instead of a freewheel on the pivotable shaft, a friction device is provided which couples the second engagement pinion with the first engagement pinion by means of its defined friction torque. The friction torque of the friction means advantageously exceeds 4 Nm. Furthermore, the friction device can have a free angle range in which the friction device generates no or only a very small friction torque. In addition to or instead of the friction device or the freewheel, the two engagement pinions can be coupled to one another by means of a spring element with a slight torsion.

List of reference numerals

10 starting device 70 pin

12 starter 72 synchronous pinion

14 Start pinion 74 Pull rod

16 primary side ring gear 76 slide block stop

18 primary side 78 slide

20 double-mass flywheel 80 swing-in spring

22 starting device

24 free wheel

26 Motor shaft

28 swingable shaft

30 first engagement pinion

32 second engagement pinion

34 secondary side ring gear

36 second free wheel

38 end stop

40 swing arm

42 adjusting rod

44 magnetic switch

46 secondary side

48 torsion spring

50 casing

Self-rotation of 52 engagement pinion

54 direction of rotation of starter

56 return spring

58 belt starting motor

60 internal combustion engine

62 foot shaft

64 engaging spring

66 stop

68 housing fixed stop

Claims

1. A starting apparatus for starting an internal combustion engine (60), comprising:

-a swingable shaft (28), wherein the swingable shaft (28) is swingable about a shaft (26, 62, 70) by a swing arm (40),

-at least one engagement pinion (30, 32) arranged on the swingable shaft (28) for engagement into at least one ring gear (16, 34) of a dual mass flywheel (20) for starting the internal combustion engine (60),

-an adjusting lever (42), wherein the adjusting lever (42) is connected with an actuator and with the swing arm (40) for transmitting the movement of the actuator to the swing arm (40) for swinging the engagement pinion (30, 32) radially into the ring gear (16, 34),

wherein the adjusting lever (42) and the swing arm (40) are connected with the shaft (26, 62, 70), a first engagement pinion (30) for contacting a primary-side toothed ring (16) on a primary side (18) of the dual mass flywheel (20) and a second engagement pinion (32) for contacting a secondary-side toothed ring (34) on a secondary side (46) of the dual mass flywheel (20) are arranged on the swingable shaft (28).

2. A starting device according to claim 1, characterized in that said first engagement pinion (30) and said second engagement pinion (32) are mutually coupled rigidly on said swingable shaft, through a free wheel, through friction means or through a spring element.

3. The starting device according to claim 1 or 2, characterized in that the swing arm (40) and the adjusting lever (42) are constructed as one piece.

4. A starting device according to claim 3, characterized in that the actuator comprises a pull rod (74) for transmitting the movement of the actuator to the adjusting rod (42), wherein a fixedly arranged slide stop (76) and a movable slide (78) are arranged on the pull rod (74), wherein the adjusting rod (42) is arranged between the slide stop (76) and the slide (78) for transmitting the movement of the actuator.

5. The starting device according to claim 1 or 2, characterized in that the swing arm (40) and the adjusting lever (42) are coupled to each other by a spring element.

6. A starting device according to claim 1 or 2, characterized in that a pinion (14, 70) is arranged on the shaft (26, 62), wherein the pinion (14, 70) is in contact engagement with the pinion (30, 32).

7. A starting device according to claim 1 or 2, characterized in that a freewheel (24) is arranged on the shaft (26, 62).

8. A starting device according to claim 2, characterized in that the first engagement pinion (30) and the second engagement pinion (32) have the same or different addendum circle diameters, respectively, for meshing into the primary-side ring gear (16) and the secondary-side ring gear (34) having the same or different addendum circle diameters.

9. The starting device according to claim 5, characterized in that the swing arm (40) and the adjusting lever (42) are coupled to each other by a torsion spring (48).

10. The starting device according to claim 5, characterized in that the swing arm (40) and the adjusting lever (42) are coupled to each other by means of a pressure spring.

11. The starting device according to claim 5, characterized in that the swing arm (40) and the adjusting lever (42) are coupled to each other by means of a joint spring (64).

12. A method for starting an internal combustion engine (60) by means of a starting device according to any one of claims 1 to 11, the method comprising the steps of:

-swinging at least one engagement pinion (30, 32) from an initial position into at least one ring gear (16, 34) of the dual mass flywheel (20);

-igniting the internal combustion engine (60) by means of a starter (12) or a belt starter motor (58);

-reaching an idle speed of the internal combustion engine (60); and

-swinging out the starting device into the initial position.