EP0518878A1 - Starter system with braking device. - Google Patents

Starter system with braking device.

Info

Publication number
EP0518878A1
EP0518878A1 EP91903883A EP91903883A EP0518878A1 EP 0518878 A1 EP0518878 A1 EP 0518878A1 EP 91903883 A EP91903883 A EP 91903883A EP 91903883 A EP91903883 A EP 91903883A EP 0518878 A1 EP0518878 A1 EP 0518878A1
Authority
EP
European Patent Office
Prior art keywords
rotor
starting device
pinion
output shaft
starting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP91903883A
Other languages
German (de)
French (fr)
Other versions
EP0518878B1 (en
Inventor
Werner Rometsch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0518878A1 publication Critical patent/EP0518878A1/en
Application granted granted Critical
Publication of EP0518878B1 publication Critical patent/EP0518878B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/003—Starters comprising a brake mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N11/00—Starting of engines by means of electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
    • F02N15/043—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer
    • F02N15/046—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer of the planetary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
    • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
    • F02N15/067—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement the starter comprising an electro-magnetically actuated lever
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/13—Machine starters
    • Y10T74/131—Automatic
    • Y10T74/132—Separate power mesher
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/13—Machine starters
    • Y10T74/131—Automatic
    • Y10T74/137—Reduction gearing

Definitions

  • the invention relates to a starter device with an output shaft which carries a pinion for driving a toothed ring of an internal combustion engine and is driven by a rotor and which is axially displaceably mounted for the engagement or disengagement process of the pinion.
  • the starting device according to the invention with the features mentioned in the main claim has the advantage that long run-out times of the pinion are prevented when the starting process is ended.
  • a braking effect is automatically triggered by the output shaft, which moves back into the disengagement position, which brakes the rotor of the drive and thus also the pinion.
  • the teaching according to the invention proposes that the return movement of the output shaft is transmitted to the rotor in such a way that the latter is also axially displaced and thereby hits the braking surface.
  • Such braking is particularly effective in gearbox starting devices, since the rotor represents an element to which a relatively low torque is assigned. Thus, even relatively small braking forces lead to a great effect.
  • the output shaft comes against a resilient contact member of the rotor.
  • This resilient support between the output shaft and the rotor is on the one hand tolerances and nevertheless leads to the transmission of axial forces to the rotor.
  • the contact member is arranged coaxially with the rotor. In this way, unbalance is avoided and even small moments of inertia are achieved.
  • a compression spring is preferably arranged between the contact member and the rotor.
  • the contact member is guided axially displaceably in an axial bore of a rotor shaft.
  • the contact element can be designed as a thrust bolt. This preferably has a circular cross section, its central axis extending coaxially to the rotor axis.
  • a good braking effect can be achieved if the braking surface is formed on a brake disc. This is preferably located between the end face of a commutator assigned to the rotor and a housing area of the starting device.
  • the housing area is formed by a contact surface surrounding a rotor bearing.
  • FIG. 2 shows a detail from the illustration in FIG. 1, with a single-track position being assumed.
  • FIG. 1 shows a longitudinal section through a turning device 1.
  • This has a housing 2, in which a direct current motor 3 and an engagement relay 4 are accommodated.
  • the DC motor 3 has a rotor 5, which acts on an output shaft 6, on the end 7 of which a pinion 8 is arranged in a rotationally fixed manner.
  • the pinion 8 advances into the position 9 shown in dashed lines in FIG. 1 and thereby engages in a ring gear 10 of the internal combustion engine.
  • the axial shifting of the pinion into position 9 is brought about by the engagement relay 4. This will be discussed in more detail below.
  • the rotor 5 is provided with a commutator 11, to the segments 12 of which a rotor winding 13 is connected.
  • the commutator 11 interacts with a carbon brush arrangement 14.
  • a stator 15 with a stator winding 16 is provided, which lies opposite the rotor 5 with a small air gap.
  • the rotor 5 has a rotor shaft 17 which is supported at one end 18 in a needle bearing 19 and is covered by a housing cap 20.
  • the the other end of the rotor shaft 17 has a central receiving bore 22 extending from its end face 21, into which one end 23 of the output shaft 6 engages.
  • the other end of the rotor shaft 17 is mounted on the end 23 of the output shaft 6 via a needle bearing 31 which is arranged in the receiving bore 22.
  • the lateral surface 24 of the end 25 of the rotor shaft 17 provided with the receiving bore 22 is designed as a sun gear 26 which meshes with planet gears 27 which are arranged on a planet carrier 28 (only one planet gear 27 is shown in FIG. 1). .
  • the planet gears 27 are arranged on bearing pins 29 with the interposition of Nadella ⁇ ger.
  • the planet gears 27 mesh with a ring gear 30 provided with internal teeth, which is arranged in a stationary manner in the housing 2.
  • the end 23 of the output shaft 6 is supported by a needle bearing 37 in the receiving bore of the axial web 39.
  • the freewheel outer ring 35 is held by a deep groove ball bearing 38, which is arranged on the axial web 39 and, on the other hand, is supported in the housing 2 (fixed bearing).
  • a cylindrical roller bearing 33 is provided in the opposite end region 32 of the output shaft 6, held by the housing 2 — to which a sealing ring 34 is connected upstream.
  • the cylindrical roller bearing 33 guides the output shaft 6 both in the axial and in the radial direction.
  • the planet carrier 28 is axially connected to a freewheel outer ring 35 via screws 36.
  • the freewheel outer ring 35 belongs to a freewheel device 40 which is designed as a roller freewheel. It has spring-loaded rollers 41 which interact with an inner ring 42 of the freewheel device 40.
  • the inner ring 42 is connected to the output shaft 6 via a steep thread 43.
  • the output shaft 6 has a groove 44, in which a snap ring 45 is arranged.
  • the snap ring 45 forms a stop which, in the event of an axial displacement of the output shaft 6 to be described in greater detail, cooperates with a step 46 of the inner ring 42.
  • a retaining ring 47 which has a radial collar 48, is attached to the output shaft 6.
  • a snap ring 50 which supports a disk 51, is located in a groove 49 of the retaining ring 47.
  • An annular channel 52 is thus formed between the disk 51 and the radial collar 48.
  • the pinion 8 is rotatably but axially displaceably mounted. It is acted upon by a helical compression spring 54. This is preloaded when a tooth-on-tooth position results when the pinion 8 is engaged in the ring gear 10.
  • the engagement relay 4 has a stationary relay winding 61 which interacts with an armature 62.
  • the armature 62 is axially displaceably mounted and is urged into the position shown in FIG. 1 by a return spring 112 in the form of a helical compression spring when the engagement relay 4 is not energized.
  • the axis 63 has a contact element 66 at its one end region 65 that can cooperate with electrical connections 67.
  • the armature 62 is connected to a plunger 68 which projects into a housing space 69 of the housing 2.
  • the plunger 68 interacts with an engagement lever 70 designed as a double lever, which is pivotably mounted approximately in its central region by means of a cross bolt 71.
  • the cross pin 71 is held on a housing-side arm 72.
  • the lower end 73 of the engagement lever 70 is provided with a projection 74 which engages in the ring channel 52.
  • a driving head 76 is formed at the other end 75 of the engagement lever 70.
  • a locking device 77 which is essentially formed by a bow spring 80, a control sleeve 108, a ring 117 and springs 99 and 112, prevents the pinion 8 from inadvertently moving in the direction of the ring gear 10 of the internal combustion engine, since this could damage the parts.
  • This unintentional axial movement could occur without a locking device 77 in that braking moments, which occur, for example, due to the bearings and shaft sealing rings, move the output shaft 6 into the engagement position, that is to say the return spring forces are smaller than the axial force components occurring on the high-helix thread.
  • the steep thread 43 allows an axial displacement of the output shaft 6 by the dimension a.
  • the receiving bore 22 in the rotor shaft 17 of the rotor 5 ends in an axial bore 131 in which a resilient contact member 132 is accommodated.
  • the contact member 132 is formed as a thrust bolt 133. This has a circular cross section which is dimensioned to the diameter of the axial bore 131 in such a way that the thrust bolt 133 is guided in the axial bore 131 in an axially displaceable manner.
  • a compression spring 135 designed as a helical spring, that is to say that one end 136 of the compression spring 135 is supported on the starting bolt 133 and the other end 137 of the compression spring 135 lies on the bottom 138 of the axial bore 131 designed as a blind bore.
  • the lateral surface 139 of the thrust bolt 133 has a radial collar 140 in the support area of the compression spring 135.
  • the remaining area of the lateral surface 139 faces the axial bore 131 at a distance from the inner wall 141.
  • the distance is dimensioned so that a snap ring 143 can be received there, which is inserted into an annular groove 142 formed on the inner wall 141.
  • the snap ring 143 forms a stop for the Thrust bolt 133; that is to say, when the starting bolt 133 is not acted on, it limits the axial movement of the starting bolt 133 caused by the compression spring 135.
  • the side 144 of the starting bolt 133 facing the output shaft 6 has a central starting elevation 145.
  • the arrangement is designed in such a way that in the track position of the output shaft 6 shown in FIG. As a result, the compression spring 135 is compressed accordingly, so that a reaction force is exerted on the rotor 5 of the direct current motor 3.
  • the displacement path c is approx. 2 to 3 mm.
  • the rotor shaft 17 is guided in a rotor bearing 147, which is designed as a needle bearing 19.
  • a brake disc 151 with a braking surface 150 is arranged between the end face 148 of the rotor 5 or commutator 11 and a housing region 149 of the starting device 1.
  • the housing region 149 is formed by a contact surface 152 surrounding the rotor bearing 147.
  • the starting device 1 operates as follows:
  • the engagement relay 4 is energized via a start switch. This leads to the armature 62 moving to the right (FIG. 1), where runs through the control sleeve 108 against the stirrup spring 80 in such a way that the latter is radially expanded. As a result, the ring 117 is released. A relative movement between the control sleeve 108 and the ring 117 is possible while consuming the free travel b because the latter is axially displaceably mounted on the control sleeve 108. If the bow spring 80 assumes its spread position, the free travel b is used up, that is to say the left side of the driving head 76 is carried along by the control sleeve 108.
  • the engagement lever 70 carries out a pivoting movement clockwise around the transverse pin 71.
  • the projection 74 shifts the output shaft 6 in the direction of the ring gear 10, as a result of which the pinion 8 can engage in the toothing of the ring gear 10.
  • the engagement forces ensure that the pinion 8 now moves completely into the ring gear 10, the output shaft 6 extending axially to the end position due to the steep thread 43, so that — as a result — the one shown in FIG. 1 with dashed lines Position 9 is taken by the pinion 8.
  • the engagement relay 4 drops out.
  • the return movement is supported by the return springs 64 and 112.
  • the ring 117 then comes against the driving head 76 of the engagement lever 70, so that the engagement lever 70 pivots counterclockwise, whereby the pinion 8 is returned to the position shown in solid line in FIG. Since in the final stage of the starting process the internal combustion engine now in operation "overtakes" the rotation of the pinion 8, the disengagement process is supported by the steep thread 43.
  • the bow spring 80 is also in the starting position again, that is to say it secures the ring 117, so that the engagement lever 70 is in the position shown in FIG. 1 is fixed. This prevents unintentional axial displacement of the output shaft 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Braking Arrangements (AREA)

Abstract

Un appareil de démarrage comprend un arbre mené qui porte un pignon de commande d'une couronne dentée d'un moteur à combustion interne et qui est entraîné par un rotor. Pour permettre l'enclenchement ou le déclenchement du pignon, l'arbre est monté de manière axialement mobile. Afin de pouvoir freiner rapidement le pignon, l'arbre mené (6) agit axialement sur le rotor (5) dans la position de déclenchement du pignon de façon à pousser le rotor contre une surface de freinage (150).A starting device comprises a driven shaft which carries a drive pinion for a ring gear of an internal combustion engine and which is driven by a rotor. To allow engagement or disengagement of the pinion, the shaft is mounted axially movable. In order to be able to brake the pinion quickly, the driven shaft (6) acts axially on the rotor (5) in the pinion release position so as to push the rotor against a braking surface (150).

Description

Andrehvorrichtung mit BremseinrichtungStarting device with braking device
Stand der TechnikState of the art
Die Erfindung betrifft eine Andrehvorrichtung mit einer ein Ritzel für den Antrieb eines Zahnkranzes einer Brennkraftmaschine tragenden, von einem Rotor angetriebenen Abtriebswelle, die für den Ein- be¬ ziehungsweise Ausspurvorgang des Ritzels axial ver- schieblich gelagert ist.The invention relates to a starter device with an output shaft which carries a pinion for driving a toothed ring of an internal combustion engine and is driven by a rotor and which is axially displaceably mounted for the engagement or disengagement process of the pinion.
In der Kraftfahrzeugtechnik dienen derartige An¬ drehvorrichtungen zum Start der Fahrzeug-Brenn- kraftmaschinen. Für den Startvorgang der Fahrzeug- Brennkraftmaschinen muß ein angetriebenes Ritzel in einen Zahnkranz der Brennkraftmaschine einspuren. Für die hierzu erforderliche Axialbewegung des Rit¬ zels ist eine dieses tragende Abtriebswelle axial verschieblich gelagert. Wird der Startvorgang been¬ det, so spurt das Ritzel aus dem Zahnkranz wieder aus, wobei die Abtriebswelle in ihre Ausgangsstel¬ lung (Ausspurstellung) zurücktritt. Nachteilig ist, wenn nach dem Ausspüren das Ritzel noch eine län- gere Zeit nachläuft, da dann bei einem möglicher¬ weise erfolgenden weiteren Startvorgang kein sau¬ beres Einspuren erfolgt, sondern durch eine zu große Relativbewegung zwischen Ritzel und Zahnkranz eine Beschädigung erfolgen könnte. Besonders lang ist die Auslaufzeit bei Getriebe-Andrehvorrichtun¬ gen gegenüber Direkt-Andrehvorrichtungen (ohne Ge¬ triebestufe) , da die Trägheitsmomente durch das Übersetzungsverhältnis im Quadrat ansteigen.In automotive engineering, such turning devices serve to start the vehicle internal combustion engines. For the starting process of the vehicle internal combustion engines, a driven pinion must mesh into a ring gear of the internal combustion engine. For the necessary axial movement of the knurl, an output shaft carrying it is axially displaceably mounted. When the starting process is ended, the pinion spurts out of the ring gear again, the output shaft returning to its starting position (disengagement position). It is disadvantageous if the pinion has been lags time, since then, in the event of a further starting process which may take place, there is no clean engagement, but damage could be caused by an excessive relative movement between pinion and ring gear. The run-down time is particularly long in the case of geared starting devices compared to direct starting devices (without a gear stage), since the moments of inertia increase by the square of the gear ratio.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Andrehvorrichtung mit den im Hauptanspruch genannten Merkmalen hat demgegenüber den Vorteil, daß lange Auslaufzeiten des Ritzels beim Beenden des Startvorgangs verhindert sind. Er¬ findungsgemäß wird durch die sich in die Ausspur- stellung zurückbewegende -Abtriebswelle selbsttätig eine Bremswirkung ausgelöst, die den Rotor des An¬ triebs und damit auch das Ritzel abbremst. Die er¬ findungsgemäße Lehre schlägt dafür vor, daß die Rückbewegung der Abtriebswelle derart auf den Rotor übertragen wird, so daß sich dieser ebenfalls axial verlagert und dabei gegen die Bremsflache tritt. Bei Getriebe-Andrehvorrichtungen ist ein derartiges Abbremsen besonders effektiv, da der Rotor ein Ele¬ ment darstellt, dem ein relativ niedriges Drehmo¬ ment zugeordnet ist. Somit führen auch schon rela¬ tiv kleine Bremskräfte zu großer Wirkung.The starting device according to the invention with the features mentioned in the main claim has the advantage that long run-out times of the pinion are prevented when the starting process is ended. According to the invention, a braking effect is automatically triggered by the output shaft, which moves back into the disengagement position, which brakes the rotor of the drive and thus also the pinion. The teaching according to the invention proposes that the return movement of the output shaft is transmitted to the rotor in such a way that the latter is also axially displaced and thereby hits the braking surface. Such braking is particularly effective in gearbox starting devices, since the rotor represents an element to which a relatively low torque is assigned. Thus, even relatively small braking forces lead to a great effect.
Nach einer Weiterbildung der Erfindung ist vorgese¬ hen, daß die Abtriebswelle gegen ein federndes An¬ lageglied des Rotors tritt. Diese federnde Abstüt- zung zwischen Abtriebswelle und Rotor gleicht ei- nerseits Toleranzen aus und führt dennoch zur Über¬ tragung von Axialkräften auf den Rotor.According to a development of the invention, it is provided that the output shaft comes against a resilient contact member of the rotor. This resilient support between the output shaft and the rotor is on the one hand tolerances and nevertheless leads to the transmission of axial forces to the rotor.
Vorteilhaft ist es, wenn das Anlageglied koaxial zum Rotor angeordnet ist. Hierdurch sind Unwuchten vermieden und auch kleine Trägheitsmomente erzielt.It is advantageous if the contact member is arranged coaxially with the rotor. In this way, unbalance is avoided and even small moments of inertia are achieved.
Um die federnde Wirkung des Anlageglieds zu erhal¬ ten, ist bevorzugt zwischen Anlageglied und Rotor eine Druckfeder angeordnet.In order to maintain the resilient effect of the contact member, a compression spring is preferably arranged between the contact member and the rotor.
Ein besonders platzsparender und dennoch einfacher Aufbau ergibt sich, wenn das Anlageglied in einer Axialbohrung einer Rotorwelle axial verschiebbar geführt ist. Insbesondere kann das Anlageglied als Anlaufbolzen ausgebildet sein. Dieser hat vorzugs¬ weise einen kreisförmigen Querschnitt, wobei sich seine Mittelachse koaxial zur Rotorachse erstreckt.A particularly space-saving, yet simple structure is obtained if the contact member is guided axially displaceably in an axial bore of a rotor shaft. In particular, the contact element can be designed as a thrust bolt. This preferably has a circular cross section, its central axis extending coaxially to the rotor axis.
Eine gute Bremswirkung läßt sich dann erzielen, wenn die Bremsfläche an einer Bremsscheibe ausge¬ bildet ist. Diese befindet sich vorzugsweise zwi¬ schen der Stirnseite eines dem Rotor zugeordneten Kommutators und einem Gehäusebereich der Andrehvor¬ richtung.A good braking effect can be achieved if the braking surface is formed on a brake disc. This is preferably located between the end face of a commutator assigned to the rotor and a housing area of the starting device.
Insbesondere ist vorgesehen, daß der Gehäusebereich von einer ein Rotorlager umgebenden Anlagefläche gebildet ist.In particular, it is provided that the housing area is formed by a contact surface surrounding a rotor bearing.
Zeichnungdrawing
Die Erfindung wird im folgenden anhand der Figuren näher erläutert. Es zeigen: Figur 1 ein Längsschnitt durch eine Andrehvor¬ richtung undThe invention is explained in more detail below with reference to the figures. Show it: 1 shows a longitudinal section through a starting device and
Figur 2 ein Ausschnitt aus der Darstellung der Figur 1, wobei eine Einspurstellung ein¬ genommen ist.FIG. 2 shows a detail from the illustration in FIG. 1, with a single-track position being assumed.
Beschreibung eines AusführungsbeispielεDescription of an embodiment
Die Figur 1 zeigt einen Längsschnitt durch eine An¬ drehvorrichtung 1. Diese weist ein Gehäuse 2 auf, in dem ein Gleichstrommotor 3 und ein Einrückrelaiε 4 untergebracht sind. Der Gleichstrommotor 3 weist einen Rotor 5 auf, der auf eine Abtriebswelle 6 wirkt, auf dessen Ende 7 ein Ritzel 8 drehfest an¬ geordnet ist. Für den Anlaßbetrieb einer nicht dar¬ gestellten Brennkraftmaschine rückt das Ritzel 8 in die in der Figur 1 gestrichelt eingezeichnete Posi¬ tion 9 vor und spurt dabei in einen Zahnkranz 10 der Brennkraftmaschine ein. Die axiale Verlagerung des Ritzels in die Position 9 wird durch das Ein¬ rückrelais 4 veranlaßt. Hierauf wird im nachfolgen¬ den noch näher eingegangen.FIG. 1 shows a longitudinal section through a turning device 1. This has a housing 2, in which a direct current motor 3 and an engagement relay 4 are accommodated. The DC motor 3 has a rotor 5, which acts on an output shaft 6, on the end 7 of which a pinion 8 is arranged in a rotationally fixed manner. For the starting operation of an internal combustion engine (not shown), the pinion 8 advances into the position 9 shown in dashed lines in FIG. 1 and thereby engages in a ring gear 10 of the internal combustion engine. The axial shifting of the pinion into position 9 is brought about by the engagement relay 4. This will be discussed in more detail below.
Der Rotor 5 ist mit einem Kommutator 11 versehen, an dessen Segmenten 12 eine Rotorwicklung 13 ange¬ schlossen ist. Der Kommutator 11 wirkt mit einer Kohlebürstenanordnung 14 zusammen. Ferner ist ein Stator 15 mit Statorwicklung 16 vorgesehen, der dem Rotor 5 mit geringem Luftspalt gegenüberliegt.The rotor 5 is provided with a commutator 11, to the segments 12 of which a rotor winding 13 is connected. The commutator 11 interacts with a carbon brush arrangement 14. Furthermore, a stator 15 with a stator winding 16 is provided, which lies opposite the rotor 5 with a small air gap.
Der Rotor 5 weist eine Rotorwelle 17 auf, die an ihrem einen Ende 18 in einem Nadellager 19 gelagert und von einer Gehausekappe 20 überfangen ist. Das andere Ende der Rotorwelle 17 weist eine von ihrer Stirnseite 21 ausgehende, zentrale Aufnahmebohrung 22 auf, in die das eine Ende 23 der Abtriebswelle 6 eingreift. Das andere Ende der Rotorwelle 17 ist über ein Nadellager 31, das in der Aufnahmebohrung 22 angeordnet ist, auf dem Ende 23 der Abtriebs- welle 6 gelagert. Die Mantelfläche 24 des mit Aufnahmebohrung 22 versehenen Endes 25 der Rotor¬ welle 17 ist als Sonnenrad 26 ausgebildet, das mit Planetenrädern 27 kämmt, die auf einem Planetenträ¬ ger 28 angeordnet sind (in der Figur 1 ist ledig¬ lich ein Planetenrad 27 dargestellt) . Die Planeten¬ räder 27 sind unter Zwischenschaltung von Nadella¬ ger auf Lagerstiften 29 angeordnet.The rotor 5 has a rotor shaft 17 which is supported at one end 18 in a needle bearing 19 and is covered by a housing cap 20. The the other end of the rotor shaft 17 has a central receiving bore 22 extending from its end face 21, into which one end 23 of the output shaft 6 engages. The other end of the rotor shaft 17 is mounted on the end 23 of the output shaft 6 via a needle bearing 31 which is arranged in the receiving bore 22. The lateral surface 24 of the end 25 of the rotor shaft 17 provided with the receiving bore 22 is designed as a sun gear 26 which meshes with planet gears 27 which are arranged on a planet carrier 28 (only one planet gear 27 is shown in FIG. 1). . The planet gears 27 are arranged on bearing pins 29 with the interposition of Nadella¬ ger.
Ferner kämmen die Planetenräder 27 mit einem mit Innenverzahnung versehenen Hohlrad 30, das ortsfest im Gehäuse 2 angeordnet ist.Furthermore, the planet gears 27 mesh with a ring gear 30 provided with internal teeth, which is arranged in a stationary manner in the housing 2.
Das Ende 23 der Abtriebswelle 6 ist über ein Nadel¬ lager 37 in der Aufnahmebohrung des Axialsteges 39 gelagert. Der Freilaufaußenring 35 wird durch ein Rillenkugellager 38, das auf dem Axialsteg 39 ange¬ ordnet und sich andererseits im Gehäuse 2 abstützt, gehalten (Feεtlager) . Im gegenüberliegenden Endbe¬ reich 32 der Abtriebswelle 6 ist -vom Gehäuse 2 ge¬ halten- ein Zylinderrollenlager 33 vorgesehen, dem -nach außen- ein Simmerring 34 vorgeschaltet ist. Das Zylinderrollenlager 33 führt die Abtriebswelle 6 sowohl in axialer als auch in radialer Richtung.The end 23 of the output shaft 6 is supported by a needle bearing 37 in the receiving bore of the axial web 39. The freewheel outer ring 35 is held by a deep groove ball bearing 38, which is arranged on the axial web 39 and, on the other hand, is supported in the housing 2 (fixed bearing). In the opposite end region 32 of the output shaft 6, a cylindrical roller bearing 33 is provided — held by the housing 2 — to which a sealing ring 34 is connected upstream. The cylindrical roller bearing 33 guides the output shaft 6 both in the axial and in the radial direction.
Der Planetenträger 28 ist axial mit einem Frei¬ laufaußenring 35 über Schrauben 36 verbunden. Der Freilaufaußenring 35 gehört einer Freilaufein- richtung 40 an, die als Rollenfreilauf ausgebildet ist. Sie weist federbeaufschlagte Rollen 41 auf, die mit einem Innenring 42 der Freilaufeinrichtung 40 zusammenwirken. Der Innenring 42 steht über ein Steilgewinde 43 mit der Abtriebswelle 6 in Verbin¬ dung. Ferner weist die -Abtriebswelle 6 eine Nut 44 auf, in der ein Sprengring 45 angeordnet ist. Der Sprengring 45 bildet einen Anschlag, der -bei einer noch näher zu beschreibenden- Axialverlagerung der Abtriebswelle 6 mit einer Stufe 46 des Innenrings 42 zusammenwirkt.The planet carrier 28 is axially connected to a freewheel outer ring 35 via screws 36. The freewheel outer ring 35 belongs to a freewheel device 40 which is designed as a roller freewheel. It has spring-loaded rollers 41 which interact with an inner ring 42 of the freewheel device 40. The inner ring 42 is connected to the output shaft 6 via a steep thread 43. Furthermore, the output shaft 6 has a groove 44, in which a snap ring 45 is arranged. The snap ring 45 forms a stop which, in the event of an axial displacement of the output shaft 6 to be described in greater detail, cooperates with a step 46 of the inner ring 42.
Auf der Abtriebswelle 6 ist ein Haltering 47 befe¬ stigt, der einen Radialkragen 48 aufweist. Ferner liegt in einer Nut 49 des Halterings 47 ein Spreng¬ ring 50 ein, der eine Scheibe 51 abstützt. Zwischen Scheibe 51 und Radialkragen 48 wird somit ein Ring¬ kanal 52 ausgebildet.A retaining ring 47, which has a radial collar 48, is attached to the output shaft 6. In addition, a snap ring 50, which supports a disk 51, is located in a groove 49 of the retaining ring 47. An annular channel 52 is thus formed between the disk 51 and the radial collar 48.
Am Ende 7 der Abtriebswelle 6 ist das Ritzel 8 drehfest, jedoch axial verschieblich gelagert. Es wird von einer Schraubendruckfeder 54 beaufschlagt. Diese wird vorgespannt, wenn sich beim Einspuren des Ritzels 8 in den Zahnkranz 10 eine Zahn-Auf- Zahn-Stellung ergibt.At the end 7 of the output shaft 6, the pinion 8 is rotatably but axially displaceably mounted. It is acted upon by a helical compression spring 54. This is preloaded when a tooth-on-tooth position results when the pinion 8 is engaged in the ring gear 10.
Das Einrückrelais 4 weist eine ortsfeste Relais¬ wicklung 61 auf, die mit einem Anker 62 zusammen¬ wirkt. Der Anker 62 ist axial verschieblich gela¬ gert und wird von einer als Schraubendruckfeder ausgebildeten Rückstellfeder 112 im nicht erregten Zustand des Einrückrelais' 4 in die in der Figur 1 dargestellte Position gedrängt. Die Achse 63 weist an ihrem einen Endbereich 65 ein Kontaktelement 66 auf, daß mit elektrischen Anschlüssen 67 zusammen¬ wirken kann.The engagement relay 4 has a stationary relay winding 61 which interacts with an armature 62. The armature 62 is axially displaceably mounted and is urged into the position shown in FIG. 1 by a return spring 112 in the form of a helical compression spring when the engagement relay 4 is not energized. The axis 63 has a contact element 66 at its one end region 65 that can cooperate with electrical connections 67.
Der Anker 62 ist mit einem Stößel 68 verbunden, der in einen Gehäuseraum 69 des Gehäuses 2 hineinragt. Der Stößel 68 wirkt mit einem als Doppelhebel aus¬ gebildeten Einrückhebel 70 zusammen, der etwa in seinem mittleren Bereich mittels eines Querbolzens 71 schwenkbeweglich gelagert ist. Der Querbolzens 71 wird an einem gehäuseseitigen Ausleger 72 gehal¬ ten. Das untere Ende 73 des Einrückhebels 70 ist mit einem Vorsprung 74 versehen, der in den Ringka¬ nal 52 eingreift. Am anderen Ende 75 des Einrückhe¬ bels 70 ist ein Mitnahmekopf 76 ausgebildet. Durch Verlagerung des Stößels 68 wird der Einrückhebel 70 mitgenommen, wodurch eine Axialverlagerung der Ab¬ triebswelle 6 erfolgt. Im nicht erregten Zustand des Einrückrelais''4 ist dafür Sorge zu tragen, daß das Ritzel 8 die in der Figur 1 mit durchgezogenen Linien dargestellte Position nicht verläßt. Eine Verriegelungsvorrichtung 77, die im wesentlichen von einer Bügelfeder 80, einer Steuerhülse 108, ei¬ nem Ring 117 sowie Federn 99 und 112 gebildet ist, verhindert, daß sich das Ritzel 8 unbeabsichtigt in Richtung auf den Zahnkranz 10 der Brennkraftma- schine bewegt, da dies zur Beschädigung der Teile führen könnte. Diese unbeabsichtigte Axialbewegung könnte ohne Verriegelungsvorrichtung 77 dadurch eintreten, daß bremsende Momente, die z.B. durch die Lager und Wellendichtringe auftreten, die Ab¬ triebswelle 6 in Einspurposition bewegen, das heißt, die Rückεtellfederkräfte sind kleiner als die am Steilgewinde auftretenden Axialkraftkompo¬ nenten. Aus der Figur 1 ist 'ersichtlich, daß der Mitnahme¬ kopf 76 den Abstand zwischen der einen Seite 119 des Rings 117 und einer Stirnfläche 120 deε Steuer¬ kragens 108 nicht voll ausfüllt; vielmehr verbleibt ein Leerweg b.The armature 62 is connected to a plunger 68 which projects into a housing space 69 of the housing 2. The plunger 68 interacts with an engagement lever 70 designed as a double lever, which is pivotably mounted approximately in its central region by means of a cross bolt 71. The cross pin 71 is held on a housing-side arm 72. The lower end 73 of the engagement lever 70 is provided with a projection 74 which engages in the ring channel 52. A driving head 76 is formed at the other end 75 of the engagement lever 70. By shifting the plunger 68, the engagement lever 70 is carried along, as a result of which the output shaft 6 is axially displaced. In the non-energized state of the contactor '' 4, care must be taken that the pinion gear 8 does not leave the position shown in Figure 1 with solid lines. A locking device 77, which is essentially formed by a bow spring 80, a control sleeve 108, a ring 117 and springs 99 and 112, prevents the pinion 8 from inadvertently moving in the direction of the ring gear 10 of the internal combustion engine, since this could damage the parts. This unintentional axial movement could occur without a locking device 77 in that braking moments, which occur, for example, due to the bearings and shaft sealing rings, move the output shaft 6 into the engagement position, that is to say the return spring forces are smaller than the axial force components occurring on the high-helix thread. ', It can be seen that the head 76 Mitnahme¬ the distance between the From Figure 1 one side 119 of the ring 117 and an end surface 120 collar 108 does not completely fill deε Steuer¬; rather, an empty path remains b.
Das Steilgewinde 43 erlaubt eine Axialverlagerung der Abtriebswelle 6 um das Maß a.The steep thread 43 allows an axial displacement of the output shaft 6 by the dimension a.
Die Aufnahmebohrung 22 in der Rotorwelle 17 des Ro¬ tors 5 läuft in einer Axialbohrung 131 aus, in der ein federndes Anlageglied 132 untergebracht ist. Das Anlageglied 132 ist als Anlaufbolzen 133 ausge¬ bildet. Dieser besitzt einen kreisförmigen Quer¬ schnitt, der derart zum Durchmeεεermaß der Axial¬ bohrung 131 bemessen ist, daß der Anlaufbolzen 133 axial verschiebbar in der Axialbohrung 131 geführt wird. Die der Abtriebswelle 6 abgewandte Seite 134 des Anlaufbolzens 133 wird von einer als Schrauben¬ feder ausgebildeten Druckfeder 135 beaufschlagt, das heißt, das eine Ende 136 der Druckfeder 135 stützt sich an dem Anlaufbolzen 133 ab und das an¬ dere Ende 137 der Druckfeder 135 liegt am Grund 138 der als Sackbohrung ausgebildeten Axialbohrung 131 an.The receiving bore 22 in the rotor shaft 17 of the rotor 5 ends in an axial bore 131 in which a resilient contact member 132 is accommodated. The contact member 132 is formed as a thrust bolt 133. This has a circular cross section which is dimensioned to the diameter of the axial bore 131 in such a way that the thrust bolt 133 is guided in the axial bore 131 in an axially displaceable manner. The side 134 of the starting bolt 133 facing away from the output shaft 6 is acted upon by a compression spring 135 designed as a helical spring, that is to say that one end 136 of the compression spring 135 is supported on the starting bolt 133 and the other end 137 of the compression spring 135 lies on the bottom 138 of the axial bore 131 designed as a blind bore.
Die Mantelfläche 139 des Anlaufbolzenε 133 weist im Abstützbereich der Druckfeder 135 einen Radialkra¬ gen 140 auf. Hierdurch steht der übrige Bereich der Mantelfläche 139 mit Abstand der Innenwandung 141 der Axialbohrung 131 gegenüber. Der Abstand ist ge¬ rade so bemessen, daß dort ein Sprengring 143 auf¬ genommen werden kann, der in eine an der Innenwan¬ dung 141 ausgebildeten Ringnut 142 eingesetzt ist. Der Sprengring 143 bildet einen Anschlag für den Anlaufbolzen 133; das heißt, er begrenzt bei nicht beaufschlagtem Anlaufbolzen 133 die durch die Druckfeder 135 bewirkte Axialbewegung des Anlauf- bolzens 133.The lateral surface 139 of the thrust bolt 133 has a radial collar 140 in the support area of the compression spring 135. As a result, the remaining area of the lateral surface 139 faces the axial bore 131 at a distance from the inner wall 141. The distance is dimensioned so that a snap ring 143 can be received there, which is inserted into an annular groove 142 formed on the inner wall 141. The snap ring 143 forms a stop for the Thrust bolt 133; that is to say, when the starting bolt 133 is not acted on, it limits the axial movement of the starting bolt 133 caused by the compression spring 135.
Die der Abtriebswelle 6 zugekehrte Seite 144 des Anlaufbolzens 133 weist eine zentrale Anlauferhe¬ bung 145 auf. Die Anordnung ist nun derart ausge¬ bildet, daß in der in der Figur 1 dargestellten Ausεpurstellung der Abtriebswelle 6 deren Stirn¬ seite 146 die Anlauferhebung 145 deε Anlaufbolzenε 133 derart beaufschlagt, daß letzterer um einen Verschiebeweg c von dem Sprengring 143 abgehoben wird. Hierdurch wird die Druckfeder 135 entspre¬ chend komprimiert, so daß eine Reaktionskraft auf den Rotor 5 des Gleichstrommotors 3 ausgeübt wird. Der Verschiebeweg c beträgt ca. 2 bis 3 mm.The side 144 of the starting bolt 133 facing the output shaft 6 has a central starting elevation 145. The arrangement is designed in such a way that in the track position of the output shaft 6 shown in FIG. As a result, the compression spring 135 is compressed accordingly, so that a reaction force is exerted on the rotor 5 of the direct current motor 3. The displacement path c is approx. 2 to 3 mm.
Am kommutatorseitigen Ende 18 ist die Rotorwelle 17 in einem Rotorlager 147 geführt, das als Nadellager 19 ausgebildet ist. Zwischen der Stirnseite 148 des Rotorε 5 beziehungsweise Kommutators 11 und einem Gehäuεebereich 149 der Andrehvorrichtung 1 ist eine mit Bremsfläche 150 versehene Bremsscheibe 151 an¬ geordnet. Der Gehäusebereich 149 wird von einer das Rotorlager 147 umgebenden Anlagefläche 152 gebil¬ det.At the commutator end 18, the rotor shaft 17 is guided in a rotor bearing 147, which is designed as a needle bearing 19. A brake disc 151 with a braking surface 150 is arranged between the end face 148 of the rotor 5 or commutator 11 and a housing region 149 of the starting device 1. The housing region 149 is formed by a contact surface 152 surrounding the rotor bearing 147.
Die erfindungsgemäße Andrehvorrichtung 1 arbeitet folgendermaßen:The starting device 1 according to the invention operates as follows:
Für einen Startvorgang der (nicht dargestellten) Brennkraftmaschine wird über einen Startschalter das Einrückrelaiε 4 erregt. Dies führt dazu, daß sich der Anker 62 nach rechts (Figur 1) bewegt, wo- durch die Steuerhülse 108 derart gegen die Bügelfe¬ der 80 anläuft, daß diese radial aufgespreizt wird. Hierdurch wird der Ring 117 freigegeben. Eine Rela¬ tivbewegung zwischen der Steuerhülse 108 und dem Ring 117 ist unter Aufzehrung des Leerweges b des¬ halb möglich, weil letzterer axial verschieblich auf der Steuerhülse 108 gelagert ist. Nimmt die Bü¬ gelfeder 80 ihre aufgespreizte Stellung ein, so ist der Leerweg b aufgebraucht, das heißt, die linke Seite deε Mitnahmekopfeε 76 wird von der Steuer¬ hülse 108 mitgenommen. Der Einrückhebel 70 führt eine Schwenkbewegung im Uhrzeigersinn um den Quer¬ bolzen 71 herum aus. Dabei verlagert der Vorsprung 74 die Abtriebswelle 6 in Richtung auf den Zahn¬ kranz 10, wodurch das Ritzel 8 in die Zahnung deε Zahnkranzeε 10 einspuren kann. Die Einspurkräfte sorgen dafür, daß nunmehr das Ritzel 8 vollständig in den Zahnkranz 10 einfährt, wobei aufgrund des Steilgewindes 43 die Abtriebswelle 6 bis in Endpo¬ sition axial herausfährt, so daß -im Ergebnis- die in der Figur 1 mit gestrichelten Linien eingezeich¬ nete Position 9 vom Ritzel 8 eingenommen wird. Da durch die Anzugsbewegung des Einrückrelais' 4 das Kontaktelement 66 in Verbindung zu den elektrischen Anschlüεsen 67 tritt, wird der Gleichstrommotor 3 erregt, das heißt, der Rotor 5 beginnt zu drehen, wodurch das Ritzel 8 über das aus Sonnenrad 26, Planetenrädern 27 und Hohlrad 30 gebildete Unter¬ setzungsgetriebe mitgenommen wird.For a starting process of the internal combustion engine (not shown), the engagement relay 4 is energized via a start switch. This leads to the armature 62 moving to the right (FIG. 1), where runs through the control sleeve 108 against the stirrup spring 80 in such a way that the latter is radially expanded. As a result, the ring 117 is released. A relative movement between the control sleeve 108 and the ring 117 is possible while consuming the free travel b because the latter is axially displaceably mounted on the control sleeve 108. If the bow spring 80 assumes its spread position, the free travel b is used up, that is to say the left side of the driving head 76 is carried along by the control sleeve 108. The engagement lever 70 carries out a pivoting movement clockwise around the transverse pin 71. The projection 74 shifts the output shaft 6 in the direction of the ring gear 10, as a result of which the pinion 8 can engage in the toothing of the ring gear 10. The engagement forces ensure that the pinion 8 now moves completely into the ring gear 10, the output shaft 6 extending axially to the end position due to the steep thread 43, so that — as a result — the one shown in FIG. 1 with dashed lines Position 9 is taken by the pinion 8. Since the contact element 66 comes into contact with the electrical connections 67 as a result of the pulling-in movement of the engagement relay 4, the DC motor 3 is excited, that is to say the rotor 5 begins to rotate, as a result of which the pinion 8 is driven by the sun gear 26, planet gears 27 and ring gear 30 reduction gear formed is taken.
Wird der Startvorgang beendet, so fällt das Ein¬ rückrelais 4 ab. Die Abfallbewegung wird von den Rückstellfedern 64 und 112 unterstützt. Dabei tritt der Ring 117 gegen den Mitnahmekopf 76 des Einrück- hebels 70, so daß der Einrückhebel 70 entgegen dem Uhrzeigersinn verschwenkt, wodurch das Ritzel 8 in die in der Figur 1 mit durchgezogener Linie darge¬ stellte Position zurückgeholt wird. Da im Endεta- dium des Startvorgangs die nunmehr im Betrieb be¬ findliche Brennkraftmaschine die Drehung des Rit¬ zels 8 "überholt" wird durch das Steilgewinde 43 der Ausspurvorgang unterstützt.If the starting process is ended, the engagement relay 4 drops out. The return movement is supported by the return springs 64 and 112. The ring 117 then comes against the driving head 76 of the engagement lever 70, so that the engagement lever 70 pivots counterclockwise, whereby the pinion 8 is returned to the position shown in solid line in FIG. Since in the final stage of the starting process the internal combustion engine now in operation "overtakes" the rotation of the pinion 8, the disengagement process is supported by the steep thread 43.
Ist wieder die Auεεpurposition (Ruheposition) ein¬ genommen (Figur 1) , so befindet sich auch die Bü¬ gelfeder 80 wieder in Ausgangsstellung, das heißt, sie sichert den Ring 117, so daß der Einrückhebel 70 in der in der Figur 1 dargestellten Position fi¬ xiert ist. Damit ist eine unbeabεichtigte Axialver¬ lagerung der Abtriebswelle 6 verhindert.If the out-of-track position (rest position) is again taken up (FIG. 1), the bow spring 80 is also in the starting position again, that is to say it secures the ring 117, so that the engagement lever 70 is in the position shown in FIG. 1 is fixed. This prevents unintentional axial displacement of the output shaft 6.
Verlagert sich die Abtriebswelle 6 -wie beschrie¬ ben- für den Startvorgang der Brennkraftmaschine in ihre Einspurstellung, die in der Figur 2 darge¬ stellt ist, so entlastet die Stirnseite 146 der Ab¬ triebswelle 6 den Anlaufbolzen 133, so daß er durch die Druckfeder 135 mit seinem Radialkragεn 140 ge¬ gen den Sprengring 143 gedrängt wird. Der Rotor 5 des Gleichstrommotors 3 unterliegt daher keiner durch den Anlaufbolzen verursachter Axialkraftbe¬ aufschlagung mehr. Wird der Startvorgang beendet, so tritt die Abtriebεwelle 6 in ihre in der Figur 1 dargeεtellte Ausrückstellung zurück, wodurch die Stirnseite 146 den Anlaufbolzen 133 unter Kompri¬ mierung der Druckfeder 135 in die in der Figur 1 dargestellte Stellung zurückdrängt. Hierdurch wird eine Reaktionskraft auf den Rotor 5 ausgeübt, wo¬ durch die Stirnseite 148 des Kommutatorε 11 gegen die Bremsεcheibe 151 gedrängt wird. Die Brems¬ scheibe 151 wiederum stützt sich an der Anlageflä¬ che 152 des Gehäuseε 2 ab. Hierdurch erfolgt eine Abbremεung der Drehbewegung deε Rotorε 5. Dieser Bremsvorgang ist besonders bei der dargestellten Getriebe-Andrehvorrichtung effektiv, da er an einer Stelle erfolgt, der ein relativ niedriges Drehmo¬ ment zugeordnet ist. Die Folge ist eine sehr kurze Auslaufzeit der Andrehvorrichtung. If the output shaft 6 shifts - as described - for the starting process of the internal combustion engine into its single-track position, which is shown in FIG. 2, the end face 146 of the output shaft 6 relieves the thrust bolt 133 so that it is supported by the compression spring 135 with its radial collar 140 is urged against the snap ring 143. The rotor 5 of the DC motor 3 is therefore no longer subject to any axial force caused by the thrust bolt. If the starting process is ended, the output shaft 6 returns to its disengagement position shown in FIG. 1, whereby the end face 146 pushes the thrust bolt 133 back into the position shown in FIG. 1 while compressing the compression spring 135. As a result, a reaction force is exerted on the rotor 5, whereby the end face 148 of the commutator 11 counteracts the brake disc 151 is pushed. The brake disk 151 in turn is supported on the contact surface 152 of the housing 2. As a result, the rotary movement of the rotor 5 is braked. This braking process is particularly effective in the case of the geared starting device shown, since it takes place at a location to which a relatively low torque is assigned. The result is a very short run-down time for the starter.

Claims

Ansprüche Expectations
1. Andrehvorrichtung mit einer ein Ritzel für den Antrieb eineε Zahnkranzes einer Brennkraftmaschine tragenden, von einem Rotor angetriebenen Abtriebs- welle, die für den Ein- beziehungsweise Ausspurvor¬ gang des Ritzelε axial verεchiebbar gelagert ist, dadurch gekennzeichnet, daß die Abtriebswelle (6) in Ausεpurstellung den Rotor (5) axial derart be¬ aufschlagt, daß er (5) gegen eine Bremsfläche (150) tritt.1. Starting device with a pinion for driving a ring gear of an internal combustion engine, driven by a rotor driven output shaft which is axially displaceably mounted for the engagement or disengagement of the pinion, characterized in that the output shaft (6) in Track position axially impacts the rotor (5) in such a way that it (5) strikes a braking surface (150).
2. Andrehvorrichtung nach Anspruch 1, dadurch ge¬ kennzeichnet, daß die Abtriebswelle (6) gegen ein federndes Anlageglied (132) des Rotors (5) tritt.2. Starting device according to claim 1, characterized ge indicates that the output shaft (6) against a resilient contact member (132) of the rotor (5).
3. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, dadurch gekennzeichnet, daß das An¬ lageglied (132) koaxial zum Rotor (5) angeordnet ist. - Λk -3. Starting device according to one of the preceding claims, characterized in that the contact member (132) is arranged coaxially with the rotor (5). - Λk -
4. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, dadurch gekennzeichnet, daß zwischen Anlageglied (132) und Rotor (5) eine Druckfeder (135) angeordnet ist.4. Starting device according to one of the preceding claims, characterized in that a compression spring (135) is arranged between the contact member (132) and the rotor (5).
5. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, dadurch gekennzeichnet, daß das An¬ lageglied (132) in einer Axialbohrung (131) einer Rotorwelle (17) axial verschiebbar geführt ist.5. Starting device according to one of the preceding claims, characterized in that the contact member (132) is guided axially displaceably in an axial bore (131) of a rotor shaft (17).
6. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, dadurch gekennzeichnet, daß das An¬ lageglied (132) als Anlaufbolzen (133) ausgebildet ist.6. Starting device according to one of the preceding claims, characterized in that the contact member (132) is designed as a starting bolt (133).
7. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, dadurch gekennzeichnet, daß die Bremsfläche (150) an einer Bremsεcheibe (151) auε- gebildet ist.7. Starting device according to one of the preceding claims, characterized in that the braking surface (150) is formed on a brake disc (151).
8. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, dadurch gekennzeichnet, daß die Bremsεcheibe (151) zwischen der Stirnseite (146) eines dem Rotor (5) zugeordneten Kommutators (11) und einem Gehäuεebereich (149) der Andrehvorrich¬ tung (1) angeordnet iεt.8. Starting device according to one of the preceding claims, characterized in that the brake disk (151) between the end face (146) of a commutator (11) assigned to the rotor (5) and a housing area (149) of the starting device (1) arranged iεt.
9. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, dadurch gekennzeichnet, daß der Ge¬ häusebereich (149) von einer ein Rotorlager (147) umgebenden Anlagefläche (152) gebildet ist.9. Starting device according to one of the preceding claims, characterized in that the housing region (149) is formed by a contact surface (152) surrounding a rotor bearing (147).
10. Andrehvorrichtung nach einem der vorhergehen¬ den Ansprüche, gekennzeichnet durch die Ausbildung als Getriebe-Andrehvorrichtung. 10. Starting device according to one of the preceding claims, characterized by the design as a gear starting device.
EP91903883A 1990-03-03 1991-02-22 Starter system with braking device Expired - Lifetime EP0518878B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4006797A DE4006797A1 (en) 1990-03-03 1990-03-03 TURNING DEVICE WITH BRAKE DEVICE
DE4006797 1990-03-03
PCT/DE1991/000140 WO1991014094A1 (en) 1990-03-03 1991-02-22 Starter system with braking device

Publications (2)

Publication Number Publication Date
EP0518878A1 true EP0518878A1 (en) 1992-12-23
EP0518878B1 EP0518878B1 (en) 1994-10-05

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EP (1) EP0518878B1 (en)
JP (1) JPH05504808A (en)
AU (1) AU638802B2 (en)
BR (1) BR9106109A (en)
CZ (1) CZ280180B6 (en)
DE (2) DE4006797A1 (en)
ES (1) ES2063495T3 (en)
HU (1) HU208725B (en)
RU (1) RU2048653C1 (en)
WO (1) WO1991014094A1 (en)

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Also Published As

Publication number Publication date
DE4006797A1 (en) 1991-09-12
HU208725B (en) 1993-12-28
CZ280180B6 (en) 1995-11-15
ES2063495T3 (en) 1995-01-01
AU7240091A (en) 1991-10-10
BR9106109A (en) 1993-02-24
DE59103176D1 (en) 1994-11-10
JPH05504808A (en) 1993-07-22
HU9202826D0 (en) 1992-12-28
WO1991014094A1 (en) 1991-09-19
US5321987A (en) 1994-06-21
HUT61612A (en) 1993-01-28
EP0518878B1 (en) 1994-10-05
RU2048653C1 (en) 1995-11-20
AU638802B2 (en) 1993-07-08

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