EP0518878B1 - Andrehvorrichtung mit bremseinrichtung - Google Patents

Andrehvorrichtung mit bremseinrichtung Download PDF

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Publication number
EP0518878B1
EP0518878B1 EP91903883A EP91903883A EP0518878B1 EP 0518878 B1 EP0518878 B1 EP 0518878B1 EP 91903883 A EP91903883 A EP 91903883A EP 91903883 A EP91903883 A EP 91903883A EP 0518878 B1 EP0518878 B1 EP 0518878B1
Authority
EP
European Patent Office
Prior art keywords
rotor
output shaft
pinion
arrangement according
cranking
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
EP91903883A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0518878A1 (de
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/de
Application granted granted Critical
Publication of EP0518878B1 publication Critical patent/EP0518878B1/de
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
    • F02N15/003—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 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, according to claim 1, part 1 (see FR- A-2536 466).
  • 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 moving 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 is an element to which a relatively low torque is assigned. This means that even relatively small braking forces have 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 the same on the one hand Tolerances and still leads to the transfer of axial forces to the rotor.
  • the contact member is arranged coaxially with the rotor. This avoids unbalance 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. 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 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 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 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 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 is supported on the other hand 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 pushed 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 on 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 annular 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 unintentionally moving in the direction of the ring gear 10 of the internal combustion engine, since this would damage the Parts could result.
  • 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 single-track position, that is to say the return spring forces are smaller than the axial force components occurring on the high-helix thread.
  • 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 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 designed as a thrust bolt 133.
  • This has a circular cross section, which is dimensioned to the diameter of the axial bore 131 that the thrust pin 133 is axially displaceably guided in the axial bore 131.
  • the side 134 of the thrust 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 thrust bolt 133 and the other end 137 of the compression spring 135 lies at the bottom 138 of the designed as a blind bore axial bore 131.
  • the lateral surface 139 of the thrust bolt 133 has a radial collar 140 in the support region 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 such 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, it limits the axial movement of the thrust bolt 133 caused by the compression spring 135 when the thrust bolt 133 is not acted upon.
  • 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. 1, its end face 146 acts on the run-up elevation 145 of the run-up bolt 133 in such a way that the latter is lifted from the snap ring 143 by a displacement path c.
  • 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. Between the end face 148 of the rotor 5 or commutator 11 and a housing region 149 of the starting device 1, a brake disk 151 provided with a braking surface 150 is arranged.
  • the housing region 149 is formed by a contact surface 152 surrounding the rotor bearing 147.
  • the starting device 1 operates as follows: For a starting process of the internal combustion engine (not shown), the engagement relay 4 is energized via a start switch. This causes the armature 62 to move to the right ( Figure 1), causing the control sleeve 108 runs against the bow spring 80 in such a way that it 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 mounted on the control sleeve 108 so as to be axially displaceable.
  • 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 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 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 position 9 of the pinion shown in broken lines in FIG. 1 8 is taken.
  • the engagement relay 4 drops out.
  • the return movement is supported by the return springs 64 and 112.
  • the ring 117 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 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.

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)
EP91903883A 1990-03-03 1991-02-22 Andrehvorrichtung mit bremseinrichtung Expired - Lifetime EP0518878B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4006797A DE4006797A1 (de) 1990-03-03 1990-03-03 Andrehvorrichtung mit bremseinrichtung
DE4006797 1990-03-03
PCT/DE1991/000140 WO1991014094A1 (de) 1990-03-03 1991-02-22 Andrehvorrichtung mit bremseinrichtung

Publications (2)

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

Family

ID=6401408

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91903883A Expired - Lifetime EP0518878B1 (de) 1990-03-03 1991-02-22 Andrehvorrichtung mit bremseinrichtung

Country Status (11)

Country Link
US (1) US5321987A (es)
EP (1) EP0518878B1 (es)
JP (1) JPH05504808A (es)
AU (1) AU638802B2 (es)
BR (1) BR9106109A (es)
CZ (1) CZ280180B6 (es)
DE (2) DE4006797A1 (es)
ES (1) ES2063495T3 (es)
HU (1) HU208725B (es)
RU (1) RU2048653C1 (es)
WO (1) WO1991014094A1 (es)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5953955A (en) * 1994-11-24 1999-09-21 Nippondenso Co., Ltd. Starter with planetary gear speed reduction mechanism
DE19911161C2 (de) * 1999-03-11 2003-10-30 Bosch Gmbh Robert Elektromechanisches Vor- und Rückspurprinzip für Koaxialstarter
RU2451206C2 (ru) * 2009-03-10 2012-05-20 Федеральное государственное образовательное учреждение высшего профессионального образования "Военный авиационный инженерный университет" (г. Воронеж) Министерства обороны Российской Федерации Механизм включения стартера
DE102009027859B4 (de) * 2009-07-21 2019-12-24 Seg Automotive Germany Gmbh Elektrische Maschine mit kommutatorseitigem Lager
FR2990729B1 (fr) * 2012-05-16 2015-11-13 Valeo Equip Electr Moteur Demarreur a lanceur muni d'une roue libre immobile en translation
CN103388527B (zh) * 2013-07-30 2016-05-04 长城汽车股份有限公司 一种汽车发动机熄火后曲轴位置限定系统
CN106014748A (zh) * 2016-07-14 2016-10-12 上海法雷奥汽车电器系统有限公司 一种减速起动机

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1107059A (fr) * 1950-12-11 1955-12-28 Magneti Marelli Spa Perfectionnements aux démarreurs électriques pour moteurs
US2759363A (en) * 1952-04-21 1956-08-21 Leo F Phaneuf Switch control apparatus
US2777328A (en) * 1954-12-30 1957-01-15 Caterpillar Tractor Co Control for starter pinion engaging mechanism
DE2448069A1 (de) * 1974-10-09 1976-04-22 Bosch Gmbh Robert Andrehvorrichtung fuer brennkraftmaschinen
DE2460114A1 (de) * 1974-12-19 1976-06-24 Bosch Gmbh Robert Andrehvorrichtung fuer brennkraftmaschinen
GB2037373B (en) * 1978-11-10 1983-02-09 Hitachi Ltd Engine starter
US4412457A (en) * 1981-04-29 1983-11-01 General Motors Corporation In-line engine cranking motor drive having reduction gear set
FR2536466B1 (fr) * 1982-11-24 1986-11-14 Paris & Du Rhone Dispositif de freinage pour demarreur de moteur a combustion interne
JPS61106974A (ja) * 1984-10-30 1986-05-24 Nippon Denso Co Ltd 遊星歯車減速機構付スタ−タ
JPS63209448A (ja) * 1987-02-23 1988-08-31 Mitsubishi Electric Corp エンジン用スタ−タ装置
JPH01247762A (ja) * 1988-03-28 1989-10-03 Hitachi Ltd 遊星歯車減速機付スタータ

Also Published As

Publication number Publication date
JPH05504808A (ja) 1993-07-22
BR9106109A (pt) 1993-02-24
HU208725B (en) 1993-12-28
EP0518878A1 (de) 1992-12-23
RU2048653C1 (ru) 1995-11-20
DE4006797A1 (de) 1991-09-12
HU9202826D0 (en) 1992-12-28
US5321987A (en) 1994-06-21
DE59103176D1 (de) 1994-11-10
AU638802B2 (en) 1993-07-08
AU7240091A (en) 1991-10-10
WO1991014094A1 (de) 1991-09-19
CZ280180B6 (cs) 1995-11-15
ES2063495T3 (es) 1995-01-01
HUT61612A (en) 1993-01-28

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