EP0742368A1 - Starter with pinion return preventing mechanism - Google Patents
Starter with pinion return preventing mechanism Download PDFInfo
- Publication number
- EP0742368A1 EP0742368A1 EP96107370A EP96107370A EP0742368A1 EP 0742368 A1 EP0742368 A1 EP 0742368A1 EP 96107370 A EP96107370 A EP 96107370A EP 96107370 A EP96107370 A EP 96107370A EP 0742368 A1 EP0742368 A1 EP 0742368A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pinion
- return
- ring gear
- starter
- regulating
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
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- 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
- F02N15/062—Starter drives
- F02N15/065—Starter drives with blocking means
Definitions
- the present invention relates to a starter for starting an engine by engaging a pinion with a ring gear of an engine and driving the pinion, and more particularly to a starter having a pinion return preventing mechanism.
- the weight of the pinion shaft is, however, about five times as great as that of the pinion. Therefore, there is a demand for the improved starter capable of shifting only the pinion to reduce energy required to shift it.
- the present invention has been made in view of the abovedescribed drawbacks and has a first object of providing an improved starter.
- the present invention has a second object of providing a starter capable of reducing to a less amount the degree of wear and rotational loss between a pinion and a member for keeping the state in which the pinion is in mesh with a ring gear.
- the present invention has a third object of providing a starter capable of reducing energy required to shift a pinion by shifting a pinion in the axial direction of an output shaft for driving the pinion.
- a return regulating member is provided at one side of a pinion in the axial direction thereof through a bearing, for regulating the return of the pinion in the axial direction thereof after engagement with a ring gear.
- the pinion does not disengage from the ring gear and the rotational torque of the motor is transmitted to the engine through the ring gear.
- an absorbing member such as a thrust bearing is provided between the pinion and the return regulating member to absorb the difference in the rotational speeds of the pinion and the return regulating member.
- a rotation restricting member is provided for regulating the rotation of the pinion to move the pinion axially for engagement with the ring gear.
- the rotation restricting member is manufactured integrally with the return regulating member to act as the return regulating member as well.
- the pinion includes a pinion inner member having a helical inner spline and a pinion outer member having a pinion gear, and those members are produced separately.
- the helical inner spline (inner teeth) and the pinion gear (outer teeth) can be manufactured by the most appropriate method, respectively.
- Figs. 1 through 15A-15C show a first embodiment, with Fig. 1 being an entire sectional view of a starter.
- the starter can be generally divided into a housing 400 containing a pinion 200 which meshes with a ring gear 100 mounted on an engine and a planetary gear speed reduction mechanism 300, a motor 500, and an end frame 700 containing a magnet switch 600. Inside the starter, the housing 400 and the motor 500 are separated by a motor spacer wall 800, and the motor 500 and the end frame 700 are separated by a brush holding member 900.
- a pinion gear 210 which meshes with the ring gear 100 of the engine is formed on the outer periphery of a pinion 200.
- a helical inner spline 211 which mates with a helical outer spline 221 formed on the outer periphery of an output shaft 220 is formed.
- the pinion 200 is spline-engaged on the output shaft 220 to be axially movable on the output shaft 220.
- the pinion 200 is so arranged to advance toward the ring gear 100 due to the differnce in rotational speeds when the output shaft 220 rotates at higher speed than the pinion 200.
- a tapered portion 222 is formed on the rear end of the output shaft 220 so that the helical inner spline 211 of the pinion 200 abuts the tapered portion 222 to stop a rearward movement of the pinion 200 further from the tapered portion 222.
- a pinion stopping ring 250 is mounted on the front side of the output shaft 220 to stop a forward movement of the pinion 200 further from the pinion stopping ring 250.
- a flange 213 of greater diameter than the external diameter dimension of the pinion gear 210 is formed in circular disk form.
- a number of convexes/concaves 214 greater than the number of outer teeth of the pinion gear 210 are formed around the entire outer circumference of this flange 213. These convexes/concaves 214 are for a return/rotation regulating claw 231 of a rotation regulating member 230 which will be discussed later to mate with.
- a thrust bearing 215 (absorbing means) is mounted on the rear end of the flange 213 to absorb the difference in rotational speeds of the pinion 200 and the return/rotation regulating claw 231.
- a bearing which bears axially applied load is called as a thrust bearing.
- the thrust bearing 215 in this embodiment uses a rolling bearing and is comprised of an orbital ring 216 which is to be abutted by the front end of the return/rotation regulating claw 231 and a plurality of balls 217 rotatable between the orbital ring 216 and the rear face of the flange 213.
- the balls 217 may be made of steel but preferably made of ceramics to improve durability.
- the thrust bearing 215 is mounted in a recess 218 formed on the rear face of the flange 213, and then an annular portion 219 formed on the rear end of the pinion 200 is bent outwardly so that it is kept rotatably on the rear face of the flange 213 and unable to come off in the axial direction.
- the pinion 200 is urged toward the rear of the output shaft 220 at all times by a return spring 240 made of a compression coil spring.
- the return spring 240 does not urge the pinion 200 directly but in this embodiment urges the pinion 200 by way of a ring body 421 of a shutter 420 which opens and closes an opening portion 410 of the housing 400 discussed later.
- the rotation regulating member 230 constituting pinion moving means is a sheet spring member wound through approximately 3/2 turns of which approximately 3/4 turn is a rotation regulating portion 232 of long axial sheet length and high spring constant and the remaining approximately 3/4 turn is a return spring portion 233 constituting urging means of short axial sheet length and low spring constant.
- the return/rotation regulating claw 231 which constitutes a regulating portion extending in the axial direction and which mates with the multiple convexes/concaves 214 formed in the flange 213 of the pinion 200 is formed at one end of a regulating portion 232.
- This return/rotation regulating claw 231 performs two functions as rotation regulating means and return regulating means; the rotation regulating meas stops rotation of the pinion 200 along the predetermined axial length at the time of start of rotation of the motor 500 to cause rotational difference between the output shaft 220 and the pinion 200 and move the pinion 200 axially, and the return regulating means drops into the axial rear end side to stop a return of the pinion 200 in a state of engagement of the pinion 200 with the ring gear 100 after the axial advance of the pinion 200 by the predetermined length.
- This return/rotation regulating claw 231, as well as mating with the convexes/concaves 214 of the pinion 200, in order to increase the rigidity of the return/rotation regulating claw 231, is formed axially long and is bent radially inward into a cross-sectional L-shape. (It is bar-like.)
- the regulating portion 232 which supports the return/rotation regulating claw 231 elastically deformably is provided with a straight portion 235 which extends vertically.
- This straight portion 235 is vertically slidably supported by two supporting arms 361 mounted projecting from the front face of a center bracket 360. That is, the straight portion 235 moving vertically causes the regulating portion 232 to move vertically also.
- a sphere 601 of the front end of a cord-shaped member 680 (for example, a wire), which will be further discussed later, for transmitting the movement of the magnet switch 600, which will be further discussed later, is in engagement with the position 180° opposite the return/rotation regulating claw 231 of the regulating portion 232.
- the end portion side of the return spring portion 233 has a large curvature of winding and one end portion 236 of the return spring portion 233 abuts the upper face of a regulating shelf 362 mounted projecting from a front face of a lower portion of the center bracket 360.
- the cord-shaped member 680 is transmitting means for transmitting the movement of the magnet switch 600 to the regulating portion 232, and the movement of the magnet switch 600 pulls the regulating portion 232 downward and causes the return/rotation regulating claw 231 to engage with the convexes/concaves 214 on the flange 213 of the pinion 200.
- the return spring portion 233 bends.
- the pinion stopping ring 250 is fixed in a circular groove of rectangular cross-section formed around the output shaft 220.
- This pinion stopping ring 250 is a piece of steel of rectangular cross-section processed into a circular shape; a substantially S-shaped corrugation 251 (an example of engaging means) is formed at each end, and the convex portion of one is in engagement with the concave portion of the other and the convex portion of the other is in engagement with the concave portion of the first.
- the planetary gear speed reduction mechanism 300 is speed reducing means for reducing the rotational speed of the motor 500, which will be further discussed later, and increasing the output torque of the motor 500.
- the planetary gear speed reduction mechanism 300 is made up of a sun gear 310 formed on the front-side outer periphery of the armature shaft 510 (discussed later) of the motor 500, a plurality of planetary gears 320 which mesh with this sun gear 310 and rotate around the circumference of the sun gear 310, a planet carrier 330 which rotatably supports these planetary gears 320 around the sun gear 310 and is formed integrally with the output shaft 220, and an internal gear 340 which is of a cylindrical shape meshing with the planetary gears 320 at the outer periphery of the planetary gears 320 and is made of resin.
- the overrunning clutch 350 supports the internal gear 340 rotatably in one direction only (only the direction in which it rotates under the rotation of the engine).
- the overrunning clutch 350 has a clutch outer 351 constituting a first cylindrical portion integrally formed in the front side of the internal gear 340, a circular clutch inner 352 constituting a second cylindrical portion formed in the rear face of the center bracket 360 constituting a fixed side covering the front of the planetary gear speed reduction mechanism 300 and disposed facing the clutch outer 351, and rollers 353 accommodated in a roller housing portion 351a formed inclined to the inner face of the clutch outer 351.
- the center bracket 360 is shown in Fig. 4 through Fig. 6 and is disposed inside the rear end of the housing 400.
- the housing 400 and the center bracket 360 are linked by a ring spring 390 having one end engaged with the housing 400 and the other end engaged with the center bracket 360 and are arranged in such a way that the rotational reaction received by a clutch inner 352 constituting the overrunning clutch 350 is absorbed by the ring spring 390 and the reaction is not directly transmitted to the housing 400.
- two supporting arms 361 which hold the rotation regulating member 230 and the regulating shelf 362 on which the lower end of the rotation regulating member 230 is loaded are mounted on the front face of the center bracket 360.
- a plurality of cutout portions 363 which mate with convex portions (not shown in the figure) on the inner side of the housing 400 are formed around the center bracket 360.
- the upper side cutout portions 363 are used also as air passages for guiding air from inside the housing 400 into a yoke 501 (this is discussed in detail later in connection with the cooling air passage).
- a concave portion 364 through which the cord-shaped member 680 (discussed later) passes in the axial direction is formed at the lower end of the center bracket 360.
- the planet carrier 330 is provided at its rear end with a flange-like projecting portion 331 which extends radially in order to support the planetary gears 320.
- Pins 332 extending rearward are fixed to this flange-like projecting portion 331, and these pins 332 rotatably support the planetary gears 320 by way of metal bearings.
- the planet carrier 330 has its front end rotatably supported by a housing bearing 440 fixed inside the front end of the housing 400 and a center bracket bearing 370 fixed inside an inner cylindrical portion 365 of the center bracket 360.
- the planet carrier 330 has an annular groove 334 at a front position of an inner cylindrical portion and a stopper ring 335 is fitted into the annular groove 334. Between the stopper ring 335 and the front end of the inner cylindrical portion 365, a washer 336 is disposed rotatably against the planet carrier 330. The stopper ring 335, abutting the front end of the inner cylindrical portion 365 through the washer 336, stops rearward movement of the planet carrier 330.
- the rear end of the center bracket bearing 370 supporting the rear side of the planet carrier 330 has a flange portion 371 which is sandwiched between the rear end of the inner cylindrical portion 365 and a flange-shaped protruding portion 331.
- a concave portion 337 extending axially is formed so that the front end of the armature shaft 510 is rotatably supported through a planet carrier bearing 380 disposed in the concave portion 337.
- the housing 400 supports the output shaft 220 with the housing bearing 440 fixed in the front end of the housing 400 and also is provided with a water barrier wall 460 which in order to minimize the incursion of rainwater and the like through the opening portion 410 minimizes the gap at the lower part of the opening portion 410 between the outer diameter of the pinion 200 and the housing 400. Also, two slide grooves 450 extending axially are provided at the lower part of the front end of the housing 400, and a shutter 420 which will be further discussed later is disposed in these slide grooves 450.
- the shutter 420 is made of a resinous member (for example nylon), is mounted on the output shaft 220 and comprises a ring body 421 sandwiched between the return spring 240 and the pinion 200 and a water-barrier portion 422 which opens and closes an opening portion 410 in the housing 400.
- a washer 480 is interposed between the ring body 421 and the pinion 200.
- the operation of the shutter 420 is such that when the starter starts to operate and the pinion 200 shifts forward along the output shaft 220 the ring body 421 shifts forward together with the pinion 200.
- the water-barrier portion 422 integral with the ring body 421 shifts forward and opens the opening portion 410 of the housing 400.
- the ring body 421 also shifts backward together with the pinion 200.
- the water-barrier portion 422 integral with the ring body 421 also shifts backward and closes the opening portion 410 of the housing 400.
- the shutter 420 which constitutes opening and closing means, by means of the water-barrier portion 422 prevents rainwater and the like which is splashed by the centrifugal force of the ring gear 100 from getting inside the housing 400 when the starter is not operating.
- a seal member 430 is disposed in the inner front end of the housing 400 to prevent the rainwater or dust which enters through the opening 410 of the housing 400 from entering further into the housing bearing 440 at the front end of the housing 400.
- a housing top seal member 470 is attached on the outer front end of the housing 400 to prevent the rainwater or dust from entering from outside into the housing bearing 440.
- the motor 500 is enclosed by a yoke 501, a motor spacer wall 800, and a brush holding member 900 which will be discussed later.
- the motor spacer wall 800 houses the planetary gear speed reduction mechanism 300 between itself and the center bracket 360, and also fulfills the role of preventing lubricating oil inside the planetary gear speed reduction mechanism 300 from getting into the motor 500.
- the motor 500 is made up of an armature 540 comprising the armature shaft 510 and an armature core 520 and armature coils 530 which are mounted on and rotate integrally with this armature shaft 510, and fixed poles 550 which rotate the armature 540, and the fixed poles 550 are mounted around the inside of the yoke 501.
- the armature shaft 510 is rotatably supported by the planet carrier bearing 380 provided at inside rear portion of the planet carrier 330 and a brush holder bearing 564 fixed on the inner periphery of the brush holder 900.
- the armature core 520 is, as shown in Fig. 7, made of a plurality of core plates 521 stacked together and the armature shaft 510 is press-fitted into a central hole of the core 520.
- Each core plate 521 is made by press-punching a thin steel plate and coated with an insulating material on its face.
- a plurality of slots (for example, 25) 524 are formed on the outer periphery of the core plate 521 to receive therein armature coils 530.
- the armature coils 530 in this embodiment multiple (for example 25) upper layer coil bars 531 and the same number of lower layer coil bars 532 as these upper layer coil bars 531 are used, and 2-layer-winding coils wherein the respective upper layer coil bars 531 and the lower layer coil bars 532 are stacked in the radial direction are employed.
- the upper layer coil bars 531 and lower layer coil bars 532 are paired, and the ends of the upper layer coil bars 531 and the ends of the lower layer coil bars 532 are electrically connected to constitute ring-shaped coils.
- the upper layer coil bars 531 are made of a material having excellent electrical conductivity (for example, copper), and are each provided with an upper layer coil arm 533 which extends in parallel with the fixed poles 550 and is held in the outer sides of slots 524 and 2 upper layer coil ends 534 which are bent inward from both ends of the upper layer coil arm 533 and extend in a direction orthogonal to the axial direction of the armature shaft 510.
- a material having excellent electrical conductivity for example, copper
- the upper layer coil arm 533 and the 2 upper layer coil ends 534 may be a member integrally molded by cold casting, may be a member shaped by bending in a press into a U-shape, or may be a member formed by joining a upper layer coil arm 533 and 2 upper layer coil ends 534 made as separate parts by a joining method such as welding.
- the lower coil bars 532 are made from a material having excellent electrical conductivity (for example copper), and each comprise a lower layer coil arm 536 which extends parallel with respect to the fixed poles 550 and is held in the inner sides of slots 524 and 2 lower layer coil ends 537 which are bent inward from the ends of this lower layer coil arm 536 and extend orthogonal to the axial direction of the armature shaft 510.
- a material having excellent electrical conductivity for example copper
- the lower layer coil arm 536 and the 2 lower layer coil ends 537 may be a member integrally molded by cold casting, may be a member shaped by bending in a press into a U-shape, or may be a member formed by joining a lower layer coil arm 536 and 2 lower layer coil ends 537 made as separate parts by a joining method such as welding.
- Insulation between the upper layer coil ends 534 and the lower layer coil ends 537 is secured by insulating spacers 560, and insulation between the lower layer coil ends 537 and the armature core 520 is secured by an insulating ring 590 made of resin (for example, nylon or phenol resin).
- the upper coil arms 533 and the lower coil arms 536 are each coated with an insulating film (not shown) to be insulated from the armature core 520 and insulated from each other.
- the upper coil ends 534 disposed at the side of the magnet switch 600 directly abuts a brush 910 described later to supply power to the armature coil 530. Therefore, at least the surface of the upper coil end 534 the which abuts the brush 910 is smoothed.
- An end portion 538 of the upper coil ends 534 and end portion 539 of the lower coil ends 537 are coupled through an insulating cap 580 to a metal collar 570 press-fitted onto the armature shaft 510.
- the upper coil end 534 and the lower coil end 537 are prevented from expanding in the axial direction, and the inner diameter of the armature coils 530 are prevented from expanding by the centrifugal force.
- the collar 570 disposed at the front side abuts the rear face of motor separating wall 800 positioned in front thereof and operates as a thrust receiving portion which restricts the forward movement of the armature 540.
- the collar 570 disposed behind the starter abuts the front face of the brush holder member 90 positioned therebehind and operates as thrust receiving portion which restricts thr rearward movement of the armature 540.
- the yoke 501 is a cylindrical body formed by rolling a steel plate, and around it are formed a plurality of concave grooves 502 extending axially and sunk toward the inner circumference. These concave grooves 502 are used for, as well as disposing through bolts, positioning fixed poles 550 on the inner circumference of the yoke 501.
- permanent magnets are used for the fixed poles 550 and, as shown in Fig. 8, they comprise a plurality of (for example 6) main poles 551 and inter-pole poles 552 disposed between these main poles 551.
- Field coils which generate magnetic force by electrical current flow may be used instead of permanent magnets for the fixed poles 550.
- the main poles 551 are positioned by the ends of the inner sides of channel grooves 502 in the above-mentioned yoke 501, and are fixed in the yoke 501 by fixing sleeves 553 disposed around the inside of the fixed poles 550 with the inter-pole poles 552 disposed between the main poles 551.
- the magnet switch 600 as shown in Fig. 1, Fig. 9 and Fig. 10, is held in a brush holder 900 which will be discussed later, is disposed inside an end frame 700 which will be discussed later, and is fixed so as to be substantially orthogonal to the armature shaft 510.
- the magnet switch 600 is structured inside a magnet switch cover 640 which is cylindrical and has a bottom and is made from magnetic parts (for example, made of iron).
- the magnet switch cover 640 is for example a pliable steel plate press-formed into a cup shape, and in the center of the bottom of the magnet switch cover 640 there is a hole 641 through which the plunger 610 passes movably in the vertical direction. Also, the upper opening of the magnet switch cover 640 is closed off by a stationary core 642 made of a magnetic body (for example, made of iron).
- the stationary core 642 consists of an upper large diameter portion 643, a lower middle diameter portion 644, and a still lower small diameter portion 645, and the stationary core 642 is fixed in the upper opening of the magnet switch cover 640 by the outer periphery of the large diameter portion 643 being caulked to the inner side of the upper end of the magnet switch cover 640.
- the upper end of an attracting coil 650 is fitted around the middle diameter portion 644.
- the upper end of a compression coil spring 660 which urges the plunger 610 downward is fitted around the periphery of the small diameter portion 645 of the stationary core 642.
- the attracting coil 650 is attracting means which generates magnetism when a current flows through it and attracts the plunger 610, and the attracting coil 650 is provided with a sleeve 651 which has its upper end fitted to the middle diameter portion 644 of the stationary core 642 and covers the plunger 610 slidably in the vertical direction.
- This sleeve 651 is made by rolling up a non-magnetic thin plate (for example, copper plate, brass, stainless steel), and insulating washers 652 made of resin or the like are provided at the upper and lower ends of this sleeve 651.
- a thin insulating film (not shown in the drawings) made of resin (for example cellophane, nylon film) or paper, and around that insulating film is wound a predetermined number of turns of a thin enamel wire, whereby the attracting coil 650 is constituted.
- the plunger 610 is made of a magnetic metal (for example, iron) and has a substantially cylindrical shape comprising an upper small diameter portion 613 and a lower large diameter portion 614.
- the lower end of the compression coil spring 660 is fitted to the small diameter portion 613, and the large diameter portion 614, which is relatively long in the axial direction, is held slidably vertically in the sleeve 651.
- a plunger shaft 615 extending upward from the plunger 610 is fixed to the upper end of the plunger 610.
- This plunger shaft 615 projects upward through a through hole provided in the stationary core 642.
- An upper movable contact 612 is fitted around the plunger shaft 615 above the stationary core 642 slidably vertically along the plunger shaft 615.
- This upper movable contact 612 is limited by a stopping ring 616 fitted to the upper end of the plunger shaft 615 so that it does not move upward of the upper end of the plunger shaft 615.
- the upper movable contact 612 is vertically slidable along the plunger shaft 615 between the stopping ring 616 and the stationary core 642.
- the upper movable contact 612 is urged upward at all times by a contact pressure spring 670 consisting of a sheet plate spring fitted to the plunger shaft 615.
- the upper movable contact 612 is made of a metal such as copper having excellent conductivity, and when both ends of the upper movable contact 612 move upward they abut with the 2 abutting portions 631 of the fixed contact 630.
- the lead wires 91oa of a pair of brushes 910 are electrically and mechanically fixed to the upper movable contact 612 by caulking or welding or the like.
- the end portion of a resistor member 617 constituting a plurality of (in this embodiment, 2) limiting means is inserted and electrically and mechanically fixed in a groove portion of the upper movable contact 612.
- the lead wires 910a are electrically and mechanically fixed to the upper movable contact 612 by caulking or welding, but the upper movable contact 612 and the lead wires 910a of the brushes 910 may alternatively be formed integrally.
- the resistor member 617 is for rotating the motor 500 at low speed when the starter starts to operate, and consists of a metal wire of high resistance wound through several turns.
- a lower movable contact 611 located below the head portion 621 of the terminal bolt 620 is fixed by caulking or the like to the other end of the resistor member 617.
- the lower movable contact 611 is made of a metal such as copper having excellent conductivity, and when the magnet switch 600 stops and the plunger 610 is in its downward position abuts the upper face of the stationary core 642, when the resistor member 617 moves upward along with the movement of the plunger shaft 615, before the upper movable contact 612 abuts the abutting portion 631 of the fixed contact 630 it abuts the head portion 621 of the terminal bolt 620.
- the lower face of the plunger 610 is provided with a recess portion 682 which accommodates a sphere 681 provided at the rear end of the cord-shaped member 680 (for example, a wire).
- a female thread 683 is formed on the inner wall of this female thread 683.
- a fixing screw 684 which fixes the sphere 681 in the recess portion 682 is screwed into this recess portion 682. This fixing screw 684 is also used to perform adjustment of the length of the cord-shaped member 680, by adjusting the extent to which the fixing screw 684 is screwed into the female thread 683.
- the length of the cord-shaped member 680 is adjusted so that when the plunger shaft 615 moves upward and the lower movable contact 611 abuts the terminal bolt 620 the return/rotation regulating claw 231 of the regulating portion 232 mates with the convexes/concaves 214 of the outer periphery of the pinion 200.
- the female thread 683 and the fixing screw 684 constitute an adjusting mechanism.
- the end frame 700 is a magnet switch cover made of resin (for example phenol resin), and accommodates the magnet switch 600.
- Spring holding pillars 710 which hold compression coil springs 914 which urge the brushes 910 forward are mounted projecting from the rear face of the end frame 700 in correspondence with the positions of the brushes 910.
- the compression coil springs 914 are disposed radially outward with respect to the axial direction of the plunger 610 of the magnet switch 600.
- the compression coil spring 914 can be used to the extent that its spring length becomes the radial length of the magnet switch 600. For this reason, the spring stress and load of the the compression coil spring 914 can be set to appropriate values with ease, resulting in prolonged life of the compression coil spring 914.
- the terminal bolt 620 is a steel bolt which passes through the end frame 700 from the inside and projects from the rear of the end frame 700 and has at its front end a head portion 621 which abuts the inner face of the end frame 700.
- the terminal bolt 620 is fixed to the end frame 700 by a caulking washer 622 being attached to the terminal bolt 620 projecting rearward of the end frame 700.
- a copper fixed contact 630 is fixed to the front end of the terminal bolt 620 by caulking.
- the fixed contact 630 has one or a plurality of (in this embodiment, 2) abutting portions 631 positioned at the top end of the inside of the end frame 700, and these abutting portions 631 are mounted so that the upper face of the upper movable contact 612 which is moved up and down by the operation of the magnet switch 600 can abut with the lower faces of the abutting portions 631.
- the brush holder 900 as well as the roles of separating the inside of the yoke 501 and the inside of the end frame 700 and rotatably supporting the rear end of the armature shaft 510 by way of the brush holder bearing 564, also fulfills the role of a brush holder, the role of holding the magnet switch 600, and the role of holding a pulley 690 which guides the cord-shaped member 680.
- the brush holder 900 has a hole portion not shown in the drawings through which the cord-shaped member 680 passes.
- the brush holder 900 is a spacing wall made of a metal such as aluminum molded by a casting method and, as shown in Fig. 12 through Fig. 14, has a plurality of (in this embodiment, 2 upper and 2 lower) brush holding holes 911, 912 which hold the brushes 910 in the axial direction.
- the upper brush holding holes 911 are holes which hold brushes 910 which receive a plus voltage, and these upper brush holding holes 911 hold the brushes 910 by way of resin (for example nylon, phenol resin) insulating cylinders 913 (Fig. 13 is a cross-section taken along A-A of Fig. 12, and Fig. 14 is a cross-section taken along B-B of Fig. 12).
- the lower brush holding holes 912 are holes which hold brushes 910 connected to earth, and these lower brush holding holes 912 hold the respective brushes 910 directly therein.
- the brushes 910 are urged against the upper layer coil ends 534 at the rear ends of the armature coils 530 by the compression coil springs 914.
- the lead wires 910a of the upper brushes 910 are electrically and mechanically joined by a joining method such as welding or caulking to the upper movable contact 612 which is moved by the magnet switch 600.
- the lead wires 910a of the lower brushes 910 are caulked and thereby electrically and mechanically joined to a concave portion 920 formed in the rear face of the brush holder 900.
- Two seats 930 with which the front side of the magnet switch 600 abuts and two fixing pillars 940 which hold the periphery of the magnet switch 600 are formed on the rear side of the brush holder 900.
- the seats 930 are shaped to match the external shape of the magnet switch 600 in order to abut with the magnet switch 600, which has a cylindrical exterior.
- a pulley holding portion 950 which holds a pulley 690 which converts the direction of movement of the cord-shaped member 680 from the vertical direction of the magnet switch 600 into the axial direction thereof is formed on the lower side of the rear side of the brush holder 900.
- a holding portion 960 is provided for holding an over-temperature protecting temperature switch (not shown).
- the temperature switch turns off the magnet switch 600 at a predetermined temperature and stops motor operation, thereby protecting the starter.
- air passages are formed for discharging the air outside in the manner that the centrifugal air flow is generated by the rotation of upper coil ends 534 positioned on the rear side of the armature coil 530, the air sucked through the housing is taken into the end frame 700 through an opening (indicated by numeral 980) of the brush holding member 900, thereafter the air is led to the rear side of the armature coil 530 through an opening (indicated by numeral 970) of the brush holding member 900 to cool the sliding surface of the brushes and peripheries, and finally the air is discharged with brush powders generated on the sliding surfaces through a dischage hole 503 formed on the bottom of the yoke 501.
- the voltage of the battery 20 is impressed on the terminal bolt 620, and the voltage of the terminal bolt 620 is transmitted through the lower movable contact 611 ⁇ the resistor member 617 ⁇ the upper movable contact 612 ⁇ the lead wires 910a to the upper brushes 910. That is, the low voltage passing through the resistor member 617 is transmitted through the upper brushes 910 to the armature coils 530. Because the lower brushes 910 are constantly grounded through the brush holder 900, a current flows at low voltage through the armature coils 530 constituted in coil form by the paired upper layer coil bars 531 and lower layer coil bars 532. When this happens, the armature coils 530 generate a relatively weak magnetic force, this magnetic force acts on (attracts or repels) the magnetic force of the fixed poles 550, and the armature 540 rotates at low speed.
- the planetary gears 320 of the planetary gear speed reduction mechanism 300 are rotationally driven by the sun gear 310 on the front end of the armature shaft 510.
- the rotation of the internal gear 340 is limited by the operation of the overrunning clutch 350. That is, because the internal gear 340 does not rotate, the rotation of the planetary gears 320 causes the planet carrier 330 to rotate at low speed.
- the pinion 200 also rotates, but because the pinion 200 has its rotation limited by the return/rotation regulating member 230 the pinion 200 advances along the helical spline 221 on the output shaft 220.
- the shutter 420 also advances, and opens the opening portion 410 of the housing 400.
- the advance of the pinion 200 causes the pinion gear 210 to mesh completely with the ring gear 100 and then abut with the pinion stopping ring 250.
- the regulating claw 231 disengages from the convexes/concaves 214 of the pinion 200 and after that the front end of the regulating claw 231 drops to the rear side of the thrust bearing 215 disposed on the rear side of the pinion 200 so that the regulating claw 231 stops return of the pinion 200 to the rearward direction.
- the upper movable contact 612 abuts the abutting portion 631 of the fixed contact 630.
- the battery voltage of the terminal bolt 620 is directly transmitted through the upper movable contact 612 ⁇ the lead wires 910a to the upper brushes 910. That is, a high current flows through the armature coils 530 consisting of the upper coil bars 531 and the lower coil bars 532, the armature coils 530 generate a strong magnetic force and the armature 540 rotates at high speed.
- the rotation of the armature shaft 510 is slowed and has its rotational torque increased by the planetary gear speed reduction mechanism 300 and rotationally drives the planet carrier 330.
- the front end of the pinion 200 abuts the pinion stopping ring 250 and the pinion 200 rotates integrally with the planet carrier 330.
- the pinion gear 210 of the pinion 200 is meshing with the ring gear 100 of the engine, the pinion gear 210 rotationally drives the ring gear 100 and rotationally drives the output shaft of the engine.
- the driver releases the key switch 10 from the start position and the flow of current to the attracting coil 650 of the magnet switch 600 is stopped.
- the plunger 610 is returned downward by the action of the compression coil spring 660.
- the upper movable contact 612 moves away from the abutting portion 631 of the fixed contact 630, and after that the lower movable contact 611 also moves away from the head portion 621 of the terminal bolt 620, and the flow of current to the upper brushes 910 is stopped.
- the thrust bearing 215 absorbs the difference between the rotational speed of the pinion 200 and that of the return/rotation regulating claw 231. Because the rotation of the pinion 200 is absorbed by the thrust bearing 215, and the rotation torque of the pinion 200 is prevented from being transmitted to the return/rotation regulating claw 231, generation of wear, heat, and rotation loss between the pinion 200 and return/rotation regulating claw 231 can be prevented.
- the thrust bearing 215 comprises an orbital ring 216 and a rolling bearing composed of the orbital ring 216 and a plurality of spheres 217
- the rotational force is transmitted to the return/rotation regulating claw 231 at a very small degree.
- the return/rotation regulating claw 231 having a low rigidity is used, there is no disadvantage that the return/rotation regulating claw 231 is damaged by the engagement into the rotation of the pinion 200.
- the rigidity of the return/rotation regulating claw 231 is allowed to be low, the force of the magnet switch 600 for operating the return/rotation regulating claw 231 can be reduced and hence, the magnet switch 600 can be allowed to be compact and light.
- the pinion 200 can be moved in the axial direction of the output shaft 220 which drives the pinion 200, and the weight of the moving member (pinion 200 + thrust bearing 215) can be allowed to be smaller by about 1/5 than that of the conventional moving member (pinion + pinion shaft).
- the force required for the magnet switch 600 is the force for operating the movable contacts 611 and 612 plus the force for operating the return/rotation regulating claw 231.
- the force to be generated by the magnet switch 600 is much smaller than that to be generated by the conventional one. Therefore, the magnet switch 600 can be made smaller and lighter than the conventional one.
- the weight of the moving member can be allowed to be smaller by about 1/5 than that of the conventional one, the energy for moving the pinion 200 can be allowed to be smaller than that for moving the conventional one. Because of this, the energy required for actuating the starter can be reduced and hence, the load to be applied to a power unit (lead storage battery, electric double-layer capacitor or the like) for driving the starter can be reduced. Consequently, the power unit can be allowed to be smaller and have a longer life than the conventional one.
- the weight of the moving member can be allowed to be smaller by about 1/5 than that of the conventional one, the shock generated when the pinion 200 engages the ring gear 100 can be reduced.
- the pinion 200 is heat-treated after the thrust bearing 215 is mounted thereon. Therefore, it is unnecessary to subject the orbital ring 216 of the thrust bearing 215 to heat treatment separately, which eliminates the need for a process of increasing the hardness of the orbital ring 216 to more than a predetermined value.
- the return/rotation regulating claw 231 is positioned rearward the pinion 200 because it exceeds the expansion force of the return spring portion 233 by the movement force of the plunger 610 of the magnet switch 600.
- the return/rotation regulating claw 231 can be securely disengaged from the rear portion of the pinion 200 owing to the expansion force of the return spring 233.
- Fig. 16 is a sectional view of a starter according to a second embodiment.
- a magnet switch 600 While in the first embodiment the magnet switch 600 is positioned rearward the motor 500 and the plunger 610 is positioned in a direction orthogonal to the armature shaft 510 of the motor 500, in a starter of the second embodiment, a magnet switch 600 is positioned below a motor 500 with its plunger being positioned in a direction parallel with an armature shaft 510 of the motor 500.
- Fig. 17 shows a third embodiment in a sectional view of a pinion 200 having a thrust bearing 215 mounted thereon.
- the pinion gear 210 (outer teeth) is formed on the peripheral face of one member and the helical inner spline 211 (inner teeth) is formed on the inner peripheral face thereof.
- a pinion inner member 200a provided with a helical inner spline 211 on the inner peripheral face thereof and a pinion outer member 200b provided with a pinion gear 210 on the peripheral face thereof are separately produced, and then nonrotatably fixed with each other.
- press fitting method may be utilized after providing a whirl-stop (for example, key way) between the pinion inner member 200a and the pinion outer member 200b or welding method may be used.
- the pinion gear 210 which is the external teeth has to be formed by machining.
- those can be formed by cold forging, respectively, which results in a reduction in manufacturing cost.
- the pinion inner member 200a can be connected with many kinds of pinion outer members 200b. Therefore, many kinds of pinions 200 can be manufactured by preparing many kinds of pinion outer members 200b. That is, in the case of the pinion 200, many kinds of specifications are required according to the specification of the engine, whereas in the case of the helical inner spline 211, only one kind or a few kinds of specifications are required. Thus, many kinds of pinions 200 can be manufactured in combination of the pinion inner member 200a and the pinion outer member 200b provided separately, which provides many kinds of starters corresponding to many kinds of engines. Further, the pinion inner member 200a can be mass-produced, which leads to the production of the pinion 200 in low cost.
- the pinion 200 of this embodiment is heavier than that of the first and second embodiments because of a cold forging-caused shear droop portion 210a of the pinion outer member 200b, but the weight of the pinion 200 of this embodiment is much lighter than that of the conventional pinion moving member.
- the third embodiment can provide the similar operation and effect as in the first embodiment.
- Figs. 18 through 21 show a fourth embodiment in which a rotation regulating member and a return regulating member are provided separately.
- the construction of the return regulating member of this embodiment is different from that of the return regulating member of the first embodiment.
- the construction of the return regulating member of this embodiment will be described below.
- a return regulating member 260 (corresponding to return regulating means) comprises an annular portion 262 (Fig. 19) having a circular hole 261 formed at the center thereof to receive an output shaft 220 therethrough; side portions 263 bent at right angle to the annular portion 262 at both sides thereof; and a pivotal support 264 pivotably supported by a supporting pin 270 fixed to a center bracket 360.
- the return regulating member 260 is constructed by mating the supporting pin 270 with a hole 265 (Fig. 20) formed on the pivotal support 264 and by mating an engaging pin 281 provided on a thrust ring 280 with a slot 266 formed on the side portion 263, so that the return regulating member 260 is rotatable or pivotable around the supporting pin 270.
- the return regulating member 260 is pressed toward a plate 290 by a spring 271 mating with the supporting pin 270. That is, the spring 271 presses the pinion 200 rearward (toward the plate 290) through the return regulating member 260, thus maintaining a stationary state and contributing to preventing the pinion 200 from moving forward when the engine is started.
- the rotation regulating member 230 of this embodiment is formed of a circular rod-shaped metal material, and both ends thereof are bent perpendicularly in the same direction at opposite positions in a radial direction thereof.
- One end of the bent portion serves as a rotation regulating bar 231 which engages convexes/concaves 214 of the pinion 200 to stop rotation of the pinion 200 at an initial time in the actuation of the starter, whereas one end of a cord-shaped member 680 engages the other end 231b of the rotation regulating member 230 to transmit the operation of the magnet switch 600 therethrogh.
- the output shaft 220 rotates and the rotation-regulated pinion 200 advances on the helical spline.
- the pinion 200 engages the ring gear 100 to start the engine.
- the return regulating member 260 biased by the spring 271 is inclined axially around the supporting pin 270 by the advance of the pinion 200, with the engaging pin 281 mounted on the thrust ring 280 and the slot 266 formed on the side portion 263 engaging each other.
- the return regulating member 260 is rotatably mounted relative to the pinion 200 through the thrust ring 280, and the rotational force of the pinion 200 is not applied to the rotation regulating bar 231 supporting the rear end of the return regulating member 260. Therefore, the rotation regulating bar 231 is prevented from being bent or worn. Further, because the side portions 263 of the return regulating member 260 contact the rear end face of the thrust ring 280 at both positions in a radial direction thereof, the pinion 200 is supported by two points. Owing to this, the pinion 200 can be prevented from being inclined with respect to the output shaft 220 and hence, a reliable operation can be provided.
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Abstract
Description
- The present invention relates to a starter for starting an engine by engaging a pinion with a ring gear of an engine and driving the pinion, and more particularly to a starter having a pinion return preventing mechanism.
- As a moving member for moving a pinion of a starter axially, the conventional art disclosed in Laid-Open Japanese Utility Model Publication No. (JP-U) 1-131872 is known. In the starter disclosed in this publication, a pinion shaft and a one-way clutch are axially movably provided relatively to each other, and the pinion shaft is driven to shift the pinion shaft and the pinion, unlike the starter in which the pinion, the pinion shaft (output shaft), and the one-way clutch are shifted integrally. The construction disclosed in this publication allows the weight to be shifted to be smaller and a magnet switch to be compact.
- The weight of the pinion shaft is, however, about five times as great as that of the pinion. Therefore, there is a demand for the improved starter capable of shifting only the pinion to reduce energy required to shift it.
- Further, in order to shift the pinion, it is necessary to provide a shift-maintaining member for maintaining a state in which the pinion and the ring gear in mesh with each other, and technique for preventing the shift-maintaining member and the pinion from being worn, and technique for reducing rotational loss between the shift-maintaining member and the pinion from being generated.
- The present invention has been made in view of the abovedescribed drawbacks and has a first object of providing an improved starter.
- The present invention has a second object of providing a starter capable of reducing to a less amount the degree of wear and rotational loss between a pinion and a member for keeping the state in which the pinion is in mesh with a ring gear.
- The present invention has a third object of providing a starter capable of reducing energy required to shift a pinion by shifting a pinion in the axial direction of an output shaft for driving the pinion.
- According to the present invention, a return regulating member is provided at one side of a pinion in the axial direction thereof through a bearing, for regulating the return of the pinion in the axial direction thereof after engagement with a ring gear. Thus, the pinion does not disengage from the ring gear and the rotational torque of the motor is transmitted to the engine through the ring gear. Further, an absorbing member such as a thrust bearing is provided between the pinion and the return regulating member to absorb the difference in the rotational speeds of the pinion and the return regulating member. Thus, generation of wear, heat, and the loss of the rotational torque between the pinion and the return regulating member can be suppressed, thus maintaining the performance of the starter for a long time.
- Preferably, a rotation restricting member is provided for regulating the rotation of the pinion to move the pinion axially for engagement with the ring gear. The rotation restricting member is manufactured integrally with the return regulating member to act as the return regulating member as well. Thus, the starter has a simple construction and hence, can be made light in weight and compact in size.
- More preferably, the pinion includes a pinion inner member having a helical inner spline and a pinion outer member having a pinion gear, and those members are produced separately. Thus, the helical inner spline (inner teeth) and the pinion gear (outer teeth) can be manufactured by the most appropriate method, respectively.
- In the accompanying drawings:
- Fig. 1 is a sectional side view showing an embodiment of a starter according to the present invention (first embodiment);
- Figs. 2A and 2B are a front view and a partial sectional side view of a rotation regulating member fitted on a pinion part (first embodiment);
- Fig. 3 is a perspective view showing the rotation regulating member (first embodiment);
- Fig. 4 is a rear view of a center bracket (first embodiment);
- Fig. 5 is a sectional side view of the center bracket (first embodiment);
- Fig. 6 is a front view of the center bracket (first embodiment);
- Fig. 7 is a sectional side view of an armature (first embodiment);
- Fig. 8 is a front view of a yoke (first embodiment);
- Fig. 9 is an exploded perspective view of a plunger and fixed contacts of a magnet switch (first embodiment);
- Fig. 10 is a perspective view showing the magnet switch (first embodiment);
- Fig. 11 is a sectional side view showing an end frame and compression coil springs (first embodiment);
- Fig. 12 is a rear view showing a brush holder (first embodiment);
- Fig. 13 is a sectional side view taken along a line XIII-XIII in Fig. 12 (first embodiment);
- Fig. 14 is a sectional side view taken along a line XIV-XIV in Fig. 12 (first embodiment);
- Figs. 15A, 15B, and 15C are electric circuit diagrams showing the operation state of the pinion (first embodiment);
- Fig. 16 is a sectional view showing a starter (second embodiment);
- Fig. 17 is a sectional view showing a pinion (third embodiment);
- Fig. 18 is a side elevational view showing a rotation regulating member and a return regulating member (fourth embodiment);
- Fig. 19 is a front view of the members shown in Fig. 18 (fourth embodiment);
- Fig. 20 is an exploded perspective view of Fig. 18 (fourth embodiment); and
- Fig. 21 is an explanatory view of the operation of a return regulating member (fourth embodiment).
- Next, the starter according to this invention will be described based on embodiments shown in the accompanying drawings.
- Figs. 1 through 15A-15C show a first embodiment, with Fig. 1 being an entire sectional view of a starter.
- The starter can be generally divided into a
housing 400 containing apinion 200 which meshes with aring gear 100 mounted on an engine and a planetary gearspeed reduction mechanism 300, amotor 500, and anend frame 700 containing amagnet switch 600. Inside the starter, thehousing 400 and themotor 500 are separated by amotor spacer wall 800, and themotor 500 and theend frame 700 are separated by abrush holding member 900. - As shown in Fig. 1 and Figs. 2A-2B, a
pinion gear 210 which meshes with thering gear 100 of the engine is formed on the outer periphery of apinion 200. A helicalinner spline 211 which mates with a helicalouter spline 221 formed on the outer periphery of anoutput shaft 220 is formed. Thus, thepinion 200 is spline-engaged on theoutput shaft 220 to be axially movable on theoutput shaft 220. Thepinion 200 is so arranged to advance toward thering gear 100 due to the differnce in rotational speeds when theoutput shaft 220 rotates at higher speed than thepinion 200. - A
tapered portion 222 is formed on the rear end of theoutput shaft 220 so that the helicalinner spline 211 of thepinion 200 abuts thetapered portion 222 to stop a rearward movement of thepinion 200 further from thetapered portion 222. A pinion stopping ring 250 is mounted on the front side of theoutput shaft 220 to stop a forward movement of thepinion 200 further from the pinion stopping ring 250. - On the opposite side of the
pinion 200 from thering gear 100, aflange 213 of greater diameter than the external diameter dimension of thepinion gear 210 is formed in circular disk form. A number of convexes/concaves 214 greater than the number of outer teeth of thepinion gear 210 are formed around the entire outer circumference of thisflange 213. These convexes/concaves 214 are for a return/rotation regulating claw 231 of arotation regulating member 230 which will be discussed later to mate with. - A thrust bearing 215 (absorbing means) is mounted on the rear end of the
flange 213 to absorb the difference in rotational speeds of thepinion 200 and the return/rotation regulating claw 231. According to the embodiment, a bearing which bears axially applied load is called as a thrust bearing. - The
thrust bearing 215 in this embodiment uses a rolling bearing and is comprised of anorbital ring 216 which is to be abutted by the front end of the return/rotation regulating claw 231 and a plurality ofballs 217 rotatable between theorbital ring 216 and the rear face of theflange 213. By the rotation of theballs 217, the rotational difference between thepinion 200 and the return/rotation regulating claw 213 is absorbed. Theballs 217 may be made of steel but preferably made of ceramics to improve durability. - The
thrust bearing 215 is mounted in arecess 218 formed on the rear face of theflange 213, and then an annular portion 219 formed on the rear end of thepinion 200 is bent outwardly so that it is kept rotatably on the rear face of theflange 213 and unable to come off in the axial direction. - By the
rotatable thrust bearing 215 being mounted on the rear face of theflange 213 of thepinion 200 in this way, when therotation regulating member 230 which will be discussed later drops in behind thepinion 200, the front end of the return/rotation regulating claw 231 abuts theorbital ring 216 of thethrust bearing 215. As a result, the rotation of thepinion 200 is absorbed by thethrust bearing 215 and the rotation torque of thepinion 200 is not transmitted to the return/rotation regulating claw 231. Thus, this prevents generation of wear, heat and rotation loss between thepinion 200 and thr return/rotation regulating claw 231. - Further, when the
pinion 200 is driven by thering gear 100 and rotated at a higher speed than theoutput shaft 220 to cause a speed difference by which a force is applied to return thepinion 200 rearward, a large load is applied between thepinion 200 and the return/rotation regulating claw 231. Since this rotational difference is absorbed by thethrust bearing 215, wear, heat generation and rotational loss between thepinion 200 and the return/rotation regulating claw 231 can be reduced. - The
pinion 200 is urged toward the rear of theoutput shaft 220 at all times by areturn spring 240 made of a compression coil spring. Thereturn spring 240 does not urge thepinion 200 directly but in this embodiment urges thepinion 200 by way of aring body 421 of ashutter 420 which opens and closes anopening portion 410 of thehousing 400 discussed later. - The
rotation regulating member 230 constituting pinion moving means, as shown in Fig. 3, is a sheet spring member wound through approximately 3/2 turns of which approximately 3/4 turn is arotation regulating portion 232 of long axial sheet length and high spring constant and the remaining approximately 3/4 turn is areturn spring portion 233 constituting urging means of short axial sheet length and low spring constant. - The return/
rotation regulating claw 231 which constitutes a regulating portion extending in the axial direction and which mates with the multiple convexes/concaves 214 formed in theflange 213 of thepinion 200 is formed at one end of a regulatingportion 232. - This return/
rotation regulating claw 231 performs two functions as rotation regulating means and return regulating means; the rotation regulating meas stops rotation of thepinion 200 along the predetermined axial length at the time of start of rotation of themotor 500 to cause rotational difference between theoutput shaft 220 and thepinion 200 and move thepinion 200 axially, and the return regulating means drops into the axial rear end side to stop a return of thepinion 200 in a state of engagement of thepinion 200 with thering gear 100 after the axial advance of thepinion 200 by the predetermined length. This return/rotation regulating claw 231, as well as mating with the convexes/concaves 214 of thepinion 200, in order to increase the rigidity of the return/rotation regulating claw 231, is formed axially long and is bent radially inward into a cross-sectional L-shape. (It is bar-like.) - The regulating
portion 232 which supports the return/rotation regulating claw 231 elastically deformably is provided with astraight portion 235 which extends vertically. Thisstraight portion 235 is vertically slidably supported by two supportingarms 361 mounted projecting from the front face of acenter bracket 360. That is, thestraight portion 235 moving vertically causes the regulatingportion 232 to move vertically also. - Also, a
sphere 601 of the front end of a cord-shaped member 680 (for example, a wire), which will be further discussed later, for transmitting the movement of themagnet switch 600, which will be further discussed later, is in engagement with the position 180° opposite the return/rotation regulating claw 231 of the regulatingportion 232. - The end portion side of the
return spring portion 233 has a large curvature of winding and oneend portion 236 of thereturn spring portion 233 abuts the upper face of aregulating shelf 362 mounted projecting from a front face of a lower portion of thecenter bracket 360. - The operation of the
rotation regulating member 230 will now be explained. The cord-shapedmember 680 is transmitting means for transmitting the movement of themagnet switch 600 to the regulatingportion 232, and the movement of themagnet switch 600 pulls the regulatingportion 232 downward and causes the return/rotation regulating claw 231 to engage with the convexes/concaves 214 on theflange 213 of thepinion 200. At that time, because theend portion 236 of thereturn spring portion 233 is in abutment with theregulating shelf 362 for position regulating, thereturn spring portion 233 bends. Because the regulatingclaw 231 is in engagement with the convexes/concaves 214 on thepinion 200, when theoutput shaft 220 starts to be rotated by way of thearmature shaft 510 of themotor 500 and the planetary gearspeed reduction mechanism 300, rotational speed difference is caused between thepinion 200 and theoutput shaft 220 and thepinion 200 advances along the helicalouter spline 221 on theoutput shaft 220. - When the
pinion 200 advances, abuts thering gear 100 and the advance of thepinion 200 is obstructed, further rotational force of theoutput shaft 210 causes therotation regulating member 230 itself to bend and thepinion 200 rotates slightly and meshes with thering gear 100. When thepinion 200 advances further under this engagement, the return/rotation regulating claw 231 disengages from the convexes/concaves 214, thereturn regulating claw 231 drops in behind theflange 213 of thepinion 200, the front end of the return/rotation regulating claw 231 abuts the rear face of thethrust bearing 215 and prevents thepinion 200 from retreating under the rotation of thering gear 100 of the engine. - As the operation of the
magnet switch 600 stops and the cord-shapedmember 680 stops pulling the regulatingportion 232 downward, the action of thereturn spring portion 233 causes the regulatingportion 232 to return to its original position. - The pinion stopping ring 250 is fixed in a circular groove of rectangular cross-section formed around the
output shaft 220. This pinion stopping ring 250 is a piece of steel of rectangular cross-section processed into a circular shape; a substantially S-shaped corrugation 251 (an example of engaging means) is formed at each end, and the convex portion of one is in engagement with the concave portion of the other and the convex portion of the other is in engagement with the concave portion of the first. - The planetary gear
speed reduction mechanism 300, as shown in Fig. 1, is speed reducing means for reducing the rotational speed of themotor 500, which will be further discussed later, and increasing the output torque of themotor 500. The planetary gearspeed reduction mechanism 300 is made up of asun gear 310 formed on the front-side outer periphery of the armature shaft 510 (discussed later) of themotor 500, a plurality ofplanetary gears 320 which mesh with thissun gear 310 and rotate around the circumference of thesun gear 310, aplanet carrier 330 which rotatably supports theseplanetary gears 320 around thesun gear 310 and is formed integrally with theoutput shaft 220, and an internal gear 340 which is of a cylindrical shape meshing with theplanetary gears 320 at the outer periphery of theplanetary gears 320 and is made of resin. - The overrunning
clutch 350 supports the internal gear 340 rotatably in one direction only (only the direction in which it rotates under the rotation of the engine). The overrunningclutch 350 has a clutch outer 351 constituting a first cylindrical portion integrally formed in the front side of the internal gear 340, a circular clutch inner 352 constituting a second cylindrical portion formed in the rear face of thecenter bracket 360 constituting a fixed side covering the front of the planetary gearspeed reduction mechanism 300 and disposed facing the clutch outer 351, and rollers 353 accommodated in a roller housing portion 351a formed inclined to the inner face of the clutch outer 351. - The
center bracket 360 is shown in Fig. 4 through Fig. 6 and is disposed inside the rear end of thehousing 400. Thehousing 400 and thecenter bracket 360 are linked by aring spring 390 having one end engaged with thehousing 400 and the other end engaged with thecenter bracket 360 and are arranged in such a way that the rotational reaction received by a clutch inner 352 constituting the overrunningclutch 350 is absorbed by thering spring 390 and the reaction is not directly transmitted to thehousing 400. - Also, two supporting
arms 361 which hold therotation regulating member 230 and theregulating shelf 362 on which the lower end of therotation regulating member 230 is loaded are mounted on the front face of thecenter bracket 360. Further, a plurality ofcutout portions 363 which mate with convex portions (not shown in the figure) on the inner side of thehousing 400 are formed around thecenter bracket 360. The upperside cutout portions 363 are used also as air passages for guiding air from inside thehousing 400 into a yoke 501 (this is discussed in detail later in connection with the cooling air passage). Also, aconcave portion 364 through which the cord-shaped member 680 (discussed later) passes in the axial direction is formed at the lower end of thecenter bracket 360. - The
planet carrier 330 is provided at its rear end with a flange-like projectingportion 331 which extends radially in order to support theplanetary gears 320.Pins 332 extending rearward are fixed to this flange-like projectingportion 331, and thesepins 332 rotatably support theplanetary gears 320 by way of metal bearings. - The
planet carrier 330 has its front end rotatably supported by ahousing bearing 440 fixed inside the front end of thehousing 400 and a center bracket bearing 370 fixed inside an innercylindrical portion 365 of thecenter bracket 360. - The
planet carrier 330 has anannular groove 334 at a front position of an inner cylindrical portion and astopper ring 335 is fitted into theannular groove 334. Between thestopper ring 335 and the front end of the innercylindrical portion 365, a washer 336 is disposed rotatably against theplanet carrier 330. Thestopper ring 335, abutting the front end of the innercylindrical portion 365 through the washer 336, stops rearward movement of theplanet carrier 330. - The rear end of the center bracket bearing 370 supporting the rear side of the
planet carrier 330 has aflange portion 371 which is sandwiched between the rear end of the innercylindrical portion 365 and a flange-shaped protrudingportion 331. The flange-shaped protrudingportion 331, abutting the rear end of the innercylindrical portion 365 through aflange portion 371, restricts forward movement of theplanet carrier 330. - On the rear face of the
planet carrier 330, aconcave portion 337 extending axially is formed so that the front end of thearmature shaft 510 is rotatably supported through a planet carrier bearing 380 disposed in theconcave portion 337. - The
housing 400 supports theoutput shaft 220 with thehousing bearing 440 fixed in the front end of thehousing 400 and also is provided with awater barrier wall 460 which in order to minimize the incursion of rainwater and the like through theopening portion 410 minimizes the gap at the lower part of theopening portion 410 between the outer diameter of thepinion 200 and thehousing 400. Also, two slide grooves 450 extending axially are provided at the lower part of the front end of thehousing 400, and ashutter 420 which will be further discussed later is disposed in these slide grooves 450. - The
shutter 420 is made of a resinous member (for example nylon), is mounted on theoutput shaft 220 and comprises aring body 421 sandwiched between thereturn spring 240 and thepinion 200 and a water-barrier portion 422 which opens and closes anopening portion 410 in thehousing 400. A washer 480 is interposed between thering body 421 and thepinion 200. - The operation of the
shutter 420 is such that when the starter starts to operate and thepinion 200 shifts forward along theoutput shaft 220 thering body 421 shifts forward together with thepinion 200. When this happens, the water-barrier portion 422 integral with thering body 421 shifts forward and opens theopening portion 410 of thehousing 400. When the starter stops operating and thepinion 200 shifts backward along theoutput shaft 220, thering body 421 also shifts backward together with thepinion 200. When this happens, the water-barrier portion 422 integral with thering body 421 also shifts backward and closes theopening portion 410 of thehousing 400. As a result, theshutter 420, which constitutes opening and closing means, by means of the water-barrier portion 422 prevents rainwater and the like which is splashed by the centrifugal force of thering gear 100 from getting inside thehousing 400 when the starter is not operating. - A
seal member 430 is disposed in the inner front end of thehousing 400 to prevent the rainwater or dust which enters through theopening 410 of thehousing 400 from entering further into thehousing bearing 440 at the front end of thehousing 400. A housing top seal member 470 is attached on the outer front end of thehousing 400 to prevent the rainwater or dust from entering from outside into thehousing bearing 440. - The
motor 500 is enclosed by ayoke 501, amotor spacer wall 800, and abrush holding member 900 which will be discussed later. Themotor spacer wall 800 houses the planetary gearspeed reduction mechanism 300 between itself and thecenter bracket 360, and also fulfills the role of preventing lubricating oil inside the planetary gearspeed reduction mechanism 300 from getting into themotor 500. - The
motor 500, as shown in Fig. 1, is made up of anarmature 540 comprising thearmature shaft 510 and anarmature core 520 and armature coils 530 which are mounted on and rotate integrally with thisarmature shaft 510, and fixedpoles 550 which rotate thearmature 540, and the fixedpoles 550 are mounted around the inside of theyoke 501. - The
armature shaft 510 is rotatably supported by the planet carrier bearing 380 provided at inside rear portion of theplanet carrier 330 and a brush holder bearing 564 fixed on the inner periphery of thebrush holder 900. - The
armature core 520 is, as shown in Fig. 7, made of a plurality ofcore plates 521 stacked together and thearmature shaft 510 is press-fitted into a central hole of thecore 520. Eachcore plate 521 is made by press-punching a thin steel plate and coated with an insulating material on its face. A plurality of slots (for example, 25) 524 are formed on the outer periphery of thecore plate 521 to receive therein armature coils 530. - For the armature coils 530, in this embodiment multiple (for example 25) upper layer coil bars 531 and the same number of lower layer coil bars 532 as these upper layer coil bars 531 are used, and 2-layer-winding coils wherein the respective upper layer coil bars 531 and the lower layer coil bars 532 are stacked in the radial direction are employed. The upper layer coil bars 531 and lower layer coil bars 532 are paired, and the ends of the upper layer coil bars 531 and the ends of the lower layer coil bars 532 are electrically connected to constitute ring-shaped coils.
- The upper layer coil bars 531, as shown in Fig. 7, are made of a material having excellent electrical conductivity (for example, copper), and are each provided with an upper
layer coil arm 533 which extends in parallel with the fixedpoles 550 and is held in the outer sides ofslots 524 and 2 upper layer coil ends 534 which are bent inward from both ends of the upperlayer coil arm 533 and extend in a direction orthogonal to the axial direction of thearmature shaft 510. The upperlayer coil arm 533 and the 2 upper layer coil ends 534 may be a member integrally molded by cold casting, may be a member shaped by bending in a press into a U-shape, or may be a member formed by joining a upperlayer coil arm 533 and 2 upper layer coil ends 534 made as separate parts by a joining method such as welding. - The lower coil bars 532, like the upper coil bars 531, are made from a material having excellent electrical conductivity (for example copper), and each comprise a lower
layer coil arm 536 which extends parallel with respect to the fixedpoles 550 and is held in the inner sides ofslots 524 and 2 lower layer coil ends 537 which are bent inward from the ends of this lowerlayer coil arm 536 and extend orthogonal to the axial direction of thearmature shaft 510. The lowerlayer coil arm 536 and the 2 lower layer coil ends 537, like the upperlayer coil bar 531, may be a member integrally molded by cold casting, may be a member shaped by bending in a press into a U-shape, or may be a member formed by joining a lowerlayer coil arm 536 and 2 lower layer coil ends 537 made as separate parts by a joining method such as welding. - Insulation between the upper layer coil ends 534 and the lower layer coil ends 537 is secured by insulating
spacers 560, and insulation between the lower layer coil ends 537 and thearmature core 520 is secured by an insulatingring 590 made of resin (for example, nylon or phenol resin). Theupper coil arms 533 and thelower coil arms 536 are each coated with an insulating film (not shown) to be insulated from thearmature core 520 and insulated from each other. - Of the two upper coil ends 534, the upper coil ends 534 disposed at the side of the
magnet switch 600 directly abuts abrush 910 described later to supply power to the armature coil 530. Therefore, at least the surface of theupper coil end 534 the which abuts thebrush 910 is smoothed. - An end portion 538 of the upper coil ends 534 and end portion 539 of the lower coil ends 537 are coupled through an insulating cap 580 to a metal collar 570 press-fitted onto the
armature shaft 510. Thus, theupper coil end 534 and thelower coil end 537 are prevented from expanding in the axial direction, and the inner diameter of the armature coils 530 are prevented from expanding by the centrifugal force. - The collar 570 disposed at the front side abuts the rear face of
motor separating wall 800 positioned in front thereof and operates as a thrust receiving portion which restricts the forward movement of thearmature 540. On the other hand, the collar 570 disposed behind the starter abuts the front face of the brush holder member 90 positioned therebehind and operates as thrust receiving portion which restricts thr rearward movement of thearmature 540. - The
yoke 501, as shown in Fig. 8, is a cylindrical body formed by rolling a steel plate, and around it are formed a plurality ofconcave grooves 502 extending axially and sunk toward the inner circumference. Theseconcave grooves 502 are used for, as well as disposing through bolts, positioningfixed poles 550 on the inner circumference of theyoke 501. - In this embodiment permanent magnets are used for the fixed
poles 550 and, as shown in Fig. 8, they comprise a plurality of (for example 6)main poles 551 andinter-pole poles 552 disposed between thesemain poles 551. Field coils which generate magnetic force by electrical current flow may be used instead of permanent magnets for the fixedpoles 550. - The
main poles 551 are positioned by the ends of the inner sides ofchannel grooves 502 in the above-mentionedyoke 501, and are fixed in theyoke 501 by fixingsleeves 553 disposed around the inside of the fixedpoles 550 with theinter-pole poles 552 disposed between themain poles 551. - The
magnet switch 600, as shown in Fig. 1, Fig. 9 and Fig. 10, is held in abrush holder 900 which will be discussed later, is disposed inside anend frame 700 which will be discussed later, and is fixed so as to be substantially orthogonal to thearmature shaft 510. - In the
magnet switch 600, as shown in Figs. 9 and 10, electrical current drives aplunger 610 upward, and 2 contacts (a lowermovable contact 611 and an upper movable contact 612) which move together with theplunger 610 are sequentially caused to abut with thehead portion 621 of aterminal bolt 620 and anabutting portion 631 of afixed contact 630. A battery cable not shown in the figures is connected to theterminal bolt 620. - The
magnet switch 600 is structured inside amagnet switch cover 640 which is cylindrical and has a bottom and is made from magnetic parts (for example, made of iron). Themagnet switch cover 640 is for example a pliable steel plate press-formed into a cup shape, and in the center of the bottom of themagnet switch cover 640 there is ahole 641 through which theplunger 610 passes movably in the vertical direction. Also, the upper opening of themagnet switch cover 640 is closed off by astationary core 642 made of a magnetic body (for example, made of iron). - The
stationary core 642 consists of an upperlarge diameter portion 643, a lowermiddle diameter portion 644, and a still lowersmall diameter portion 645, and thestationary core 642 is fixed in the upper opening of themagnet switch cover 640 by the outer periphery of thelarge diameter portion 643 being caulked to the inner side of the upper end of themagnet switch cover 640. The upper end of an attractingcoil 650 is fitted around themiddle diameter portion 644. The upper end of acompression coil spring 660 which urges theplunger 610 downward is fitted around the periphery of thesmall diameter portion 645 of thestationary core 642. - The attracting
coil 650 is attracting means which generates magnetism when a current flows through it and attracts theplunger 610, and the attractingcoil 650 is provided with asleeve 651 which has its upper end fitted to themiddle diameter portion 644 of thestationary core 642 and covers theplunger 610 slidably in the vertical direction. Thissleeve 651 is made by rolling up a non-magnetic thin plate (for example, copper plate, brass, stainless steel), and insulatingwashers 652 made of resin or the like are provided at the upper and lower ends of thissleeve 651. Around thesleeve 651 between these two insulatingwashers 652 there is wound a thin insulating film (not shown in the drawings) made of resin (for example cellophane, nylon film) or paper, and around that insulating film is wound a predetermined number of turns of a thin enamel wire, whereby the attractingcoil 650 is constituted. - The
plunger 610 is made of a magnetic metal (for example, iron) and has a substantially cylindrical shape comprising an uppersmall diameter portion 613 and a lowerlarge diameter portion 614. The lower end of thecompression coil spring 660 is fitted to thesmall diameter portion 613, and thelarge diameter portion 614, which is relatively long in the axial direction, is held slidably vertically in thesleeve 651. - A
plunger shaft 615 extending upward from theplunger 610 is fixed to the upper end of theplunger 610. Thisplunger shaft 615 projects upward through a through hole provided in thestationary core 642. An uppermovable contact 612 is fitted around theplunger shaft 615 above thestationary core 642 slidably vertically along theplunger shaft 615. - This upper
movable contact 612, as shown in Fig. 9, is limited by a stoppingring 616 fitted to the upper end of theplunger shaft 615 so that it does not move upward of the upper end of theplunger shaft 615. As a result, the uppermovable contact 612 is vertically slidable along theplunger shaft 615 between the stoppingring 616 and thestationary core 642. The uppermovable contact 612 is urged upward at all times by acontact pressure spring 670 consisting of a sheet plate spring fitted to theplunger shaft 615. - The upper
movable contact 612 is made of a metal such as copper having excellent conductivity, and when both ends of the uppermovable contact 612 move upward they abut with the 2 abuttingportions 631 of the fixedcontact 630. The lead wires 91oa of a pair ofbrushes 910 are electrically and mechanically fixed to the uppermovable contact 612 by caulking or welding or the like. Also, the end portion of aresistor member 617 constituting a plurality of (in this embodiment, 2) limiting means is inserted and electrically and mechanically fixed in a groove portion of the uppermovable contact 612. - The
lead wires 910a are electrically and mechanically fixed to the uppermovable contact 612 by caulking or welding, but the uppermovable contact 612 and thelead wires 910a of thebrushes 910 may alternatively be formed integrally. - The
resistor member 617 is for rotating themotor 500 at low speed when the starter starts to operate, and consists of a metal wire of high resistance wound through several turns. A lowermovable contact 611 located below thehead portion 621 of theterminal bolt 620 is fixed by caulking or the like to the other end of theresistor member 617. - The lower
movable contact 611 is made of a metal such as copper having excellent conductivity, and when themagnet switch 600 stops and theplunger 610 is in its downward position abuts the upper face of thestationary core 642, when theresistor member 617 moves upward along with the movement of theplunger shaft 615, before the uppermovable contact 612 abuts the abuttingportion 631 of the fixedcontact 630 it abuts thehead portion 621 of theterminal bolt 620. - The lower face of the
plunger 610 is provided with arecess portion 682 which accommodates asphere 681 provided at the rear end of the cord-shaped member 680 (for example, a wire). Afemale thread 683 is formed on the inner wall of thisfemale thread 683. A fixingscrew 684 which fixes thesphere 681 in therecess portion 682 is screwed into thisrecess portion 682. This fixingscrew 684 is also used to perform adjustment of the length of the cord-shapedmember 680, by adjusting the extent to which the fixingscrew 684 is screwed into thefemale thread 683. The length of the cord-shapedmember 680 is adjusted so that when theplunger shaft 615 moves upward and the lowermovable contact 611 abuts theterminal bolt 620 the return/rotation regulating claw 231 of the regulatingportion 232 mates with the convexes/concaves 214 of the outer periphery of thepinion 200. Thefemale thread 683 and the fixingscrew 684 constitute an adjusting mechanism. - The
end frame 700, as shown in Fig. 11, is a magnet switch cover made of resin (for example phenol resin), and accommodates themagnet switch 600. -
Spring holding pillars 710 which holdcompression coil springs 914 which urge thebrushes 910 forward are mounted projecting from the rear face of theend frame 700 in correspondence with the positions of thebrushes 910. - Also, the compression coil springs 914, as shown in Fig. 1, are disposed radially outward with respect to the axial direction of the
plunger 610 of themagnet switch 600. - The
compression coil spring 914 can be used to the extent that its spring length becomes the radial length of themagnet switch 600. For this reason, the spring stress and load of the thecompression coil spring 914 can be set to appropriate values with ease, resulting in prolonged life of thecompression coil spring 914. - The
terminal bolt 620 is a steel bolt which passes through theend frame 700 from the inside and projects from the rear of theend frame 700 and has at its front end ahead portion 621 which abuts the inner face of theend frame 700. Theterminal bolt 620 is fixed to theend frame 700 by acaulking washer 622 being attached to theterminal bolt 620 projecting rearward of theend frame 700. - A copper fixed
contact 630 is fixed to the front end of theterminal bolt 620 by caulking. The fixedcontact 630 has one or a plurality of (in this embodiment, 2) abuttingportions 631 positioned at the top end of the inside of theend frame 700, and these abuttingportions 631 are mounted so that the upper face of the uppermovable contact 612 which is moved up and down by the operation of themagnet switch 600 can abut with the lower faces of the abuttingportions 631. - The
brush holder 900, as well as the roles of separating the inside of theyoke 501 and the inside of theend frame 700 and rotatably supporting the rear end of thearmature shaft 510 by way of the brush holder bearing 564, also fulfills the role of a brush holder, the role of holding themagnet switch 600, and the role of holding apulley 690 which guides the cord-shapedmember 680. Thebrush holder 900 has a hole portion not shown in the drawings through which the cord-shapedmember 680 passes. - The
brush holder 900 is a spacing wall made of a metal such as aluminum molded by a casting method and, as shown in Fig. 12 through Fig. 14, has a plurality of (in this embodiment, 2 upper and 2 lower)brush holding holes brushes 910 in the axial direction. The upperbrush holding holes 911 are holes which hold brushes 910 which receive a plus voltage, and these upperbrush holding holes 911 hold thebrushes 910 by way of resin (for example nylon, phenol resin) insulating cylinders 913 (Fig. 13 is a cross-section taken along A-A of Fig. 12, and Fig. 14 is a cross-section taken along B-B of Fig. 12). The lowerbrush holding holes 912 are holes which hold brushes 910 connected to earth, and these lowerbrush holding holes 912 hold therespective brushes 910 directly therein. - In this way, by holding the
brushes 910 by means of thebrush holder 900, there is no need to provide the starter with independent brush holders. As a result, the number of parts in the starter can be reduced and assembly man-hours can be reduced. - The
brushes 910 are urged against the upper layer coil ends 534 at the rear ends of the armature coils 530 by the compression coil springs 914. - The
lead wires 910a of theupper brushes 910 are electrically and mechanically joined by a joining method such as welding or caulking to the uppermovable contact 612 which is moved by themagnet switch 600. Thelead wires 910a of thelower brushes 910 are caulked and thereby electrically and mechanically joined to aconcave portion 920 formed in the rear face of thebrush holder 900. - Two
seats 930 with which the front side of themagnet switch 600 abuts and two fixingpillars 940 which hold the periphery of themagnet switch 600 are formed on the rear side of thebrush holder 900. - The
seats 930 are shaped to match the external shape of themagnet switch 600 in order to abut with themagnet switch 600, which has a cylindrical exterior. The two fixingpillars 940, with themagnet switch 600 in abutment with theseats 930, by having their rear ends caulked to the inner side, hold themagnet switch 600. - A
pulley holding portion 950 which holds apulley 690 which converts the direction of movement of the cord-shapedmember 680 from the vertical direction of themagnet switch 600 into the axial direction thereof is formed on the lower side of the rear side of thebrush holder 900. - On the rear face of the
brush holding member 900, a holdingportion 960 is provided for holding an over-temperature protecting temperature switch (not shown). The temperature switch turns off themagnet switch 600 at a predetermined temperature and stops motor operation, thereby protecting the starter. - In the starter, air passages are formed for discharging the air outside in the manner that the centrifugal air flow is generated by the rotation of upper coil ends 534 positioned on the rear side of the armature coil 530, the air sucked through the housing is taken into the
end frame 700 through an opening (indicated by numeral 980) of thebrush holding member 900, thereafter the air is led to the rear side of the armature coil 530 through an opening (indicated by numeral 970) of thebrush holding member 900 to cool the sliding surface of the brushes and peripheries, and finally the air is discharged with brush powders generated on the sliding surfaces through adischage hole 503 formed on the bottom of theyoke 501. - Next, the operation of the starter described above will be explained with reference to the electrical circuit diagrams of Figs. 15A through 15C.
- When a
key switch 10 is set to the start position by a driver, electricity flows from thebattery 20 to the attractingcoil 650 of themagnet switch 600. When current flows through the attractingcoil 650, theplunger 610 is pulled by the magnetic force produced by the attractingcoil 650, and theplunger 610 ascends from its lower position to its upper position. - When the
plunger 610 starts to ascend, together with the ascent of theplunger shaft 615 the uppermovable contact 612 and the lowermovable contact 611 ascend, and the rear end of the cord-shapedmember 680 also ascends. When the rear end of the cord-shapedmember 680 ascends, the front end of the cord-shapedmember 680 is pulled down, and the regulatingportion 232 descends. When the descent of the regulatingportion 232 causes the return/rotation regulating claw 231 to mate with the convexes/concaves 214 of the periphery of thepinion 200, the lowermovable contact 611 abuts thehead portion 621 of the terminal bolt 620 (see Fig. 15A). - The voltage of the
battery 20 is impressed on theterminal bolt 620, and the voltage of theterminal bolt 620 is transmitted through the lowermovable contact 611 → theresistor member 617 → the uppermovable contact 612 → thelead wires 910a to the upper brushes 910. That is, the low voltage passing through theresistor member 617 is transmitted through theupper brushes 910 to the armature coils 530. Because thelower brushes 910 are constantly grounded through thebrush holder 900, a current flows at low voltage through the armature coils 530 constituted in coil form by the paired upper layer coil bars 531 and lower layer coil bars 532. When this happens, the armature coils 530 generate a relatively weak magnetic force, this magnetic force acts on (attracts or repels) the magnetic force of the fixedpoles 550, and thearmature 540 rotates at low speed. - When the
armature shaft 510 rotates, theplanetary gears 320 of the planetary gearspeed reduction mechanism 300 are rotationally driven by thesun gear 310 on the front end of thearmature shaft 510. When theplanetary gears 320 exert a rotational torque through theplanet carrier 330 on the internal gear 340 in the direction which rotationally drives thering gear 100, the rotation of the internal gear 340 is limited by the operation of the overrunningclutch 350. That is, because the internal gear 340 does not rotate, the rotation of theplanetary gears 320 causes theplanet carrier 330 to rotate at low speed. When theplanet carrier 330 rotates, thepinion 200 also rotates, but because thepinion 200 has its rotation limited by the return/rotation regulating member 230 thepinion 200 advances along thehelical spline 221 on theoutput shaft 220. - Together with the advance of the
pinion 200, theshutter 420 also advances, and opens theopening portion 410 of thehousing 400. The advance of thepinion 200 causes thepinion gear 210 to mesh completely with thering gear 100 and then abut with the pinion stopping ring 250. Also, when thepinion 200 advances thus, the regulatingclaw 231 disengages from the convexes/concaves 214 of thepinion 200 and after that the front end of the regulatingclaw 231 drops to the rear side of thethrust bearing 215 disposed on the rear side of thepinion 200 so that the regulatingclaw 231 stops return of thepinion 200 to the rearward direction. - With the
pinion 200 advanced, the uppermovable contact 612 abuts the abuttingportion 631 of the fixedcontact 630. When this happens, the battery voltage of theterminal bolt 620 is directly transmitted through the uppermovable contact 612 → thelead wires 910a to the upper brushes 910. That is, a high current flows through the armature coils 530 consisting of the upper coil bars 531 and the lower coil bars 532, the armature coils 530 generate a strong magnetic force and thearmature 540 rotates at high speed. - The rotation of the
armature shaft 510 is slowed and has its rotational torque increased by the planetary gearspeed reduction mechanism 300 and rotationally drives theplanet carrier 330. At this time, the front end of thepinion 200 abuts the pinion stopping ring 250 and thepinion 200 rotates integrally with theplanet carrier 330. Because thepinion gear 210 of thepinion 200 is meshing with thering gear 100 of the engine, thepinion gear 210 rotationally drives thering gear 100 and rotationally drives the output shaft of the engine. - Next, when the engine starts and the
ring gear 100 of the engine rotates faster than the rotation of thepinion 200, the action of the helical spline creates a force tending to retract thepinion 200. However, the regulatingclaw 231 which has dropped to behind thepinion 200 prevents thepinion 200 from retracting, prevents early disengagement of thepinion 200, and enables the engine to be started surely (see Fig. 15B). - When the engine starting causes the
ring gear 100 to rotate faster than the rotation of thepinion 200, the rotation of thering gear 100 rotationally drives thepinion 200. When this happens, the rotational torque transmitted from thering gear 100 to thepinion 200 is transmitted through theplanet carrier 330 to thepins 332 which support theplanetary gears 320. That is, theplanetary gears 320 are driven by theplanet carrier 330. When this happens, because a torque rotationally opposite to that during engine starting is exerted on the internal gear 340, the overrunningclutch 350 allows the rotation of thering gear 100. That is, when a torque rotationally opposite to that during engine starting is exerted on the internal gear 340, the roller 353 of the overrunningclutch 350 detaches to outside theconcave portion 355 of the clutch inner 352 and rotation of the internal gear 340 becomes possible. - In other words, the relative rotation with which the
ring gear 100 rotationally drives thepinion 200 when the engine starts is absorbed by the overrunningclutch 350, and thearmature 540 is never rotationally driven by the engine. - When the engine starts, the driver releases the
key switch 10 from the start position and the flow of current to the attractingcoil 650 of themagnet switch 600 is stopped. When the flow of current to the attractingcoil 650 stops, theplunger 610 is returned downward by the action of thecompression coil spring 660. - When this happens, the upper
movable contact 612 moves away from the abuttingportion 631 of the fixedcontact 630, and after that the lowermovable contact 611 also moves away from thehead portion 621 of theterminal bolt 620, and the flow of current to theupper brushes 910 is stopped. - When the
plunger 610 is returned downward, the action of thereturn spring portion 233 of the return/rotation regulating member 230 causes the return/rotation regulating claw 231 to return upward, and the return/rotation regulating claw 231 moves away from the rear of thepinion 200. When this happens, thepinion 200 is returned rearward by the action of thereturn spring 240, the meshing of thepinion gear 210 with thering gear 100 of the engine is disengaged, and the rear end of thepinion 200 abuts the taperedportion 222 of theoutput shaft 220. That is, thepinion 200 is returned to the position it was in before the starter was started (see Fig. 15C). - Also, the
plunger 610 being returned downward causes the lowermovable contact 611 to abut with the upper face of thestationary core 642 of themagnet switch 600, and the lead wires of theupper brushes 910 conduct electrical current in the order the uppermovable contact 612 → theresistor member 617 → the lowermovable contact 611 → thestationary core 642 → themagnet switch cover 640 → thebrush holder 900. In other words, theupper brushes 910 and thelower brushes 910 short-circuit through thebrush holder 900. Meanwhile, inertial rotation of thearmature 540 generates an electromotive force in the armature coils 530. Because this electromotive force is short-circuited through theupper brushes 910, thebrush holder 900 and thelower brushes 910, a braking force is exerted on the inertial rotation of thearmature 540. As a result, thearmature 540 rapidly stops. - In the state in which the return/
rotation regulating claw 231 is positioned rearward thepinion 200 and the return of thepinion 200 from thering gear 100 is regulated, thethrust bearing 215 absorbs the difference between the rotational speed of thepinion 200 and that of the return/rotation regulating claw 231. Because the rotation of thepinion 200 is absorbed by thethrust bearing 215, and the rotation torque of thepinion 200 is prevented from being transmitted to the return/rotation regulating claw 231, generation of wear, heat, and rotation loss between thepinion 200 and return/rotation regulating claw 231 can be prevented. Further, when thepinion 200 is driven by thering gear 100 and rotates at a higher speed than theoutput shaft 220 and consequently the force for moving thepinion 200 rearward is applied to thepinion 200 due to the difference in the rotational speeds, a great load is applied between thepinion 200 and the return/rotation regulating claw 231. Thethrust bearing 215, however, absorbs the difference between the rotational speeds, the generation of wear, heat, and rotation loss between thepinion 200 and return/rotation regulating claw 231 can be prevented, which allows the performance of the starter to be maintained for a long time. - In this embodiment, because the
thrust bearing 215 comprises anorbital ring 216 and a rolling bearing composed of theorbital ring 216 and a plurality ofspheres 217, the rotational force is transmitted to the return/rotation regulating claw 231 at a very small degree. Thus, even though the return/rotation regulating claw 231 having a low rigidity is used, there is no disadvantage that the return/rotation regulating claw 231 is damaged by the engagement into the rotation of thepinion 200. Moreover, because the rigidity of the return/rotation regulating claw 231 is allowed to be low, the force of themagnet switch 600 for operating the return/rotation regulating claw 231 can be reduced and hence, themagnet switch 600 can be allowed to be compact and light. - According to this embodiment, the
pinion 200 can be moved in the axial direction of theoutput shaft 220 which drives thepinion 200, and the weight of the moving member (pinion 200 + thrust bearing 215) can be allowed to be smaller by about 1/5 than that of the conventional moving member (pinion + pinion shaft). Further, because thepinion 200 can be moved axially by utilizing the rotational force of themotor 500, the force required for themagnet switch 600 is the force for operating themovable contacts rotation regulating claw 231. Thus, the force to be generated by themagnet switch 600 is much smaller than that to be generated by the conventional one. Therefore, themagnet switch 600 can be made smaller and lighter than the conventional one. - In addition, because the weight of the moving member can be allowed to be smaller by about 1/5 than that of the conventional one, the energy for moving the
pinion 200 can be allowed to be smaller than that for moving the conventional one. Because of this, the energy required for actuating the starter can be reduced and hence, the load to be applied to a power unit (lead storage battery, electric double-layer capacitor or the like) for driving the starter can be reduced. Consequently, the power unit can be allowed to be smaller and have a longer life than the conventional one. - Moreover, because the weight of the moving member can be allowed to be smaller by about 1/5 than that of the conventional one, the shock generated when the
pinion 200 engages thering gear 100 can be reduced. - The
pinion 200 is heat-treated after thethrust bearing 215 is mounted thereon. Therefore, it is unnecessary to subject theorbital ring 216 of the thrust bearing 215 to heat treatment separately, which eliminates the need for a process of increasing the hardness of theorbital ring 216 to more than a predetermined value. - Further, the return/
rotation regulating claw 231 is positioned rearward thepinion 200 because it exceeds the expansion force of thereturn spring portion 233 by the movement force of theplunger 610 of themagnet switch 600. Thus, when themagnet switch 600 is turned off, the return/rotation regulating claw 231 can be securely disengaged from the rear portion of thepinion 200 owing to the expansion force of thereturn spring 233. - Fig. 16 is a sectional view of a starter according to a second embodiment.
- While in the first embodiment the
magnet switch 600 is positioned rearward themotor 500 and theplunger 610 is positioned in a direction orthogonal to thearmature shaft 510 of themotor 500, in a starter of the second embodiment, amagnet switch 600 is positioned below amotor 500 with its plunger being positioned in a direction parallel with anarmature shaft 510 of themotor 500. - Fig. 17 shows a third embodiment in a sectional view of a
pinion 200 having athrust bearing 215 mounted thereon. - In the abovedescribed first and second embodiments, the pinion gear 210 (outer teeth) is formed on the peripheral face of one member and the helical inner spline 211 (inner teeth) is formed on the inner peripheral face thereof. Unlike the first and second embodiments, in a
pinion 200 of the third embodiment, a pinioninner member 200a provided with a helicalinner spline 211 on the inner peripheral face thereof and a pinionouter member 200b provided with apinion gear 210 on the peripheral face thereof are separately produced, and then nonrotatably fixed with each other. As an example of a method of fixing the twomembers inner member 200a and the pinionouter member 200b or welding method may be used. - In the first and second embodiments, it is difficult to form both the
pinion gear 210 and the helicalinner spline 211 on one member by cold forging. Thus, in the first and second embodiments, thepinion gear 210 which is the external teeth has to be formed by machining. In this third embodiment, however, those can be formed by cold forging, respectively, which results in a reduction in manufacturing cost. - Furthermore, the pinion
inner member 200a can be connected with many kinds of pinionouter members 200b. Therefore, many kinds ofpinions 200 can be manufactured by preparing many kinds of pinionouter members 200b. That is, in the case of thepinion 200, many kinds of specifications are required according to the specification of the engine, whereas in the case of the helicalinner spline 211, only one kind or a few kinds of specifications are required. Thus, many kinds ofpinions 200 can be manufactured in combination of the pinioninner member 200a and the pinionouter member 200b provided separately, which provides many kinds of starters corresponding to many kinds of engines. Further, the pinioninner member 200a can be mass-produced, which leads to the production of thepinion 200 in low cost. - The
pinion 200 of this embodiment is heavier than that of the first and second embodiments because of a cold forging-causedshear droop portion 210a of the pinionouter member 200b, but the weight of thepinion 200 of this embodiment is much lighter than that of the conventional pinion moving member. Thus, the third embodiment can provide the similar operation and effect as in the first embodiment. - Figs. 18 through 21 show a fourth embodiment in which a rotation regulating member and a return regulating member are provided separately.
- The construction of the return regulating member of this embodiment is different from that of the return regulating member of the first embodiment. The construction of the return regulating member of this embodiment will be described below.
- A return regulating member 260 (corresponding to return regulating means) comprises an annular portion 262 (Fig. 19) having a
circular hole 261 formed at the center thereof to receive anoutput shaft 220 therethrough;side portions 263 bent at right angle to theannular portion 262 at both sides thereof; and apivotal support 264 pivotably supported by a supportingpin 270 fixed to acenter bracket 360. Thereturn regulating member 260 is constructed by mating the supportingpin 270 with a hole 265 (Fig. 20) formed on thepivotal support 264 and by mating anengaging pin 281 provided on athrust ring 280 with aslot 266 formed on theside portion 263, so that thereturn regulating member 260 is rotatable or pivotable around the supportingpin 270. - The
return regulating member 260 is pressed toward aplate 290 by aspring 271 mating with the supportingpin 270. That is, thespring 271 presses thepinion 200 rearward (toward the plate 290) through thereturn regulating member 260, thus maintaining a stationary state and contributing to preventing thepinion 200 from moving forward when the engine is started. - As shown in Fig. 20, the
rotation regulating member 230 of this embodiment is formed of a circular rod-shaped metal material, and both ends thereof are bent perpendicularly in the same direction at opposite positions in a radial direction thereof. One end of the bent portion serves as arotation regulating bar 231 which engages convexes/concaves 214 of thepinion 200 to stop rotation of thepinion 200 at an initial time in the actuation of the starter, whereas one end of a cord-shapedmember 680 engages theother end 231b of therotation regulating member 230 to transmit the operation of themagnet switch 600 therethrogh. Further, as shown in Fig. 21, when thereturn regulating member 260 is inclined axially by a forward movement of thepinion 200, therotation regulating bar 231 enters into a rear portion of theannular portion 262 of thereturn regulating member 260, thus maintaining the posture of thereturn regulating member 260 by supporting an end of theannular portion 262. - The operation of this embodiment is described below.
- Similarly to the first embodiment, when a starter switch is turned on, the
magnet switch 600 is actuated, and consequently, therotation regulating bar 231 of therotation regulating member 230 engages the convexes/concaves 214 of thepinion 200, thus regulating the rotation of thepinion 200. - Receiving the rotational force of the
starter motor 500, theoutput shaft 220 rotates and the rotation-regulatedpinion 200 advances on the helical spline. As a result, thepinion 200 engages thering gear 100 to start the engine. - As shown in Fig. 21, at this time, the
return regulating member 260 biased by thespring 271 is inclined axially around the supportingpin 270 by the advance of thepinion 200, with theengaging pin 281 mounted on thethrust ring 280 and theslot 266 formed on theside portion 263 engaging each other. - When the
pinion 200 engages thering gear 100 completely, the leading end of therotation regulating bar 231 disengages from the convexes/concavee 214 of thepinion 200 and is placed at the rear side of thethrust ring 280, thus permitting the rotation of thepinion 200 and supporting the rear end of thereturn regulating member 260. Therefore, the posture of thereturn regulating member 260 inclined axially by being pulled by thethrust ring 280 is maintained. - Owing to the above, when the
pinion 200 is rotated by thering gear 100 and a retraction force is applied to thepinion 200, the retraction of thepinion 200 can be prevented by the cooperation of thereturn regulating member 260 and therotation regulating member 230. - Thereafter, when the starter switch is turned off, the
rotation regulating member 230 is raised up in Fig. 21 and returned to the original position by the force of the return spring. As a result, the leading end of therotation regulating bar 231 disengages from the rear end of thereturn regulating member 260, thus returning thepinion 200 to the stationary state (Fig. 18.) together with thereturn regulating member 260. - In this embodiment, the
return regulating member 260 is rotatably mounted relative to thepinion 200 through thethrust ring 280, and the rotational force of thepinion 200 is not applied to therotation regulating bar 231 supporting the rear end of thereturn regulating member 260. Therefore, therotation regulating bar 231 is prevented from being bent or worn. Further, because theside portions 263 of thereturn regulating member 260 contact the rear end face of thethrust ring 280 at both positions in a radial direction thereof, thepinion 200 is supported by two points. Owing to this, thepinion 200 can be prevented from being inclined with respect to theoutput shaft 220 and hence, a reliable operation can be provided. - Although in each of the embodiments only the
pinion 200 engages the helicalouter spline 221 of theoutput shaft 220, it is possible to design a starter to have a pinion moving member composed of thepinion 200 and separate functional parts (for example, one-way clutch or the like) mounted thereon and engageable with the helicalouter spline 221 of theoutput shaft 220. - Other modifications and alterations are of course possible for those skilled in the art without departing from the spirit and scope of the invention.
Claims (9)
- A starter comprising:a pinion (210) engageable with a ring gear (100) of an engine;a starter motor (500) for generating a rotational force to be transmitted to the pinion;pinion moving member (200) for moving the pinion to a ring gear side;return regulating means (230, 260) for regulating a return of the pinion from the ring gear when the pinion has engaged the ring gear through the pinion moving member; andabsorbing means (215) provided between the pinion moving member and the return regulating means and absorbing a difference between a rotational speed of the pinion and that of the return regulating means, the absorbing means excluding a sliding-type bearing.
- A starter comprising:an output shaft (220) having a helical spline (221) thereon;a pinion moving member (200) having a pinion (210) engageable with a ring gear (100) of an engine and mounted axially movably through an engagement with the helical spline of the output shaft;a motor (500) for driving the output shaft, said motor moving the pinion to a ring gear side by a difference of rotational speed relative to the pinion moving member to engage the pinion with the ring gear;return regulating means (230, 260) for regulating a return of the pinion from the ring gear when the pinion has engaged the ring gear; andabsorbing means (215) provided between the pinion moving member and the return regulating means and absorbing a difference between a rotational speed of the pinion and that of the return regulating means, the absorbing means excluding a sliding-type bearing.
- A starter according to claims 1 or 2, wherein said absorbing means is a torque-reduction suppressing means for preventing loss of rotational torque in spite of a difference between a rotational speed of the pinion and that of the return regulating means.
- A starter according to claim 1 or 2, wherein:the absorbing means includes a rolling bearing (216-218) provided on the pinion moving member.
- A starter according to any one of claims 1 through 4, further comprising:rotation regulating means (230) for regulating a rotation of the pinion by contacting therewith, the rotation regulating means being adapted to move into a position adjacent to the pinion and opposite to the pinion when the pinion moves to the ring gear side by a predetermined distance, thus acting as the return regulating means for regulating the return of the pinion from the ring gear.
- A starter according to any one of claims 1 through 5, wherein:the pinion moving member includes;a pinion inner member (200a) engaged with the helical spline of the output shaft, anda pinion outer member (200b) having a pinion gear rotatable integrally with the pinion inner member.
- A starter according to any one of claims 1 through 4, further comprising:
- A starter according to claim 7, wherein:the return regulating means is pivotably supported and coupled with the pinion to be movable therewith.
- A starter according to claim 8, wherein:the return regulating means has a plurality of sides (263) contacting the pinion moving means at a plurality of locations around a central axis of the pinion moving member.
Applications Claiming Priority (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11211995 | 1995-05-10 | ||
JP112119/95 | 1995-05-10 | ||
JP11211995 | 1995-05-10 | ||
JP12167895 | 1995-05-19 | ||
JP12167895 | 1995-05-19 | ||
JP121678/95 | 1995-05-19 | ||
JP61363/96 | 1996-03-18 | ||
JP6136396 | 1996-03-18 | ||
JP06136396A JP3578184B2 (en) | 1995-05-19 | 1996-03-18 | Starter |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0742368A1 true EP0742368A1 (en) | 1996-11-13 |
EP0742368B1 EP0742368B1 (en) | 1999-07-28 |
Family
ID=27297477
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96107370A Expired - Lifetime EP0742368B1 (en) | 1995-05-10 | 1996-05-09 | Starter with pinion return preventing mechanism |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0742368B1 (en) |
DE (1) | DE69603408T2 (en) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1330326A (en) * | 1919-04-09 | 1920-02-10 | Eclipse Machine Co | Engine-starter |
US1527588A (en) * | 1915-05-13 | 1925-02-24 | Eclipse Machine Co | Gearing for starting internal-combustion engines |
EP0091689A1 (en) * | 1982-04-13 | 1983-10-19 | Hitachi, Ltd. | A starter apparatus |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2332986A (en) * | 1942-07-02 | 1943-10-26 | Bendix Aviat Corp | Engine starting device |
-
1996
- 1996-05-09 EP EP96107370A patent/EP0742368B1/en not_active Expired - Lifetime
- 1996-05-09 DE DE1996603408 patent/DE69603408T2/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1527588A (en) * | 1915-05-13 | 1925-02-24 | Eclipse Machine Co | Gearing for starting internal-combustion engines |
US1330326A (en) * | 1919-04-09 | 1920-02-10 | Eclipse Machine Co | Engine-starter |
EP0091689A1 (en) * | 1982-04-13 | 1983-10-19 | Hitachi, Ltd. | A starter apparatus |
Also Published As
Publication number | Publication date |
---|---|
DE69603408T2 (en) | 2000-04-13 |
EP0742368B1 (en) | 1999-07-28 |
DE69603408D1 (en) | 1999-09-02 |
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