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

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 starting device for starting an internal combustion engine, having at least one engaging 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 with the aid of such a starting device.

Background technique

A flywheel assembly with a first flywheel and a second flywheel is known from German publication DE 197 29 421 A1, in which, with a defined relative torsion between the first and the second flywheel, a lever mechanism acts on the second flywheel. part of the flywheel thereby preventing further twisting between the first and second flywheels. From the German publication DE 10 2011 117 395 A1 a dual-mass flywheel with a multi-part primary flywheel is known, which includes a first disc wheel and a second disc wheel which can be connected to a starter, wherein in the first A locking mechanism is arranged between the disc wheel and the second disc wheel, which, at a critical rotational speed, changes from an open state in which there is no force between the first disc wheel and the second disc wheel to having the first disc wheel and the In the locked state of the force locking between the second disc wheels. A device for starting an internal combustion engine is known from German publication DE 10 2010 012 514 A1 by means of a preferably electric starter motor, the pinion of which is always meshed with a ring gear arranged on a flange wheel, wherein , between the hub of the flanged wheel and the force output shaft of the internal combustion engine is a free wheel that transmits torque only in the driving direction of the starter motor, wherein the flanged wheel and the free wheel are arranged in at least one Between the driven flange and the downstream connected clutch element of the variable speed transmission, the driven flange being on the force output shaft, the clutch element is dynamically connected to the driven flange.

SUMMARY OF THE INVENTION

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

According to the invention, the solution of this task is achieved by a starting device having the features of the invention. Preferred configurations of the invention are given in the description, which preferred configurations can illustrate an aspect of the invention, alone or in combination.

The invention relates to a starting device for starting an internal combustion engine, comprising: a pivotable shaft, wherein the pivotable shaft can be pivoted about an axis by means of a swing arm; at least one engagement pinion arranged on the pivotable shaft for meshed into at least one ring gear of the dual mass flywheel for starting the internal combustion engine; an adjusting rod, wherein the adjusting rod is connected with the actuator and the swing arm for transmitting the movement of the actuator to the swing arm for The engagement pinion is swung into the ring gear, wherein the adjustment lever and the swing arm are connected to the shaft.

By means of the pivotable shaft, the at least one engaging pinion can be swung radially into at least one ring gear of the dual-mass flywheel due to the pivoting movement of the pivotable shaft during the start-up process of the internal combustion engine.

在该独立解决方案中，起动装置能够仅仅将摆入装置视作独立的结构组，包括：致动器、调整杆、摆臂、可摆动轴、轴和至少一个接合小齿轮。如果内燃机在起动过程中例如通过皮带起动电机驱动，则起动装置的独立实施方式会是必要的。此外，如果使用根据现有技术的起动器，则这样的实施方式会是必要的，然而，由于安装空间原因，起动装置必须在周向方向上错位地安装。In this case, the starter can be connected via a shaft to the starter, in particular the electric motor, or can be constructed as a stand-alone solution

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

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 adjustment lever and the swing arm so that the at least one engagement pinion can be pivotably moved about the shaft. Furthermore, the shaft can be fixedly connected to the adjustment lever and at the same time be rotatably mounted in the housing.

The actuator can be a magnetic switch.

When starting the internal combustion engine, the rocker lever can firstly be actuated by the actuator in order to pivot the pivotable shaft in order to pivot the at least one engaging pinion into the at least one ring gear of the dual-mass flywheel. Thereafter, a starter (eg an electric motor or belt starter motor) is supplied with current in order to accelerate the dual mass flywheel. Here, the primary side of the dual-mass flywheel can first be accelerated. If the first ignition of the internal combustion engine can occur, the primary side can be accelerated further, wherein the secondary side can be accelerated by means of the arc spring. In the following ignition during engine start, the primary side will again lead the secondary side, thereby further increasing the preload of the arc springs.

During the starting process, the primary side and the secondary side can already be tensioned with each other by 150 Nm, for example. With a ring gear diameter of eg 300mm and a mesh angle of eg 20°, there would be a flank normal force of 1064N. With a steel/steel (dry) friction coefficient of μ=0.5, there would be a friction force of 532N.

Due to the radially pivoted arrangement of the starting device, there is a radially repulsive force due to the tooth engagement angle, which radially repulsive force can be directed against the frictional force and thus compensate for said frictional force. Furthermore, the pivotable shaft can be swung out of the ring gear immediately radially at any time with minimal effort.

By means of the radially swiveled starter, a significantly larger clearance can be provided for the cogging search compared to the axial engagement according to the prior art. This is of significance mainly in the case of a "change of mind" start, which occurs more frequently, for example, in vehicles with stop-start systems. There is a "change of mind" when the internal combustion engine is switched off during a stop phase (eg when a red signal light is on) and a new starting process is started again during deceleration of the engine because the signal light just switches to green. In this case, the ring gear is to be engaged in the still rotating ring gear of the torsional vibration damper. Therefore, a larger clearance for finding the teeth or for synchronizing during the radially swiveling in allows a larger relative rotational speed between the ring gear and the engaging pinion.

In particular, the teeth can be embodied as helical teeth, which results in a significantly quieter tooth meshing compared to the axially engaged starter 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 and a second engagement pinion are arranged on the pivotable shaft, the first engagement pinion for contacting the primary side teeth on the primary side of the dual mass flywheel The second engagement pinion is used to contact the secondary side ring gear on the secondary side of the dual mass flywheel. In this way, the primary side as well as the secondary side of the dual mass flywheel can be accelerated during start-up.

Preferably, the first engagement pinion and the second engagement pinion are rigidly coupled to each other on the pivotable shaft, via freewheels, via friction means or via spring elements. In the case of a rigid coupling of the two engaging pinions, the teeth for transmitting the ignition torque to the secondary side must be designed significantly more solidly. In the case of a freewheel connection, the first engagement pinion exceeds the second engagement pinion in rotational speed during starting, however, the second engagement pinion can accelerate the first engagement pinion. For example, when the starter is energized, the primary side can be accelerated first. In this case, the free wheel slips, so that the primary side can accelerate the secondary side with a phase offset by the curved spring of the damper. During ignition of the internal combustion engine, the primary side can be accelerated further. Here, the free wheel slips again, so that the secondary side can only be accelerated by the arc spring. Here, the arc spring of the dual-mass flywheel can be compressed and remain preloaded, so that the freewheel is locked. Therefore, by means of the free wheel, it is possible to avoid that the teeth have to transmit a large ignition torque, whereby the structure of the starting device can be simplified. In the case of a friction device, the second engagement pinion can be coupled to the first engagement pinion by means of a defined friction torque. The friction torque of the friction device can advantageously exceed 1 Nm, particularly preferably 3 Nm, in particular 4 Nm. Furthermore, the friction device can have a free angular 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 engaging pinions can be coupled to each other in a slight torsion.

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 adjustment rod, wherein a fixedly arranged slider stop and a movable slider are arranged on the pull rod, wherein the adjustment rod It is arranged between the slider stop and the slider for transmitting the movement of the actuator. For example, it is provided in an embodiment that the adjustment lever and the pivot arm are combined into one component, in which a sliding block is arranged on the pull rod of the actuator, in particular of the magnetic actuator, which is movable on the pull rod. . The sliding block can be pressed by a preferably prestressed elastic element, in particular a spring element, against a sliding block stop arranged relative to the sliding block, wherein the sliding block stop is fixedly connected to the tie rod. With the aid of the slide, preferably with the aid of an additional elastic element, the function of a fast residual swivel can be achieved when the teeth of the pinion are not immediately in the tooth space of the ring gear at the beginning of the starting process, but instead The ground is the tip of the tooth against the tip of the tooth. The embodiment described here in which the adjustment lever and the swing 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 synchronizing pinion.

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

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

Preferably, a pinion gear is arranged on the shaft, wherein the pinion gear is in contact engagement with the pinion gear. By means of an additional pinion on the shaft, torque can be transmitted from the shaft to at least one engaging pinion of the pivotable shaft. In particular, the torque of the starter can be transmitted to the ring gear by engaging the pinion. Here, the pinion can always mesh with the engaging pinion and thus drive the pivotable shaft.

In a preferred embodiment, freewheels are provided on the shaft. By means of a free wheel on the shaft, the shaft can accelerate the primary side of the ring gear of the dual mass flywheel through the pinion and engaging the pinion, however, the ring gear can exceed the rotational speed of the shaft.

Preferably, the first engagement pinion and the second engagement pinion have the same or different addendum circle diameters, respectively, for engaging into the primary and secondary side ring gears having the same or different addendum circle diameters . With the same addendum circle diameter, the same transmission ratio can be achieved in the gear pairs formed by the engaging pinion and the ring gear, respectively. Furthermore, when the engagement pinions and/or ring gears have different addendum circle diameters, it can be advantageous to improve cogging finding during engagement. For example, the first engagement pinion can have a larger addendum 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 also acts as the first gear during engagement produced.

The invention also relates to a method for starting an internal combustion engine by means of a starting device constructed or developed as described above, the method comprising the step of pivoting at least one engaging pinion from an initial position into at least one of the dual-mass flywheels in the ring gear; ignite the internal combustion engine by means of a starter or a belt starter motor; reach the idling speed of the internal combustion engine; and swing the starter into the initial position.

Starting the internal combustion engine can be further simplified and/or improved by this method.

Description of drawings

The invention is explained below by way of example on the basis of preferred embodiments with reference to the attached drawings, wherein the features shown below can each represent an aspect of the invention individually or in combination. which shows:

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

Figure 2 is a schematic drawing of a first embodiment of the starting device;

Figure 3 is part of a cross-sectional view of the starting device of Figure 2;

Fig. 4 is part of a detail view of the starting device of Fig. 2 in an initial position;

Figures 5 to 9 are part of a detail view of the starter device of Figure 4 during operation;

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

Figure 11 is a schematic view of a third embodiment of the starting device;

Figure 12 is part of a cross-sectional view of the starting device according to Figure 10 or Figure 11;

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

Figures 14 to 17 part of a detail view of the starter device of Figure 13 during operation;

Figures 18 and 19 in the starting device according to Figure 12, part of a detail view of different embodiments of the arrangement of the shafts;

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

Figures 21 to 24 are part of a detail view of the starter device of Figure 20 when actuated;

Figure 25 is part of a cross-sectional view of a third embodiment of the starter;

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

Figures 27 to 32 are part of a detail view of the starter device of Figure 25 during operation;

FIG. 33 is part of a cross-sectional view of a fourth embodiment of a starter;

Fig. 34 is part of a detail view of the starter of Fig. 33 when operated;

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

Figures 36 to 38 are part of a detail view of the starter device of Figure 35 during manipulation;

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

Figures 40 to 43 are part of a detail view of the starter device of Figure 39 when actuated.

The same reference numerals are used for the same components/terms in the following description of the figures.

Detailed ways

FIG. 1 shows a schematic representation of a starting device 10 according to the prior art. All components of the starter 10 are surrounded by dashed boxes. The starting device includes an axially engaged starter. The starter includes a starter 12 coupled to a motor shaft 26 . The starter pinion 12 is arranged on the motor shaft 26 . When the engine is started, the starter pinion 12 engages axially into the ring gear 16 . The ring gear 16 is mounted on the primary side 18 of the dual mass flywheel 20 . All components of the dual mass flywheel 20 are surrounded by a dashed frame.

FIG. 2 shows a schematic representation of a first embodiment of a starting device 22 according to the invention. The starting device 22 is therefore provided with a starter 12 which has a starter pinion 14 on its motor shaft 26 coupled via a free wheel 24 . The starting device 22 also has an additional pivotable shaft 28 on which a first engagement pinion 30 and a second engagement pinion 32 are mounted. The pivotable shaft 28 is pivotably mounted about 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 oscillating shaft 28 . Here, the first engagement pinion 30 meshes into the primary-side-mounted ring gear 16 of the dual-mass flywheel 20 . The second engagement pinion 32 meshes into a ring gear 34 which is additionally fitted on the secondary side. The two engaging pinions 30 , 32 mounted on the pivotable shaft 28 are coupled to each other via a second free wheel 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 simplified as one component. In addition to the swing arm 40 and the adjustment lever 42, the starter device 22 also includes a starter 12 in the form of an electric motor, which has a planetary gear set and a motor shaft 26 connected to the starter 12; arranged on said motor shaft 26 the free wheel 24; the starter pinion 14 arranged on the motor shaft; the magnetic switch 44 connected with the adjustment lever 42; the starter pinion 14 connected with the swing arm 40 and extending parallel to the motor shaft 26 Connected swingable shaft 28. On the swingable shaft 28 , the first engagement pinion 30 and the second engagement pinion 32 are connected to each other by a second free wheel 36 . The first engagement pinion 32 meshes with the starter pinion 14 and meshes 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 so that the starter 12 can accelerate the primary side 18 through 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 freewheel 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 capable of accelerating the first engagement pinion 30 .

FIG. 4 shows part of a detail view of the starting device 22 in the initial position. The adjusting lever 42 and the swing arm 40 are coupled to each other via a preloaded torsion spring 48 . The entire end view does not show the freewheel. The first engagement pinion 30 and the second engagement pinion 32 and the primary side ring gear 16 and the secondary side ring gear 34 are successively overlapped. For this reason, only the first engagement pinion 30 and the primary side ring gear 16 are shown in FIG. 4 . Only the swing-in process of the first engagement pinion 30 and the primary-side ring gear 16 will be described below. The second engagement pinion 32 is performed analogously to the swing-in of the primary-side ring gear 34 .

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

Figure 5 shows how the magnetic switch 44 is energized. The adjusting lever 42 is attracted by the magnetic switch 44 , whereby the first engagement pinion 30 is swung in until it hits the ring gear teeth of the primary-side ring gear 16 . The starter 12 is not yet energized, so that the starter pinion 14 can still be considered stationary at this point.

Due to the oscillating movement of the swing arm 40 about 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 attracts the adjustment lever 42 further and the torsion spring 48 is further preloaded here.

The starter 12 is now powered up and begins to spin. Here, the starter pinion 14 drives the first engagement pinion 30 until it can find the next tooth slot in the primary-side ring gear 16 and continues the swing-in process.

FIG. 7 shows how the rotational speed of the starter continues to increase during the further swing-in operation of the starter. As a result of the oscillating movement, the first engagement pinion 30 executes an autorotation 52 again, wherein this autorotation is opposite to the direction of rotation 54 caused by the starter 12 . Thus, the superimposed rotation and drive rotation are at least partially canceled during the swing-in.

FIG. 8 shows how the primary-side ring gear 16 and thus the internal combustion engine (not shown) is driven after the end stop 38 on the housing 50 has been reached and thus the opposite rotation 52 of the first engagement pinion 30 has ended. .

FIG. 9 shows how the current flow of the starting device 22 is interrupted after the internal combustion engine has been reliably started. The return spring 56 is responsible for the quick swing out.

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

This 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 .

The following embodiment is also necessary, although using the starting device 10 according to the prior art, however, due to installation space reasons, the swing-in device must be installed offset in the circumferential direction, as shown in FIG. 11 .

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

The second freewheel 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 capable of accelerating the first engagement pinion 30 .

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

The pivotable shaft 28 is connected to the 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 to the dual mass flywheel 20 via a first engagement pinion 30 and a second engagement pinion 32 .

The second freewheel 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 capable of accelerating the first engagement pinion 30 .

FIG. 12 shows a part of a cross-sectional view of a swing unit without an electric motor, for example when a belt starter motor is used for starting the internal combustion engine 60 . The embodiment shown in FIG. 12 includes a second freewheel 36 . An implementation without freewheels at all is also possible. The swing arm 40 and the adjustment lever 42 are shown here as one component for simplicity. A practical implementation provides that the swing arm 40 and the adjustment lever 42 are separate components, which are coupled to each other by a preloaded spring element, not shown.

The second freewheel 36 is configured such that the first engagement pinion 30 can exceed the second engagement pinion 32 in rotational speed, however, the second engagement pinion 32 can accelerate the first engagement pinion 30 .

The starting device of FIG. 12 is shown in FIG. 13 in the initial position. The necessary freewheels are not shown. The adjustment lever 42 and the swing arm 40 are separate components that are coupled to each other by an engagement spring 64 . The engagement spring 64 is necessary in order to achieve a quick snap-in into the tooth slot. 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 swing arm 40 and the adjustment lever 42 are in contact on a stop 66 so that the engagement spring 64 can be preloaded.

Figure 14 shows how the magnetic switch 44 is energized. As a result, the auto switch 44 attracts the adjustment lever 42 . Here, the first engagement pinion 30 is in tooth contact with the primary side ring gear 16 and is therefore not in engagement. Here, the first engagement pinion 30 is in contact with a housing-fixed end stop 68 . This prevents further movement of the first engagement pinion 30 in the direction to the right of the magnetic switch 44 .

In Figure 15, the magnetic switch 44 continues to move to its stop. Here, the engagement spring 64 is further preloaded. As a result, the contact between the adjustment lever 42 and the swing arm 40 is released at the stop 66 .

FIG. 16 shows how the primary-side ring gear wheel 16 is accelerated by a starter not shown (eg a belt starter motor). This occurs by energizing the starter and thereby accelerating the primary side. In the next tooth gap, the preloaded engagement spring 64 is responsible for the rapid “remaining” swing-in of the swing arm 40 into the primary-side ring gear 16 .

It is shown in FIG. 17 that after ignition of the internal combustion engine, the internal combustion engine reaches the idle speed. After passing the resonant rotational 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 each other in the swung-in state. Depending on the direction of rotation of the ring gear 16 and the presence of tension between the primary side and the secondary side of the dual-mass flywheel, undesired swing-out forces engaging the pinion gear 16 occur.

Figure 19 shows the ideal arrangement of the central axis. Ideally, the arrangement is chosen such that the central axes of the ring gears 16 , 34 and the central axes of the engagement pinions 30 , 32 and the bearing pin 70 lie as far as possible in 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 forces thus have no or only very small lever arms to cause the swing out.

FIG. 20 shows the embodiment of the starting device according to FIG. 19 in the initial position. Here, the adjustment lever 42 and the swing arm 40 are coupled via a preloaded torsion spring 48 .

Figure 21 shows how the magnetic switch 44 is energized. The adjusting lever 42 is attracted by the magnetic switch 44 , whereby the first engagement pinion 30 is swung in until it hits the ring gear teeth of the primary-side ring gear 16 .

In FIG. 22 it is shown how the magnetic switch 44 further attracts the adjustment lever. And the torsion spring 48 is further pretensioned here. Furthermore, a separately mounted starter or belt starter motor, not shown, is supplied with current.

Figure 23 shows how the primary side ring gear 16 is now driven when the first engagement pinion 30 has found the next cogging and can continue the swing-in process.

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

Figure 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 simplified as one component.

In order to optimize the swivel-in behavior even further with respect to the previous embodiments, it can be advantageous to use an additional synchronizing pinion 72 which is coupled to the swivel shaft 62 via the free wheel 24 . In this case, the pivot shaft 62 is fixedly connected to the adjustment lever 42 and at the same time is rotatably mounted in the housing 50 . The mode of action of the synchronizing pinion 72 is explained in FIGS. 26 to 32 .

If the magnetic switch 44 attracts the adjusting lever 42 , the free wheel 24 is switched so that the adjusting lever 42 entrains the synchronizing pinion 72 and thus also twists the first engaging pinion 30 . However, when the primary-side ring gear 16 is driven by the internal combustion engine, the synchronizing pinion 72 can exceed the adjusting rod 42 in rotational speed.

The first engagement pinion 30 may exceed the second engagement pinion 32 in rotational speed, however, the second engagement pinion 32 can accelerate the first engagement pinion 30 .

In principle, the secondary-side ring gear 34 and the dual-mass flywheel (not shown) deep groove ball bearing lie as far as possible in the same plane, so that the tipping moment on the deep groove ball bearing can be kept low.

Figure 26 shows the starting device of Figure 25 in an initial position. The adjustment lever 42 and the swing arm are coupled via a preloaded torsion spring 48 . The necessary freewheels are not shown in the illustration.

How the magnetic switch 44 is energized is shown in FIG. 27 . The adjusting lever 42 is attracted by the magnetic switch 44 , whereby the first engagement pinion 30 is swung in until it hits the ring gear teeth of the primary-side ring gear 16 .

FIG. 28 shows how the magnetic switch 44 further attracts the adjustment lever 42 . Here, the synchronizing pinion 72 and thus also the first engaging pinion 30 is twisted until this first engaging pinion can find the next tooth slot in the primary-side ring gear 16 and can continue the swing-in process.

In FIG. 29 it is shown how the teeth of the first engagement pinion 30 swing into the tooth slots of the primary side ring gear 16 .

Figure 30 shows how the magnetic switch 44 reaches its end position when the synchronization pinion 72 is twisted further. Here, the first engagement pinion 16 hits the end stop 38 . Furthermore, current is supplied to a starter not shown. At the same time, the first engagement pinion 30 is fully swung in, wherein the pivoting movement causes a rotation of the engagement pinion 30 , which is opposite to the direction of rotation caused by the synchronizing pinion 72 . Therefore, the two rotational movements are at least partially canceled during the remaining swing-in period.

In FIG. 31 , the starter drives the primary side ring gear 16 . This primary side ring gear in turn drives the synchronizing pinion 72 through the first engaging pinion 30 . A free wheel (not shown), which is arranged on the pivot shaft 62 , enables a rotational speed overtaking of the synchronizing pinion 72 relative to the adjusting rod 42 .

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

Figure 33 shows another embodiment of the starting device. The starting device includes only the first engagement pinion 30 . Furthermore, in order to simplify the illustration, the adjustment lever 42 and the swing arm 40 are shown as one-piece components without spring elements.

FIG. 34 shows the swing-in process of the starting device of FIG. 33 . With the aid of an advantageous cogging finding, only the primary-side engagement for starting the internal combustion engine takes place. Here, the swing-in process takes place as in FIG. 2 .

Figure 35 shows the starting position of another embodiment of the starting device. The starting device includes a magnetic switch 44 on which a pull rod 74 is arranged. The pull rod 74 includes 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 swing-in spring 80 is arranged between the slide 78 and the end of the pull rod 74 which is arranged opposite the magnetic switch 44 . The return spring 56 as well as the swing-in spring 80 are preloaded. The adjusting lever 42 is arranged between the slide stop 76 and the slide 78 . The preloaded swivel spring 80 presses the slide 78 against the adjusting rod 42 and thus the adjusting rod 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 prestressed swivel spring 80 , the slide 78 is pressed against the adjusting rod 42 , so that the adjusting rod 42 is pressed against the slide stop 76 . Furthermore, the adjustment rod 42 further transmits the movement of the pull rod 74 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 engagement pinion 30 is in tooth contact with the primary side ring gear 16 .

FIG. 37 shows how the magnetic switch 44 draws the pull rod 74 further until the end position is reached, so that the current loop for the starter motor, not shown, is closed. Here, both the return spring 56 and the swivel spring 80 are preloaded to the greatest extent. The ring gear 16 is twisted by the starter motor until the next cogging is found.

Figure 38 shows how the rest of the swing-in process is performed once the next backlash is found. In this case, the swivel spring 80 with maximum pretension causes the sliding block 78 to move abruptly towards the adjustment lever 42 . Once the engine, not shown, reaches firing speed, the engine is cranked to idle speed.

FIG. 39 shows the initial state of another embodiment of the starting device. In contrast to the starting device of FIGS. 35 to 38 , the one-piece component comprising the adjustment lever 42 and the swing arm 40 is arranged on the motor shaft with the starting pinion 14 . The preloaded swivel spring 80 presses the slide 78 against the adjusting rod 42 and thus the adjusting rod 42 against the slide stop 76 .

How the magnetic switch 44 is energized is shown in FIG. 40 . As a result, the magnetic switch 44 attracts the pull rod 74 . Here, the return spring 56 is increasingly compressed. The engagement pinion 30 collides with the teeth of the ring gear 16 .

FIG. 41 shows how the magnetic switch 44 draws the pull rod 74 further 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 swivel spring 80 are preloaded to the greatest extent.

Figure 42 shows how the starter motor builds up to speed. Here, the engaging pinion 16 is also twisted until the next tooth slot is found in order to sink into this tooth slot.

Figure 43 shows the remaining swing-in process. In this case, the swiveling spring 80 with maximum pretension causes the sliding block 78 to move again abruptly towards the adjustment lever 42 . The engine reaches firing speed and starts to idle speed.

The possibility of helical teeth is likewise advantageous.

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

It is also possible to envisage an embodiment in which the two engaging pinions are rigidly coupled to each other, ie an embodiment without a freewheel on the coupling shaft. However, in order to transmit the ignition torque to the secondary side, the teeth must be designed significantly more rigidly.

It is also conceivable to combine the adjustment lever and the pivot arm into one component, wherein the spring element is omitted. In its simplest form, the embodiment of Figure 12 can consist of a magnetic switch, a swing element and a swingable shaft with two rigidly coupled engagement pinions.

Embodiments are also conceivable in which, instead of the freewheel on the pivotable shaft, a friction device is provided which couples the second engagement pinion with the first engagement pinion via its defined friction torque. The friction torque of the friction device advantageously exceeds 4 Nm. Furthermore, the friction device can have a free angular 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 freewheel, the two engaging pinions can be coupled to each other in a slightly torsional manner by means of a spring element.

List of reference signs

10 starter 70 pins

12 starter 72 synchro pinion

14 Start pinion 74 Tie rod

16 Primary side ring gear 76 Slide stopper

18 primary side 78 slider

20 dual mass flywheels 80 pendulum springs

22 starter

24 Free Wheels

26 motor shaft

28 swingable shaft

30 First engagement pinion

32 Second engagement pinion

34 Secondary side ring gear

36 Second free round

38 end stop

40 swing arm

42 adjustment lever

44 Magnetic switch

46 Secondary side

48 Torsion Spring

50 shells

52 Self-rotation of the engaged pinion

54 The direction of rotation of the starter

56 return spring

58 belt starter motor

60 internal combustion engine

62 foot shaft

64 engagement spring

66 stop

68 Housing fixed stop

Claims (12)

1. A starting device for starting an internal combustion engine (60), comprising: - a pivotable shaft (28), wherein the pivotable shaft (28) is pivotable about the shafts (26, 62, 70) by means of a swing arm (40), - at least one engagement pinion (30, 32) arranged on said pivotable shaft (28) for meshing into at least one ring gear (16, 34) of the dual mass flywheel (20) for starting all the internal combustion engine (60), - an adjustment lever (42), wherein the adjustment 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 engaging pinions (30, 32) into the ring gears (16, 34) in the radial direction, Wherein, the adjustment rod (42) and the swing arm (40) are connected with the shafts (26, 62, 70), and a first engagement pinion (30) is arranged on the swingable shaft (28) and a second engagement pinion (32) for contacting the primary side ring gear (16) on the primary side (18) of the dual mass flywheel (20), the second engagement pinion Gears are used to contact the secondary side ring gear (34) on the secondary side (46) of the dual mass flywheel (20). 2. A starting device according to claim 1, characterized in that the first engagement pinion (30) and the second engagement pinion (32) are rigidly on the pivotable shaft via a freewheel , are coupled to each other by friction means or by spring elements. 3. The starting device according to claim 1 or 2, characterized in that the swing arm (40) and the adjustment lever (42) are configured as one component. 4. The 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 adjustment rod (42), wherein, A fixedly arranged slide stop ( 76 ) and a movable slide ( 78 ) are arranged on the draw rod ( 74 ), wherein the adjustment rod ( 42 ) is arranged on the slide stop (76) and the slider (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 adjustment lever (42) are coupled to each other by a spring element. 6. Starter 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) contacts Engage pinions (30, 32). 7. The starting device according to claim 1 or 2, characterized in that a freewheel (24) is arranged on the shaft (26, 62). 8. The starting device according to claim 2, wherein the first engagement pinion (30) and the second engagement pinion (32) respectively have the same or different addendum circle diameters for Mesh into the primary side ring gear (16) and the secondary side ring gear (34) having the same or different tip circle diameters. 9 . The starting device according to claim 5 , wherein the swing arm ( 40 ) and the adjustment rod ( 42 ) are coupled to each other by a torsion spring ( 48 ). 10 . 10 . The starting device according to claim 5 , wherein the swing arm ( 40 ) and the adjustment rod ( 42 ) are coupled to each other by a compression spring. 11 . 11. The starting device according to claim 5, wherein the swing arm (40) and the adjustment lever (42) are coupled to each other by an engagement 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, said method comprising the steps of: - swinging at least one engaging pinion (30, 32) from an initial position into at least one ring gear (16, 34) of said dual-mass flywheel (20); - ignition of the internal combustion engine (60) by means of a starter (12) or a belt starter motor (58); - reaching the idle speed of said internal combustion engine (60); and - swinging out the starting device into the initial position.

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