WO2016175135A1 - Internal gear and reduction gear comprising same - Google Patents
Internal gear and reduction gear comprising same Download PDFInfo
- Publication number
- WO2016175135A1 WO2016175135A1 PCT/JP2016/062699 JP2016062699W WO2016175135A1 WO 2016175135 A1 WO2016175135 A1 WO 2016175135A1 JP 2016062699 W JP2016062699 W JP 2016062699W WO 2016175135 A1 WO2016175135 A1 WO 2016175135A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear
- main body
- internal gear
- tooth
- resin
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
- F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
Definitions
- the present invention relates to an internal gear and a speed reducer having the internal gear.
- a starter used for starting an automobile engine inputs an output of a motor to an overrunning clutch (hereinafter simply referred to as a clutch) via a reduction gear, and a pinion gear attached to an output shaft of the clutch by switching an electromagnetic switch.
- a clutch an overrunning clutch
- a configuration is adopted in which the pinion gear is engaged and disengaged with respect to the ring gear on the engine side by reciprocating in the axial direction.
- a reduction gear used for a starter a planetary gear mechanism having a sun gear driven by a motor, a ring gear fixed to a stationary side, and a planetary gear that meshes with both the sun gear and the ring gear to rotate and revolve may be used.
- a ring gear an internal gear (internal gear) having a tooth surface on the inner periphery is usually used.
- an internal gear of a starter planetary gear mechanism for example, a resin internal gear described in Japanese Patent Application Laid-Open No. 2007-77810 (Patent Document 1) is known. As shown in FIG. 6, the resin internal gear 100 is fixed to the inner peripheral surface of the center case 101.
- the output shaft 104 of the eaves speed reducer 103 needs to be rotatably supported at its shaft end with respect to a stationary member (for example, the center case 101).
- a stationary member for example, the center case 101.
- the inner diameter end of the center case 101 holding the internal gear 100 is extended in the axial direction to form a shaft support portion 105.
- the output shaft 104 of the speed reducer 103 is rotatably supported by a slide bearing 106 press-fitted and fixed to the inner periphery of the shaft support portion 105.
- an object of the present invention is to increase the durability of the internal gear for the speed reducer while minimizing the increase in cost and weight.
- the present invention is an internal gear incorporated in a speed reducer and having a tooth surface on the inner periphery, and a ring-shaped gear portion having the tooth surface and an output shaft of the speed reducer And a main body portion having an outer peripheral portion for holding the outer periphery of the gear portion, the gear portion is formed of sintered metal, and the main body portion is made of resin using the gear portion as an insert part. It is characterized by being formed of a molded body formed by injection molding.
- the gear portion is formed of sintered metal in this way, the fatigue resistance and mechanical strength of the tooth surface can be improved as compared with the case of forming the gear portion.
- the main body is formed of resin
- the internal gear can be reduced in cost and weight.
- the center case 101 having a complicated shape as required in Patent Document 1 (see FIG. 6) is not required, and the weight and cost are reduced. This is even more advantageous for achieving the above.
- the outer peripheral portion for holding the outer periphery of the gear portion is provided in the main body portion, after the main body portion is injection-molded, the outer peripheral portion is pressed against the outer peripheral surface of the gear portion by molding shrinkage when cooled and solidified. And the bonding strength of the main body can be strengthened. Therefore, the durability life of the internal gear can be increased while suppressing an increase in weight and cost.
- the surface porosity of the surface that contacts the main body is made larger than the surface porosity of the tooth surface, or the open porosity of the part of the gear that contacts the main body is determined by the tooth part. If it is larger than the open porosity, the coupling force between the gear part and the main body part can be increased by the anchor effect by the resin that has entered the surface pores. On the other hand, the fatigue resistance and mechanical strength of the tooth surface can be increased.
- the surface area ratio of the surface that contacts the main body portion is preferably 10% or more and 50% or less. Moreover, it is preferable that the surface aperture ratio of the tooth surface of the gear portion is 40% or less.
- the open porosity of the part in contact with the main body part is preferably 10% or more and 50% or less. The open porosity of the gear teeth is preferably 40% or less.
- this reduction gear is a reduction gear having an internal gear of more than, its durability life can be increased while avoiding an increase in weight and cost of the reduction gear. Further, if this reduction gear is used for a starter of a vehicle equipped with an idling stop mechanism, early replacement of the reduction gear and the starter can be prevented, and the maintenance cost of the vehicle can be reduced.
- Fig. 1 shows a simplified configuration of a typical starter ST.
- the starter ST includes a motor 4, a speed reducer 5, an overrunning clutch 6 (hereinafter simply referred to as a clutch), a pinion gear 7, a lever 8, and an electromagnetic switch 9 as main components. It is.
- the lever 8 is rotatable about a fulcrum O, and the tip thereof is disposed on the input side (motor 4 side) of the overrunning clutch 6.
- the overrunning clutch 6 is a one-way clutch, and an output shaft 5a (reduction gear output shaft) of the speed reducer 5 is coupled to an input side of the overrunning clutch 6 through a spline or the like so as to be slidable in the axial direction.
- a pinion gear 7 is attached to the output shaft 6 a (clutch output shaft) of the clutch 6. Therefore, the clutch 6 can move in the axial direction integrally with the clutch output shaft 6 a and the pinion gear 7.
- the reduction gear 5 and the clutch 6 are disposed inside a first case 11 as a gear case, and the motor 4 is disposed inside a second case 12 as a motor case.
- the first case 11 and the second case 12 are connected by an appropriate connection structure such as a bolt.
- the electromagnetic switch 9 When an engine start command is input, the electromagnetic switch 9 is turned on to apply a rotational force in the direction of the arrow in the drawing to the lever 8, and the clutch 6, the clutch output shaft 6a, and the pinion gear 7 are integrated into the shaft. Move to the opposite side of the motor 4 in the direction. As a result, the pinion gear 7 meshes with the ring gear 10 coupled to the crankshaft of the engine. Further, the motor 4 is driven, and the output torque is transmitted to the pinion gear 7 via the speed reducer 5 and the clutch 6. As a result, the motor output is transmitted to the crankshaft via the ring gear 10 and the engine is started.
- the electromagnetic switch 9 is turned off, the clutch 6 and the pinion gear 7 are retracted, and the pinion gear 7 is disengaged from the meshing position with the ring gear 10.
- the engine torque immediately after starting the engine is not transmitted to the motor 4 because it is interrupted by the clutch 6.
- FIG. 2 shows a typical configuration example of the speed reducer 5 used in the starter ST.
- the speed reducer 5 is a planetary gear mechanism, and includes a sun gear 51 made of an external gear disposed on an axis O, an internal gear 52 fixed to a stationary member, a planetary gear 53 made of an external gear, and a planetary gear. And a plate-like carrier 54 that supports 53.
- the planetary gear 53 is disposed between the sun gear 51 and the internal gear 52 and is in mesh with both the gears 51 and 52.
- An output shaft 4a of the motor 4 is coupled to the sun gear 51 through a serration 61 (including splines; the same applies hereinafter) so as to transmit torque.
- the planetary gears 53 are arranged at a plurality of locations (for example, 3 locations) equally distributed in the circumferential direction.
- a pin 55 having one end fitted and fixed to a hole in a plate-like carrier 54 is inserted into the inner periphery of each planetary gear 53, and each planetary gear 53 is arranged on the inner periphery thereof.
- a sliding bearing 56 is supported so as to be rotatable with respect to the pin 55.
- the reduction gear output shaft 5 a is inserted into the inner periphery of the carrier 54, and the reduction gear output shaft 5 a and the carrier 54 are coupled via a serration 62 so that torque can be transmitted.
- one end (for example, the motor output shaft 4a) of the output shaft 4a of the motor 4 and the output shaft 5a of the speed reducer is formed at the shaft end of the other (for example, the speed reducer output shaft 5a).
- the shafts 4a and 5a can be rotated relative to each other in a coaxial state.
- a shielding plate 65 having an inner diameter end close to the outer peripheral surface of the output shaft 4a of the motor 4 is arranged. Intrusion of foreign matter into the speed reducer 5 is prevented.
- the internal gear 52 includes a gear portion 52a and a main body portion 52b.
- the gear part 52a is made of a ring-shaped sintered metal material, and a tooth part 525 having a large number of tooth surfaces 521 (see FIG. 3) is formed on the inner periphery thereof.
- the main body 52b has a substantially cylindrical shape with a reduced diameter on one axial end (on the side opposite to the motor), a large-diameter outer peripheral portion 522 that covers the outer diameter of the gear 52a, and an axial end on the one end.
- a small-diameter shaft support portion 523 extending in the axial direction at the inner diameter end, and an outer peripheral portion 522 and the shaft support portion 523 are connected to each other, and a connecting portion 524 whose diameter is gradually reduced from the outer peripheral portion 522 to the shaft support portion 523 is integrally provided.
- the end surface of the gear portion 52a and the end surface of the main body portion 52b are flush with each other.
- a carrier 54 is disposed on the inner diameter side of the connecting portion 524.
- the internal gear 52 is fixed to the stationary side (the first case 11 or the second case) by sandwiching the outer peripheral portion 522 of the main body portion 52b between the first case 11 and the second case 12 from both sides in the axial direction. .
- a rotation stopper between the main body 52b and one case (for example, the first case 11).
- a sliding bearing 64 is press-fitted and fixed to the inner peripheral surface of the shaft support portion 523 in the main body portion 52 b, and one end (motor side end portion) of the reduction gear output shaft 5 a is connected to the internal gear 52 by the sliding bearing 64. Is supported so as to be freely rotatable.
- the internal gear 52 described above is an insert part in which a gear part 52a manufactured by a powder metallurgy method is placed in a mold, and the gear part 52a is positioned in a predetermined position in the mold. It is manufactured by injecting resin and molding (insert molding) the main body 52b.
- resin and molding insert molding
- the gear part 52a is formed of an iron-based sintered body. Specifically, iron powder is the main component, a raw material powder in which copper powder and graphite powder are mixed is compressed to form a green compact, and then the green compact is sintered to form the gear portion 52a. A sintered body having a corresponding shape is obtained.
- This sintered body contains, for example, Cu: 1 to 8% by mass, C: 0.2 to 1% by mass, with the balance being Fe and inevitable impurities.
- the sintering temperature is preferably 1100 ° C. to 1150 ° C. By sintering at this temperature, the molten Cu diffuses into Fe and strengthens the bonding force between the Fe structures. Moreover, since Fe reacts with C contained in the graphite powder, the Fe structure after sintering becomes a hard pearlite phase. Therefore, the strength of the sintered body can be increased.
- the atmosphere gas of the sintering furnace is a gas containing carbon such as carbon monoxide or carbon dioxide, for example, liquefied petroleum gas such as butane gas or propane gas and air, and Ni catalyst. It is preferable to use an endothermic gas (RX gas) pyrolyzed in (1).
- RX gas endothermic gas
- Toothed surface is shaped (sizing) by plastic working on the sintered body after fired sintering.
- the portion 521 ′ corresponding to the tooth surface 521 of the gear portion 52a is formed in a rough shape, but this portion 521 ′ is formed by rolling or the like.
- the portion 521 ′ is shaped into a finished shape (indicated by a solid line) such as an involute shape, and a gear portion 52a having a tooth surface 521 on the inner periphery is completed.
- it is preferable to finish each tooth portion 525 including the tooth surface 521 by compressing in the circumferential direction and extending and deforming in the radial direction.
- the porous structure of the surface layer portion including the tooth surface 521 is densified, and pores serving as stress concentration sources in the surface layer portion are reduced. Further, the hardness of the tooth surface 521 becomes higher than that of the core portion (at this time, the hardness is maximum at the tooth surface 521, gradually decreases toward the core portion, and becomes constant when exceeding a predetermined depth). Therefore, it is possible to obtain a tooth surface 521 having excellent mechanical strength, particularly fatigue strength.
- This plastic working may be performed in any temperature range between cold, warm feeling, or hot, but is preferably performed cold considering the shaping accuracy and durability life of the tooth surface 521.
- each surface (end surface, outer peripheral surface, etc.) other than the tooth surface 521 of the gear portion 52a is also shaped.
- at least the surface of the gear portion 52a in contact with the main body portion 52b (particularly the outer peripheral surface of the gear portion 52a) is made smaller than the amount of compression at the tooth surface 521.
- the surface area ratio of the surface in contact with the main body portion 52b is larger than that of the tooth surface 521.
- the resin enters the outer peripheral surface of the gear portion 52a or the surface opening of one end surface to exert an anchor effect, so that the coupling between the gear portion 52a and the main body 52b is performed.
- Strength can be increased.
- the lower limit value of the surface area ratio of the surface (particularly the outer peripheral surface) of the gear portion 52a in contact with the main body portion 52b is 10% or more, preferably 15% or more, more preferably 20% or more.
- the open porosity of the portion of the gear portion 52a that contacts the main body portion 52b is 10% or more, preferably 15% or more, and more preferably 20% or more.
- the surface porosity or the open porosity is too large, the strength of the entire gear portion 52a is reduced. Therefore, the surface porosity is 50% or less, preferably 40% or less, and the open porosity is 50% or less, preferably 40% or less.
- the surface open area referred to here is calculated, for example, by taking an image (for example, 500 times) taken with a metal microscope such as Nikon Corporation: ECLIPSE ME600 as image data and calculating the area of the pore portion. You can ask for it.
- the open porosity is defined by JIS Z 2501: 2000.
- the open porosity of the measurement object is expressed as a percentage of the volume, and is obtained by dividing the volume of oil after complete impregnation by the volume of the measurement object and multiplying by 100.
- the surface area ratio of the tooth surface 521 is 40% or less, preferably 20% or less, more preferably 10% or less, in order to ensure the strength.
- the open porosity of the tooth portion 525 is 40% or less, preferably 20% or less, and more preferably 10% or less. If the open porosity of the tooth surface 521 is too small, the molding pressure when molding the compact must be excessively increased, which is disadvantageous in terms of cost and the like. Is preferably set to 5% or more. For the same reason, the open porosity of the tooth portion 525 is preferably set to 5% or more.
- Each of the above limit values only needs to satisfy one of the surface porosity and the open porosity. Of course, you may be satisfied with both.
- main body 52b which is a resin molded body
- any material that can be injection-molded can be used.
- the resin materials those based on polyamide resins having excellent fatigue resistance are preferred.
- the polyamide resin include polyamide 6, polyamide 66, polyamide 46, polyamide 610, polyamide 612, polyamide 11, polyamide 12, polyamide MXD, polyamide 6T, and polyamide 6I.
- a fibrous filler mix blended with these resin, carbon fiber, aromatic polyamide fiber, or a mixture thereof can be widely used besides glass fiber.
- the outer peripheral portion 522 of the main body portion 52b tends to deform in the diameter-reducing direction due to molding shrinkage that occurs at the time of solidification after injection molding, so that the anchor effect is enhanced and the gear portion 52a and the main body portion 52b are strengthened.
- the molding shrinkage rate of unfilled polyamide 6 resin is generally 0.5 to 1.5%
- the molding shrinkage rate of unfilled polyamide 66 resin is generally 0.8 to 1.5%.
- the molding shrinkage ratio of the polyamide 6 resin is generally 0.4 to 0.8%
- the molding shrinkage ratio of the polyamide 66 resin filled with glass fiber or the like is generally 0.2 to 1.0%.
- the apparent melt viscosity of the base resin is preferably in the range of 1000 poise to 10,000 poise. If the apparent melt viscosity is lower than the lower limit value, there remains anxiety about the strength of the main body 52b. On the other hand, if the apparent melt viscosity is higher than the upper limit value, the melt viscosity becomes too high and the moldability is lowered, and the resin material in the molten state is less likely to enter the open pores on the surface of the gear portion 52a, thus reducing the anchor effect. To do.
- the molecular weight of the base resin is preferably in the range of 13,000 to 30000 in terms of number average molecular weight in view of injection moldability, and in the range of 18000 to 25000 in terms of number average molecular weight in consideration of fatigue resistance and high molding accuracy.
- the number average molecular weight is less than 13,000, the molecular weight is too low and the fatigue resistance becomes low.
- the number average molecular weight exceeds 30000 the fatigue resistance is improved.
- 10 to 50% by mass of glass fiber is contained, for example, in order to achieve the required mechanical strength such as impact strength, The melt viscosity exceeds the upper limit (10000 poise), and it becomes difficult to ensure the molding accuracy of the main body 52b during injection molding.
- a copolymerized polyamide resin can be used as the base resin.
- the copolymerized polyamide resin include polycaproamide / polyhexamethylene adipamide copolymer (polyamide 6/66), polyhexamethylene adipamide / polyhexamethylene terephthalamide copolymer (polyamide 66 / 6T), polyhexa Methylene adipamide / polyhexamethylene isophthalamide copolymer (polyamide 66 / 6I), polyhexamethylene adipamide / polyhexamethylene terephthalamide / polyhexamethylene isophthalamide copolymer (polyamide 66 / 6T / 6I), polyxylylene azide Pamide (polyamide XD6) etc. are mentioned.
- Examples of the amount of each component of the above-mentioned polycaproamide / polyhexamethylene adipamide copolymer include a co-polymer consisting of 98 to 80% by mass of polyamide resin 6 component and 2 to 20% by mass of polyamide resin 66 component. Examples thereof include a polymerized polyamide resin, or a copolymerized polyamide resin comprising 98 to 80% by mass of 66 components of polyamide resin and 2 to 20% by mass of 6 components of polyamide resin.
- the affinity with glass fibers is improved as compared with a case where a homopolymerized polyamide resin is a main component. Therefore, the orientation of the glass fiber in the molten resin composition is moderately relaxed, and for example, the difference in molding shrinkage (%) between the flow direction and the direction perpendicular to the flow can be reduced. On the other hand, it is possible to maintain the excellent tensile strength, bending strength, and compressive strength exhibited by ordinary glass fiber reinforced polyamide resins.
- the copolymerized polyamide resin having such good characteristics for example, a 6/66 copolymerized polyamide resin having a polyamide resin 6 and a polyamide resin 66 as a copolymerization component is preferably used.
- the gear portion 52a of the internal gear 52 is formed of sintered metal, the fatigue resistance and mechanical strength of the tooth surface 521 can be increased.
- the main body portion 52b other than the gear portion 52a of the internal gear 52 is formed of resin, the cost and weight of the internal gear 54 can be reduced. Therefore, compared with the conventional product (Patent Document 1) in which the entire internal gear 52 is formed of resin, the life can be extended while suppressing the increase in weight and cost. Therefore, even when the internal gear 52 of the present invention is used for the speed reducer 5 for the vehicle starter equipped with the idling stop mechanism, the starter does not reach the end of its life early, and the maintenance cost of the vehicle can be reduced.
- the main body 52b of the internal gear 52 is configured to include a shaft support 523 that supports the reduction gear output shaft 5a, and the entire main body 52b including the shaft support 523 is formed of resin. Therefore, the center case 101 (see FIG. 6) having a complicated shape as described in Patent Document 1 is not necessary. Therefore, the reduction gear 5 is further effective in reducing the weight and cost.
- the outer peripheral portion 522 that holds the outer periphery of the gear portion 52a is provided in the main body portion 52b, after the main body portion 52b is injection-molded, the outer peripheral portion 522 is compressed in the diameter reducing direction by molding shrinkage when cooled and solidified. Can generate power. Accordingly, the coupling force between the gear portion 52a and the main body portion 52b can be strengthened.
- the thickness in the radial direction of the outer peripheral portion 522 is the largest in the main body portion 52b, the amount of molding shrinkage in the reduced diameter direction generated in the outer peripheral portion 522 can be increased, and the gear portion and the main body portion 52b can be increased.
- the binding force can be further strengthened.
- the thickness in the radial direction of the shaft support portion 523 is made the smallest in the main body portion 52b, it is possible to avoid an adverse effect on the slide bearing 64 (variation of the bearing gap, etc.) due to molding shrinkage in this portion.
- the surface porosity of the tooth surface 521 and the teeth are set so that the surface porosity of the surface in contact with the main body portion 52b and the open porosity of the portion in contact with the main body portion 52b are 10% or more and 50% or less.
- concave portions and convex portions are formed on the outer peripheral surface of the gear portion 52a, and the outer periphery of the gear portion 52a and the main body portion 52a.
- the part 522 may be engaged in the circumferential direction.
- the slide bearing 64 is press-fitted and fixed to the inner periphery of the shaft support portion 523 of the main body portion 52b is illustrated.
- the main body portion 52b is injected with resin by using the slide bearing 64 as an insert part together with the gear portion 52a. You may shape
- the main body 52b is formed of a resin material having excellent slidability, the reduction gear output shaft 5a can be supported directly on the inner peripheral surface of the shaft support 523 without using the sliding bearing 64.
- the internal gear 52 is used for the planetary gear mechanism.
- the internal gear 52 of the present invention is not limited to the planetary gear mechanism, and can be widely used for reduction gears of other configurations. Can do.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Thermal Sciences (AREA)
- Gears, Cams (AREA)
Abstract
Provided is an internal gear (52) constituted by: a ring-shaped gear part (52a) that includes a tooth flank (521); and a main body part (52b) that includes a shaft support part (523) which supports an output shaft (5a) of a reduction gear, and an outer peripheral part (522) which retains the outer periphery of the gear part (52a). The gear part (52a) is formed with sintered metal, and the main body part (52b) is injection molded using a resin, with the gear part (52a) as an insert component.
Description
本発明は、インターナルギヤ、およびこれを有する減速機に関する。
The present invention relates to an internal gear and a speed reducer having the internal gear.
自動車エンジンの始動に用いられるスタータは、モータの出力を、減速機を介してオーバーランニングクラッチ(以下、単にクラッチと呼ぶ)に入力すると共に、クラッチの出力軸に取り付けたピニオンギヤを電磁スイッチの切り替えで軸方向に往復移動させ、ピニオンギヤをエンジン側のリングギヤに対して係合および離脱させる構成を有する。
A starter used for starting an automobile engine inputs an output of a motor to an overrunning clutch (hereinafter simply referred to as a clutch) via a reduction gear, and a pinion gear attached to an output shaft of the clutch by switching an electromagnetic switch. A configuration is adopted in which the pinion gear is engaged and disengaged with respect to the ring gear on the engine side by reciprocating in the axial direction.
スタータに用いられる減速機としては、モータに駆動されるサンギヤと、静止側に固定されたリングギヤと、サンギヤおよびリングギヤの双方に噛み合って自転および公転するプラネタリギヤとを有する遊星歯車機構を使用する場合が多い。リングギヤとしては、内周に歯面を有するインターナルギヤ(内歯車)を用いるのが通例である。スタータ用遊星歯車機構のインターナルギヤとして、例えば特開2007-77810号公報(特許文献1)に記載される樹脂製のインターナルギヤが公知である。図6に示すように、この樹脂製インターナルギヤ100は、センターケース101の内周面に固定されている。
As a reduction gear used for a starter, a planetary gear mechanism having a sun gear driven by a motor, a ring gear fixed to a stationary side, and a planetary gear that meshes with both the sun gear and the ring gear to rotate and revolve may be used. Many. As the ring gear, an internal gear (internal gear) having a tooth surface on the inner periphery is usually used. As an internal gear of a starter planetary gear mechanism, for example, a resin internal gear described in Japanese Patent Application Laid-Open No. 2007-77810 (Patent Document 1) is known. As shown in FIG. 6, the resin internal gear 100 is fixed to the inner peripheral surface of the center case 101.
減速機103の出力軸104は、その軸端において静止側の部材(例えばセンターケース101)に対して回転自在に支持する必要がある。このように減速機103の出力軸104を回転自在に支持するため、特許文献1のスタータでは、インターナルギヤ100を保持するセンターケース101の内径端を軸方向に延ばして軸支部105とし、この軸支部105の内周に圧入固定したすべり軸受106で減速機103の出力軸104を回転自在に支持するようにしている。
The output shaft 104 of the eaves speed reducer 103 needs to be rotatably supported at its shaft end with respect to a stationary member (for example, the center case 101). Thus, in order to rotatably support the output shaft 104 of the speed reducer 103, in the starter of Patent Document 1, the inner diameter end of the center case 101 holding the internal gear 100 is extended in the axial direction to form a shaft support portion 105. The output shaft 104 of the speed reducer 103 is rotatably supported by a slide bearing 106 press-fitted and fixed to the inner periphery of the shaft support portion 105.
近年の自動車では、車両が一時停止した際にそれを感知してエンジンを自動停止させ、車両の再発進時にスタータを駆動してエンジンを再始動させるアイドリングストップ機構を搭載する例が多くなっている。アイドリングストップ機構の搭載車両では、エンジンの停止および再始動が頻繁に繰り返されるため、スタータに組み込まれる減速機の各ギヤには、該機構の非搭載車両用のギヤに比べて、10倍以上の耐久寿命が求められることになる。
In recent automobiles, there is an increasing number of examples equipped with an idling stop mechanism that detects when a vehicle is temporarily stopped, automatically stops the engine, and drives the starter to restart the engine when the vehicle restarts. . In a vehicle equipped with an idling stop mechanism, the engine is frequently stopped and restarted. Therefore, each gear of the reduction gear incorporated in the starter is 10 times or more compared to a gear for a vehicle not equipped with the mechanism. A durable life is required.
しかしながら、一般に樹脂部品の耐疲労性は金属部品に比べて劣るため、特許文献1のようにインターナルギヤ100全体を樹脂で形成すると、インターナルギヤの耐久性が低くなる。従って、このインターナルギヤ100をアイドリングストップ機構搭載車用のスタータに使用すると、減速機に要求される耐久寿命を満足できなくなるおそれがある。その一方で、インターナルギヤ100は、減速機103の他のギヤ(サンギヤあるいはプラネタリギヤ)に比べて大型であるため、その全体を金属製にすると重量増加が著しくなり、自動車部品の軽量化要請に反する結果となる。また、減速機の出力軸104を支持する軸支部105を金属製とした場合、スタータ全体の重量増加を招くことになる。
However, since the fatigue resistance of resin parts is generally inferior to that of metal parts, if the entire internal gear 100 is formed of resin as in Patent Document 1, the durability of the internal gear is lowered. Therefore, when this internal gear 100 is used for a starter for a vehicle equipped with an idling stop mechanism, there is a possibility that the durability life required for the reduction gear cannot be satisfied. On the other hand, the internal gear 100 is larger than the other gears (sun gear or planetary gear) of the speed reducer 103. Therefore, if the entire gear is made of metal, the weight increases remarkably, and there is a demand for weight reduction of automobile parts. The result will be contrary. In addition, when the shaft support portion 105 that supports the output shaft 104 of the reduction gear is made of metal, the weight of the entire starter is increased.
そこで、本発明は、減速機用のインターナルギヤのコストアップや重量増を最低限に抑えつつ、その耐久性を高めることを目的とする。
Therefore, an object of the present invention is to increase the durability of the internal gear for the speed reducer while minimizing the increase in cost and weight.
以上の目的を達成するため、本発明は、減速機に組み込まれる、内周に歯面を有するインターナルギヤであって、前記歯面を備えたリング状のギヤ部と、減速機の出力軸を支持する軸支持部およびギヤ部の外周を保持する外周部を備えた本体部とを有し、ギヤ部を焼結金属で形成すると共に、前記本体部を、ギヤ部をインサート部品として樹脂で射出成形してなる成形体で形成したことを特徴とするものである。
In order to achieve the above object, the present invention is an internal gear incorporated in a speed reducer and having a tooth surface on the inner periphery, and a ring-shaped gear portion having the tooth surface and an output shaft of the speed reducer And a main body portion having an outer peripheral portion for holding the outer periphery of the gear portion, the gear portion is formed of sintered metal, and the main body portion is made of resin using the gear portion as an insert part. It is characterized by being formed of a molded body formed by injection molding.
このようにギヤ部を焼結金属で形成すれば、樹脂で形成する場合よりも歯面の耐疲労性や機械的強度を高めることができる。その一方で、本体部を樹脂で形成すれば、インターナルギヤの低コストや軽量化も図ることができる。また、軸支部を含む本体部の全体を樹脂で形成しているため、特許文献1で必要とされるような複雑形状のセンターケース101(図6参照)が不要となり、軽量化や低コスト化を図る上でより一層有利となる。加えて、本体部にギヤ部の外周を保持する外周部を設けているので、本体部を射出成形した後、冷却固化する際の成形収縮で外周部をギヤ部の外周面に押し付けてギヤ部と本体部の結合力を強化することができる。従って、重量アップや高コスト化を抑制しつつ、インターナルギヤの耐久寿命を高めることができる。
If the gear portion is formed of sintered metal in this way, the fatigue resistance and mechanical strength of the tooth surface can be improved as compared with the case of forming the gear portion. On the other hand, if the main body is formed of resin, the internal gear can be reduced in cost and weight. In addition, since the entire body including the shaft support is formed of resin, the center case 101 having a complicated shape as required in Patent Document 1 (see FIG. 6) is not required, and the weight and cost are reduced. This is even more advantageous for achieving the above. In addition, since the outer peripheral portion for holding the outer periphery of the gear portion is provided in the main body portion, after the main body portion is injection-molded, the outer peripheral portion is pressed against the outer peripheral surface of the gear portion by molding shrinkage when cooled and solidified. And the bonding strength of the main body can be strengthened. Therefore, the durability life of the internal gear can be increased while suppressing an increase in weight and cost.
ギヤ部のうち、本体部と接触する面の表面開孔率を歯面の表面開孔率よりも大きくし、あるいは、ギヤ部のうち、本体部と接触する部分の開放気孔率を歯部の開放気孔率よりも大きくすれば、表面気孔に入り込んだ樹脂によるアンカー効果でギヤ部と本体部の結合力を高めることができる。その一方で、歯面の耐疲労性や機械的強度を高めることもできる。
Of the gear part, the surface porosity of the surface that contacts the main body is made larger than the surface porosity of the tooth surface, or the open porosity of the part of the gear that contacts the main body is determined by the tooth part. If it is larger than the open porosity, the coupling force between the gear part and the main body part can be increased by the anchor effect by the resin that has entered the surface pores. On the other hand, the fatigue resistance and mechanical strength of the tooth surface can be increased.
ギヤ部のうち、本体部と接触する面の表面開孔率は10%以上、50%以下にするのが好ましい。また、ギヤ部の歯面の表面開孔率は40%以下にするのが好ましい。
ギヤ部のうち、本体部と接触する部分の開放気孔率は10%以上、50%以下にするのが好ましい。また、ギヤ部の歯部の開放気孔率は40%以下にするのが好ましい。 Of the gear portion, the surface area ratio of the surface that contacts the main body portion is preferably 10% or more and 50% or less. Moreover, it is preferable that the surface aperture ratio of the tooth surface of the gear portion is 40% or less.
Of the gear part, the open porosity of the part in contact with the main body part is preferably 10% or more and 50% or less. The open porosity of the gear teeth is preferably 40% or less.
ギヤ部のうち、本体部と接触する部分の開放気孔率は10%以上、50%以下にするのが好ましい。また、ギヤ部の歯部の開放気孔率は40%以下にするのが好ましい。 Of the gear portion, the surface area ratio of the surface that contacts the main body portion is preferably 10% or more and 50% or less. Moreover, it is preferable that the surface aperture ratio of the tooth surface of the gear portion is 40% or less.
Of the gear part, the open porosity of the part in contact with the main body part is preferably 10% or more and 50% or less. The open porosity of the gear teeth is preferably 40% or less.
以上のインターナルギヤを有する減速機であれば、減速機の重量増やコストアップを避けつつ、その耐久寿命を高めることができる。また、この減速機をアイドリングストップ機構搭載車両のスタータに使用すれば、減速機、さらにスタータの早期交換を防止し、車両のメンテナンスコストを低廉化することができる。
If it is a reduction gear having an internal gear of more than, its durability life can be increased while avoiding an increase in weight and cost of the reduction gear. Further, if this reduction gear is used for a starter of a vehicle equipped with an idling stop mechanism, early replacement of the reduction gear and the starter can be prevented, and the maintenance cost of the vehicle can be reduced.
以上のように、本発明によれば、減速機用のインターナルギヤのコストアップや重量増を最低限に抑えつつ、その耐久性を高めることが可能となる。
As described above, according to the present invention, it is possible to increase the durability of the internal gear for the speed reducer while minimizing cost increase and weight increase.
以下、本発明の実施形態を図1~図5に基づいて説明する。
Hereinafter, embodiments of the present invention will be described with reference to FIGS.
図1に、スタータSTの代表的構成を簡略化して示す。図1に示すように、このスタータSTは、モータ4、減速機5、オーバーランニングクラッチ6(以下、単にクラッチと呼ぶ)、ピニオンギヤ7、レバー8、および電磁スイッチ9を主要な構成要素とするものである。レバー8は支点Oを中心として回転可能であり、その先端はオーバーランニングクラッチ6の入力側(モータ4側)に配置されている。オーバーランニングクラッチ6はワンウェイクラッチであり、その入力側には減速機5の出力軸5a(減速機出力軸)がスプライン等を介して軸方向に摺動可能に結合されている。また、クラッチ6の出力軸6a(クラッチ出力軸)にはピニオンギヤ7が取り付けられている。従って、クラッチ6は、クラッチ出力軸6aおよびピニオンギヤ7と一体となって軸方向に移動可能である。減速機5およびクラッチ6は、ギヤケースとしての第一ケース11の内部に配置され、モータ4は、モータケースとしての第二ケース12の内部に配置されている。第一ケース11と第二ケース12は、ボルト等の適宜の連結構造によって連結された状態にある。
Fig. 1 shows a simplified configuration of a typical starter ST. As shown in FIG. 1, the starter ST includes a motor 4, a speed reducer 5, an overrunning clutch 6 (hereinafter simply referred to as a clutch), a pinion gear 7, a lever 8, and an electromagnetic switch 9 as main components. It is. The lever 8 is rotatable about a fulcrum O, and the tip thereof is disposed on the input side (motor 4 side) of the overrunning clutch 6. The overrunning clutch 6 is a one-way clutch, and an output shaft 5a (reduction gear output shaft) of the speed reducer 5 is coupled to an input side of the overrunning clutch 6 through a spline or the like so as to be slidable in the axial direction. A pinion gear 7 is attached to the output shaft 6 a (clutch output shaft) of the clutch 6. Therefore, the clutch 6 can move in the axial direction integrally with the clutch output shaft 6 a and the pinion gear 7. The reduction gear 5 and the clutch 6 are disposed inside a first case 11 as a gear case, and the motor 4 is disposed inside a second case 12 as a motor case. The first case 11 and the second case 12 are connected by an appropriate connection structure such as a bolt.
エンジンの始動指令が入力されると、電磁スイッチ9がオンとなってレバー8に図中の矢印方向の回転力が与えられ、クラッチ6、クラッチ出力軸6a、およびピニオンギヤ7が一体となって軸方向の反モータ4側に移動する。これにより、エンジンのクランクシャフトと結合されたリングギヤ10にピニオンギヤ7が噛み合う。また、モータ4が駆動され、その出力トルクが減速装置5およびクラッチ6を介してピニオンギヤ7に伝達される。これにより、モータ出力がリングギヤ10を経てクランクシャフトに伝達され、エンジンが始動する。エンジンの始動後は電磁スイッチ9がオフとなり、クラッチ6およびピニオンギヤ7が後退してピニオンギヤ7がリングギヤ10との噛み合い位置から離脱する。エンジン始動直後のエンジントルクは、クラッチ6で遮断されるためにモータ4には伝達されない。
When an engine start command is input, the electromagnetic switch 9 is turned on to apply a rotational force in the direction of the arrow in the drawing to the lever 8, and the clutch 6, the clutch output shaft 6a, and the pinion gear 7 are integrated into the shaft. Move to the opposite side of the motor 4 in the direction. As a result, the pinion gear 7 meshes with the ring gear 10 coupled to the crankshaft of the engine. Further, the motor 4 is driven, and the output torque is transmitted to the pinion gear 7 via the speed reducer 5 and the clutch 6. As a result, the motor output is transmitted to the crankshaft via the ring gear 10 and the engine is started. After the engine is started, the electromagnetic switch 9 is turned off, the clutch 6 and the pinion gear 7 are retracted, and the pinion gear 7 is disengaged from the meshing position with the ring gear 10. The engine torque immediately after starting the engine is not transmitted to the motor 4 because it is interrupted by the clutch 6.
図2に、スタータSTに用いられる減速機5の代表的構成例を示す。この減速機5は遊星歯車機構であり、軸心O上に配置された外歯車からなるサンギヤ51と、静止側の部材に固定されたインターナルギヤ52と、外歯車からなるプラネタリギヤ53と、プラネタリギヤ53を支持するプレート状のキャリア54とを有する。プラネタリギヤ53はサンギヤ51とインターナルギヤ52の間に配置され、かつ両ギヤ51,52と噛み合った状態にある。サンギヤ51にはセレーション61(スプラインも含む。以下同じ)を介してモータ4の出力軸4aがトルク伝達可能に結合されている。
FIG. 2 shows a typical configuration example of the speed reducer 5 used in the starter ST. The speed reducer 5 is a planetary gear mechanism, and includes a sun gear 51 made of an external gear disposed on an axis O, an internal gear 52 fixed to a stationary member, a planetary gear 53 made of an external gear, and a planetary gear. And a plate-like carrier 54 that supports 53. The planetary gear 53 is disposed between the sun gear 51 and the internal gear 52 and is in mesh with both the gears 51 and 52. An output shaft 4a of the motor 4 is coupled to the sun gear 51 through a serration 61 (including splines; the same applies hereinafter) so as to transmit torque.
図3および図4に示すように、プラネタリギヤ53は円周方向に等配した複数個所(例えば3個所)に配置されている。図2~図4に示すように、各プラネタリギヤ53の内周には、一端を板状のキャリア54の孔に嵌合固定したピン55が挿入され、各プラネタリギヤ53は、その内周に配置したすべり軸受56によりピン55に対して回転自在に支持されている。図2に示すように、減速機出力軸5aは、キャリア54の内周に挿入されており、減速機出力軸5aとキャリア54は、セレーション62を介してトルク伝達可能に結合されている。
お よ び As shown in FIGS. 3 and 4, the planetary gears 53 are arranged at a plurality of locations (for example, 3 locations) equally distributed in the circumferential direction. As shown in FIGS. 2 to 4, a pin 55 having one end fitted and fixed to a hole in a plate-like carrier 54 is inserted into the inner periphery of each planetary gear 53, and each planetary gear 53 is arranged on the inner periphery thereof. A sliding bearing 56 is supported so as to be rotatable with respect to the pin 55. As shown in FIG. 2, the reduction gear output shaft 5 a is inserted into the inner periphery of the carrier 54, and the reduction gear output shaft 5 a and the carrier 54 are coupled via a serration 62 so that torque can be transmitted.
図2に示すように、モータ4の出力軸4aと減速機の出力軸5aのうち、一方(例えばモータ出力軸4a)の端部を他方(例えば減速機出力軸5a)の軸端に形成した孔に挿入し、且つ両者間にすべり軸受63を介在させることで、両軸4a,5aが同軸状態で相対回転可能となる。インターナルギヤ52のモータ4側には、内径端をモータ4の出力軸4aの外周面に近接させた遮蔽プレート65が配置されており、この遮蔽プレート65によって、モータ4で生じるブラシ粉等の異物の減速機5への侵入が防止されている。
As shown in FIG. 2, one end (for example, the motor output shaft 4a) of the output shaft 4a of the motor 4 and the output shaft 5a of the speed reducer is formed at the shaft end of the other (for example, the speed reducer output shaft 5a). By inserting the slide bearing 63 between the two, the shafts 4a and 5a can be rotated relative to each other in a coaxial state. On the motor 4 side of the internal gear 52, a shielding plate 65 having an inner diameter end close to the outer peripheral surface of the output shaft 4a of the motor 4 is arranged. Intrusion of foreign matter into the speed reducer 5 is prevented.
以上の構成において、モータ4でサンギヤ51を回転駆動すると、プラネタリギヤ53が自転しつつ軸心Oの周囲を公転する。このプラネタリギヤ53の公転運動を受けてキャリア54が軸心Oを中心として回転するため、キャリア54とトルク伝達可能に結合された減速機出力軸5aが回転する。これによりモータ4の出力が減速して減速機出力軸5aに伝達され、さらにクラッチ6(図1参照)を介してピニオンギヤ7に伝達される。
In the above configuration, when the sun gear 51 is rotationally driven by the motor 4, the planetary gear 53 revolves around the axis O while rotating. In response to the revolution movement of the planetary gear 53, the carrier 54 rotates about the axis O, so that the speed reducer output shaft 5a coupled to the carrier 54 so as to transmit torque is rotated. As a result, the output of the motor 4 is decelerated and transmitted to the reducer output shaft 5a, and further transmitted to the pinion gear 7 via the clutch 6 (see FIG. 1).
図2に示すように、インターナルギヤ52は、ギヤ部52aと本体部52bとで構成される。ギヤ部52aはリング状の焼結金属材からなり、その内周に、多数の歯面521(図3参照)を備えた歯部525が形成される。
As shown in FIG. 2, the internal gear 52 includes a gear portion 52a and a main body portion 52b. The gear part 52a is made of a ring-shaped sintered metal material, and a tooth part 525 having a large number of tooth surfaces 521 (see FIG. 3) is formed on the inner periphery thereof.
また、本体部52bは、その軸方向一端側(反モータ側)を縮径させた概略円筒状をなし、ギヤ部52aの外径側を覆う大径の外周部522と、軸方向一端側の内径端で軸方向に延びる小径の軸支部523と、外周部522と軸支部523を接続し、外周部522から軸支部523にかけて段階的に縮径した連結部524とを一体に有する。インターナルギヤ52のモータ4側では、ギヤ部52aの端面と本体部52bの端面が面一になっている。連結部524の内径側にキャリア54が配置されている。
The main body 52b has a substantially cylindrical shape with a reduced diameter on one axial end (on the side opposite to the motor), a large-diameter outer peripheral portion 522 that covers the outer diameter of the gear 52a, and an axial end on the one end. A small-diameter shaft support portion 523 extending in the axial direction at the inner diameter end, and an outer peripheral portion 522 and the shaft support portion 523 are connected to each other, and a connecting portion 524 whose diameter is gradually reduced from the outer peripheral portion 522 to the shaft support portion 523 is integrally provided. On the motor 4 side of the internal gear 52, the end surface of the gear portion 52a and the end surface of the main body portion 52b are flush with each other. A carrier 54 is disposed on the inner diameter side of the connecting portion 524.
インターナルギヤ52は、本体部52bの外周部522を、第一ケース11と第二ケース12とで軸方向両側から挟み込むことで、静止側(第一ケース11もしくは第二ケース)に固定される。この際、本体部52bと一方のケース(例えば第一ケース11)との間に回り止めを設けておくのが好ましい。また、本体部52bのうち、軸支部523の内周面にはすべり軸受64が圧入固定されており、このすべり軸受64によって減速機出力軸5aの一端(モータ側端部)がインターナルギヤ52に対して回転自在に支持されている。
The internal gear 52 is fixed to the stationary side (the first case 11 or the second case) by sandwiching the outer peripheral portion 522 of the main body portion 52b between the first case 11 and the second case 12 from both sides in the axial direction. . At this time, it is preferable to provide a rotation stopper between the main body 52b and one case (for example, the first case 11). In addition, a sliding bearing 64 is press-fitted and fixed to the inner peripheral surface of the shaft support portion 523 in the main body portion 52 b, and one end (motor side end portion) of the reduction gear output shaft 5 a is connected to the internal gear 52 by the sliding bearing 64. Is supported so as to be freely rotatable.
以上に述べたインターナルギヤ52は、粉末冶金法により製作したギヤ部52aを金型内に配置するインサート部品とし、このギヤ部52aを金型内の規定位置に位置決めした状態で金型内に樹脂を射出して本体部52bを成形(インサート成形)することで製作される。以下、ギヤ部52bおよび本体部52bの組成および製造手順を詳細に述べる。
The internal gear 52 described above is an insert part in which a gear part 52a manufactured by a powder metallurgy method is placed in a mold, and the gear part 52a is positioned in a predetermined position in the mold. It is manufactured by injecting resin and molding (insert molding) the main body 52b. Hereinafter, the composition and manufacturing procedure of the gear part 52b and the main body part 52b will be described in detail.
[ギヤ部]
ギヤ部52aは、鉄系の焼結体で形成される。具体的には、鉄粉を主成分とし、これに銅粉および黒鉛粉を混合した原料粉末を圧縮して圧粉体を成形し、その後、圧紛体を焼結することにより、ギヤ部52aに対応する形状の焼結体が得られる。 [Gear part]
Thegear part 52a is formed of an iron-based sintered body. Specifically, iron powder is the main component, a raw material powder in which copper powder and graphite powder are mixed is compressed to form a green compact, and then the green compact is sintered to form the gear portion 52a. A sintered body having a corresponding shape is obtained.
ギヤ部52aは、鉄系の焼結体で形成される。具体的には、鉄粉を主成分とし、これに銅粉および黒鉛粉を混合した原料粉末を圧縮して圧粉体を成形し、その後、圧紛体を焼結することにより、ギヤ部52aに対応する形状の焼結体が得られる。 [Gear part]
The
この焼結体は、例えばCu:1~8質量%、C:0.2~1質量%含み、残部をFeおよび不可避的不純物としたものとする。焼結温度は、1100℃~1150℃とするのが好ましい。この温度で焼結することにより、溶融したCuがFeに拡散してFe組織同士の結合力が強化される。また、Feが黒鉛粉に含まれるCと反応するため、焼結後のFe組織は硬いパーライト相となる。従って、焼結体の強度アップを図ることができる。パーライト相を十分に形成するため、焼結炉の雰囲気ガスとしては、一酸化炭素あるいは二酸化炭素等の炭素を含むガス、例えば、ブタンガスやプロパンガス等の液化石油ガスと空気を混合し、Ni触媒で熱分解させた吸熱型ガス(RXガス)を使用するのが好ましい。
焼 結 This sintered body contains, for example, Cu: 1 to 8% by mass, C: 0.2 to 1% by mass, with the balance being Fe and inevitable impurities. The sintering temperature is preferably 1100 ° C. to 1150 ° C. By sintering at this temperature, the molten Cu diffuses into Fe and strengthens the bonding force between the Fe structures. Moreover, since Fe reacts with C contained in the graphite powder, the Fe structure after sintering becomes a hard pearlite phase. Therefore, the strength of the sintered body can be increased. In order to sufficiently form the pearlite phase, the atmosphere gas of the sintering furnace is a gas containing carbon such as carbon monoxide or carbon dioxide, for example, liquefied petroleum gas such as butane gas or propane gas and air, and Ni catalyst. It is preferable to use an endothermic gas (RX gas) pyrolyzed in (1).
焼結後の焼結体には、塑性加工による歯面の整形(サイジング)が行われる。焼結体の時点では、図5に二点鎖線で示すように、ギヤ部52aの歯面521に相当する部分521’は粗形状に形成されているが、この部分521’を転造等により塑性加工することで、該部分521’がインボリュート形状等の仕上がり形状(実線で示す)に整形され、内周に歯面521を有するギヤ部52aが完成する。この塑性加工に際しては、図5に示すように、歯面521を含む各歯部525を、周方向で圧縮すると共に、半径方向で伸長変形させて仕上げるのが好ましい。
Toothed surface is shaped (sizing) by plastic working on the sintered body after fired sintering. At the time of the sintered body, as shown by a two-dot chain line in FIG. 5, the portion 521 ′ corresponding to the tooth surface 521 of the gear portion 52a is formed in a rough shape, but this portion 521 ′ is formed by rolling or the like. By plastic working, the portion 521 ′ is shaped into a finished shape (indicated by a solid line) such as an involute shape, and a gear portion 52a having a tooth surface 521 on the inner periphery is completed. In this plastic working, as shown in FIG. 5, it is preferable to finish each tooth portion 525 including the tooth surface 521 by compressing in the circumferential direction and extending and deforming in the radial direction.
このように転造等で塑性加工を行うことで、歯面521を含む表層部の多孔質組織が緻密化され、該表層部において応力集中源となる空孔が少なくなる。また、歯面521の硬度が芯部よりも高くなる(この時、硬度は歯面521で最大となり、芯部に向かうにつれて徐々に低下し、所定の深さを超えると一定となる)。従って、機械的強度、特に疲労強度に優れた歯面521を得ることが可能となる。この塑性加工は、冷間、温感、又は熱間の何れの温度領域で行ってもよいが、歯面521の整形精度や耐久寿命を考えると、冷間で行うのが好ましい。
塑 By performing plastic working by rolling or the like in this manner, the porous structure of the surface layer portion including the tooth surface 521 is densified, and pores serving as stress concentration sources in the surface layer portion are reduced. Further, the hardness of the tooth surface 521 becomes higher than that of the core portion (at this time, the hardness is maximum at the tooth surface 521, gradually decreases toward the core portion, and becomes constant when exceeding a predetermined depth). Therefore, it is possible to obtain a tooth surface 521 having excellent mechanical strength, particularly fatigue strength. This plastic working may be performed in any temperature range between cold, warm feeling, or hot, but is preferably performed cold considering the shaping accuracy and durability life of the tooth surface 521.
歯面521の整形に伴って、ギヤ部52aの歯面521以外の各面(端面および外周面等)も整形される。この際、ギヤ部52aのうち、少なくとも本体部52bと接する面(特にギヤ部52aの外周面)における圧縮量を、歯面521での圧縮量よりも小さくする等して、ギヤ部52aの少なくとも本体部52bと接する面の表面開孔率を歯面521よりも大きくするのが好ましい。あるいはギヤ部52aの少なくとも本体部52bと接する部分の開放気孔率を歯部525よりも大きくするのが好ましい。これにより、本体部52bを樹脂で射出成形した際に、樹脂がギヤ部52aの外周面や一方の端面の表面開孔に入り込んでアンカー効果を発揮するため、ギヤ部52aと本体部52bの結合強度を高めることができる。なお、上記の大小関係は、表面開孔率および開放気孔率のどちらか一方を満足していれば足りる。もちろん双方を満足していても構わない。
With the shaping of the toothed surface 521, each surface (end surface, outer peripheral surface, etc.) other than the tooth surface 521 of the gear portion 52a is also shaped. At this time, at least the surface of the gear portion 52a in contact with the main body portion 52b (particularly the outer peripheral surface of the gear portion 52a) is made smaller than the amount of compression at the tooth surface 521. It is preferable that the surface area ratio of the surface in contact with the main body portion 52b is larger than that of the tooth surface 521. Or it is preferable to make open porosity of the part which contacts the main-body part 52b at least of the gear part 52a larger than the tooth | gear part 525. FIG. As a result, when the main body 52b is injection-molded with resin, the resin enters the outer peripheral surface of the gear portion 52a or the surface opening of one end surface to exert an anchor effect, so that the coupling between the gear portion 52a and the main body 52b is performed. Strength can be increased. In addition, it is sufficient for the above-described magnitude relationship to satisfy either one of the surface porosity and the open porosity. Of course, you may be satisfied with both.
かかるアンカー効果を十分に得るため、ギヤ部52aの本体部52bと接する面(特に外周面)の表面開孔率の下限値は、10%以上、好ましくは15%以上、さらに好ましくは20%以上とする。また、ギヤ部52aの本体部52bと接する部分(ギヤ部52aのうち歯部525を除く部分)の開放気孔率は、10%以上、好ましくは15%以上、さらに好ましくは20%以上とする。その一方で、表面開孔率や開放気孔率が大きすぎると、ギヤ部52a全体の強度低下を招く。従って、上記表面開孔率は50%以下、好ましくは40%以下とし、上記開放気孔率は50%以下、好ましくは40%以下とする。上記の各限界値は、表面開孔率および開放気孔率のどちらか一方を満足していれば足りる。もちろん双方を満足していても構わない。なお、ここでいう表面開孔率は、便宜的には例えば、Nikon社製:ECLIPSE ME600等の金属顕微鏡で撮影した画像(例えば500倍)を画像データとしてコンピュータに取り込み、気孔部分の面積を演算することで求めることができる。また、開放気孔率は、JIS Z 2501:2000で定義されるものである。ちなみに測定対象物の開放気孔率は、体積に対する百分率で表され、完全含浸後の油の体積を測定対象物の体積で除し、100を乗じることにより求められる。
In order to sufficiently obtain such an anchor effect, the lower limit value of the surface area ratio of the surface (particularly the outer peripheral surface) of the gear portion 52a in contact with the main body portion 52b is 10% or more, preferably 15% or more, more preferably 20% or more. And Further, the open porosity of the portion of the gear portion 52a that contacts the main body portion 52b (the portion of the gear portion 52a excluding the tooth portion 525) is 10% or more, preferably 15% or more, and more preferably 20% or more. On the other hand, if the surface porosity or the open porosity is too large, the strength of the entire gear portion 52a is reduced. Therefore, the surface porosity is 50% or less, preferably 40% or less, and the open porosity is 50% or less, preferably 40% or less. Each of the above limit values only needs to satisfy either the surface porosity or the open porosity. Of course, you may be satisfied with both. For the sake of convenience, the surface open area referred to here is calculated, for example, by taking an image (for example, 500 times) taken with a metal microscope such as Nikon Corporation: ECLIPSE ME600 as image data and calculating the area of the pore portion. You can ask for it. The open porosity is defined by JIS Z 2501: 2000. Incidentally, the open porosity of the measurement object is expressed as a percentage of the volume, and is obtained by dividing the volume of oil after complete impregnation by the volume of the measurement object and multiplying by 100.
また、歯面521の表面開孔率は、その強度確保のため、40%以下、好ましくは、20%以下、さらに好ましくは10%以下とする。同様の理由から、歯部525の開放気孔率は、40%以下、好ましくは、20%以下、さらに好ましくは10%以下とする。なお、歯面521の開放気孔率が小さすぎると、圧紛体を成形する際の成形圧力を過剰に大きくしなければならず、コスト面等で不利となるので、歯面521の表面開孔率は5%以上に設定するのが好ましい。同様の理由から、歯部525の開放気孔率は5%以上に設定するのが好ましい。なお、上記の各限界値は、表面開孔率および開放気孔率のどちらか一方を満足していれば足りる。もちろん双方を満足していても構わない。
表面 Further, the surface area ratio of the tooth surface 521 is 40% or less, preferably 20% or less, more preferably 10% or less, in order to ensure the strength. For the same reason, the open porosity of the tooth portion 525 is 40% or less, preferably 20% or less, and more preferably 10% or less. If the open porosity of the tooth surface 521 is too small, the molding pressure when molding the compact must be excessively increased, which is disadvantageous in terms of cost and the like. Is preferably set to 5% or more. For the same reason, the open porosity of the tooth portion 525 is preferably set to 5% or more. Each of the above limit values only needs to satisfy one of the surface porosity and the open porosity. Of course, you may be satisfied with both.
[本体部]
樹脂の成形体である本体部52bを構成する樹脂材料としては、射出成形可能となる任意の材料が使用可能である。樹脂材料の中でも、耐疲労性に優れるポリアミド樹脂をベース樹脂とするものが好ましい。ポリアミド樹脂として、例えばポリアミド6、ポリアミド66、ポリアミド46、ポリアミド610、ポリアミド612、ポリアミド11、ポリアミド12、ポリアミドMXD、ポリアミド6T、ポリアミド6Iなどを挙げることができる。なお、これら樹脂に配合する繊維状充填材としては、ガラス繊維の他、炭素繊維、芳香族ポリアミド繊維またはこれらの混合物等が広く使用可能である。 [Main unit]
As a resin material constituting themain body 52b, which is a resin molded body, any material that can be injection-molded can be used. Of the resin materials, those based on polyamide resins having excellent fatigue resistance are preferred. Examples of the polyamide resin include polyamide 6, polyamide 66, polyamide 46, polyamide 610, polyamide 612, polyamide 11, polyamide 12, polyamide MXD, polyamide 6T, and polyamide 6I. In addition, as a fibrous filler mix | blended with these resin, carbon fiber, aromatic polyamide fiber, or a mixture thereof can be widely used besides glass fiber.
樹脂の成形体である本体部52bを構成する樹脂材料としては、射出成形可能となる任意の材料が使用可能である。樹脂材料の中でも、耐疲労性に優れるポリアミド樹脂をベース樹脂とするものが好ましい。ポリアミド樹脂として、例えばポリアミド6、ポリアミド66、ポリアミド46、ポリアミド610、ポリアミド612、ポリアミド11、ポリアミド12、ポリアミドMXD、ポリアミド6T、ポリアミド6Iなどを挙げることができる。なお、これら樹脂に配合する繊維状充填材としては、ガラス繊維の他、炭素繊維、芳香族ポリアミド繊維またはこれらの混合物等が広く使用可能である。 [Main unit]
As a resin material constituting the
例示した樹脂材料を使用すると、射出成形後の固化時に生じる成形収縮により、本体部52bの外周部522が縮径方向に変形しようとするため、アンカー効果が強化されてギヤ部52aと本体部52bの結合力が増す。従って、このように樹脂の成形収縮を活用することで、ギヤ部52aと本体部52bを一体化させ、インターナルギヤ52の耐久性を向上させることが可能となる。ちなみに、非充填のポリアミド6樹脂の成形収縮率は、一般に0.5~1.5%、非充填のポリアミド66樹脂の成形収縮率は、一般に0.8~1.5%、ガラス繊維等充填のポリアミド6樹脂の成形収縮率は、一般に0.4~0.8%、ガラス繊維等充填のポリアミド66樹脂の成形収縮率は、一般に0.2~1.0%である。
When the illustrated resin material is used, the outer peripheral portion 522 of the main body portion 52b tends to deform in the diameter-reducing direction due to molding shrinkage that occurs at the time of solidification after injection molding, so that the anchor effect is enhanced and the gear portion 52a and the main body portion 52b are strengthened. The bond strength of increases. Therefore, by utilizing the molding shrinkage of the resin in this way, the gear portion 52a and the main body portion 52b can be integrated, and the durability of the internal gear 52 can be improved. Incidentally, the molding shrinkage rate of unfilled polyamide 6 resin is generally 0.5 to 1.5%, and the molding shrinkage rate of unfilled polyamide 66 resin is generally 0.8 to 1.5%. The molding shrinkage ratio of the polyamide 6 resin is generally 0.4 to 0.8%, and the molding shrinkage ratio of the polyamide 66 resin filled with glass fiber or the like is generally 0.2 to 1.0%.
また、ベース樹脂の見かけの溶融粘度は、1000ポアズ以上10000ポアズ以下の範囲とするのが好ましい。見かけの溶融粘度が下限値よりも低いと、本体部52bの強度に不安が残る。一方、見かけの溶融粘度が上限値よりも高いと、溶融粘度が高くなり過ぎて成形性が低下すると共に、ギヤ部52a表面の開放気孔に溶融状態の樹脂材料が入り込みにくくなり、アンカー効果が低下する。
The apparent melt viscosity of the base resin is preferably in the range of 1000 poise to 10,000 poise. If the apparent melt viscosity is lower than the lower limit value, there remains anxiety about the strength of the main body 52b. On the other hand, if the apparent melt viscosity is higher than the upper limit value, the melt viscosity becomes too high and the moldability is lowered, and the resin material in the molten state is less likely to enter the open pores on the surface of the gear portion 52a, thus reducing the anchor effect. To do.
また、ベース樹脂の分子量は、射出成形性を考慮すると、数平均分子量で13000~30000、更に耐疲労性、高成形精度を考慮すると、数平均分子量で18000~25000の範囲が好ましい。数平均分子量が13000未満の場合には、分子量が低すぎて、耐疲労性が低くなる。一方、数平均分子量が30000を越える場合には耐疲労性は向上するものの、必要な衝撃強度等の機械的強度を達成するために例えば10~50質量%のガラス繊維を含有させると、成形時の溶融粘度が上記の上限値(10000ポアズ)を超え、射出成形時に本体部52bの成形精度を確保することが難しくなる。
In addition, the molecular weight of the base resin is preferably in the range of 13,000 to 30000 in terms of number average molecular weight in view of injection moldability, and in the range of 18000 to 25000 in terms of number average molecular weight in consideration of fatigue resistance and high molding accuracy. When the number average molecular weight is less than 13,000, the molecular weight is too low and the fatigue resistance becomes low. On the other hand, when the number average molecular weight exceeds 30000, the fatigue resistance is improved. However, when 10 to 50% by mass of glass fiber is contained, for example, in order to achieve the required mechanical strength such as impact strength, The melt viscosity exceeds the upper limit (10000 poise), and it becomes difficult to ensure the molding accuracy of the main body 52b during injection molding.
また、ベース樹脂としては、共重合ポリアミド樹脂を使用することもできる。共重合ポリアミド樹脂の具体例としては、ポリカプロアミド/ポリヘキサメチレンアジパミドコポリマー(ポリアミド6/66)、ポリヘキサメチレンアジパミド/ポリヘキサメチレンテレフタルアミドコポリマー(ポリアミド66/6T)、ポリヘキサメチレンアジパミド/ポリヘキサメチレンイソフタルアミドコポリマー(ポリアミド66/6I)、ポリヘキサメチレンアジパミド/ポリヘキサメチレンテレフタルアミド/ポリヘキサメチレンイソフタルアミドコポリマー(ポリアミド66/6T/6I)、ポリキシリレンアジパミド(ポリアミドXD6)などが挙げられる。
In addition, a copolymerized polyamide resin can be used as the base resin. Specific examples of the copolymerized polyamide resin include polycaproamide / polyhexamethylene adipamide copolymer (polyamide 6/66), polyhexamethylene adipamide / polyhexamethylene terephthalamide copolymer (polyamide 66 / 6T), polyhexa Methylene adipamide / polyhexamethylene isophthalamide copolymer (polyamide 66 / 6I), polyhexamethylene adipamide / polyhexamethylene terephthalamide / polyhexamethylene isophthalamide copolymer (polyamide 66 / 6T / 6I), polyxylylene azide Pamide (polyamide XD6) etc. are mentioned.
前記したポリカプロアミド/ポリヘキサメチレンアジパミドコポリマー(ポリアミド6/66)の各成分量の例としては、ポリアミド樹脂6成分98~80質量%およびポリアミド樹脂66成分2~20質量%からなる共重合ポリアミド樹脂、またはポリアミド樹脂66成分98~80質量%およびポリアミド樹脂6成分2~20質量%からなる共重合ポリアミド樹脂が挙げられる。
Examples of the amount of each component of the above-mentioned polycaproamide / polyhexamethylene adipamide copolymer (polyamide 6/66) include a co-polymer consisting of 98 to 80% by mass of polyamide resin 6 component and 2 to 20% by mass of polyamide resin 66 component. Examples thereof include a polymerized polyamide resin, or a copolymerized polyamide resin comprising 98 to 80% by mass of 66 components of polyamide resin and 2 to 20% by mass of 6 components of polyamide resin.
共重合ポリアミド樹脂を使用すると、ガラス繊維との親和性が単独重合のポリアミド樹脂を主成分とする場合に比べて改善される。そのため、ガラス繊維の溶融樹脂組成物中の配向性が適度に緩和され、例えば成形収縮率(%)における流れ方向および流れに直角方向の差を小さくすることができる。その一方で、通常のガラス繊維強化のポリアミド樹脂が奏する優れた引張強度、曲げ強度、圧縮強度を維持することができる。このような良好な特性を有する共重合ポリアミド樹脂としては、例えばポリアミド樹脂6およびポリアミド樹脂66を共重合成分とする6/66共重合ポリアミド樹脂を使用するのが好ましい。
When a copolyamide resin is used, the affinity with glass fibers is improved as compared with a case where a homopolymerized polyamide resin is a main component. Therefore, the orientation of the glass fiber in the molten resin composition is moderately relaxed, and for example, the difference in molding shrinkage (%) between the flow direction and the direction perpendicular to the flow can be reduced. On the other hand, it is possible to maintain the excellent tensile strength, bending strength, and compressive strength exhibited by ordinary glass fiber reinforced polyamide resins. As the copolymerized polyamide resin having such good characteristics, for example, a 6/66 copolymerized polyamide resin having a polyamide resin 6 and a polyamide resin 66 as a copolymerization component is preferably used.
以上に説明したインターナルギヤ52を減速機5に使用すれば、以下の作用効果を得ることができる。
If the internal gear 52 described above is used for the speed reducer 5, the following operational effects can be obtained.
インターナルギヤ52のギヤ部52aを焼結金属で形成しているため、歯面521の耐疲労性や機械的強度を高めることができる。その一方で、インターナルギヤ52のうち、ギヤ部52a以外の本体部52bを樹脂で形成しているため、インターナルギヤ54の低コストや軽量化も図ることができる。従って、インターナルギヤ52全体を樹脂で形成した従来品(特許文献1)に比べ、その重量アップや高コスト化を抑制しつつ、寿命を長期化することができる。そのため、本発明のインターナルギヤ52をアイドリングストップ機構搭載車両用スタータの減速機5に使用した場合も、スタータが早期に寿命を迎えることはなく、車両のメンテナンスコストを低廉化することができる。
ギ ヤ Since the gear portion 52a of the internal gear 52 is formed of sintered metal, the fatigue resistance and mechanical strength of the tooth surface 521 can be increased. On the other hand, since the main body portion 52b other than the gear portion 52a of the internal gear 52 is formed of resin, the cost and weight of the internal gear 54 can be reduced. Therefore, compared with the conventional product (Patent Document 1) in which the entire internal gear 52 is formed of resin, the life can be extended while suppressing the increase in weight and cost. Therefore, even when the internal gear 52 of the present invention is used for the speed reducer 5 for the vehicle starter equipped with the idling stop mechanism, the starter does not reach the end of its life early, and the maintenance cost of the vehicle can be reduced.
また、本発明では、インターナルギヤ52の本体部52bを、減速機出力軸5aを支持する軸支部523を包含する形態とし、この軸支部523を含む本体部52b全体を樹脂で形成しているため、特許文献1に記載されるような複雑な形状のセンターケース101(図6参照)が不要となる。従って、減速機5の軽量化や低コスト化を図る上でより一層有効となる。
In the present invention, the main body 52b of the internal gear 52 is configured to include a shaft support 523 that supports the reduction gear output shaft 5a, and the entire main body 52b including the shaft support 523 is formed of resin. Therefore, the center case 101 (see FIG. 6) having a complicated shape as described in Patent Document 1 is not necessary. Therefore, the reduction gear 5 is further effective in reducing the weight and cost.
加えて、本体部52bにギヤ部52aの外周を保持する外周部522を設けているので、本体部52bを射出成形した後、冷却固化する際の成形収縮で外周部522に縮径方向の圧迫力を生じさせることができる。従って、ギヤ部52aと本体部52bとの結合力を強化することができる。好ましくは外周部522の半径方向の肉厚を本体部52bの中で最も大きくすれば、外周部522で生じる縮径方向の成形収縮量を大きくすることができ、ギヤ部と本体部52bとの結合力をさらに強化することができる。また、軸支部523の半径方向の肉厚を本体部52bの中で最も小さくすれば、この部分での成形収縮によるすべり軸受64への悪影響(軸受隙間の変動等)を回避することができる。
In addition, since the outer peripheral portion 522 that holds the outer periphery of the gear portion 52a is provided in the main body portion 52b, after the main body portion 52b is injection-molded, the outer peripheral portion 522 is compressed in the diameter reducing direction by molding shrinkage when cooled and solidified. Can generate power. Accordingly, the coupling force between the gear portion 52a and the main body portion 52b can be strengthened. Preferably, if the thickness in the radial direction of the outer peripheral portion 522 is the largest in the main body portion 52b, the amount of molding shrinkage in the reduced diameter direction generated in the outer peripheral portion 522 can be increased, and the gear portion and the main body portion 52b can be increased. The binding force can be further strengthened. Further, if the thickness in the radial direction of the shaft support portion 523 is made the smallest in the main body portion 52b, it is possible to avoid an adverse effect on the slide bearing 64 (variation of the bearing gap, etc.) due to molding shrinkage in this portion.
この時、ギヤ部52aのうち、本体部52bと接する面の表面開孔率や本体部52bと接する部分の開放気孔率を10%以上50%以下として、歯面521の表面開孔率や歯部525の開放気孔率よりも大きくすることで、ギヤ部52aと本体部52bの境界部分でのアンカー効果を強化することができ、ギヤ部と本体部52bの結合力をさらに高めることが可能となる。ギヤ部52aと本体部52bの特に周方向における結合力をさらに高めるため、ギヤ部52aの外周面に凹部や凸部(キー溝、セレーション等)を形成し、ギヤ部52aと本体部52aの外周部522とを円周方向で係合させてもよい。
At this time, in the gear portion 52a, the surface porosity of the tooth surface 521 and the teeth are set so that the surface porosity of the surface in contact with the main body portion 52b and the open porosity of the portion in contact with the main body portion 52b are 10% or more and 50% or less. By making it larger than the open porosity of the portion 525, the anchor effect at the boundary between the gear portion 52a and the main body portion 52b can be strengthened, and the coupling force between the gear portion and the main body portion 52b can be further increased. Become. In order to further increase the coupling force between the gear portion 52a and the main body portion 52b, particularly in the circumferential direction, concave portions and convex portions (key grooves, serrations, etc.) are formed on the outer peripheral surface of the gear portion 52a, and the outer periphery of the gear portion 52a and the main body portion 52a. The part 522 may be engaged in the circumferential direction.
なお、以上の説明では、本体部52bの軸支部523の内周にすべり軸受64を圧入固定する場合を例示したが、ギヤ部52aと共にすべり軸受64をインサート部品として、本体部52bを樹脂で射出成形してもよい。また、本体部52bを摺動性に優れる樹脂材料で形成すれば、すべり軸受64を使用せずに軸支部523の内周面で直接、減速機出力軸5aを支持することもできる。
In the above description, the case where the slide bearing 64 is press-fitted and fixed to the inner periphery of the shaft support portion 523 of the main body portion 52b is illustrated. However, the main body portion 52b is injected with resin by using the slide bearing 64 as an insert part together with the gear portion 52a. You may shape | mold. Further, if the main body 52b is formed of a resin material having excellent slidability, the reduction gear output shaft 5a can be supported directly on the inner peripheral surface of the shaft support 523 without using the sliding bearing 64.
また、以上の説明では、インターナルギヤ52を遊星歯車機構に用いる場合を説明したが、本発明のインターナルギヤ52は、遊星歯車機構に限らず、他の構成の減速機にも広く用いることができる。
In the above description, the case where the internal gear 52 is used for the planetary gear mechanism has been described. However, the internal gear 52 of the present invention is not limited to the planetary gear mechanism, and can be widely used for reduction gears of other configurations. Can do.
4 モータ
4a モータ出力軸
5 減速機
5a 減速機出力軸
6 オーバーランニングクラッチ
7 ピニオンギヤ
52 インターナルギヤ
52a ギヤ部
52b 本体部
64 すべり軸受
521 歯面
522 外周部
523 軸支部
4Motor 4a Motor output shaft 5 Reducer 5a Reducer output shaft 6 Overrunning clutch 7 Pinion gear 52 Internal gear 52a Gear portion 52b Body portion 64 Slide bearing 521 Tooth surface 522 Outer portion 523 Shaft support portion
4a モータ出力軸
5 減速機
5a 減速機出力軸
6 オーバーランニングクラッチ
7 ピニオンギヤ
52 インターナルギヤ
52a ギヤ部
52b 本体部
64 すべり軸受
521 歯面
522 外周部
523 軸支部
4
Claims (9)
- 減速機に組み込まれる、内周に歯面を有するインターナルギヤであって、
前記歯面を含む歯部を備えたリング状のギヤ部と、減速機の出力軸を支持する軸支持部およびギヤ部の外周を保持する外周部を備えた本体部とを有し、ギヤ部を焼結金属で形成すると共に、前記本体部を、ギヤ部をインサート部品として樹脂で射出成形してなる成形体で形成したことを特徴とするインターナルギヤ。 An internal gear incorporated in the speed reducer and having a tooth surface on the inner periphery,
A gear portion having a ring-shaped gear portion including a tooth portion including the tooth surface, a shaft support portion that supports an output shaft of the reduction gear, and a peripheral portion that holds an outer periphery of the gear portion; The internal gear is formed of a sintered metal, and the main body portion is formed of a molded body formed by injection molding with a resin using the gear portion as an insert part. - ギヤ部のうち、本体部と接触する面の表面開孔率を歯面の表面開孔率よりも大きくした請求項1に記載のインターナルギヤ。 2. The internal gear according to claim 1, wherein a surface area ratio of a surface contacting the main body part of the gear part is larger than a surface area ratio of the tooth surface.
- ギヤ部のうち、本体部と接触する部分の開放気孔率を歯部の開放気孔率よりも大きくした請求項1または2に記載のインターナルギヤ。 The internal gear according to claim 1 or 2, wherein an open porosity of a portion in contact with the main body portion of the heel gear portion is larger than an open porosity of the tooth portion.
- ギヤ部のうち、本体部と接触する面の表面開孔率を10%以上、50%以下にした請求項1~3何れか1項に記載のインターナルギヤ。 The internal gear according to any one of claims 1 to 3, wherein a surface area ratio of a surface in contact with the main body portion of the flange gear portion is 10% or more and 50% or less.
- ギヤ部のうち、本体部と接触する部分の開放気孔率を10%以上、50%以下にした請求項1~4何れか1項に記載のインターナルギヤ。 The internal gear according to any one of claims 1 to 4, wherein an open porosity of a portion of the heel gear portion that contacts the main body portion is 10% or more and 50% or less.
- ギヤ部の歯面の表面開孔率を40%以下にした請求項1~5何れか1項に記載のインターナルギヤ。 The internal gear according to any one of claims 1 to 5, wherein a surface hole area ratio of a tooth surface of the flange gear portion is 40% or less.
- ギヤ部の歯部の開放気孔率を40%以下にした請求項1~6何れか1項に記載のインターナルギヤ。 The internal gear according to any one of claims 1 to 6, wherein an open porosity of a tooth portion of the gear portion is 40% or less.
- 請求項1~7何れか1項に記載のインターナルギヤを有する減速機。 A speed reducer having the internal gear according to any one of claims 1 to 7.
- アイドリングストップ機構搭載車両のスタータに使用される請求項8に記載の減速機。 The speed reducer according to claim 8, which is used for a starter of a vehicle equipped with an idling stop mechanism.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015093115 | 2015-04-30 | ||
JP2015-093115 | 2015-04-30 | ||
JP2016069040A JP2016211728A (en) | 2015-04-30 | 2016-03-30 | Internal gear and speed reducer having the same |
JP2016-069040 | 2016-03-30 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016175135A1 true WO2016175135A1 (en) | 2016-11-03 |
Family
ID=57198369
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2016/062699 WO2016175135A1 (en) | 2015-04-30 | 2016-04-22 | Internal gear and reduction gear comprising same |
Country Status (1)
Country | Link |
---|---|
WO (1) | WO2016175135A1 (en) |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6152758U (en) * | 1984-09-11 | 1986-04-09 | ||
JP2005233002A (en) * | 2004-02-17 | 2005-09-02 | Denso Corp | Auxiliary machine driving type engine starter |
JP2007077810A (en) * | 2005-09-12 | 2007-03-29 | Denso Corp | Starter |
JP2013061008A (en) * | 2011-09-13 | 2013-04-04 | Jtekt Corp | Worm wheel |
-
2016
- 2016-04-22 WO PCT/JP2016/062699 patent/WO2016175135A1/en active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6152758U (en) * | 1984-09-11 | 1986-04-09 | ||
JP2005233002A (en) * | 2004-02-17 | 2005-09-02 | Denso Corp | Auxiliary machine driving type engine starter |
JP2007077810A (en) * | 2005-09-12 | 2007-03-29 | Denso Corp | Starter |
JP2013061008A (en) * | 2011-09-13 | 2013-04-04 | Jtekt Corp | Worm wheel |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US10907685B2 (en) | Sintered bearing and manufacturing process therefor | |
JP3122775U (en) | Rotating elastic coupling | |
JP6741730B2 (en) | Sintered bearing and manufacturing method thereof | |
US20120227529A1 (en) | Intermediate bearing device with toothing reinforcement for starter | |
JP3815658B2 (en) | Cylinder block | |
US6222293B1 (en) | Starter | |
KR20060035727A (en) | Gear, speed reducer using the gear, and electric power steering device with the speed reducer | |
KR20130031454A (en) | Synchronizer sleeve and manufacturing method thereof | |
JP2016211728A (en) | Internal gear and speed reducer having the same | |
JP2007176227A (en) | Reduction gear for electric power steering device | |
WO2016175135A1 (en) | Internal gear and reduction gear comprising same | |
KR20010078007A (en) | Oil pump | |
US5035151A (en) | Engine starter motor | |
JP2011522148A (en) | Overhang type starter | |
US20170203367A1 (en) | Synchronizer hub for vehicles and method for manufacturing the same | |
US9816597B2 (en) | Sintered pulley | |
JP2009014074A (en) | Meshing clutch | |
US20180187779A1 (en) | Coating method for vehicle shift fork and shift fork with amorphous coating layer formed by the same | |
KR20090050694A (en) | Casting method of sleeve bearing by bi-metal centrifucal casting | |
JP6548952B2 (en) | Sintered bearing and method of manufacturing the same | |
US20080004147A1 (en) | Starter | |
JP4918954B2 (en) | Electric power steering device | |
JP3818012B2 (en) | Resin molded product made by casting metal parts and its manufacturing method | |
CN204419906U (en) | Steel-based composite resin-based synchronizer ring for heavy-duty vehicle | |
KR20050068364A (en) | Inner clutch for motorcycle engine parts and it's method for manufacturing |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 16786412 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 16786412 Country of ref document: EP Kind code of ref document: A1 |