WO2021024610A1 - 差動装置 - Google Patents

差動装置 Download PDF

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Publication number
WO2021024610A1
WO2021024610A1 PCT/JP2020/022798 JP2020022798W WO2021024610A1 WO 2021024610 A1 WO2021024610 A1 WO 2021024610A1 JP 2020022798 W JP2020022798 W JP 2020022798W WO 2021024610 A1 WO2021024610 A1 WO 2021024610A1
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WO
WIPO (PCT)
Prior art keywords
groove portion
groove
gear
lubricating oil
differential
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.)
Ceased
Application number
PCT/JP2020/022798
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English (en)
French (fr)
Japanese (ja)
Inventor
亜久人 関口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Musashi Seimitsu Industry Co Ltd
Original Assignee
Musashi Seimitsu Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Musashi Seimitsu Industry Co Ltd filed Critical Musashi Seimitsu Industry Co Ltd
Priority to CN202080054959.7A priority Critical patent/CN114207322B/zh
Priority to DE112020003679.0T priority patent/DE112020003679T5/de
Priority to US17/627,765 priority patent/US11655888B2/en
Publication of WO2021024610A1 publication Critical patent/WO2021024610A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/037—Gearboxes for accommodating differential gearings
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0409—Features relating to lubrication or cooling or heating characterised by increasing efficiency, e.g. by reducing splash losses
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F16H2048/087—Differential gearings with gears having orbital motion comprising bevel gears characterised by the pinion gears, e.g. their type or arrangement

Definitions

  • the differential device includes a differential case (differential case) and a differential gear mechanism housed in the differential case.
  • the differential case has a case body and a rotating shaft portion.
  • a storage space for accommodating the differential gear mechanism is formed in the case body.
  • the rotating shaft portion has a tubular shape that protrudes from the case body and has a case through hole that communicates with the accommodating space of the case body, and is rotatably supported around the first rotating shaft.
  • the differential gear mechanism is rotatably arranged around a side gear rotatably arranged around the first rotation axis and a second rotation axis orthogonal to the first rotation axis, and is also rotatably arranged.
  • a differential device having a configuration for supplying lubricating oil to the back side of the pinion gear (between the back side of the pinion gear and the inner surface of the case body).
  • an introduction groove for introducing lubricating oil into the accommodation space of the case body is formed on the inner peripheral surface of the rotating shaft portion.
  • an inner groove is formed on the inner surface of the case body so as to communicate with the introduction groove and extend toward the back side of the pinion gear.
  • the supplied lubricating oil flows toward the back side of the pinion gear in the inner groove due to the centrifugal force applied to the rotating differential case, and reaches the back side of the pinion gear, for example, seizure or destruction of the back surface of the pinion gear and the inner surface of the case body. Is suppressed. As a result, the smooth rotational operation of the pinion gear is maintained (for example, Patent Document 1).
  • An object of the present invention is to provide a differential device capable of solving the above-mentioned problems.
  • the differential device disclosed in the present specification has a case main body in which a storage space is formed and a tubular shape having a case through hole that protrudes from the case main body and communicates with the storage space.
  • a differential case having a rotary shaft portion rotatably supported around the first rotary shaft, and a differential case housed in the accommodation space of the differential case, and rotatably arranged around the first rotary shaft.
  • an introduction groove for introducing lubricating oil into the accommodation space of the case body is formed on the inner peripheral surface of the rotating shaft portion, and the inner surface of the case body communicates with the introduction groove.
  • an inner groove extending toward the back surface side of the pinion gear is formed, and the inner groove is located radially outside the first groove portion and the first groove portion in the case body.
  • the shape of at least a part of the first groove portion includes the second groove portion, and the shape of at least a part of the first groove portion has a shape that makes it difficult for the lubricating oil to get over when the vehicle advances, as compared with the shape of the second groove portion.
  • an inner surface groove communicating with the introduction groove formed in the rotating shaft portion is formed on the inner surface of the case body, and the inner surface groove includes a second groove portion and a first groove portion. Includes.
  • the second groove portion is arranged radially outside the first groove portion.
  • the shape of at least a part of the first groove portion has a shape that makes it difficult for the lubricating oil to get over when the vehicle advances, as compared with the shape of the second groove portion.
  • the inner wall surface on the rear side in the forward rotation direction which is the rotation direction of the differential case when the vehicle is moving forward
  • the groove portion may be configured to be steeper than the inner wall surface on the rear side in the forward rotation direction.
  • the inner groove portion has a relatively simple configuration in which the steepness of the inner wall surface on the rear side in the forward rotation direction is different from each other for the second groove portion and the first groove portion.
  • the inner surface groove has a third groove portion located radially inside the first groove portion, and at least a part of the shape of the third groove portion has a shape.
  • the shape is such that the lubricating oil can easily get over when the vehicle is moving forward, and the third groove portion may be covered with the back surface of the side gear.
  • the shape of the third groove portion of the inner groove portion which is located radially inside the first groove portion, is such that the lubricating oil is removed when the vehicle is advanced as compared with the first groove portion. The shape is easy to get over.
  • the inner wall surface on the rear side in the forward rotation direction which is the rotation direction of the differential case when the vehicle is moving forward
  • the groove portion may have a configuration in which the inclination is gentler than that of the inner wall surface on the rear side in the forward rotation direction.
  • the inner groove portion has a relatively simple configuration in which the steepness of the inner wall surface on the rear side in the forward rotation direction is different from each other for the first groove portion and the third groove portion. The smooth rotation operation of the side gear is maintained while suppressing unnecessary scattering of the lubricating oil on the inner side in the radial direction.
  • the second groove portion may be covered with the back surface of the pinion gear. According to this differential device, the amount of lubricating oil that reaches the back surface of the pinion gear more effectively is suppressed because the unnecessary scattering of the lubricating oil inside the inner groove in the radial direction is suppressed until the lubricating oil reaches the back surface of the pinion gear. Is increased, and the smooth rotation operation of the pinion gear is maintained.
  • the first groove portion may be located between the back surface of the side gear and the back surface of the pinion gear. According to this differential device, wasteful scattering of lubricating oil between the back surface of the side gear and the back surface of the pinion gear is suppressed, so that the pinion gear is smoothly supplied by supplying sufficient lubricating oil to the back side of the pinion gear. The rotational operation can be maintained.
  • FIG. 1 is a cross-sectional view showing the configuration of the differential device 1 in the present embodiment.
  • FIG. 1 shows a planar configuration of the drive shafts 62 and 64 and the bolt 29, which will be described later.
  • FIG. 1 shows XYZ axes that are orthogonal to each other to specify the direction.
  • the Z-axis positive direction upper direction of the paper surface
  • the Z-axis negative direction downward direction
  • the X-axis positive direction is referred to as a right direction
  • the negative axis direction is referred to as the left direction.
  • the differential device 1 is housed in, for example, a transmission case 2 of an automobile together with a transmission (not shown).
  • a circular right hole 3 centered on the first rotation axis X1 along the left-right direction (X-axis direction) is formed, and the left side of the right hole 3 (of the mission case 2).
  • an annular right-hand bearing 5 centered on the first rotation axis X1 is arranged.
  • a circular left hole 4 centered on the first rotation axis X1 is formed on the left wall of the mission case 2, and a first hole 4 is formed on the right side of the left hole 4 (on the internal space side of the mission case 2).
  • An annular left bearing 6 centered on the rotating shaft X1 is arranged.
  • the differential device 1 includes a differential case 10 and a differential gear mechanism 50.
  • the differential case 10 is rotatably supported by the pair of bearings 5 and 6 described above in the transmission case 2, and also houses the differential gear mechanism 50 inside.
  • the differential case 10 has a case main body 20 and a pair of rotating shaft portions (right side rotating shaft portion 30 and left rotating shaft portion 40).
  • the differential case 10 is made of, for example, metal.
  • the case body 20 is, for example, a hollow substantially spherical body.
  • An accommodation space 22 for accommodating the differential gear mechanism 50 is formed inside the case body 20.
  • a pair of openings 24 (also referred to as "work windows”, see FIG. 2 below) that open from the accommodation space 22 to the outside of the case body 20 are formed on the peripheral wall of the case body 20.
  • the pair of openings 24 are formed in the peripheral wall of the case body 20 at positions facing each other with the first rotation axis X1 interposed therebetween.
  • the components of the differential gear mechanism 50 are inserted into the accommodation space 22 of the case body 20 through the opening 24.
  • An annular flange 26 centered on the first rotation shaft X1 is provided on the outer peripheral surface of the case body 20, and a ring gear 28 is fastened to the flange 26 via a bolt 29.
  • the ring gear 28 meshes with the output gear 8 of the transmission.
  • the ring gear 28 may be joined to the flange 26 by welding or the like without using the bolt 29. Further, the ring gear 28 may be integrally formed with the case body 20.
  • the right side rotation shaft portion 30 has a cylindrical shape in which a right side through hole 32 is formed, and is formed so as to project from the right outer surface of the peripheral wall of the case body 20 to the right side.
  • the left rotation shaft portion 40 has a cylindrical shape in which a left through hole 42 is formed, and is formed so as to project to the left from the outer surface of the left end of the peripheral wall of the case body 20.
  • the central axis of both the right side rotating shaft portion 30 and the left side rotating shaft portion 40 substantially coincides with the first rotating shaft X1. Both the right through hole 32 of the right rotating shaft portion 30 and the left through hole 42 of the left rotating shaft portion 40 communicate with the accommodation space 22 of the case body 20.
  • the right rotary shaft portion 30 is rotatably supported by the right bearing 5 arranged in the mission case 2, and the left rotary shaft portion 40 is rotatably supported by the left bearing 6 arranged in the mission case 2.
  • the differential case 10 can rotate about the first rotation axis X1 in the mission case 2.
  • the differential gear mechanism 50 includes a pinion shaft 52, a pair of pinion gears 54, and a right side gear 56 and a left side gear 58. Both the pinion gear 54 and the side gears 56 and 58 are composed of bevel gears.
  • the pinion shaft 52 is arranged along a second rotation axis Z1 substantially orthogonal to the first rotation axis X1, and both ends of the pinion shaft 52 are inserted and fixed in holes 23 formed through the peripheral wall of the case body 20. Has been done.
  • the pair of pinion gears 54 are arranged so as to be separated from each other, and are rotatably supported by the pinion shaft 52 about a second rotation shaft Z1.
  • the pinion gear 54 is not limited to a pair, and may be configured to include, for example, three, four, or more. Further, the pinion shaft 52 may be fixed to, for example, a ring gear 28, instead of being fixed to the differential case 10 (case body 20).
  • the fixing method is not limited to the same method as in the present embodiment, and may be, for example, a method using a fixture, welding, or the like.
  • the right side gear 56 is located on the right side of the pair of pinion gears 54 and is arranged so as to mesh with both of the pair of pinion gears 54. Further, the right side gear 56 is formed with a gear inner peripheral portion 57 penetrating in the direction of the first rotating shaft X1, and the right side connected to the gear inner peripheral portion 57 to the right axle (not shown).
  • the drive shaft 62 is fixed by being fitted, and can rotate integrally with the right drive shaft 62.
  • the left side gear 58 is located on the left side of the pair of pinion gears 54 and is arranged so as to mesh with both of the pair of pinion gears 54.
  • the left side gear 58 is formed with a gear inner peripheral portion 57 penetrating in the direction of the first rotating shaft X1, and the left side connected to the gear inner peripheral portion 57 to the left axle (not shown). It is fixed to the drive shaft 64 and can rotate integrally with the left drive shaft 64.
  • the right drive shaft 62 is rotatably supported in the right hole 3 formed in the transmission case 2 via the seal member 7.
  • the left drive shaft 64 is rotatably supported in the left hole 4 formed in the transmission case 2 via the seal member 7.
  • a common passage R1 (in FIG. 1, only the common passage R1 on the right side of the rotating shaft portion 30 is shown) is formed.
  • the common passage R1 is formed by, for example, a spiral-shaped guide groove 33 formed on the inner peripheral surface 32A of each of the rotating shaft portions 30 and 40.
  • One end of the common communication passage R1 (guide groove 33) communicates with, for example, an introduction path R formed in the mission case 2 (in FIG.
  • the other end of the common communication passage R1 (guide groove 33) is a communication passage between the outer peripheral surfaces of the side gears 56 and 58 and the inner surface 21 (inner wall) of the differential case 10 (hereinafter referred to as "gear outer peripheral side communication passage R2"). Communicate with. Further, the other end of the common communication passage R1 is a communication passage between the gear inner peripheral portion 57 of each side gear 56, 58 and the outer peripheral surface of each drive shaft 62, 64 (hereinafter, “gear inner peripheral side communication passage R3””. It also communicates with).
  • the gear inner peripheral side continuous passage R3 extends to the space on the pinion shaft 52 side.
  • the gear inner peripheral side continuous passage R3 is formed as follows, for example.
  • the side gears 56 and 58 are spline-coupled to the drive shafts 62 and 64, and for example, a part of the plurality of spline teeth formed on the inner peripheral portion 57 of the gear is missing, so that the inside of the gear is in the gear.
  • a peripheral communication passage R3 is formed.
  • the guide groove 33 corresponds to the introduction groove in the claims, and the right through hole 32 corresponds to the case through hole in the claims.
  • differential device 1 With the above configuration, in the differential device 1, when power from a power source (not shown) is transmitted to the transmission and the output gear 8 rotates, the ring gear 28 that meshes with the output gear 8 rotates. When the ring gear 28 rotates, the differential case 10 rotates about the first rotation shaft X1 as the ring gear 28 rotates. When the differential case 10 rotates, the right drive shaft 62 and the left drive shaft 64 are rotationally driven via a pair of pinion gears 54 and a pair of side gears 56 and 58, respectively.
  • the lubricating oil U is introduced into the guide grooves 33 of the rotating shaft portions 30 and 40 of the differential case 10 via the introduction path R.
  • the lubricating oil U enters the accommodation space 22 of the differential case 10 via the common communication passage R1 (guide groove 33) due to the screw pumping action due to the spiral shape of the guide groove 33 as the differential case 10 rotates. Is supplied to.
  • a part of the lubricating oil U supplied into the accommodation space 22 via the common communication passage R1 passes through the gear outer peripheral side communication passage R2, so that seizure or destruction of the side gears 56 and 58 and the differential case 10 occurs.
  • FIG. 2 is an explanatory view partially showing the configuration of the case body 20 of the differential case 10 on the inner surface 21 side.
  • FIG. 2 shows the YZ cross-sectional configuration of the differential case 10 at the position II-II of FIG. That is, FIG. 2 shows a region on the inner surface 21 of the case body 20 on the right side rotation shaft portion 30 side.
  • the configuration (pinion shaft 52, pinion gear 54, side gears 56, 58) housed in the differential case 10 is omitted. Further, FIG.
  • FIG. 3 is a cross-sectional view showing the configuration of the inner surface groove 25 at the position III-III of FIG.
  • the clockwise direction of the first rotation axis X1 in FIG. 2 is the rotation direction when the vehicle moves forward (hereinafter, referred to as "forward rotation direction L").
  • the region on the right side rotating shaft portion 30 side of the inner surface 21 of the case body 20 includes the side gear facing region 21A, the intermediate region 21B, and the pinion gear facing region 21C.
  • the side gear facing region 21A is an annular region of the inner surface 21 of the case body 20 that is covered with the back surface (outer peripheral surface) of the right side gear 56 and is in contact with and supported by the back surface of the right side gear 56.
  • the back surface of the right side gear 56 is a surface of the right side gear 56 facing the inner surface 21 of the case body 20.
  • the intermediate region 21B is located on the inner surface 21 of the case body 20 outside the case body 20 in the radial direction (direction orthogonal to the first rotation axis X1) from the side gear facing region 21A, and is located on the back surface of the right side gear 56. It is an annular region that is not covered by any of the back surface of the pinion gear 54.
  • the intermediate region 21B includes a region corresponding to a portion where the teeth 54A and 56A of the right side gear 56 and the pinion gear 54 are in mesh with each other.
  • the pinion gear facing region 21C is located on the inner surface 21 of the case body 20 and outside the intermediate region 21B in the radial direction, and is covered with the back surface (outer peripheral surface) of the pinion gear 54 and in contact with the back surface of the pinion gear 54. It is an annular region that supports and supports.
  • the back surface of the pinion gear 54 is a surface of the pinion gear 54 facing the inner surface 21 of the case body 20.
  • an inner groove 25 is formed on the inner surface 21 of the case body 20.
  • the inner surface groove 25 communicates with the guide groove 33 formed in the right rotating shaft portion 30, and the inner surface groove 25 extends toward the back surface side of the pinion gear 54.
  • the fact that the inner surface groove 25 and the guide groove 33 are in communication is not limited to the case where the inner surface groove 25 and the guide groove 33 are in direct communication with each other, but also in a predetermined space (right side gear 56 and right rotation shaft). It also includes the case of communicating through a gap (gap between the portions 30) (see FIG. 2).
  • the inner surface groove 25 extends so that the closer to the back surface side of the pinion gear 54, the longer the distance from the first rotation shaft X1.
  • the centrifugal force received by the rotation of the differential case 10 increases toward the portion of the inner groove 25 closer to the back surface side of the pinion gear 54, and as a result, the lubricating oil U flowing from the guide groove 33 to the inner groove 25 mainly flows. , Flows along the inner groove 25 to the back side of the pinion gear 54.
  • the end on the guide groove 33 side may be referred to as the "base end of the inner surface groove 25", and the end on the pinion gear 54 side may be referred to as the "tip of the inner surface groove 25".
  • the inner surface groove 25 extends from the vicinity of the guide groove 33 formed in the right rotating shaft portion 30 to the side gear facing region 21A and the intermediate region 21B and extends to the pinion gear facing region 21C. ing.
  • the tip of the inner surface groove 25 does not reach the hole 23 formed in the inner surface 21 of the case body 20.
  • the portion of the inner surface groove 25 located in the side gear facing region 21A is referred to as a "base end gutter portion 25A”
  • the portion located in the intermediate region 21B is referred to as an “intermediate groove portion 25B” and is located in the pinion gear facing region 21C.
  • the portion to be used is referred to as "tip side groove portion 25C".
  • the base end side groove portion 25A is a portion covered by the back surface of the right side gutter 56
  • the tip end side groove portion 25C is a portion covered by the back surface of the pinion gear 54
  • the intermediate groove portion 25B is a portion that is not covered by either the back surface of the right side gear 56 or the back surface of the pinion gear 54.
  • FIG. 4 is an explanatory view showing a cross-sectional shape of the inner groove 25.
  • the cross-sectional shape of the inner surface groove 25 means a shape of a cross section substantially perpendicular to the longitudinal direction (stretching direction) of the inner surface groove 25.
  • the second cross-sectional shape shown in FIG. 4B has a shape that makes it difficult for the lubricating oil U to get over the inner groove 25 when the vehicle is moving forward, as compared with the first cross-sectional shape (A) shown in FIG. 4A.
  • the inner surface groove 25 is a V-shaped groove, and the reference numeral N in FIGS. 2 and 4 means the bottom portion of the inner surface groove 25.
  • the inner wall surface (rear inner wall surface) 74 on the rear side (left side of FIG. 4 (B)) in the forward rotation direction L in the shape (B) is a substantially flat surface.
  • the rear inner wall surface 74 in the second cross-sectional shape (B) is steeper than the rear inner wall surface 74 in the first cross-sectional shape (A).
  • FIGS. 4A and 4B a straight line parallel to the straight line connecting the contact points P between the inner surface groove 25 and each of the pair of inner surface 21 portions adjacent to the inner surface groove 25 is referred to as a virtual straight line Q. To do. Further, the inner wall surface (hereinafter, referred to as “front inner wall surface”) 72 on the front side (right side of FIGS. 4A and 4B) in the forward rotation direction L in each of the cross-sectional shapes (A) and (B) is used.
  • the inclination angle of the rear inner wall surface 74 with respect to the virtual straight line Q is set to “first inclination angle ⁇ 1”, and the inclination angle of the front inner wall surface 72 with respect to the virtual straight line Q is set to “third”.
  • the tilt angle ⁇ 3 is set in the second cross-sectional shape (B), the inclination angle of the rear inner wall surface 74 with respect to the virtual straight line Q is set to "second inclination angle ⁇ 2", and the inclination angle of the front inner wall surface 72 with respect to the virtual straight line Q is set to "fourth”.
  • the tilt angle ⁇ 4 The second tilt angle ⁇ 2 is larger than the first tilt angle ⁇ 1.
  • the second cross-sectional shape (B) has a shape that makes it difficult for the lubricating oil U to get over the inner groove 25 when the vehicle is moving forward, as compared with the first cross-sectional shape (A).
  • the degree of difficulty in overcoming the above can be determined from the magnitude of the amount of oil that the lubricating oil U flows out from the inner groove 25 when the differential case 10 is rotated. For example, it can be determined that the smaller the amount of lubricating oil U that flows out, the more difficult it is to overcome.
  • the third tilt angle ⁇ 3 is substantially the same as the first tilt angle ⁇ 1. That is, the lubricating oil U is prevented from getting over the inner groove 25 when the vehicle is moving forward and when the vehicle is moving backward, and the difficulty of getting over is about the same.
  • the fourth tilt angle ⁇ 4 is smaller than the second tilt angle ⁇ 2. That is, when the vehicle is moving backward, the lubricating oil U is more likely to get over the inner groove 25 than when the vehicle is moving forward.
  • FIG. 5 is an explanatory view showing a pattern of the cross-sectional shape of the inner surface groove 25 in Examples 1 to 4.
  • the arrangement relationship between the inner surface groove 25 and each region (side gear facing region 21A, intermediate region 21B, pinion gear facing region 21C) on the inner surface 21 of the case body 20 is schematically shown.
  • the cross-sectional shape of the white portion of the inner groove 25 in each pattern which is labeled "(A)" and is not shaded, is the first cross-sectional shape (A) described above, and is "(B). ) ”,
  • the cross-sectional shape of the shaded portion shall be the second cross-sectional shape (B) described above.
  • the arrangement of the groove portion having the first cross-sectional shape (A) and the groove portion having the second cross-sectional shape (B) in the inner surface groove 25 is different from each other.
  • the cross-sectional shape of the white portion in the base end side groove portion 25A and the tip end side groove portion 25C of the inner surface groove 25 is the first cross-sectional shape (A), and the intermediate groove.
  • the cross-sectional shape of the portion 25B and the shaded portion in the proximal end gutter portion 25A and the distal end gutter portion 25C is the second cross-sectional shape (B).
  • the white portion of the tip side groove portion 25C is located radially outside the case body 20 from the shaded portion of the intermediate groove portion 25B and the tip side groove portion 25C.
  • the cross-sectional shape of the shaded portion of the intermediate groove portion 25B and the tip side groove portion 25C has a shape that makes it difficult for the lubricating oil U to get over when the vehicle advances, as compared with the cross-sectional shape of the white portion of the tip side groove portion 25C.
  • the lubricating oil U when the vehicle is moving forward, the lubricating oil U is suppressed from being unnecessarily scattered in the intermediate groove portion 25B of the inner surface groove 25, and the inner surface groove 25 is radially outside (the tip side groove portion 25C). It becomes easy to be supplied to the tip). As a result, the amount of lubricating oil U reaching the back surface of the pinion gear 54 increases, and the smooth rotational operation of the pinion gear 54 is maintained.
  • the tip side groove portion 25C is located in the pinion gear facing region 21C on the inner surface 21 of the case body 20, and is covered with the back surface of the pinion gear 54. Therefore, until the lubricating oil U reaches the back surface of the pinion gear 54, unnecessary scattering of the lubricating oil U inside the inner groove 25 in the radial direction is suppressed, so that the lubricating oil U reaching the back surface of the pinion gear 54 more effectively. The amount of the pinion gear 54 is increased, and the smooth rotation operation of the pinion gear 54 is maintained.
  • the intermediate groove portion 25B is located between the back surface of the right side gear 56 and the back surface of the pinion gear 54.
  • the white portion of the base end side groove portion 25A is located inside the case body 20 in the radial direction from the shaded portion of the intermediate groove portion 25B and the base end side groove portion 25A.
  • the cross-sectional shape of the white portion of the base end gutter portion 25A has a shape that allows the lubricating oil U to easily get over when the vehicle advances, as compared with the cross-sectional shape of the shaded portion of the intermediate groove portion 25B and the base end gutter portion 25A. There is.
  • the cross-sectional shape of the inner groove 25 is not only the entire intermediate groove portion 25B, but also a part of the proximal end side groove portion 25A and the distal end side groove portion 25C adjacent to the intermediate groove portion 25B. It has a second cross-sectional shape (B).
  • the cross-sectional shape of a part of the intermediate groove portion 25B is the first cross-sectional shape (A)
  • the cross-sectional shape of only the intermediate groove portion 25B is the first cross-sectional shape (A). It is possible to more effectively suppress unnecessary scattering of the lubricating oil U from the inner groove 25 when the vehicle is moving forward.
  • the intermediate groove portion 25B and the shaded portion in the proximal end side groove portion 25A and the distal end side groove portion 25C correspond to the first groove portion in the claims and are white in the distal end side groove portion 25C.
  • the hollow portion corresponds to the second groove portion in the claims, and the white portion in the proximal gutter portion 25A corresponds to the third groove portion in the claims.
  • the second embodiment is different from the first embodiment in that not only the intermediate groove portion 25B but also the entire proximal end side groove portion 25A of the inner surface groove 25 has a second cross-sectional shape (B). ..
  • B second cross-sectional shape
  • unnecessary scattering of the lubricating oil U on the radial inside of the inner surface groove 25 (intermediate groove portion 25B and the proximal end side groove portion 25A) is suppressed when the vehicle advances, and the lubricating oil U is suppressed. Is easily supplied to the radial outer side of the inner surface groove 25 (tip side groove portion 25C).
  • the intermediate groove portion 25B, the base end side groove portion 25A, and the shaded portion in the tip end side groove portion 25C correspond to the first groove portion in the claims, and the tip end side groove portion 25C.
  • the white portion corresponds to the second groove portion in the claims.
  • the cross-sectional shape is the first cross-sectional shape (A) of only the tip portion of the tip side groove portion 25C of the inner surface groove 25 with respect to the second embodiment, and the intermediate groove portion 25B side from the tip portion.
  • the cross-sectional shape is the second cross-sectional shape (B).
  • Example 3 the intermediate groove portion 25B and the shaded portion in the proximal end side groove portion 25A and the distal end side groove portion 25C correspond to the first groove portion in the claims, and the white portion in the distal end side groove portion 25C.
  • the hollow portion corresponds to the second groove portion in the claims, and the white portion in the proximal gutter portion 25A corresponds to the third groove portion in the claims.
  • the fourth embodiment is different from the third embodiment in that not only the intermediate groove portion 25B but also the entire proximal end side groove portion 25A of the inner surface groove 25 has a second cross-sectional shape (B). ..
  • B second cross-sectional shape
  • the fourth embodiment when the vehicle is moving forward, unnecessary scattering of the lubricating oil U in the middle of the intermediate groove portion 25B, the base end side groove portion 25A, and the tip end side groove portion 25C of the inner surface groove 25 is suppressed, and lubrication is performed.
  • the oil U is easily supplied to the tip of the inner groove 25.
  • the intermediate groove portion 25B, the base end side groove portion 25A, and the shaded portion in the tip end side groove portion 25C correspond to the first groove portion in the claims, and the tip end side groove portion 25C.
  • the white portion corresponds to the second groove portion in the claims.
  • the inner wall surfaces of the groove portion of the first cross-sectional shape (A) and the groove portion of the second cross-sectional shape (B) may be connected to each other via a step, but lubrication may be performed.
  • the inner wall surfaces of both groove portions are continuously connected to each other via a curved surface without a step (see FIG. 2).
  • the connecting portion (transition portion) between the groove portion of the first cross-sectional shape (A) and the groove portion of the second cross-sectional shape (B) is an intermediate groove in the inner surface groove 25. It is preferable to arrange it in a portion other than the portion 25B.
  • the scattering of the lubricating oil U in the intermediate region 21B can be suppressed more effectively.
  • the lubricating oil U when the differential case 10 is rotated in the forward rotation direction L, the lubricating oil U is biased toward the rear inner wall surface 74 of the inner surface groove 25, so that there is a convex step on the rear inner wall surface 74. , The transmission of the lubricating oil U to the back surface side of the pinion gear 54 may be hindered. Therefore, as shown in FIG. 2, the rear inner wall surface 74 in the intermediate groove portion 25B is located on the rear side in the forward rotation direction L with respect to the rear inner wall surface 74 in the proximal end side groove portion 25A, and is a connecting portion (transition).
  • the rear inner wall surface 74 of the portion does not form a convex step.
  • the rear inner wall surface 74 in the tip side groove portion 25C is located on the rear side in the forward rotation direction L with respect to the rear inner wall surface 74 in the intermediate groove portion 25B, and the rear inner wall surface 74 of the connecting portion (transition portion) is convex. It is preferable that there is no stepped shape. As a result, it is possible to suppress a decrease in the transmission efficiency of the lubricating oil U at the connecting portion between the groove portion of the first cross-sectional shape (A) and the groove portion of the second cross-sectional shape (B) in the inner surface groove 25. .. As shown in FIG. 2, the bottom portion N of the base end side groove portion 25A, the intermediate groove portion 25B, and the tip end side groove portion 25C is continuously connected over the entire length of the inner surface groove 25.
  • the differential case 10 in the above embodiment is just an example and can be variously modified.
  • the differential case 10 has a configuration in which a pair of openings 24 are formed, but for example, a configuration in which only one opening 24 is formed or three or more openings 24 are formed. It may have a configuration or a configuration in which the opening 24 is not formed.
  • the space between the inner peripheral surfaces 32A and 42A constituting the through holes 32 and 42 of the rotating shaft portions 30 and 40 and the outer peripheral surfaces of the drive shafts 62 and 64 (common passage R1). was formed by the spiral guide groove 33, but the space may be formed by, for example, a groove linearly extending along the direction of the first rotation axis X1.
  • FIG. 6 is an explanatory view showing a pattern of the cross-sectional shape of the inner surface groove 25 in the modified examples 1 and 2.
  • FIG. 6 for each pattern, the arrangement relationship between the inner surface groove 25 and each region (side gear facing region 21A, intermediate region 21B) on the inner surface 21 of the case body 20 is schematically shown.
  • the meanings of "(A)" and "(B)” in FIG. 6 and the presence or absence of shading are the same as those in FIG. 5 described above.
  • Modifications 1 and 2 differ from Examples 1 to 4 in that the inner surface groove 25 has a base end side groove portion 25A and an intermediate groove portion 25B, but does not have a tip end side groove portion 25C.
  • the inner surface groove 25 crosses the side gear facing region 21A from the vicinity of the guide groove 33 formed in the right side rotating shaft portion 30, and the tip of the inner surface groove 25 reaches the middle of the intermediate region 21B. It is extending.
  • the arrangement of the groove portion having the first cross-sectional shape (A) and the groove portion having the second cross-sectional shape (B) in the inner surface groove 25 is different from each other.
  • the cross-sectional shape of the white portion in the base end side groove portion 25A and the intermediate groove portion 25B in the inner surface groove 25 is the first cross-sectional shape (A), and the base end.
  • the cross-sectional shape of the shaded portion in the gutter portion 25A and the intermediate groove portion 25B is the second cross-sectional shape (B).
  • the white portion of the intermediate groove portion 25B is located radially outside the case body 20 from the shaded portion of the intermediate groove portion 25B and the proximal end side groove portion 25A.
  • the lubricating oil U when the vehicle is moving forward, the lubricating oil U is prevented from being unnecessarily scattered on the most basic end side of the intermediate groove portion 25B of the inner surface groove 25, and the intermediate groove portion 25B of the inner surface groove 25 is suppressed. It becomes easy to be supplied to the tip of. As a result, the amount of lubricating oil U reaching the back surface of the pinion gear 54 increases, and the smooth rotational operation of the pinion gear 54 is maintained.
  • the white portion of the base end side groove portion 25A is located inside the case body 20 in the radial direction from the shaded portion of the intermediate groove portion 25B and the base end side groove portion 25A.
  • the amount of lubricating oil U that reaches the back surface of the right side gear 56 on the most proximal side of the proximal gutter portion 25A increases, and the smooth rotation operation of the right side gear 56 is maintained.
  • the shaded portion in the intermediate groove portion 25B and the base end side groove portion 25A corresponds to the first groove portion in the claims, and the white portion in the intermediate groove portion 25B is claimed for patent.
  • the white portion in the proximal end side groove portion 25A corresponds to the third groove portion in the claims.
  • the modified example 2 is different from the modified example 1 in that not only the intermediate groove portion 25B but also the entire proximal end side groove portion 25A of the inner surface groove 25 has a cross-sectional shape of the second cross-sectional shape (B). ..
  • the modified example 2 wasteful scattering of the lubricating oil U on the radial inside of the inner surface groove 25 (the proximal end side and the proximal end side groove portion 25A of the intermediate groove portion 25B) is suppressed when the vehicle advances.
  • Lubricating oil U is easily supplied to the radial outer side of the inner surface groove 25 (the tip end portion of the intermediate groove portion 25B).
  • the shaded portion of the intermediate groove portion 25B and the base end side groove portion 25A correspond to the first groove portion in the claims, and the white portion in the intermediate groove portion 25B is claimed for patent. Corresponds to the second groove portion in the range of.
  • FIG. 7 is an explanatory view showing the second cross-sectional shapes (B1 to B3) of the inner surface grooves 25 in the modified examples 3 to 5.
  • the second cross-sectional shape (B1) in the modified example 3 is rearward with respect to the second cross-sectional shape (B) in the above embodiment (see FIG. 4 (B)).
  • the difference is that the wall surface 74a is a curved surface rather than a flat surface.
  • the second cross-sectional shape (B1) is arcuate.
  • the fifth tilt angle ⁇ 5 which is the tilt angle with respect to the virtual straight line Q on the opening side (near the contact point P) of the rear inner wall surface 74a of the second cross-sectional shape (B1), is the first cross-sectional shape (A) in the above embodiment. ) Is larger than the first inclination angle ⁇ 1 (see FIG. 4 (A)).
  • the second cross-sectional shape (B2, B3) in the modified examples 4 and 5 has a rear inner wall surface 74b with respect to the second cross-sectional shape (B) in the above embodiment.
  • 74c is different in that it is composed of a plurality of planes.
  • the rear inner wall surface 74b is composed of two planes (first plane 76 and second plane 77). Of the two planes, at least the first plane 76 close to the contact point P has a sixth tilt angle ⁇ 6, which is an tilt angle with respect to the virtual straight line Q, and is the first of the first cross-sectional shapes (A) in the above embodiment.
  • the inclination angle of is larger than ⁇ 1.
  • the seventh inclination angle ⁇ 7 which is the inclination angle of the second plane 77 separated from the contact point P with respect to the virtual straight line Q, is also the first of the first cross-sectional shapes (A) in the above embodiment.
  • the rear inner wall surface 74c is composed of three planes (third plane 78, fourth plane 79, fifth plane 80).
  • the eighth inclination angle ⁇ 8, which is the inclination angle with respect to the virtual straight line Q of at least the third plane 78 closest to the contact point P among the three planes, is the first cross-sectional shape (A) in the above embodiment. It is larger than the inclination angle ⁇ 1 of 1.
  • the ninth inclination angle ⁇ 9 which is the inclination angle of the fifth plane 80 separated from the contact point P with respect to the virtual straight line Q, is also the first of the first cross-sectional shapes (A) in the above embodiment.
  • the ninth tilt angle ⁇ 9 may be the same as the first tilt angle ⁇ 1 or may be smaller than the first tilt angle ⁇ 1.
  • the inclination angle of the fourth plane 79 separated from the contact point P with respect to the virtual straight line Q is the first inclination angle ⁇ 1 of the first cross-sectional shape (A) in the above embodiment. Smaller.
  • the inclination angle of the fourth plane 79 may be the same as the first inclination angle ⁇ 1 or may be larger than the first inclination angle ⁇ 1.
  • the inclination angle of the surface portion (in the case of a curved surface, the tangent to the curved surface) of the rear inner wall surfaces 74a to 74c of each second cross-sectional shape (B1 to B3) located closer to the contact point P with respect to the virtual straight line Q.
  • the rear inner wall surface 74 may be composed of four or more surfaces (plane or curved surface).
  • the present invention is applied to the inner surface groove 25 formed in the region on the inner surface 21 of the case body 20 on the right side rotation shaft portion 30 side has been given, but the left rotation shaft portion on the inner surface 21 of the case body 20 has been described.
  • the present invention may be applied to an inner groove formed in the region on the 40 side.
  • the rear inner wall surface 74 in the second cross-sectional shape (B) is steeper than the rear inner wall surface 74 in the first cross-sectional shape (A), so that the lubricating oil U is applied to the inner surface when the vehicle advances.
  • the shape was such that it was difficult to get over the groove 25.
  • the present invention is not limited to this, for example, the inclination angle of the rear inner wall surface 74 of the first cross-sectional shape (A) and the second cross-sectional shape (B) is the same, and the second cross-sectional shape (B) Since the surface roughness (surface resistance) of the rear inner wall surface 74 in the first cross-sectional shape (A) is larger than the surface roughness of the rear inner wall surface 74 in the first cross-sectional shape (A), the lubricating oil U forms the inner surface groove 25 when the vehicle advances. The shape may be difficult to overcome.
  • the lubricating oil U is more likely to get over the inner groove 25 when the vehicle is moving backward than when the vehicle is moving forward.
  • the difficulty of getting over the lubricating oil U may be the same when the vehicle is moving backward and when the vehicle is moving forward.
  • the fourth inclination angle ⁇ 4 of the front inner wall surface 72 may be larger than the first inclination angle ⁇ 1 of the rear inner wall surface 74 in the first cross-sectional shape (A).
  • it may be larger than the third inclination angle ⁇ 3 of the front inner wall surface 72.
  • the rotation speed of the differential case 10 is slower and less frequent than when the vehicle is moving forward. Therefore, as shown in FIG. 4, the front inner wall surface 72 of the inner surface groove 25 (the front inner wall surface in FIG. 7). Even if the present invention is not applied to 72a, 72b, 72c), the amount of the lubricating oil U scattered is small, and the influence on the smooth rotation operation of the pinion gear 54 and the like is small.
  • a thrust washer (not shown) may be arranged between the back surface of the right side gear 56 and the inner surface 21 of the differential case 10.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)
PCT/JP2020/022798 2019-08-02 2020-06-10 差動装置 Ceased WO2021024610A1 (ja)

Priority Applications (3)

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CN202080054959.7A CN114207322B (zh) 2019-08-02 2020-06-10 差动装置
DE112020003679.0T DE112020003679T5 (de) 2019-08-02 2020-06-10 Differentialvorrichtung
US17/627,765 US11655888B2 (en) 2019-08-02 2020-06-10 Differential device

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JP2019143124A JP7306911B2 (ja) 2019-08-02 2019-08-02 差動装置
JP2019-143124 2019-08-02

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WO2024013993A1 (ja) * 2022-07-15 2024-01-18 武蔵精密工業株式会社 伝動装置
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JPH10159943A (ja) * 1996-11-27 1998-06-16 Tochigi Fuji Ind Co Ltd デファレンシャル装置
JP2007002885A (ja) * 2005-06-22 2007-01-11 Aisin Takaoka Ltd 差動装置
JP2017116035A (ja) * 2015-12-25 2017-06-29 トヨタ自動車株式会社 差動ギヤ装置の潤滑構造
JP2019011849A (ja) * 2017-06-30 2019-01-24 トヨタ自動車株式会社 車両用差動装置

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JPH0854097A (ja) * 1994-08-09 1996-02-27 Nissan Diesel Motor Co Ltd 自動車用終減速機差動装置の潤滑構造
EP1895197A3 (en) * 2006-08-28 2011-02-23 Jtekt Corporation Differential case for vehicle
JP2012112516A (ja) 2010-11-05 2012-06-14 Gkn Driveline Japan Ltd デファレンシャル装置
JP6119575B2 (ja) * 2013-11-25 2017-04-26 アイシン・エィ・ダブリュ株式会社 プラネタリキャリヤ
JP2016194362A (ja) * 2015-03-31 2016-11-17 武蔵精密工業株式会社 車両用差動装置
JP2016191418A (ja) * 2015-03-31 2016-11-10 武蔵精密工業株式会社 差動装置
JP2019100504A (ja) * 2017-12-06 2019-06-24 トヨタ自動車株式会社 ディファレンシャル装置
JP6975075B2 (ja) * 2018-03-01 2021-12-01 本田技研工業株式会社 差動装置
JP7014074B2 (ja) * 2018-07-18 2022-02-01 トヨタ自動車株式会社 車両用差動装置
JP7026037B2 (ja) * 2018-12-13 2022-02-25 武蔵精密工業株式会社 差動装置用測定具、および、差動装置の潤滑油量測定方法

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Publication number Priority date Publication date Assignee Title
JPH10159943A (ja) * 1996-11-27 1998-06-16 Tochigi Fuji Ind Co Ltd デファレンシャル装置
JP2007002885A (ja) * 2005-06-22 2007-01-11 Aisin Takaoka Ltd 差動装置
JP2017116035A (ja) * 2015-12-25 2017-06-29 トヨタ自動車株式会社 差動ギヤ装置の潤滑構造
JP2019011849A (ja) * 2017-06-30 2019-01-24 トヨタ自動車株式会社 車両用差動装置

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JP2021025570A (ja) 2021-02-22
US11655888B2 (en) 2023-05-23
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JP7306911B2 (ja) 2023-07-11
CN114207322B (zh) 2023-12-15
CN114207322A (zh) 2022-03-18

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