EP0518895B1 - Starting device with drive shaft lock - Google Patents

Starting device with drive shaft lock Download PDF

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Publication number
EP0518895B1
EP0518895B1 EP91904528A EP91904528A EP0518895B1 EP 0518895 B1 EP0518895 B1 EP 0518895B1 EP 91904528 A EP91904528 A EP 91904528A EP 91904528 A EP91904528 A EP 91904528A EP 0518895 B1 EP0518895 B1 EP 0518895B1
Authority
EP
European Patent Office
Prior art keywords
spring
starting device
armature
engagement
ring
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.)
Expired - Lifetime
Application number
EP91904528A
Other languages
German (de)
French (fr)
Other versions
EP0518895A1 (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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0518895A1 publication Critical patent/EP0518895A1/en
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Publication of EP0518895B1 publication Critical patent/EP0518895B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02N15/02—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
    • 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
    • F02N15/023—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the overrunning type
    • 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

Definitions

  • the invention relates to a starting device according to the preamble of patent claim 1.
  • a thrust screwing operation is provided which engages a pinion of the changing device into a squab ring of the internal combustion engine.
  • the engagement relay picks up and moves the pinion in the axial direction via an engagement lever in such a way that it can come into effect with the ring gear of the internal combustion engine.
  • a starter motor starts to rotate. As soon as the pinion engages in the ring gear due to the thrust movement, it is moved further in the axial direction against a stop by the rotation of the starter motor with the aid of a steep thread assigned to the output shaft.
  • a return spring presses the armature of the engagement relay and thus - via the engagement lever - the pinion back into its rest position.
  • This disengagement is supported by the steep thread when overtaking by starting the internal combustion engine.
  • the freewheel device protects the starter rotor from excessive speeds when overtaking by the internal combustion engine.
  • the output shaft carrying the pinion and provided with the steep thread tends to move towards the toothed ring of the internal combustion engine when this movement due to braking moments, for example due to a shaft sealing ring and / or the existing bearings opposing forces of the return spring are smaller than the axial force component on the high-helix thread.
  • the pinion on the running gear ring of the internal combustion engine can start up and be damaged.
  • known starting devices are e.g. provided with a ball lock.
  • a spring-loaded slide secures the axial position of the output shaft carrying the pinion.
  • the aforementioned slide is moved so that the ball can be moved radially outwards.
  • the output shaft is released for axial movement.
  • This ball lock requires highly precise and elaborately designed components, which leads to a complicated and expensive design.
  • a locking device is known in which a part actuated by the armature of the engagement relay is provided with clamping rollers which, on the one hand, take the engagement lever to engage the pinion when the internal combustion engine is turned on by pulling in the armature and, on the other hand, when the engagement relay is switched off by the return spring of the armature, run onto wedge-shaped surfaces of the engagement lever and the locking device attached to the starter housing and are clamped there.
  • clamping effect is particularly dependent on the force of the return spring of the armature, so that over time there are wear and tear on the clamping surfaces and rollers, which reduce the clamping effect or increase it so much that the subsequent one Single-track operation is hindered or even blocked.
  • the present invention strives to provide a structurally simple and reliable locking device.
  • the starting device according to the invention with the characterizing features mentioned in the main claim has the advantage that it reliably prevents the leading of the output shaft carrying the pinion in the non-energized state of the engagement relay with a simple structure. Since, according to the invention, the locking device acts on the armature of the engagement relay in order to secure the rest position of the pinion, no complicated locking is required, but it is possible to resort to structurally simple solutions, since sufficient space is available for such solutions in the area of the engagement relay.
  • the locking device according to the invention which acts on the armature of the engagement relay and thus on the engagement lever, can also be easily assembled since, as in the known ball locking, special mounting positions for introducing the balls do not have to be used.
  • the locking device has a locking member which engages behind a stop of the armature in the drop-out position of the engagement relay and which is operated by means of a positive control by the tightening movement the anchor can be moved to the release position.
  • the armature By energizing the engagement relay, which is caused by the triggering of the starting process of the internal combustion engine, the armature starts to pull in, which releases the locking by means of a positive control, that is to say the locking member is shifted into the release position.
  • the engagement lever is released and can be pivoted by the armature, as a result of which the pinion arranged on the output shaft is axially displaced so that it engages in the ring gear of the internal combustion engine.
  • the engagement relay At the end of the starting process, the engagement relay is de-energized so that the return spring moves the armature back into the rest position (drop position), the output shaft being carried along via the engagement lever.
  • the locking member secures the anchor position, so that inadmissible re-toe-in is prevented.
  • the armature runs through an empty path to bring about the release position before the engagement lever is carried along. Because of this free travel, it is possible that the locking member can first be moved into its release position, that is to say that an unlocking position is brought about by the movement of the armature, so that subsequently -im In the course of the further anchor movement - the entrainment of the engagement lever for engaging the pinion becomes possible.
  • the locking member is preferably a first spring provided with at least one rear grip step, which can be deflected in the release position by means of a control sleeve arranged on a plunger of the armature.
  • the control sleeve moving with the armature thus displaces the locking member in the release position.
  • the control sleeve releases the locking member, which is designed as a spring, in the drop position of the engagement relay, so that the rear grip step for securing the armature position of the engagement relay brings about securing the position.
  • the stop is preferably formed by a ring mounted on the control sleeve.
  • the axial position of the ring can be fixed or released by means of the locking member.
  • the fixed position of the ring prevents a pivoting movement of the engagement lever, so that the output shaft cannot get into its toe-in position.
  • the control sleeve bears against an armature stop by the force of a second spring.
  • This position of the control sleeve is only left with further tensioning of the second spring if engagement of the pinion in the toothed ring of the internal combustion engine is initially prevented due to a tooth-on-tooth position.
  • the second spring nevertheless enables the engagement relay to be tightened, so that contacts of the engagement relay 'are closed at the start of the rotary movement of the starting device. This results in a relative movement between pinion and ring gear, so that a corresponding pinion tooth can enter a tooth gap on the ring gear.
  • a compression spring assigned to the pinion can also be tensioned, which enables a relative movement between pinion and output shaft.
  • control sleeve is arranged axially displaceable relative to the armature in the direction of its fall against the force of the second spring.
  • one side of the ring interacts with the engagement lever, taking into account the free travel.
  • a third spring acts on the other side of the ring.
  • the ring assumes a securing position for the engagement lever when the engagement relay is not energized.
  • one end of the third spring is supported on the housing of the starter and the other end on the ring.
  • a control sleeve stop which limits a displacement path of the ring which is possible in the drop direction and is possible by the force of the third spring.
  • the control sleeve stop thus allows a displacement of the ring by the force of the third spring only up to a certain position.
  • the first spring is designed in particular as a bow spring, which has a rear grip step on each leg having. By shifting the control sleeve, the bow spring can be spread to the release position.
  • the second spring is preferably a helical compression spring, which coils the tappet and is supported at one end against a tappet stop and, at the other end, strikes a control sleeve step.
  • the control sleeve is biased towards the armature so that it rests against the armature stop.
  • the third spring can be designed as a helical compression spring which surrounds the control sleeve. This results in a simple and space-saving structure.
  • the control sleeve has a control collar for spreading the bow spring.
  • the bow spring is fastened to the housing of the starting device in the direction of the longitudinal extension of the plunger.
  • FIG. 1 shows a longitudinal section through a starter 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 starter 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 to the position 9 shown in broken lines in FIG.
  • the engagement of relay 4 causes the pinion to move axially to position 9. This will be discussed in more detail below.
  • the starter 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 is opposite the starter rotor 5 with a small air gap.
  • the starter rotor 5 has a rotor shaft 17 which is supported at one end 18 in a needle bearing 19 and covered by a housing cap 20.
  • the other end of the rotor shaft 17 has a central receiving bore 22 extending from its end face 21, into which the 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 with the interposition of needle bearings on bearing pins 29.
  • 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 mounted in the receiving bore of the axial web 39 via a needle bearing 37.
  • 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 — held by the housing 2, to which a sealing ring 34 is connected upstream — to the outside.
  • 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 fastened on the output shaft 6. Furthermore, a snap ring 50, which supports a disk 51, lies 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 fixed relay winding 61 which interacts with an armature 62.
  • the armature 62 is axially displaceably mounted and is not excited by a return spring 113 designed as a helical compression spring State of the engagement relay 4 pushed into the position shown in FIG.
  • the axis 63 has at its one end region 65 a contact element 66 that can interact 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 annular channel 52.
  • a driving head 76 is formed at the other end 75 of the engagement lever 70.
  • a locking device 77 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 can occur due to the fact 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 formation of the locking device 77 will now be discussed.
  • the locking device 77 fixes the position of the engagement lever 70 shown in FIG. 1 in the deenergized state of the engagement relay 4, so that the output shaft 6 assumes a fixed axial position.
  • the locking device 77 acts on the armature 62, in particular on the plunger 68, of the engagement relay 4 in order to secure the idle position of the pinion 8.
  • the locking device 77 has a locking member 78 which is designed as a first spring 79.
  • the first spring 79 is a bow spring 80 (compare in particular also FIG. 2).
  • the bow spring 80 has two legs 81 which are shaped such that each is provided with a rear grip step 82.
  • the ends 83 of the two legs 81 are divergingly bent outwards, as a result of which bevel slopes 84 are formed.
  • the areas 85 of the legs 81 opposite the run-up bevels 84 are each designed such that - starting from the rear grip step 82 - a section 86 initially runs approximately parallel to the plunger 68, to which a control section 87 then adjoins, which runs diverging outwards and in an arc section 88 merges, which is curved in the opposite direction to the control section 87, with a bend at an angle greater than 90 °.
  • the subsequent end 89 of each leg 81 is fastened in a holder 90.
  • the holder 90 is connected to a threaded screw 91 which extends coaxially to the plunger 68 and is mounted in a bore 92 in the housing 2.
  • the end 93 of the threaded screw 91 protruding outward from the housing 2 is secured by means of a lock nut 94.
  • the plunger 68 connected to the armature 62 of the engagement relay 4 has at its free end 95 an annular groove 96 into which a snap ring 97 is inserted.
  • a disk 98 is supported on the snap ring 97, which is supported on the tappet 68 and is acted upon by a second spring 99. The disk 98 therefore forms a tappet stop 100.
  • the second spring 99 is designed as a helical compression spring 101, which surrounds the tappet 68 and is supported with one end 102 on the tappet stop 100 and with its other end 103 on a control sleeve step 104 of a control sleeve 108.
  • the latter is mounted on the ram 68.
  • the control sleeve step 104 is formed in that the control sleeve 108 is axially penetrated by a stepped bore 105.
  • the force of the helical compression spring 101 pushes the end face 106 facing the armature 62 against an armature stop 107.
  • the helical compression spring 101 is mounted in the section of the stepped bore 105 having the larger diameter.
  • control sleeve 108 At its end facing away from the armature 62, the control sleeve 108 has an axially protruding control collar 109 which, as described in more detail below, interacts with the control sections 87 of the bow spring 80.
  • the control sleeve 108 has different outer diameters, whereby a control sleeve stop 110 is formed.
  • the control sleeve stop 110 faces the armature 62.
  • a disk 111 is pressed against the control sleeve stop 110 by means of a third spring 112, which is designed as a helical compression spring 113.
  • One end 114 of the helical compression spring 113 is supported on the housing 2 and the other end 115 on the disk 111.
  • a stop 116 bears against the disk 111, which is designed as a ring 117 and is located on the larger-diameter section of the control sleeve 108.
  • the bow spring 80 is supported on the lateral surface 118 of the ring 117 in the positions shown in FIGS. 1 and 2.
  • the driving head 76 does not completely fill the distance between the one side 119 of the ring 117 and an end face 120 of the control collar 108; rather, an empty path remains b.
  • the steep thread 43 allows an axial displacement of the output shaft 6 by the dimension a.
  • 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), as a result of which the control collar 109 runs against the control sections 87 of the bow spring 80 in such a way that the latter is expanded radially. This gives the rear grip levels 82 the leg 81 the ring 117 free. As long as the ring 117 is engaged by the rear grip steps 82, 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 larger diameter of the control sleeve 108.
  • the dragging of the control sleeve 108 by axial displacement of the plunger 68 is effected via the helical compression spring 101.
  • the bow spring 80 assumes its spread position (FIG. 3)
  • the free travel b is used up, that is to say the left side of the driving head 76 is carried along by the end face 120.
  • the engagement lever 70 pivots clockwise around the cross 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 engages in the toothing of the ring gear 10.
  • the occurring engagement forces ensure that the pinion 8 now completely retracts into the ring gear 10, the output shaft 6 extending axially due to the steep thread 43, so that — as a result — the position 9 shown in FIG.
  • the engagement relay 4 drops out.
  • the return movement is supported by the return springs 64 and 112.
  • the ring 117 comes with its side 119 against the driving head 76 of the engagement lever 70, so that the engagement lever 70 pivots counterclockwise, whereby the pinion 8 is brought back into the position shown in solid line in FIG. Since the internal combustion engine, which is now in operation, "overtakes” the rotation of the pinion 8 in the final stage of the starting process, the disengagement process is supported by the steep thread 43.

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  • 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)
  • Valve Device For Special Equipments (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

The invention relates to a starting device with a starting relay the armature of which, by means of a starting lever, axially displaces a pinion gear for driving a ring gear of an internal combustion engine, said pinion gear having a free-wheeling device and co-operating with a starter rotor. The starting device also has a locking device which prevents the pinion from being pushed forward if the starting relay is not energized. To obtain a simple construction, the locking device (77) engages on the armature (62) of the starting (4) to maintain the pinion (8) in its rest position.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Andrehvorrichtung nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a starting device according to the preamble of patent claim 1.

In der Kraftfahrzeugtechnik dienen derartige Andrehvorrichtungen zum Start der Fahrzeug-Brennkraftmaschinen. Bei mit Einrückrelais versehenen Einspursystemen ist ein Schubschraubbetrieb vorgesehen, der ein Ritzel der Ändrehvorrichtung in einen Zankranz der Brennkraftmaschine einspurt. Beim Auslösen des Startvorgangs zieht das Einrückrelais an und bewegt über einen Einrückhebel das Ritzel derart in axialer Richtung, daß es mit dem Zahnkranz der Brennkraftmaschine in Wirkung treten kann. Gleichzeitig beginnt ein Startermotor zu drehen. Sobald das Ritzel durch die Schubbewegung in den Zahnkranz einspurt, wird es durch die Drehung des Startermotors mit Hilfe eines der Abtriebswelle zugeordneten Steilgewindes weiter in axialer Richtung bis gegen einen Anschlag bewegt. Beim Beenden des Startvorgangs drückt eine Rückstellfeder den Anker des Einrückrelais und damit über - den Einrückhebel - das Ritzel in seine Ruhelage zurück. Dieses Ausspuren wird durch das Steilgewinde beim durch Anspringen der Brennkraftmaschine erfolgenden Überholen unterstützt. Die Freilaufeinrichtung schützt den Starterrotor vor zu hohen Drehzahlen beim Überholen durch die Brennkraftmaschine. Insbesondere bei freiausstoßenden Andrehvorrichtungen neigt die das Ritzel tragende, mit dem Steilgewinde versehene Abtriebswelle beim Starterauslauf durch bremsende Momente, z.B. durch einen Wellendichtring und/oder die vorhandenen Lager, dazu, sich in Richtung auf den Zahnkranz der Brennkraftmaschine zu bewegen, wenn die dieser Bewegung entgegenwirkenden Kräfte der Rückstellfeder kleiner sind, als die Axialkraftkomponente am Steilgewinde. Dadurch kann das Ritzel am laufenden Zahnkranz der Brennkraftmaschine anlaufen und beschädigt werden.In automotive engineering, such starting devices are used to start the vehicle internal combustion engines. In the case of single-track systems provided with engagement relays, a thrust screwing operation is provided which engages a pinion of the changing device into a squab ring of the internal combustion engine. When the starting process is triggered, the engagement relay picks up and moves the pinion in the axial direction via an engagement lever in such a way that it can come into effect with the ring gear of the internal combustion engine. At the same time, a starter motor starts to rotate. As soon as the pinion engages in the ring gear due to the thrust movement, it is moved further in the axial direction against a stop by the rotation of the starter motor with the aid of a steep thread assigned to the output shaft. When the starting process is ended, a return spring presses the armature of the engagement relay and thus - via the engagement lever - the pinion back into its rest position. This disengagement is supported by the steep thread when overtaking by starting the internal combustion engine. The freewheel device protects the starter rotor from excessive speeds when overtaking by the internal combustion engine. Particularly in the case of free-ejecting starting devices, the output shaft carrying the pinion and provided with the steep thread tends to move towards the toothed ring of the internal combustion engine when this movement due to braking moments, for example due to a shaft sealing ring and / or the existing bearings opposing forces of the return spring are smaller than the axial force component on the high-helix thread. As a result, the pinion on the running gear ring of the internal combustion engine can start up and be damaged.

Um dies zu verhindern, sind bekannte Andrehvorrichtungen z.B. mit einer Kugelverriegelung versehen. In der Ruhelage sichert ein federbelasteter Schieber die Axialposition der das Ritzel tragenden Abtriebswelle. Für den Entriegelungvorgang wird der erwähnte Schieber verlagert, so daß die Kugel radial auswärts verlagert werden kann. Hierdurch wird die Abtriebswelle für eine Axialbewegung freigegeben. Diese Kugelverriegelung erfordert hochpräzise und aufwendig gestaltete Bauteile, was zu einer komplizierten und teuren Bauform führt.To prevent this, known starting devices are e.g. provided with a ball lock. In the rest position, a spring-loaded slide secures the axial position of the output shaft carrying the pinion. For the unlocking process, the aforementioned slide is moved so that the ball can be moved radially outwards. As a result, the output shaft is released for axial movement. This ball lock requires highly precise and elaborately designed components, which leads to a complicated and expensive design.

Aus der FR-A- 1 512 520 (Figur 6) ist eine Verriegelungsvorrichtung bekannt, bei der ein vom Anker des Einrückrelais betätigtes Teil mit Klemmrollen versehen ist, die einerseits beim Andrehvorgang der Brennkraftmaschine durch das Einziehen des Ankers den Einrückhebel zum Einspuren des Ritzels mitnehmen und die andererseits beim Abschalten des Einrückrelais durch die Rückstellfeder des Ankers auf keilförmig verlaufende Flächen des Einrückhebels und der am Startergehäuse befestigte Verriegelungsvorrichtung auflaufen und dort eingeklemmt werden. Dabei ist nachteilig, daß die Klemmwirkung insbesondere von der Kraft der Rückstellfeder des Ankers abhängig ist, so daß sich im Laufe der Zeit durch Stöße und Erschütterungen an den Klemmflächen und Rollen Abnutzungen ergeben, welche die Klemmwirkung verringern oder auch so weit verstärken, daß der nachfolgende Einspurvorgang behindert oder gar blockiert wird.From FR-A-1 512 520 (FIG. 6) a locking device is known in which a part actuated by the armature of the engagement relay is provided with clamping rollers which, on the one hand, take the engagement lever to engage the pinion when the internal combustion engine is turned on by pulling in the armature and, on the other hand, when the engagement relay is switched off by the return spring of the armature, run onto wedge-shaped surfaces of the engagement lever and the locking device attached to the starter housing and are clamped there. It is disadvantageous that the clamping effect is particularly dependent on the force of the return spring of the armature, so that over time there are wear and tear on the clamping surfaces and rollers, which reduce the clamping effect or increase it so much that the subsequent one Single-track operation is hindered or even blocked.

Mit der vorliegenden Erfindung wird angestrebt, eine konstruktiv einfache und zuverlässige Verriegelungsvorrichtung zu schaffen.The present invention strives to provide a structurally simple and reliable locking device.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Andrehvorrichtung mit den im Hauptanspruch genannten kennzeichnenden Merkmalen hat demgegenüber den Vorteil, daß sie bei einfachem Aufbau sicher das Vorspuren der das Ritzel tragenden Abtriebswelle im nicht erregten Zustand des Einrückrelais verhindert. Da erfindungsgemäß die Verriegelungseinrichtung am Anker des Einrückrelais zur Sicherung der Ruhestellung des Ritzels angreift, ist keine komplizierte Verriegelung erforderlich, sondern es kann auf konstruktiv einfache Lösungen zurückgegriffen werden, da im Bereich des Einrückrelais hinreichend Raum für derartige Lösungen zur Verfgügung steht. Die am Anker des Einrückrelais und damit am Einrückhebel angreifende erfindungsgemäße Verriegelungsvorrichtung läßt sich ferner einfach montieren, da nicht - wie bei der bekannten Kugelverrriegelung - auf spezielle Montagepositionen zum Einbringen der Kugeln zurückgegriffen werden muß.The starting device according to the invention with the characterizing features mentioned in the main claim has the advantage that it reliably prevents the leading of the output shaft carrying the pinion in the non-energized state of the engagement relay with a simple structure. Since, according to the invention, the locking device acts on the armature of the engagement relay in order to secure the rest position of the pinion, no complicated locking is required, but it is possible to resort to structurally simple solutions, since sufficient space is available for such solutions in the area of the engagement relay. The locking device according to the invention, which acts on the armature of the engagement relay and thus on the engagement lever, can also be easily assembled since, as in the known ball locking, special mounting positions for introducing the balls do not have to be used.

Nach einer Weiterbildung der Erfindung ist vorgesehen, daß die Verriegelungseirichtung ein einen Anschlag des Ankers in Abfallstellung des Einrückrelais hintergreifendes Verriegelungsglied aufweist, das mittels einer Zwangssteuerung durch die Anzugsbewegung des Ankers in Freigabestellung verlagerbar ist. Solange sich also der Anker des Einrückrelais' in Abfallstellung befindet, wird dessen Anker und damit der Einrückhebel und somit die mit Ritzel versehene Abtriebswelle in einer Stellung verriegelt, in der das Ritzel nicht gegen den Zahnkranz der Brennkraftmaschine anlaufen kann. Durch Erregung des Einrückrelais', welche durch das Auslösen des Startvorgangs der Brennkraftmaschine hervorgerufen wird, stetzt die Anzugsbewegung des Ankers ein, die mittels einer Zwangssteuerung die Verriegelung aufhebt, das heißt, das Verriegelungsglied wird in Freigabestellung verlagert. Hierdurch wird der Einrückhebel freigegeben und kann durch den Anker verschwenkt werden, wodurch das auf der Abtriebswelle angeordnete Ritzel axial verlagert wird, so daß es in den Zahnkranz der Brennkraftmaschine einspurt. Zur Beendigung des Startvorgangs erfolgt eine Entregung des Einrückrelais', so daß die Rückstellfeder den Anker in Ruheposition (Abfallstellung) Zurückbewegt, wobei über den Einrückhebel die Abtriebswelle mitgenommen wird. Beim Erreichen der Abfall-Endstellung sichert das Verriegelungsglied die Ankerposition, so daß ein unzulässiges Wiedervorspuren verhindert ist.According to a development of the invention, it is provided that the locking device has a locking member which engages behind a stop of the armature in the drop-out position of the engagement relay and which is operated by means of a positive control by the tightening movement the anchor can be moved to the release position. As long as the armature of the engagement relay is in the drop position, its armature and thus the engagement lever and thus the pinion-provided output shaft are locked in a position in which the pinion cannot start against the ring gear of the internal combustion engine. By energizing the engagement relay, which is caused by the triggering of the starting process of the internal combustion engine, the armature starts to pull in, which releases the locking by means of a positive control, that is to say the locking member is shifted into the release position. As a result, the engagement lever is released and can be pivoted by the armature, as a result of which the pinion arranged on the output shaft is axially displaced so that it engages in the ring gear of the internal combustion engine. At the end of the starting process, the engagement relay is de-energized so that the return spring moves the armature back into the rest position (drop position), the output shaft being carried along via the engagement lever. When the final waste position is reached, the locking member secures the anchor position, so that inadmissible re-toe-in is prevented.

Insbesondere ist vorgesehen, daß der Anker einen Leerweg zur Herbeiführung der Freigabestellung durchläuft, bevor eine Mitnahme des Einrückhebels erfolgt. Aufgrund dieser Leerwegs ist es möglich, daß zunächst das Verriegelungsglied in seine Freigabestellung überführt werden kann, das heißt also durch die Bewegung des Ankers eine Entriegelungsstellung herbeigeführt ist, so daß anschließend -im Zuge der weiteren Ankerbewegung- die Mitnahme des Einrückhebels zum Einspuren des Ritzels möglich wird.In particular, it is provided that the armature runs through an empty path to bring about the release position before the engagement lever is carried along. Because of this free travel, it is possible that the locking member can first be moved into its release position, that is to say that an unlocking position is brought about by the movement of the armature, so that subsequently -im In the course of the further anchor movement - the entrainment of the engagement lever for engaging the pinion becomes possible.

Vorzugsweise ist das Verriegelungsglied eine mit mindestens einer Hintergriffstufe versehene, erste Feder, die mittels einer auf einem Stößel des Ankers angeordneten Steuerhülse in Freigabestellung auslenkbar ist. Die sich mit dem Anker bewegende Steuerhülse verlagert somit das Verriegelungsglied in Freigabestellung. Andererseits gibt die Steuerhülse in der Abfallstellung des Einrückrelais' das als Feder ausgebildete Verriegelungsglied frei, so daß die Hintergriffstufe zur Sicherung der Ankerposition des Einrückrelais' eine Lagensicherung bewirkt.The locking member is preferably a first spring provided with at least one rear grip step, which can be deflected in the release position by means of a control sleeve arranged on a plunger of the armature. The control sleeve moving with the armature thus displaces the locking member in the release position. On the other hand, the control sleeve releases the locking member, which is designed as a spring, in the drop position of the engagement relay, so that the rear grip step for securing the armature position of the engagement relay brings about securing the position.

Vorzugsweise wird der Anschlag von einem auf der Steuerhülse gelagerten Ring gebildet. Die Axialposition des Rings kann mittels des Verriegelungsglieds fixiert bzw. freigegeben werden. Durch die fixierte Position des Rings ist eine Schwenkbewegung des Einrückhebels verhindert, so daß die Abtriebswelle nicht in ihre Vorspurposition gelangen kann.The stop is preferably formed by a ring mounted on the control sleeve. The axial position of the ring can be fixed or released by means of the locking member. The fixed position of the ring prevents a pivoting movement of the engagement lever, so that the output shaft cannot get into its toe-in position.

Nach einer bevorzugten Ausführungsform liegt die Steuerhülse durch die Kraft einer zweiten Feder gegen einen Ankeranschlag an. Diese Position der Steuerhülse wird nur dann unter weiterem Spannen der zweiten Feder verlassen, wenn ein Einspuren des Ritzels in den Zahnkranz der Brennkraftmaschine aufgrund einer Zahn-Auf-Zahn-Stellung zunächst verhindert ist. Die zweite Feder ermöglicht dabei dennoch das Anziehen des Einrückrelais', so daß Kontakte des Einrückrelais' zum Start der Drehbewegung der Andrehvorrichtung geschlossen werden. Hierdurch erfolgt eine Relativbewegung zwischen Ritzel und Zahnkranz, so daß ein entsprechender Ritzelzahn in eine Zahnlücke am Zahnkranz eintreten kann. Bei der genannten Zahn-Auf-Zahn-Stellung kann überdies auch eine dem Ritzel zugeordnete Druckfeder gespannt werden, die eine Relativbewegung zwischen Ritzel und Abtriebswelle ermöglicht.According to a preferred embodiment, the control sleeve bears against an armature stop by the force of a second spring. This position of the control sleeve is only left with further tensioning of the second spring if engagement of the pinion in the toothed ring of the internal combustion engine is initially prevented due to a tooth-on-tooth position. The second spring nevertheless enables the engagement relay to be tightened, so that contacts of the engagement relay 'are closed at the start of the rotary movement of the starting device. This results in a relative movement between pinion and ring gear, so that a corresponding pinion tooth can enter a tooth gap on the ring gear. In the tooth-on-tooth position mentioned, a compression spring assigned to the pinion can also be tensioned, which enables a relative movement between pinion and output shaft.

Aus dem vorstehenden wird deutlich, daß die Steuerhülse gegen die Kraft der zweiten Feder relativ zum Anker in dessen Abfallrichtung axial verlagerbar angeordnet ist.From the above it is clear that the control sleeve is arranged axially displaceable relative to the armature in the direction of its fall against the force of the second spring.

Wie bereits erwähnt, wirkt die eine Seite des Rings -unter Berücksichtigung des Leerwegs- mit dem Einrückhebel zusammen. Die andere Seite des Rings wird von einer dritten Feder beaufschlagt. Hierdurch nimmt der Ring bei nicht erregtem Einrückrelais eine Sicherungsposition für den Einrückhebel ein. Insbesondere stützt sich das eine Ende der dritten Feder am Gehäuse der Andrehvorrichtung und das andere Ende am Ring ab.As already mentioned, one side of the ring interacts with the engagement lever, taking into account the free travel. A third spring acts on the other side of the ring. As a result, the ring assumes a securing position for the engagement lever when the engagement relay is not energized. In particular, one end of the third spring is supported on the housing of the starter and the other end on the ring.

Nach einem bevorzugten Ausführungsbeispiel ist ein Steuerhülsenanschlag vorgesehen, der einen durch die Kraft der dritten Feder möglichen, in Abfallrichtung weisenden Verschiebeweg des Rings begrenzt. Der Steuerhülsenanschlag läßt somit eine Verlagerung des Rings durch die Kraft der dritten Feder nur bis in eine bestimmte Stellung zu.According to a preferred exemplary embodiment, a control sleeve stop is provided which limits a displacement path of the ring which is possible in the drop direction and is possible by the force of the third spring. The control sleeve stop thus allows a displacement of the ring by the force of the third spring only up to a certain position.

Die erste Feder ist insbesondere als Bügelfeder ausgebildet, die an jedem Schenkel eine Hintergriffstufe aufweist. Durch Verlagerung der Steuerhülse läßt sich die Bügelfeder für das Einnehmen Freigabestellung aufspreizen.The first spring is designed in particular as a bow spring, which has a rear grip step on each leg having. By shifting the control sleeve, the bow spring can be spread to the release position.

Vorzugsweise ist die zweite Feder eine Schraubendruckfeder, die den Stößel umwendelt und sich mit einem Ende an einen Stößelanschlag abstützt und mit ihrem anderen Ende gegen eine Steuerhülsenstufe tritt. Hierdurch wird die Steuerhülse in Richtung auf den Anker vorgespannt, so daß sie gegen den Ankeranschlag anliegt.The second spring is preferably a helical compression spring, which coils the tappet and is supported at one end against a tappet stop and, at the other end, strikes a control sleeve step. As a result, the control sleeve is biased towards the armature so that it rests against the armature stop.

Die dritte Feder kann als Wendeldruckfeder ausgebildet sein, die die Steuerhülse umgibt. Hierdurch ist ein einfacher und platzsparender Aufbau erzielt.The third spring can be designed as a helical compression spring which surrounds the control sleeve. This results in a simple and space-saving structure.

Für das Aufspreizen der Bügelfeder weist die Steuerhülse einen Steuerkragen auf.The control sleeve has a control collar for spreading the bow spring.

Für eine Justierung der Vorrichtung ist die Bügelfeder am Gehäuse der Andrehvorrichtung in Richtung der Längserstreckung des Stößels einstellbar befestigt.For an adjustment of the device, the bow spring is fastened to the housing of the starting device in the direction of the longitudinal extension of the plunger.

Zeichnungdrawing

Die Erfindung wird im folgenden anhand der Figuren näher erläutert. Es zeigen:

Figur 1
einen Längsschnitt durch eine Andrehvorrichtung,
Figur 2
eine Detailansicht des Stößels eines Ankers eines Einrückrelais' der Vorrichtung der Figur 1 und
Figur 3
ein Ausschnitt der Darstellung der Figur 1, jedoch in Freigabestellung einer mit dem Anker des Einrückrelais' zusammenwirkenden Verriegelungseinrichtung.
The invention is explained in more detail below with reference to the figures. Show it:
Figure 1
a longitudinal section through a starting device,
Figure 2
a detailed view of the plunger of an armature of an engagement relay 'of the device of Figures 1 and
Figure 3
a section of the illustration of Figure 1, but in the release position of a locking device cooperating with the armature of the engagement relay '.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die Figur 1 zeigt einen Längsschnitt durch eine Andrehvorrichtung 1. Diese weist ein Gehäuse 2 auf, in dem ein Gleichstrommotor 3 und ein Einrückrelais 4 untergebracht sind. Der Gleichstrommotor 3 weist einen Starterrotor 5 auf, der auf eine Abtriebswelle 6 wirkt, auf dessen Ende 7 ein Ritzel 8 drehfest angeordnet ist. Für den Anlaßbetrieb einer nicht dargestellten Brennkraftmaschine rückt das Ritzel 8 in die in der Figur 1 gestrichelt eingezeichnete Position 9 vor und spurt dabei in einen Zahnkranz 10 der Brennkraftmaschine ein. Die axiale Verlagerung des Ritzels in die Position 9 wird durch das Einrückrelais 4 veranlaßt. Hierauf wird im nachfolgenden noch näher eingegangen.FIG. 1 shows a longitudinal section through a starter 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 starter 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 to the position 9 shown in broken lines in FIG. The engagement of relay 4 causes the pinion to move axially to position 9. This will be discussed in more detail below.

Der Starterrotor 5 ist mit einem Kommutator 11 versehen, an dessen Segmenten 12 eine Rotorwicklung 13 angeschlossen ist. Der Kommutator 11 wirkt mit einer Kohlebürstenanordnung 14 zusammen. Ferner ist ein Stator 15 mit Statorwicklung 16 vorgesehen, der dem Starterrotor 5 mit geringem Luftspalt gegenüberliegt.The starter 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 is opposite the starter rotor 5 with a small air gap.

Der Starterrotor 5 weist eine Rotorwelle 17 auf, die an ihrem einen Ende 18 in einem Nadellager 19 gelagert und von einer Gehäusekappe 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 Abtriebswelle 6 gelagert. Die Mantelfläche 24 des mit Aufnahmebohrung 22 versehenen Endes 25 der Rotorwelle 17 ist als Sonnenrad 26 ausgebildet, das mit Planetenrädern 27 kämmt, die auf einem Planetenträger 28 angeordnet sind (in der Figur 1 ist lediglich ein Planetenrad 27 dargestellt). Die Planetenräder 27 sind unter Zwischenschaltung von Nadellager auf Lagerstiften 29 angeordnet.The starter rotor 5 has a rotor shaft 17 which is supported at one end 18 in a needle bearing 19 and covered by a housing cap 20. The other end of the rotor shaft 17 has a central receiving bore 22 extending from its end face 21, into which the 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 with the interposition of needle bearings on bearing pins 29.

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 Nadellager 37 in der Aufnahmebohrung des Axialsteges 39 gelagert. Der Freilaufaußenring 35 wird durch ein Rillenkugellager 38, das auf dem Axialsteg 39 angeordnet ist und sich andererseits im Gehäuse 2 abstützt, gehalten (Festlager). Im gegenüberliegenden Endbereich 32 der Abtriebswelle 6 ist -vom Gehäuse 2 gehalten- 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 mounted in the receiving bore of the axial web 39 via a needle bearing 37. 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 — to the outside. 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 Freilaufaußenring 35 über Schrauben 36 verbunden.The planet carrier 28 is axially connected to a freewheel outer ring 35 via screws 36.

Der Freilaufaußenring 35 gehört einer Freilaufeinrichtung 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 Verbindung. 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 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 befestigt, der einen Radialkragen 48 aufweist. Ferner liegt in einer Nut 49 des Halterings 47 ein Sprengring 50 ein, der eine Scheibe 51 abstützt. Zwischen Scheibe 51 und Radialkragen 48 wird somit ein Ringkanal 52 ausgebildet.A retaining ring 47, which has a radial collar 48, is fastened on the output shaft 6. Furthermore, a snap ring 50, which supports a disk 51, lies 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 Relaiswicklung 61 auf, die mit einem Anker 62 zusammenwirkt. Der Anker 62 ist axial verschieblich gelagert und wird von einer als Schraubendruckfeder ausgebildeten Rückstellfeder 113 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 zusammenwirken kann.The engagement relay 4 has a fixed relay winding 61 which interacts with an armature 62. The armature 62 is axially displaceably mounted and is not excited by a return spring 113 designed as a helical compression spring State of the engagement relay 4 pushed into the position shown in FIG. The axis 63 has at its one end region 65 a contact element 66 that can interact 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 ausgebildeten 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 gehalten. Das untere Ende 73 des Einrückhebels 70 ist mit einem Vorsprung 74 versehen, der in den Ringkanal 52 eingreift. Am anderen Ende 75 des Einrückhebels 70 ist ein Mitnahmekopf 76 ausgebildet. Durch Verlagerung des Stößels 68 wird der Einrückhebel 70 mitgenommen, wodurch eine Axialverlagerung der Abtriebswelle 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 verhindert, daß sich das Ritzel 8 unbeabsichtigt in Richtung auf den Zahnkranz 10 der Brennkraftmaschine bewegt, da dies zur Beschädigung der Teile führen könnte. Diese unbeabsichtigte Axialbewegung kann dadurch eintreten, daß bremsende Momente, die z.B. durch die Lager und Wellendichtringe auftreten, die Abtriebswelle 6 in Einspurposition bewegen, das heißt, die Rückstellfederkräfte sind kleiner als die am Steilgewinde auftretenden Axialkraftkomponenten. Im einzelnen soll nunmehr auf die Ausbildung der Verriegelungsvorrichtung 77 eingegangen werden.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 annular channel 52. At the other end 75 of the engagement lever 70, a driving head 76 is formed. By shifting the plunger 68, the engagement lever 70 is carried along, as a result of which the output shaft 6 is axially displaced. When the engagement relay 4 is not energized, care must be taken to ensure that the pinion 8 does not leave the position shown in solid lines in FIG. A locking device 77 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 can occur due to the fact 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. In detail The formation of the locking device 77 will now be discussed.

Die Verriegelungsvorrichtung 77 fixiert die in der Figur 1 dargestellte Stellung des Einrückhebels 70 im nicht erregten Zustand des Einrückrelais' 4, so daß die Abtriebswelle 6 eine feste Axialposition einnimmt. Erfindungsgemäß greift -wie bereits angedeutet- die Verriegelungseinrichtung 77 am Anker 62, insbesondere an dem Stößel 68, des Einrückrelais 4 zur Sicherung der Ruhestellung des Ritzels 8 an. Die Verriegelungseinrichtung 77 weist ein Verriegelungsglied 78 auf, das als eine erste Feder 79 ausgebildet ist. Die erste Feder 79 ist eine Bügelfeder 80 (vergleiche insbesondere auch Figur 2). Die Bügelfeder 80 weist zwei Schenkel 81 auf, die derart geformt sind, daß jeder mit einer Hintergriffstufe 82 versehen ist. Die Enden 83 der beiden Schenkel 81 sind divergierend nach außen gebogen, wodurch Auflaufschrägen 84 ausgebildet werden. Die den Auflaufschrägen 84 gegenüberliegenden Bereiche 85 der Schenkel 81 sind jeweils derart ausgebildet, daß -von der Hintergriffstufe 82 ausgehend- ein Abschnitt 86 zunächst etwa parallel zum Stößel 68 verläuft, an den sich dann ein Steuerabschnitt 87 anschließt, der divergierend nach außen verläuft und in einen Bogenabschnitt 88 übergeht, der -gegenüber dem Steuerabschnitt 87- entgegengesetzt gekrümmt verläuft, wobei eine Abbiegung mit einem Winkel größer als 90° vorliegt. Das anschließende Ende 89 jedes Schenkels 81 ist in einem Halter 90 befestigt.The locking device 77 fixes the position of the engagement lever 70 shown in FIG. 1 in the deenergized state of the engagement relay 4, so that the output shaft 6 assumes a fixed axial position. According to the invention, as already indicated, the locking device 77 acts on the armature 62, in particular on the plunger 68, of the engagement relay 4 in order to secure the idle position of the pinion 8. The locking device 77 has a locking member 78 which is designed as a first spring 79. The first spring 79 is a bow spring 80 (compare in particular also FIG. 2). The bow spring 80 has two legs 81 which are shaped such that each is provided with a rear grip step 82. The ends 83 of the two legs 81 are divergingly bent outwards, as a result of which bevel slopes 84 are formed. The areas 85 of the legs 81 opposite the run-up bevels 84 are each designed such that - starting from the rear grip step 82 - a section 86 initially runs approximately parallel to the plunger 68, to which a control section 87 then adjoins, which runs diverging outwards and in an arc section 88 merges, which is curved in the opposite direction to the control section 87, with a bend at an angle greater than 90 °. The subsequent end 89 of each leg 81 is fastened in a holder 90.

Der Halter 90 ist mit einer Gewindeschraube 91 verbunden, die koaxial zum Stößel 68 verläuft und in einer Bohrung 92 des Gehäuses 2 gelagert ist. Das aus dem Gehäuse 2 nach außen herausragende Ende 93 der Gewindeschraube 91 wird mittels einer Kontermutter 94 gesichert.The holder 90 is connected to a threaded screw 91 which extends coaxially to the plunger 68 and is mounted in a bore 92 in the housing 2. The end 93 of the threaded screw 91 protruding outward from the housing 2 is secured by means of a lock nut 94.

Der mit dem Anker 62 des Einrückrelais 4 verbundene Stößel 68 weist an seinem freien Ende 95 eine Ringnut 96 auf, in die ein Sprengring 97 eingesetzt ist. Am Sprengring 97 stützt sich eine Scheibe 98 ab, die auf dem Stößel 68 lagert und von einer zweiten Feder 99 beaufschlagt wird. Mithin bildet die Scheibe 98 einen Stößelanschlag 100.The plunger 68 connected to the armature 62 of the engagement relay 4 has at its free end 95 an annular groove 96 into which a snap ring 97 is inserted. A disk 98 is supported on the snap ring 97, which is supported on the tappet 68 and is acted upon by a second spring 99. The disk 98 therefore forms a tappet stop 100.

Die zweite Feder 99 ist als Schraubendruckfeder 101 ausgebildet, die den Stößel 68 umwendelt und sich mit einem Ende 102 an dem Stößelanschlag 100 und mit ihrem anderen Ende 103 an einer Steuerhülsenstufe 104 einer Steuerhülse 108 abstützt. Letztere ist auf dem Stößel 68 gelagert. Die Steuerhülsenstufe 104 wird dadurch gebildet, daß die Steuerhülse 108 axial von einer Stufenbohrung 105 durchsetzt ist. Durch die Kraft der Schraubendruckfeder 101 wird die dem Anker 62 zugewandte Stirnseite 106 gegen einen Ankeranschlag 107 gedrängt. In dem den größeren Durchmesser aufweisenden Abschnitt der Stufenbohrung 105 ist die Schraubendruckfeder 101 gelagert.The second spring 99 is designed as a helical compression spring 101, which surrounds the tappet 68 and is supported with one end 102 on the tappet stop 100 and with its other end 103 on a control sleeve step 104 of a control sleeve 108. The latter is mounted on the ram 68. The control sleeve step 104 is formed in that the control sleeve 108 is axially penetrated by a stepped bore 105. The force of the helical compression spring 101 pushes the end face 106 facing the armature 62 against an armature stop 107. The helical compression spring 101 is mounted in the section of the stepped bore 105 having the larger diameter.

An ihrem dem Anker 62 abgewandten Ende weist die Steuerhülse 108 einen axial ausladenden Steuerkragen 109 auf, der -wie nachstehend noch näher beschrieben- mit den Steuerabschnitten 87 der Bügelfeder 80 zusammenwirkt.At its end facing away from the armature 62, the control sleeve 108 has an axially protruding control collar 109 which, as described in more detail below, interacts with the control sections 87 of the bow spring 80.

Die Steuerhülse 108 weist unterschiedlich große Außendurchmesser auf, wodurch ein Steuerhülsenanschlag 110 gebildet wird. Der Steuerhülsenanschlag 110 ist dem Anker 62 zugewandt. Gegen den Steuerhülsenanschlag 110 wird eine Scheibe 111 mittels einer dritten Feder 112 gepreßt, die als Wendeldruckfeder 113 ausgebildet ist. Das eine Ende 114 der Wendeldruckfeder 113 stützt sich am Gehäuse 2 und das andere Ende 115 an der Scheibe 111 ab. Gegen die Scheibe 111 liegt ein Anschlag 116 an, der als Ring 117 ausgebildet ist und sich auf dem durchmessergrößeren Abschnitt der Steuerhülse 108 befindet. Auf der Mantelfläche 118 des Rings 117 stützt sich -in den in den Figuren 1 und 2 dargestellten Stellungen- die Bügelfeder 80 ab.The control sleeve 108 has different outer diameters, whereby a control sleeve stop 110 is formed. The control sleeve stop 110 faces the armature 62. A disk 111 is pressed against the control sleeve stop 110 by means of a third spring 112, which is designed as a helical compression spring 113. One end 114 of the helical compression spring 113 is supported on the housing 2 and the other end 115 on the disk 111. A stop 116 bears against the disk 111, which is designed as a ring 117 and is located on the larger-diameter section of the control sleeve 108. The bow spring 80 is supported on the lateral surface 118 of the ring 117 in the positions shown in FIGS. 1 and 2.

Aus der Figur 1 ist ersichtlich, daß der Mitnahmekopf 76 den Abstand zwischen der einen Seite 119 des Rings 117 und einer Stirnfläche 120 des Steuerkragens 108 nicht voll ausfüllt; vielmehr verbleibt ein Leerweg b.It can be seen from FIG. 1 that the driving head 76 does not completely fill the distance between the one side 119 of the ring 117 and an end face 120 of the control collar 108; 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 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 Einrückrelais 4 erregt. Dies führt dazu, daß sich der Anker 62 nach rechts (Figur 1) bewegt, wodurch der Steuerkragen 109 derart gegen die Steuerabschnitte 87 der Bügelfeder 80 anläuft, daß diese radial aufgespreizt wird. Hierdurch geben die Hintergriffstufen 82 der Schenkel 81 den Ring 117 frei. Solange der Ring 117 von den Hintergriffstufen 82 hintergriffen wird, ist eine Relativbewegung zwischen der Steuerhülse 108 und dem Ring 117 unter Aufzehrung des Leerweges b deshalb möglich, weil letzterer axial verschieblich auf dem größeren Durchmesser der Steuerhülse 108 gelagert ist. Die Mitnahme der Steuerhülse 108 durch Axialverlagerung des Stößels 68 wird über die Schraubendruckfeder 101 bewirkt. Nimmt die Bügelfeder 80 ihre aufgespreizte Stellung (Figur 3) ein, so ist der Leerweg b aufgebraucht, das heißt, die linke Seite des Mitnahmekopfes 76 wird von der Stirnfläche 120 mitgenommen. Der Einrückhebel 70 führt eine Schwenkbewegung im Uhrzeigersinn um den Querbolzen 71 herum aus. Dabei verlagert der Vorsprung 74 die Abtriebswelle 6 in Richtung auf den Zahnkranz 10, wodurch das Ritzel 8 in die Zahnung des Zahnkranzes 10 einspurt. Die auftretenden Einspurkräfte sorgen dafür, daß nunmehr das Ritzel 8 vollständig in den Zahnkranz 10 einfährt, wobei aufgrund des Steilgewindes 43 die Abtriebswelle 6 axial herausfährt, so daß -im Ergebnis- die in der Figur 1 mit gestrichelten Linien eingezeichnete Position 9 vom Ritzel 8 eingenommen wird. Sollte bei dem eben beschriebenen Einspurvorgang zunächst eine Zahn-Auf-Zahn-Stellung von Ritzel 8 und Zahnkranz 10 erfolgen, so wird die Anzugsbewegung des Einrückrelais 4 nicht unterbrochen, da sich der Stößel 68 relativ zur Steuerhülse 108 aufgrund der zweiten Feder 99 bewegen kann.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), as a result of which the control collar 109 runs against the control sections 87 of the bow spring 80 in such a way that the latter is expanded radially. This gives the rear grip levels 82 the leg 81 the ring 117 free. As long as the ring 117 is engaged by the rear grip steps 82, 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 larger diameter of the control sleeve 108. The dragging of the control sleeve 108 by axial displacement of the plunger 68 is effected via the helical compression spring 101. If the bow spring 80 assumes its spread position (FIG. 3), the free travel b is used up, that is to say the left side of the driving head 76 is carried along by the end face 120. The engagement lever 70 pivots clockwise around the cross 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 engages in the toothing of the ring gear 10. The occurring engagement forces ensure that the pinion 8 now completely retracts into the ring gear 10, the output shaft 6 extending axially due to the steep thread 43, so that — as a result — the position 9 shown in FIG. 1 with dashed lines is taken up by the pinion 8 becomes. If the toothing-on-tooth position of the pinion 8 and ring gear 10 is first carried out in the meshing process just described, the tightening movement of the engagement relay 4 is not interrupted since the plunger 68 can move relative to the control sleeve 108 due to the second spring 99.

Ferner ist auch eine axiale Relativbewegung zwischen Ritzel 8 und Abtriebswelle 6 aufgrund der Schraubendruckfeder 54 möglich. Da durch die Anzugsbewegung des Einrückrelais' 4 das Kontaktelement 66 in Verbindung zu den elektrischen Anschlüssen 67 tritt, wird der Gleichstrommotor 3 erregt, das heißt, der Starterrotor 5 beginnt zu drehen, wodurch das Ritzel 8 über das aus Sonnenrad 26, Planetenrädern 27 und Hohlrad 30 gebildete Untersetzungsgetriebe mitgenommen wird. Hierdurch wird die Zahn-Auf-Zahn-Stellung zwischen Ritzel 8 und Zahnkranz 10 aufgehoben, so daß ein Einspuren erfolgen kann.Furthermore, an axial relative movement between pinion 8 and output shaft 6 is also possible due to the helical compression spring 54. Since the contact element by the tightening movement of the engagement relay 4 66 connects to the electrical connections 67, the DC motor 3 is excited, that is, the starter rotor 5 begins to rotate, whereby the pinion 8 is carried along via the reduction gear formed by the sun gear 26, planet gears 27 and ring gear 30. As a result, the tooth-on-tooth position between pinion 8 and ring gear 10 is canceled so that engagement can take place.

Wird der Startvorgang beendet, so fällt das Einrückrelais 4 ab. Die Abfallbewegung wird von den Rückstellfedern 64 und 112 unterstützt. Dabei tritt der Ring 117 mit seiner Seite 119 gegen den Mitnahmekopf 76 des Einrückhebels 70, so daß der Einrückhebel 70 entgegen dem Uhrzeigersinn verschwenkt, wodurch das Ritzel 8 in die in der Figur 1 mit durchgezogener Linie dargestellte Position zurückgeholt wird. Da im Endstadium des Startvorgangs die nunmehr im Betrieb befindliche Brennkraftmaschine die Drehung des Ritzels 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. In this case, the ring 117 comes with its side 119 against the driving head 76 of the engagement lever 70, so that the engagement lever 70 pivots counterclockwise, whereby the pinion 8 is brought back into the position shown in solid line in FIG. Since the internal combustion engine, which is now in operation, "overtakes" the rotation of the pinion 8 in the final stage of the starting process, the disengagement process is supported by the steep thread 43.

Ist wieder die Ruheposition eingenommen (Figur 1), so befindet sich auch die Bügelfeder 80 wieder in Ausgangstellung, das heißt, ihre Hintergriffstufen 82 hintergreifen den Ring 117, so daß der Einrückhebel 70 in der in der Figur 1 dargestellten Position gesichert wird. Damit ist eine unbeabsichtigte Axialverlagerung der Abtriebswelle 6 verhindert.When the rest position is reached again (FIG. 1), the bow spring 80 is also in the starting position again, that is to say its rear grip steps 82 engage behind the ring 117, so that the engagement lever 70 is secured in the position shown in FIG. This prevents unintentional axial displacement of the output shaft 6.

Claims (12)

  1. Starting device, in particular self-engaging starting device, with engagement relay (4) whose armature displaces axially, via an engagement lever (70), a pinion (8), which interacts with a free-wheeling device (40) and with a starter rotor (5), for driving a gear ring (10) of an internal combustion engine, and with a locking device (77) which prevents the pinion from being pushed forward when the engagement relay is not excited, the locking device (77) engaging with a fixed locking element (78), on a part (117) which is actuated by the armature (62) of the engagement relay (4), in order to maintain the pinion (8) in its position of rest, characterized in that the locking element (78) is a first spring (79) which is provided with at least one rear-engagement step (82) and which can be deflected in the release position by means of a control sleeve (108) arranged on a tappet (68) of the armature (62).
  2. Starting device according to Claim 1, characterized in that the locking element (78) is a spring clip (80) which is bent in U-shape and engages, with its legs (81), behind a stop (116) of the armature (62) in the dropout position of the engagement relay (4).
  3. Starting device according to Claim 2, characterized in that the armature experiences (62) with the tappet (68) and the control sleeve (108) an idle motion (b) in order to bring about the release position before driving of the engagement lever (70) takes place.
  4. Starting device according to Claim 2, characterized in that the stop (116) is formed by a ring (117) which is mounted on the control 'sleeve (108).
  5. Starting device according to one of Claims 1 to 4, characterized in that the control sleeve (108) rests, as the result of a force of a second spring (99), against an armature stop (107) and can be displaced axially in relation to the armature (62) in its dropout direction.
  6. Starting device according to either of Claims 4 and 5, characterized in that the one end side (119) of the ring (117) interacts with the engagement lever (70) and the other end side of the ring (117) interacts with a third spring (112), in such a way that the one end (114) of the third spring (112) is supported on the housing (2) of the starting device (1) and the other end (115) of the third spring (112) is supported on the ring (117).
  7. Starting device according to Claim 6, characterized by a control sleeve stop (110) which limits a displacement path of the ring (117) which is possible as a result of the force of the third spring (112) and points in the dropout direction.
  8. Starting device according to Claim 2, characterized in that the spring clip (80) has a rear-engagement step (82) on each leg (81).
  9. Starting device according to Claim 2, characterized in that, by means of displacement of the control sleeve (108), the spring clip (80) can be spread apart by a collar (109) of the control sleeve (108) in order to achieve the release position.
  10. Starting device according to one of Claims 1 to 9, characterized in that the spring clip (8) is attached to the housing (2) of the starting device (1) so as to be adjustable in the direction of the longitudinal extent of the tappet (68).
  11. Starting device according to one of Claims 5 to 10, characterized in that the second spring (99) is a helical compression spring (101) which is coiled around the tappet (68) and is supported with one end (102) on a tappet stop (100) and presses with its other end (103) against a control sleeve step (104).
  12. Starting device according to one of Claims 6 to 11, characterized in that the third spring (112) is a cylindrical helical spring (113) which surrounds the control sleeve (108).
EP91904528A 1990-03-03 1991-02-22 Starting device with drive shaft lock Expired - Lifetime EP0518895B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4006796A DE4006796A1 (en) 1990-03-03 1990-03-03 TURNING DEVICE WITH OUTPUT SHAFT LOCKING
DE4006796 1990-03-03
PCT/DE1991/000142 WO1991014096A1 (en) 1990-03-03 1991-02-22 Starting device with drive shaft lock

Publications (2)

Publication Number Publication Date
EP0518895A1 EP0518895A1 (en) 1992-12-23
EP0518895B1 true EP0518895B1 (en) 1994-07-27

Family

ID=6401407

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91904528A Expired - Lifetime EP0518895B1 (en) 1990-03-03 1991-02-22 Starting device with drive shaft lock

Country Status (8)

Country Link
US (1) US5245881A (en)
EP (1) EP0518895B1 (en)
JP (1) JPH05504811A (en)
DE (2) DE4006796A1 (en)
ES (1) ES2057871T3 (en)
HU (1) HU208726B (en)
RU (1) RU2048654C1 (en)
WO (1) WO1991014096A1 (en)

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FR2760491A1 (en) * 1997-03-07 1998-09-11 Bosch Gmbh Robert FREE CLEARANCE STARTER

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FR2722037B1 (en) * 1994-07-04 1996-08-02 Valeo Equip Electr Moteur ROTATING ELECTRIC MACHINE ARMATURE AND MOTOR VEHICLE STARTER COMPRISING SUCH AN ARMATURE
FR2745854B1 (en) * 1996-03-08 1998-04-10 Valeo Equip Electr Moteur MOTOR VEHICLE STARTER COMPRISING A GEAR WITHOUT FREE WHEEL
DE29704209U1 (en) 1997-03-07 1998-07-02 Robert Bosch Gmbh, 70469 Stuttgart Free-kicking starter
DE19963626C2 (en) * 1999-12-29 2001-10-31 Bosch Gmbh Robert Starting device for internal combustion engines
DE10046987A1 (en) 2000-09-22 2002-04-18 Bosch Gmbh Robert Starter for internal combustion engine has holding winding in series with control switch element controlled into conducting state by timing element connected to starting signal connection
JP2007132296A (en) * 2005-11-11 2007-05-31 Denso Corp Starter with intermediate gear
JP4661721B2 (en) * 2006-07-26 2011-03-30 株式会社デンソー Starter
JP4618516B2 (en) * 2006-11-16 2011-01-26 株式会社デンソー Starter
EP2239453B8 (en) * 2008-08-07 2017-08-02 Denso Corporation A starting device for engines
DE102013225174A1 (en) 2013-12-06 2015-06-25 Robert Bosch Gmbh Electric lifting magnet, electric machine and method for producing a lifting magnet
CN105895452B (en) * 2016-05-27 2017-11-10 浙江英洛华新能源科技有限公司 Closed type HVDC relay
JP6668997B2 (en) * 2016-07-29 2020-03-18 オムロン株式会社 Electromagnetic relay
JP6828294B2 (en) * 2016-07-29 2021-02-10 オムロン株式会社 Electromagnetic relay
JP2019083174A (en) * 2017-10-31 2019-05-30 オムロン株式会社 Electromagnetic relay
JP6801629B2 (en) * 2017-10-31 2020-12-16 オムロン株式会社 Electromagnetic relay
JP6919504B2 (en) * 2017-10-31 2021-08-18 オムロン株式会社 Electromagnetic relay

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Also Published As

Publication number Publication date
DE59102367D1 (en) 1994-09-01
RU2048654C1 (en) 1995-11-20
HU9202825D0 (en) 1992-12-28
WO1991014096A1 (en) 1991-09-19
HU208726B (en) 1993-12-28
JPH05504811A (en) 1993-07-22
HUT61613A (en) 1993-01-28
DE4006796A1 (en) 1991-09-12
US5245881A (en) 1993-09-21
ES2057871T3 (en) 1994-10-16
EP0518895A1 (en) 1992-12-23

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