CN111577855B - Differential device - Google Patents
Differential device Download PDFInfo
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- CN111577855B CN111577855B CN202010417669.6A CN202010417669A CN111577855B CN 111577855 B CN111577855 B CN 111577855B CN 202010417669 A CN202010417669 A CN 202010417669A CN 111577855 B CN111577855 B CN 111577855B
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Classifications
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- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
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- 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
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- 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
- F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
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- 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
- F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
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- 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
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- 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
- F16H2048/387—Shields or washers
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- 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
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Retarders (AREA)
Abstract
The invention provides a differential device, which can restrain the reduction of the support rigidity of a region part of a surface of an input member positioned on the back side of a meshing part of a differential gear and an output gear, wherein the region part is opposite to the back side of the output gear and is particularly applied with a large thrust reaction force, thereby realizing the durability of the input member. The device is provided with: an input member to which a driving force is input; a differential gear supported by the input member, capable of rotating relative to the input member, and capable of revolving around a rotation center of the input member in association with rotation of the input member; a pair of output gears having a tooth portion meshing with the differential gear and a shaft portion radially inward of the tooth portion; washers interposed between the back surfaces of the tooth portions of the respective output gears and the input member; and an oil groove provided in a surface of the input member facing the rear surface of the output gear, the oil groove extending from the periphery of the shaft portion of the output gear to the rear surface of the washer, the oil groove being offset in the circumferential direction of the output gear with respect to the intermeshing portion of the tooth portion and the differential gear.
Description
The present application is a divisional application of chinese invention patent application with the application date of 2016, 6, 17, the name of the differential device and the application number of 201610436532.9.
Technical Field
The present utility model relates to a differential device provided in a vehicle such as an automobile.
Background
Conventionally, patent document 1 discloses: in the differential device, a washer is interposed between the back surface of the tooth portion of each output gear and an input member (for example, differential case), and an oil groove for guiding lubricating oil is recessed in an opposing surface of the input member opposing the back surface of the output gear.
Prior art literature
Patent literature
Patent document 1: japanese patent application laid-open No. 2606235
Patent document 2: japanese patent No. 4803871
Patent document 3: japanese patent laid-open No. 2002-364728
Disclosure of Invention
Problems to be solved by the utility model
In the above-described conventional device, a large thrust reaction force acts from the meshing portion of the output gear and the differential gear via the tooth portion of the output gear and the washer, in particular, in a region portion on the back side of the meshing portion of the output gear and the differential gear, on the opposing surface of the input member opposing the back surface of the output gear.
However, since the oil groove of the conventional device is formed in the region portion of the opposing surface of the input member opposing the rear surface of the output gear, which is located on the rear surface side of the meshing portion, that is, the region portion on which the large thrust reaction force acts, this region portion becomes a factor of decreasing the support rigidity in the region portion where the load is large, and there is a possibility that the durability of the region portion and thus the input member is decreased. Further, the load concentrates on the edge portion of the oil groove, which may cause a decrease in durability of the input member.
Further, such a problem may be particularly remarkable in a differential device such as a differential device in which a thin wall and a light weight of an input member are particularly required, and the differential device is configured to sufficiently enlarge a diameter of an output gear with respect to the differential gear so that, for example, the number of teeth of the output gear can be set sufficiently larger than the number of teeth of the differential gear, thereby realizing flattening of the differential device in the output gear shaft direction.
The present invention has been made in view of the above circumstances, and an object thereof is to provide a differential device capable of solving the above-described problems with a simple structure.
Means for solving the problems
In order to achieve the above object, a differential device of the present invention includes: an input member to which a driving force is input; a differential gear supported by the input member, capable of rotating with respect to the input member, and capable of revolving around a rotation center of the input member in association with rotation of the input member; a pair of output gears having a tooth portion meshing with the differential gear and a shaft portion located radially inward of the tooth portion; a washer interposed between the back surface of the tooth portion of each of the output gears and the input member; and an oil groove recessed in an opposing surface of the input member opposing the rear surface of the output gear, the oil groove extending from a periphery of the shaft portion of the output gear to the rear surface of the washer, the oil groove being disposed offset in a circumferential direction of the output gear with respect to a meshing portion between the tooth portion and the differential gear (this is characteristic 1).
Preferably, the input member has a side wall portion facing the rear surface of the output gear, the side wall portion having a plurality of through holes or recessed holes arranged at intervals in the circumferential direction, and the oil groove is disposed so as to pass between 2 adjacent through holes or recessed holes in the circumferential direction (this is feature 2).
Preferably, an oil reservoir portion facing the outer periphery of the shaft portion of the output gear is recessed in an inner peripheral portion of an opposing surface of the input member opposing the output gear (this is characteristic 3).
Preferably, the oil groove is arranged near the meshing portion in the circumferential direction of the output gear (this is the 4 th feature).
Preferably, the oil grooves are arranged in pairs with the meshing portion interposed therebetween as viewed in a projection plane perpendicular to the rotation axis of the output gear (this is characteristic 5).
Preferably, the differential gear is supported on the input member via a differential gear support portion supported on the input member, and when the number of teeth of the output gear is Z1, the number of teeth of the differential gear is Z2, the diameter of the differential gear support portion is d2, and the pitch cone distance is PCD, the following is satisfied
And Z1/Z2 > 2 is satisfied (this is feature 6).
And preferably Z1/Z2.gtoreq.4 (this is characteristic 7).
And preferably meets Z1/Z2.gtoreq.5.8 (this is characteristic 8).
ADVANTAGEOUS EFFECTS OF INVENTION
According to the 1 st feature of the present invention, there is provided: washers interposed between the back surfaces of the teeth of the respective output gears and the input member; and an oil groove recessed in an opposing surface of the input member opposing the rear surface of the output gear, the oil groove extending from the periphery of the shaft portion of the output gear to the rear surface of the washer, whereby the lubricating oil can be efficiently supplied from the periphery of the shaft portion of the output gear to the rear surface of the washer through the oil groove by centrifugal force, and therefore even if a large thrust reaction force acts on the washer from the differential gear via the output gear, the sliding portion between the washer and the rear surface of the output gear can be sufficiently lubricated. Further, since the oil groove is arranged offset in the circumferential direction of the output gear with respect to the meshing portion between the tooth portion of the output gear and the differential gear, the oil groove can be offset from the region portion of the opposing surface of the input member opposing the rear surface of the output gear, in particular, the region portion on the rear surface side of the meshing portion, which is particularly subjected to a large thrust reaction force, whereby a reduction in the support rigidity of the region portion with a large load can be suppressed, and the durability of the input member can be advantageously improved.
Further, according to feature 2, since the input member has the side wall portion facing the rear surface of the output gear, and the side wall portion has the plurality of through holes or concave holes arranged at intervals in the circumferential direction, the oil groove is disposed so as to pass between the 2 through holes or concave holes adjacent in the circumferential direction, the weight of the input member can be reduced by providing the through holes or concave holes in particular, while taking into consideration the weight balance of the input member, and the oil groove can be formed sufficiently long (i.e., without being interrupted by the through holes or the like in the middle) while avoiding the through holes or concave holes.
Further, in particular, according to feature 3, since the oil reservoir portion facing the outer periphery of the shaft portion of the output gear is recessed in the inner peripheral portion of the facing surface of the input member facing the output gear, the supply of the lubricating oil to the oil reservoir can be appropriately adjusted by the oil reservoir portion, for example, in the early stage of the differential operation of the differential device, the lubricating oil can be smoothly supplied to the oil reservoir and further to the gasket or the like by the lubricating oil of the oil reservoir portion, and the remaining lubricating oil can be temporarily stored in the oil reservoir portion to prepare for the shortage of the supply to the oil reservoir.
Further, according to the 4 th aspect in particular, since the oil groove is arranged in the vicinity of the meshing portion in the circumferential direction of the output gear, the oil groove can be displaced as close as possible to the region portion on the opposite surface of the input member, which is opposite to the back surface of the output gear, in which a large thrust reaction force acts in particular, that is, the region portion on the back surface side of the meshing portion, and therefore, the reduction in the support rigidity of the region portion with a large load can be suppressed, and the region portion can be effectively lubricated.
Further, in particular, according to feature 5, the oil grooves are arranged in pairs with the engagement portions interposed therebetween, so that it is possible to suppress a decrease in the supporting rigidity of the region portion where the load is large, and to lubricate the region portion more effectively.
In particular, according to feature 6, since the differential device can be sufficiently narrowed in the axial direction of the output shaft while ensuring the same degree of strength (for example, static torsional load strength) and maximum torque transmission as those of the conventional device, the differential device can be easily assembled with a high degree of freedom even in a transmission system having a large limitation in layout around the differential device, and the transmission system can be advantageously miniaturized.
In particular, according to each of the features 7 and 8, the differential device as a whole can be further sufficiently narrowed in the axial direction of the output shaft while ensuring the same degree of strength (for example, static torsional load strength) and maximum torque transmission amount as those of the conventional device.
Drawings
Fig. 1 is a longitudinal sectional view (sectional view taken along line 1A-1A in fig. 2) of a main portion of a differential device and a reduction gear mechanism according to embodiment 1 of the present invention.
Fig. 2 is a cross-sectional view taken along line 2A-2A in fig. 1.
Fig. 3 is a cross-sectional view taken along line 3A-3A in fig. 1.
Fig. 4 is an enlarged view of the 4A arrow pointing portion in fig. 1 and a partial enlarged view thereof, and a load distribution diagram.
Fig. 5 is an enlarged cross-sectional view showing a main portion (a meshing portion of a pinion gear and a side gear) of a differential device according to embodiment 2 of the present invention.
Fig. 6 is an enlarged cross-sectional view (corresponding to the enlarged partial view of fig. 4) showing a main part of the differential device according to embodiment 3 of the present invention.
Fig. 7 is a longitudinal sectional view showing an example of a conventional differential device.
Fig. 8 is a graph showing the relationship between the gear strength change rate and the gear ratio when the number of teeth of the pinion is 10.
Fig. 9 is a graph showing the relationship of the gear strength change rate with respect to the change rate of pitch cone distance.
Fig. 10 is a graph showing the relationship of the rate of change of the pitch cone with respect to the gear ratio in the case where the gear strength is maintained at 100% at the gear number of the pinion gear of 10.
FIG. 11 is a chart showing the relationship between the gear ratio and the ratio of the shaft diameter/pitch cone when the number of teeth of the pinion is set to 10.
FIG. 12 is a chart showing the relationship between the gear ratio and the ratio of the shaft diameter/pitch cone when the number of teeth of the pinion is set to 6.
FIG. 13 is a chart showing the relationship between the gear ratio and the ratio of the shaft diameter/pitch cone when the number of teeth of the pinion gear is 12.
FIG. 14 is a chart showing the relationship between the gear ratio and the ratio of the shaft diameter/pitch cone when the number of teeth of the pinion gear is set to 20.
Description of the reference numerals
Cs: a side wall portion;
d: a differential device;
DC: a transmission case (input member);
g: an oil groove;
h: a through hole;
i: an engagement portion;
p: pinion (differential gear);
PCD: pitch cone distance;
PS: pinion shafts (differential gear supporting portions);
PS': a support shaft (differential gear support portion);
s: side gears (output gears);
sg: a tooth portion;
sj: a shaft portion;
t: an oil storage section;
d2: the diameter of the pinion shaft, the diameter of the support shaft (the diameter of the differential gear support portion);
f: the back of the side gear (back of the output gear).
Detailed Description
Embodiments of the present invention will be described based on the drawings.
First, embodiment 1 of the present invention will be described with reference to fig. 1 to 4. In fig. 1, a differential device D is connected to an engine (not shown) as a power source mounted on an automobile via a reduction gear mechanism RG. The differential device D distributes and transmits a rotational force transmitted from the engine to the differential case DC via the reduction gear mechanism RG to output shafts J, J' connected to a pair of axles arranged in the vehicle width direction, respectively, thereby allowing the two axles to be driven in a differential rotation, and is housed in a transmission case M disposed near the engine at the front of the vehicle body together with the reduction gear mechanism RG in a state adjacent to the reduction gear mechanism RG, for example. A conventionally known power disconnecting mechanism and a forward/reverse switching mechanism (both not shown) are interposed between the engine and the reduction gear mechanism RG. The rotation axis L of the differential case DC coincides with the central axis of the output shaft J, J'. In the present specification, "axial" refers to a direction along the central axis of the output shaft J, J' (i.e., the rotational axis L of the differential case DC and the side gear S), and "radial" refers to a radial direction of the differential case DC and the side gear S. The "back surface" is a surface on the opposite side of the pinion gear (differential gear) P to be described later in the axial direction of the side gear (output gear) S.
The reduction gear mechanism RG is constituted by, for example, a planetary gear mechanism having: a sun gear 20 that rotates in conjunction with a crankshaft of the engine; a ring gear 21 concentrically surrounding the sun gear 20 and fixed to an inner wall of the transmission case M; a plurality of planetary gears 22 interposed between the sun gear 20 and the ring gear 21 and meshed with both gears 20, 21; and a carrier 23 that rotatably supports the planetary gear 22. Instead of such a planetary gear mechanism, a reduction gear mechanism composed of a plurality of flat gear trains may be used.
The carrier 23 is rotatably supported by the transmission case M via a bearing, not shown. In the present embodiment, the carrier 23 is integrally rotatably coupled to one end portion (a cover portion C described below) of the differential case DC of the differential device D, and the other end portion (the cover portion C described below) of the differential case DC is rotatably supported by the transmission case M via the bearing 2. Therefore, the joint of the differential case DC and the carrier 23, which rotate integrally with each other, is rotatably and stably supported by the transmission case M via a plurality of bearings.
A through hole Ma into which each output shaft J, J 'is fitted is formed in the transmission case M, and an annular seal member 3 for sealing between the inner periphery of the through hole Ma and the outer periphery of each output shaft J, J' is inserted. Further, an oil pan (not shown) for accumulating a predetermined amount of lubricating oil is provided at the bottom of the transmission case M so as to face the internal space 1 of the transmission case M, and the lubricating oil accumulated in the oil pan is lifted and dispersed to the periphery by the rotation of the movable element of the reduction gear mechanism RG, the differential case DC, and the like in the internal space 1 of the transmission case M, whereby the mechanically moving parts existing inside and outside the differential case DC can be lubricated.
Further, the lubricating oil stored in the oil pan may be sucked by an oil pump (not shown), and the lubricating oil may be forcibly injected or dispersed toward a specific portion of the internal space 1 of the transmission M, for example, the reduction gear mechanism RG and the differential case DC, or the inner wall of the transmission M around the reduction gear mechanism RG and the differential case DC. The differential case DC of the present embodiment may be partially immersed or not immersed in the lubricating oil accumulated in the inner bottom portion of the transmission case M below the oil surface of the outer peripheral portion of the differential case DC.
Referring to fig. 2 to 4, the differential device D includes: differential case DC; a plurality of pinion gears P housed in the differential case DC; a pinion shaft PS housed in the differential case DC and rotatably supporting the pinion gear P; and a pair of side gears S housed in the differential case DC, meshed with the pinion gears P from both left and right sides, and connected to a pair of output shafts J, J', respectively. The side gear S is an example of an output gear, the pinion gear P is an example of a differential gear, and the differential case DC is an example of an input member. The pinion gear P is housed in the differential case DC and supported by the differential case DC, and is rotatable relative to the differential case DC and revolvable around the rotation center of the differential case DC in accordance with the rotation of the differential case DC, as in the conventional differential device.
The differential case DC has, for example: a short cylindrical (tubular) housing portion 4 that rotatably supports the pinion shaft PS together with the pinion shaft PS; and a pair of cover portions C, C' which cover the outer sides of the pair of side gears S, respectively, and which rotate integrally with the housing portion 4.
Either one of the pair of cover portions C, C ', for example, the cover portion C' on the reduction gear mechanism RG side is formed separately from the housing portion 4, and is detachably coupled to the housing portion 4 by a bolt B or other suitable coupling means. The carrier 23 of the reduction gear mechanism RG is coupled to the cover C 'by welding or other suitable coupling means so as to be rotatable integrally with the cover C'. The cover C on the other side is integrally formed with the cylindrical housing 4, for example, but the cover C may be formed separately from the housing 4 as in the case of the cover C' on one side and may be coupled to the housing 4 by bolts B or other suitable coupling means.
Each cover C, C' includes: a cylindrical boss Cb concentrically surrounding a shaft portion Sj of the side gear S, and rotatably fitted to the shaft portion Sj; and a plate-shaped and annular side wall portion Cs integrally connected to an axially inner end of the boss portion Cb, and having all or most of an outer side surface thereof formed as a flat surface perpendicular to the rotation axis L of the differential case DC, an outer peripheral end of the side wall portion Cs being integrally or detachably joined to the case portion 4. The side wall portion Cs of each cover portion C, C' is disposed so as to be substantially coplanar with or slightly protrude from the axial end surface of the housing portion 4. This suppresses the side wall Cs from greatly protruding outward in the axial direction, which is advantageous in realizing the axial flattening of the differential device D.
A plurality of (e.g., 8) through holes H are provided in parallel at intervals in the circumferential direction in the side wall portion Cs of each cover portion C, C', and the through holes H penetrate the side wall portion Cs so as to intersect in the axial direction. The formation portion and the size of the through hole H are appropriately set from the viewpoint of ensuring the weight balance and the necessary rigidity of each cap portion C, C ', but a bottomed concave hole which is opened only to the inside may be formed in the inner side surface of the side wall portion Cs of each cap portion C, C' instead of such a through hole H or while retaining such a through hole H. In addition, particularly when the through hole H is used, the lubricating oil scattered in the transmission case M can be introduced into the differential case DC through the through hole H, and therefore lubrication of the sliding portions and the engaging portions of the movable elements in the differential case DC can be performed more effectively.
An outer peripheral surface of the output shaft J is fitted directly to an inner peripheral surface of the boss portion Cb of the one cover portion C so as to be rotatable relative to each other. A spiral groove 8 capable of forcibly conveying lubricating oil from the axially outer end to the inner end of the boss portion Cb in accordance with the relative rotation is formed in the inner peripheral surface of the boss portion Cb. Further, a spiral groove 8 'is formed in the inner peripheral surface of the boss portion Cb of the other cover portion C', and the groove 8 'can forcibly convey the lubricating oil from the axially outer end to the inner end side of the boss portion Cb in accordance with the relative rotation between the other cover portion C' and the shaft portion Sj of the same side gear S.
The pinion shaft PS is disposed in the differential case DC so as to be perpendicular to the rotation axis L of the differential case DC, and both ends of the pinion shaft PS are inserted in a manner capable of being inserted and removed into a pair of through-holes 4a provided in the cylindrical case portion 4, respectively, the pair of through-holes 4a being located on one diameter line of the case portion 4. The pinion shaft PS is fixed to the housing 4 by a slip-off preventing pin 5 inserted into the housing 4 through one end of the pinion shaft PS. The drop-preventing pin 5 is prevented from dropping out of the housing portion 4 by abutting the outer end of the pin 5 against the other cover portion C'.
In the present embodiment, the following structure is shown: the pinion shaft PS is formed in a linear bar shape, and two pinions P are supported at both end portions of the pinion shaft PS, but 3 or more pinions P may be provided. In this case, the pinion shaft PS is formed in a cross bar shape (for example, in the case of 4 pinions, a cross shape) such that the pinion shaft PS is radially extended from the rotation axis L of the differential case DC to three or more directions in correspondence with 3 or more pinions P, the pinions P are supported by the respective front end portions of the pinion shaft PS, and the case portion 4 is divided into a plurality of case elements so that the respective end portions of the pinion shaft PS can be mounted and supported.
The pinion gear P may be fitted directly to the pinion shaft PS or may be fitted via a bearing housing or other unit. The pinion shaft PS may be formed in a shaft shape having an equal diameter over the entire length as shown in fig. 2, or may be formed in a stepped shaft shape. A flat cut surface 6 (see fig. 2) for sufficiently ensuring the flow of the lubricating oil to the fitting surface is formed on the fitting surface of the pinion shaft PS to be fitted to the pinion gear P, and an oil passage through which the lubricating oil can flow is ensured between the cut surface 6 and the inner peripheral surface of the pinion gear P.
The pinion gear P and the side gear S are formed as bevel gears, for example, and the entirety of the pinion gear P and the side gear S, including the tooth portions, is formed by plastic working such as forging. Therefore, the teeth portions of the pinion gears P and the side gears S can be formed with high accuracy at an arbitrary gear ratio without being restricted by machining such as cutting. Instead of bevel gears, other gears may be used as the pinion gears P and the side gears S, and for example, the side gears S may be formed as face gears and the pinion gears P may be formed as flat gears or helical gears.
The pair of side gears S includes: a cylindrical shaft portion Sj spline-fitted 7 to inner end portions of the pair of output shafts J, J'; an annular tooth portion Sg located at a position radially outward from the shaft portion Sj and having a tooth surface meshing with the pinion gear P; and an intermediate wall portion Sm formed in a flat annular plate shape extending from an inner end portion of the shaft portion Sj radially outward toward an inner peripheral end portion of the tooth portion Sg, the shaft portion Sj and the inner peripheral end portion of the tooth portion Sg being integrally connected by the intermediate wall portion Sm. In the back surface f of the side gear S, a back surface portion fg of the tooth portion Sg protrudes axially outward from a back surface portion fm of the intermediate wall portion Sm.
The shaft portion Sj of the side gear S is directly fitted to the boss portion Cb of the cover portion C, C' in a freely rotatable manner, for example, but may be fitted via a bearing.
A plurality of through oil passages 9 are formed at intervals in the circumferential direction in the intermediate wall portion Sm of at least one (two in the present embodiment) of the right and left side gears S, and the through oil passages 9 penetrate the intermediate wall portion Sm so as to intersect in the axial direction. Accordingly, the lubricating oil smoothly flows between the inside and the outside of the side gears S through the through oil passage 9 in the differential case DC. In addition, from the viewpoint of ensuring weight balance and necessary rigidity strength of the side gears S, the formation site and the size of the through oil passage 9 are appropriately set.
Further, a back surface portion fg of the tooth portion Sg of the side gear S (i.e., a portion of the back surface f of the side gear S located on the back surface side of the mutual meshing portion I of the side gear S and the pinion gear P) is rotatably abutted and supported on an inner surface of the side wall portion Cs of the cover portion C, C', i.e., an opposing surface opposing the back surface f of the side gear S via the washer W. The washer W is fitted and held in the annular washer holding groove 10, and the washer holding groove 10 is formed on at least one of the inner surface of the side wall portion Cs of the cover portion C, C' and the opposite surface of the back surface of the tooth portion Sg of the side gear S (in the present embodiment, the inner surface of the side wall portion Cs).
Further, annular oil storage portions T are provided in a recessed manner at inner peripheral end portions of inner side surfaces (i.e., opposing surfaces opposing the back surfaces f of the side gears S) of the side wall portions Cs of the cover portion C, C', respectively, and the oil storage portions T face the outer periphery of the shaft portions Sj of the side gears S. In particular, the oil reservoir T on the cover C side communicates with the inner end of the groove 8 in the inner peripheral surface of the boss Cb via a lubrication passage 11, the lubrication passage 11 being formed between the end of the inner peripheral surface of the boss Cb of the cover C and the facing surface of the outer peripheral portion and the outer end surface of the shaft portion Sj of the side gear S on the cover C side, and the outer end of the groove 8 being open to the internal space 1 of the transmission case M. The inner end of the groove 8 communicates with the spline fitting portion 7 between the inner peripheral portion of the shaft portion Sj of the side gear S and the inner outer periphery of the output shaft J, and the lubricating oil can be supplied from the groove 8 to the spline fitting portion 7.
In addition, the oil reservoir T on the other cover portion C 'side communicates with the inner end of the groove 8' formed on the inner peripheral surface of the boss portion Cb of the cover portion C ', and the outer end of the groove 8' communicates with the internal space 1 of the transmission case M.
In addition, in correspondence with the case where the rear surface portion fg of the tooth portion Sg of the side gear S protrudes outward in the axial direction than the rear surface portion fm of the intermediate wall portion Sm as described above, the inner side surface of the side wall portion Cs of the cover portion C, C' is formed to protrude inward in the axial direction (i.e., the axial wall thickness) than the portion of the side wall portion Cs corresponding to the rear surface portion fm of the intermediate wall portion Sm. In this way, the cover portion C, C' (and thus the differential case DC) can sufficiently ensure the support rigidity of the back surface of the tooth portion Sg of the side gear S, and the intermediate wall portion Sm of the side gear S can be formed as thin as possible, so that the differential device D can be further reduced in weight and flattened in the axial direction.
Further, a plurality of oil grooves G extending linearly from the periphery of the shaft portion Sj of the side gear S to the back surface of the washer W are recessed on the inner surface of the side wall portion Cs of the cover portion C, C' (i.e., the opposing surface opposing the back surface f of the side gear S). As shown in fig. 3 in particular, the plurality of oil grooves G are arranged offset in the circumferential direction of the side gear S with respect to the meshing portion I between the tooth portion Sg of the side gear S and the pinion gear P.
In particular, the oil groove G of the present embodiment is arranged so as to extend radially with respect to the rotation axis L of the differential case DC, and passes between 2 through holes H adjacent in the circumferential direction of the side gear S. That is, the oil groove G is arranged at a position not overlapping the pinion gear P in the circumferential direction, as viewed in a projection plane perpendicular to the rotation axis L of the side gear S. The oil groove G is arranged in a V-shape in a pair of meshing portions I between the side gear S and the pinion gears P, and is located in the vicinity of the meshing portions I, as viewed in a plane perpendicular to the rotation axis L of the side gear S (fig. 3). And the inner end of each oil groove G is directly communicated with the oil storage portion T. Further, the pair of oil grooves G sandwiching the meshing portion I may be arranged in parallel to each other along the pinion shaft PS, for example, instead of being arranged in a V-shape as in the present embodiment.
In the back surface f of each side gear S, as shown in fig. 4, the outermost peripheral end fwe of the washer contact surface fw with the washer W is also located at the same position in the radial direction of the side gear S with respect to the outermost peripheral end Ie of the meshing portion I between the side gear S and the pinion P, and the outer peripheral end We of the washer W extends radially outward from the washer contact surface fw. In the present embodiment, the outermost peripheral end fwe of the washer contact surface fw of each side gear S becomes the largest outer diameter portion of the side gear S.
Next, the operation of embodiment 1 will be described. In the differential device D of the present embodiment, when the differential case DC receives rotational force from the engine via the reduction gear mechanism RG, the pinion gear P revolves around the rotational axis L of the differential case DC together with the differential case DC without rotating around the pinion shaft PS, the left and right side gears S are rotationally driven at the same speed from the differential case DC via the pinion gear P, and the driving force of the side gears S is transmitted equally to the left and right output shafts J, J'. When a rotational speed difference occurs between the left and right output shafts J, J' due to turning of the automobile, the pinion gear P rotates and revolves, thereby allowing differential rotation to transmit rotational driving force from the pinion gear P to the left and right side gears S. The above operation is the same as that of the conventionally known differential device.
When the power of the engine is transmitted to the left and right output shafts J, J' via the reduction gear mechanism RG and the differential device D in, for example, the forward running state of the automobile, the lubricating oil is strongly scattered everywhere in the transmission case M with the rotation of the respective movable elements of the reduction gear mechanism RG and the differential case DC, but a part of the scattered lubricating oil flows into the differential case DC from the plurality of through holes H as described above. A part of the lubricating oil flowing in is directed to the sliding portion between the back surface of the tooth portion Sg of the side gear S and the washer W along the gap between the side wall portion Cs of the cover portion C, C' and the back surface f of the side gear S by centrifugal force, and lubricates the sliding portion. The other part of the lubricating oil flowing into the differential case DC also flows into the inner space of the side gear S through the through oil passage 9 of the side gear S, flows radially outward along the inner surface of the side gear S by centrifugal force, and flows to the tooth surface of the tooth portion Sg of the side gear S and the meshing portion I of the tooth portion Sg of the side gear S and the pinion gear P, thereby lubricating the meshing portion I.
A part of the lubricating oil scattered in the transmission case M and reaching the vicinity of the outer end of the boss portion Cb of one cover portion C of the differential case DC is supplied to the axial inner end side of the boss portion Cb through the groove 8 in the inner peripheral surface of the boss portion Cb along with the relative rotation of the boss portion Cb and the output shaft J, and flows from the inner end of the groove 8 into the inner end of the oil groove G through the lubricating oil passage 11 and the oil reservoir portion T in this order. A part of the lubricating oil reaching the inner end of the groove 8 also flows into the spline fitting portion 7, and flows from the spline fitting portion 7 into the inner side surface side of the side gear S.
On the other hand, a part of the lubricating oil scattered in the transmission case M and reaching the vicinity of the outer end of the boss portion Cb of the other cover portion C ' of the differential case DC is supplied to the axial inner end side of the boss portion Cb through the groove 8' of the inner peripheral surface of the boss portion Cb along with the relative rotation of the boss portion Cb and the shaft portion Sj of the side gear S, and flows from the inner end of the groove 8' into the inner end of the oil groove G through the oil reservoir T.
According to the present embodiment, the side gear S has a flat annular intermediate wall portion Sm between the shaft portion Sj on the inner peripheral side and the tooth portion Sg of the side gear S on the outer peripheral side that is radially outwardly spaced from the shaft portion Sj, and the radial width t1 of the intermediate wall portion Sm is longer than the maximum diameter d1 of the pinion gear P. Therefore, the diameter of the side gear S can be sufficiently increased with respect to the pinion gear P, and the number of teeth Z1 of the side gear S can be set sufficiently larger than the number of teeth Z2 of the pinion gear P, so that the load on the pinion shaft PS when torque is transmitted from the pinion gear P to the side gear S can be reduced, and the effective diameter d2 of the pinion shaft PS can be reduced, and further, the reduction in the width (diameter reduction) of the pinion gear P in the axial direction of the output shaft J, J' can be realized.
In addition, the load on the pinion shaft PS is reduced, the reaction force applied to the side gear S is reduced, and the back surface f of the side gear S (particularly, the back surface portion fg on the back surface side of the meshing portion I between the side gear S and the pinion P) is supported by the side wall portion Cs of the cover portion C, C' via the washer W, whereby even if the intermediate wall portion Sm is thinned, the rigidity required for the side gear S can be easily ensured, that is, the support rigidity for the side gear S can be ensured, and the intermediate wall portion Sm of the side gear S can be sufficiently thinned. In the present embodiment, the maximum wall thickness t2 of the intermediate wall portion Sm of the side gear S is smaller than the effective diameter d2 of the pinion shaft PS that can be reduced in diameter, and therefore, the intermediate wall portion Sm of the side gear S can be further reduced in thickness. The side wall portion Cs of the cover portion C, C 'is formed in a flat plate shape in which the outer side surface of the side wall portion Cs is a flat surface perpendicular to the rotation axis L of the differential case DC, and thereby the side wall portion Cs itself of the cover portion C, C' is thinned.
Further, according to the present embodiment, since the rear surface portion fg of the tooth portion Sg protrudes outward in the axial direction than the rear surface portion fm of the intermediate wall portion Sm in the rear surface f of the side gear S, the rigidity of the tooth portion Sg of the side gear S can be sufficiently ensured, and the intermediate wall portion Sm of the side gear S can be formed as thin as possible, so that the differential device D can be reduced in weight and flattened in the axial direction.
As a result, the differential device D can ensure the same degree of strength (for example, static torsional load strength) and maximum torque transmission as those of the conventional device, and is sufficiently narrowed in the axial direction as a whole, so that even in a transmission system having a large limitation in layout around the differential device D, the differential device D can be easily assembled with a high degree of freedom without effort, and the transmission system of the differential device D is advantageously miniaturized.
Further, according to the present embodiment, most of the lubricating oil flowing into each oil groove G of the cover portion C, C' smoothly flows radially outward in the oil groove G by centrifugal force, and is efficiently supplied to the back surface of the gasket W. Therefore, even if a large thrust reaction force acts on the washer W from the pinion P through the side gear S, the sliding portion between the washer W and the back surface f of the side gear S (particularly, the back surface portion fg of the tooth portion Sg) can be sufficiently lubricated. Further, since the oil groove G is arranged offset in the circumferential direction of the side gear S with respect to the meshing portion I between the tooth portion Sg of the side gear S and the pinion gear P, the oil groove G can be circumferentially offset from a region portion of the opposing surface of the differential case DC (i.e., the side wall portion Cs of the cover portion C, C') opposing the back surface f of the side gear S, in particular, a region portion on the back surface side of the meshing portion I, on which a large thrust reaction force acts. In this way, in the differential case DC, the reduction in the support rigidity in the region where the load is large is suppressed, and the durability of the differential case DC is improved.
Further, according to the present embodiment, since the plurality of through holes H are provided in the side wall portion Cs of each cover portion C, C' in the differential case DC in parallel with each other with a gap therebetween in the circumferential direction, the oil groove G passes between the adjacent two through holes H, it is preferable to not only reduce the weight of the differential case DC while taking into account the weight balance of the differential case DC by providing the through holes H in particular, but also to avoid the through holes H and form the oil groove G sufficiently long (i.e., without being interrupted by the through holes H or the like in the middle).
Further, according to the present embodiment, the rear surface portion fg of the rear surface f of the side gear S, which is present on the rear surface side of the meshing portion I, and the washer W are arranged so as to partially overlap each other when viewed in a projection plane (fig. 3) perpendicular to the rotation axis L of the side gear S. Accordingly, the thrust reaction force is transmitted from the side gear S to the region portion of the opposing surface of the differential case DC (i.e., the inner side surface of the side wall portion Cs of the cover portion C, C') opposing the back surface f of the side gear S via the washer W, on which a large thrust reaction force acts in particular, and excessive concentration of the load to the region portion can be avoided. This can more effectively suppress the decrease in the support rigidity of the region where the load is large, and thus further improves the durability of the differential case DC.
Further, according to the present embodiment, the oil reservoir T facing the outer periphery of the shaft portion Sj of the side gear S is recessed in the inner peripheral end portion of the facing surface of the differential case DC facing the side gear S (i.e., the inner peripheral end portion of the inner side surface of the side wall portion Cs of the cover portion C, C'), so that the supply amount of lubricating oil to the oil groove G can be appropriately adjusted by the oil reservoir T. For example, at the initial stage of the differential operation of the differential device D, the lubricant oil accumulated in the oil reservoir T is smoothly supplied to the oil groove G, and further to the gasket W and the rear surface f of the side gear S, and the remaining lubricant oil is temporarily stored in the oil reservoir T, so that the oil groove G is not sufficiently supplied.
Further, according to the present embodiment, since the oil groove G is arranged in the vicinity of the meshing portion I in the circumferential direction of the side gear S, the oil groove G can be shifted as close as possible to the region portion on the opposite surface of the differential case DC to the back surface f of the side gear S, in particular, the region portion on the back surface side of the meshing portion I, to which a large thrust reaction force acts. As a result, in the differential case DC, the reduction in the support rigidity of the region portion with a large load can be suppressed as much as possible, and the region portion can be effectively lubricated. Further, since the oil grooves G are arranged in pairs with the engagement portions I interposed therebetween, it is possible to suppress a decrease in the supporting rigidity of the region portion where the load is large, and to lubricate the region portion more effectively.
Further, according to the present embodiment, even in the case where the tooth portion Sg of the side gear S is separated from the output shaft J, J' by enlarging the diameter of the side gear S and in the case of a severe operation condition in which the pinion gear P rotates at a high speed, the lubricant can be efficiently supplied to the meshing portion I and the sliding portion between the back surface f of the side gear S and the washer W, and thus the portions can be effectively prevented from being ablated.
In the present embodiment, since the outermost peripheral end fwe of the washer contact surface fw with which the washer W is in contact is also located at the same position in the radial direction of the side gear S as the outermost peripheral end Ie of the meshing portion I between the side gear S and the pinion gear P in the rear surface f of each side gear S as shown in fig. 4, there is no fear that a large thrust reaction force from the pinion gear P is excessively concentrated on the outermost peripheral end of the washer contact surface fw of the side gear S through the tooth portion Sg of the outer periphery of the side gear S, and the load on the tooth portion Sg itself of the outer periphery of the side gear S is also reduced. In the present invention, the washer contact surface fw may be set so that the outermost peripheral end fwe of the washer contact surface fw is positioned radially outward of the outermost peripheral end Ie of the meshing portion I, and similar effects to those described above can be expected in this case.
Further, since the outer peripheral end We of the washer W extends radially outward from the washer contact surface fw of the side gear S, as is clear from the load distribution diagram of fig. 4, load distribution of the washer support portion (i.e., the bottom portion of the washer holding groove 10 in the side wall portion Cs of the cover portion C, C') of the differential case DC is achieved, and thus an increase in load on the washer support portion can be effectively avoided. In the load distribution diagram of fig. 4, a comparative example (broken line) in which the outer peripheral end We of the washer W is not extended radially outward from the washer contact surface fw of the side gear S is shown, and the load of the washer support portion of the differential case DC that contacts the outermost peripheral end of the washer W is excessively large.
According to the structure of the relationship between the back surface f of the side gear S and the washer W and the washer support portion of the differential case DC in this embodiment, the differential case DC (particularly, the side wall portion Cs of the cover portion C, C') and the side gear S (particularly, the peripheral tooth portion Sg) can be reduced in thickness and weight, and the differential device D can be advantageously flattened and reduced in weight in the axial direction. Further, since the outermost peripheral end fwe of the gasket contact surface fw is the largest outer diameter portion of the side gear S, the side gear S can be appropriately dispersed and supported by the gasket support portion of the differential case DC without unnecessarily enlarging the diameter thereof. This can further reduce the wall Cs of the differential case DC and the tooth Sg of the side gear S.
Next, embodiment 2 of the present invention will be described with reference to fig. 5. The same components as those of embodiment 1 are denoted by the same reference numerals, and detailed description thereof is omitted.
In embodiment 1, there is shown a structure in which: a long pinion shaft PS is used as a support portion (i.e., differential gear support portion) of the pinion gear P, but in embodiment 2, the support portion (i.e., differential gear support portion) of the pinion gear P is constituted by a support shaft PS' that is coaxially and integrally coupled to an end surface on the large diameter side of the pinion gear P. According to this configuration, since it is not necessary to provide the pinion gear P with the through hole fitted to the pinion shaft PS, the diameter of the pinion gear P can be reduced (the axial direction can be narrowed) accordingly, and flattening of the differential device D in the axial direction can be further achieved. That is, in the case where the pinion shaft PS penetrates the pinion gear P, a through hole of a size corresponding to the diameter of the pinion shaft PS must be formed in the pinion gear P, whereas in the case where the support shaft PS ' is integrated with the end face of the pinion gear P, the diameter of the pinion gear P can be reduced (narrowing of the output shaft J, J ' in the axial direction) irrespective of the outer diameter (i.e., the effective diameter d 2) of the support shaft PS '.
A bearing housing 12 is inserted between the outer peripheral surface of the support shaft PS 'and the outer peripheral wall of the differential case DC, that is, the inner peripheral surface of the through-hole 4a provided in the cylindrical case portion 4, and the bearing housing 12 serves as a bearing unit that allows relative rotation between the outer peripheral surface of the support shaft PS' and the inner peripheral surface of the through-hole 4a. In addition, a bearing such as a needle bearing may be used as the bearing unit. The bearing may be omitted, and the support shaft PS' may be fitted directly into the through-hole 4a of the differential case DC.
In addition, the effect substantially equivalent to that of embodiment 1 is obtained in embodiment 2.
Next, embodiment 3 of the present invention will be described with reference to fig. 6. In embodiments 1 and 2, the outermost peripheral end fwe of the washer contact surface fw with which the washer W is in contact is located at the same position or a position radially outward of the engagement portion I between the side gear S and the pinion P in the radial direction of the side gear S, and the outermost peripheral end fwe of the washer contact surface fw becomes the maximum outer diameter portion of the side gear S, whereas in embodiment 3, the outer peripheral end surface of the tooth portion Sg of the side gear S and the rear surface of the tooth portion Sg (particularly the washer contact surface fw) are smoothly connected by a chamfer r having an arc-shaped cross section. Therefore, the outermost peripheral end fwe of the washer abutting surface fw is located radially inward of the largest outer diameter portion (i.e., the outer peripheral end surface) of the side gear S, while the outer peripheral end We of the washer W extends radially outward of the washer abutting surface fw as in embodiment 1 and 2, so that the washer abutting surface fw is located on the back surface side of the meshing portion I.
In embodiment 3, since the other structures are the same as those in embodiment 1, only the same reference numerals as those in the corresponding components in embodiment 1 are given to the respective components, and the other description is omitted.
Therefore, the present embodiment 3 can achieve substantially the same operational effects as those of embodiments 1 and 2. In embodiment 3, the outer peripheral end surface of the tooth portion Sg of the side gear S and the back surface of the tooth portion Sg (in particular, the washer contact surface fw) may be connected by a flat tapered surface having a straight cross section, instead of the chamfer r.
In addition, in the conventional differential devices (in particular, the conventional differential device having a pinion (differential gear) and a pair of side gears (output gears) meshing with the pinion (differential gear) in an input member) as exemplified in patent documents 2 and 3 described above, for example, 14×10, 16×10, or 13×9 as shown in patent document 3 are generally used as the number of teeth Z1 of the side gears (output gears) and the number of teeth Z2 of the pinion (differential gear). In this case, the gear ratios Z1/Z2 of the output gears with respect to the differential gears are 1.4, 1.6, 1.44, respectively. In the conventional differential device, for example, 15×10, 17×10, 18×10, 19×10, or 20×10 are known as other combinations of the teeth numbers Z1 and Z2, and the tooth ratios Z1/Z2 in this case are 1.5, 1.7, 1.8, 1.9, and 2.0, respectively.
On the other hand, there is a growing number of differential devices that are accompanied by restrictions on the layout around the differential devices, and there is a demand in the market for securing the gear strength of the differential devices and sufficiently narrowing (i.e., flattening) the differential devices in the axial direction of the output shaft. However, in the conventional differential device, since the gear ratio is combined to have a wide width in the axial direction of the output shaft, it is difficult to satisfy the market demands.
Therefore, from the viewpoints different from the above-described embodiments, a configuration example of the differential device D that can sufficiently narrow (i.e., flatten) the differential device in the axial direction of the output shaft while securing the gear strength of the differential device is specifically determined. Since the configuration of each component of the differential device D according to this configuration example is the same as that of the differential device D according to the above-described embodiment described with reference to fig. 1 to 6 (particularly, fig. 1 to 4 and 6), the same reference numerals as those of the above-described embodiment are used for each component, and the description thereof is omitted.
First, a basic idea for sufficiently narrowing (i.e., flattening) the differential device D in the axial direction of the output shaft J, J' will be described with reference to fig. 7, which is:
[1] the gear ratio Z1/Z2 of the side gear S, i.e., the output gear, to the pinion gear P, i.e., the differential gear, is increased compared to the gear ratio of the conventional differential gear. (thereby, the modulus (thus, the tooth thickness) of the gear decreases, the gear strength decreases, on the other hand, the pitch diameter of the side gear S increases, the transmission load at the gear meshing portion decreases and the gear strength increases, but as a whole, the gear strength decreases as described later.)
[2] The pitch PCD of the pinion P is increased compared to the pitch of the conventional differential device. (As a result, the modulus of the gear increases, the gear strength increases, the pitch diameter of the side gear S increases, the transmission load at the gear meshing portion decreases, and the gear strength increases, and therefore, as a whole, the gear strength greatly increases as described later.)
Therefore, by setting the gear ratio Z1/Z2 and the pitch PCD such that the gear strength of the above-described [1] is reduced by the same amount as the gear strength of the above-described [2] is increased or such that the gear strength of the above-described [2] is increased by the same amount as the gear strength of the above-described [1] is reduced, the gear strength can be made equal to or greater than that of the conventional differential device as a whole.
Next, the manner of change in the gear strength based on the above-mentioned [1] and [2] is specifically verified by the mathematical expression. In the following embodiment, verification will be described. First, the differential device D' when the number of teeth Z1 of the side gear S is 14 and the number of teeth Z2 of the pinion gear P is 10 is referred to as a "reference differential device". The "change rate" refers to the change rate of various variables with reference to the reference differential device D' (i.e., 100%).
For [1]
The modulus of the side gear S is MO, and the pitch circle diameter is PD 1 Let the pitch angle be theta 1 Assuming that the pitch cone distance is PCD, the transmission load at the gear mesh is FO, and the transmission torque is TO, the transmission torque is represented by the general expression of bevel gears
MO＝PD 1 /Z1
PD 1 ＝2PCD·sinθ 1
θ 1 ＝tan -1 (Z1/Z2)
According to these expressions, the modulus of the gear is
MO＝2PCD·sin{tan -1 (Z1/Z2)}/Z1…(1)，
And the modulus of the reference differential device D' is 2PCD.sin { tan ] -1 (7/5)}/14。
Therefore, by dividing the right term of the two expressions, the modulus change rate with respect to the reference differential device D' is shown as the following expression (2).
[ math 1]
The section coefficient of the tooth portion corresponding to the gear strength (i.e., the bending strength of the tooth portion) is proportional to the square of the tooth thickness, and the tooth thickness is substantially linear with the modulus MO. Therefore, the square of the modulus change rate corresponds to the change rate of the section coefficient of the tooth portion, and thus the change rate of the gear strength. That is, the gear strength change rate is shown in the following equation (3) according to equation (2). The equation (3) is shown by L1 of fig. 8 when the number of teeth Z2 of the pinion gear P is 10, and it is understood that as the gear ratio Z1/Z2 increases, the gear strength decreases due to the decrease in the module.
[ formula 2 ]
In addition, according to the general formula of the bevel gear described above, the torque transmission distance of the side gear S is as shown in the following formula (4).
PD 1 /2＝PCD·sin{tan -1 (Z1/Z2)}…(4)
Further, based on the torque transmission distance PD 1 The transfer load FO of/2 is fo=2to/PD 1 . Therefore, in the side gear S of the reference differential device D', if the torque TO is set TO be constant, the load FO and the pitch diameter PD are transmitted 1 In an inversely proportional relationship. Further, since the rate of change of the transmission load FO is inversely proportional to the rate of change of the gear strength, the rate of change of the gear strength is inversely proportional to the pitch diameter PD 1 Is equal.
As a result, the pitch diameter PD 1 The rate of change of (a) is represented by the following formula (5) using formula (4).
[ formula 3 ]
The equation (5) is shown by L2 of fig. 8 when the number of teeth Z2 of the pinion gear P is 10, and it is understood that as the gear ratio Z1/Z2 increases, the gear strength increases due to a decrease in the transmission load.
As a result, the rate of change of the gear strength due to the decrease in modulus MO (the right term of the above equation (3)) is multiplied by the rate of change of the gear strength due to the decrease in the transmission load (the right term of the above equation (5)), and the rate of change of the gear strength accompanying the increase in the gear ratio Z1/Z2 is expressed by the following equation (6).
[ math figure 4 ]
Equation (6) is shown by L3 of fig. 8 when the number of teeth Z2 of the pinion gear P is 10, and it is understood that as the gear ratio Z1/Z2 increases, the gear strength decreases as a whole.
For [2]
When the pitch cone distance PCD of the pinion gear P is increased as compared with the pitch cone distance of the reference differential device D', if PCD1 is the PCD before modification and PCD2 is the PCD after modification, the modulus change rate before and after modification of the PCD is (PCD 2/PCD 1) if the number of teeth is constant according to the general formula of bevel gears described above.
On the other hand, as is clear from the process of deriving the expression (3), the rate of change in the gear strength of the side gear S is equivalent to the square of the modulus rate of change, and as a result,
rate of change in gear strength due to modulus increase= (PCD 2/PCD 1) 2 … (7)
Equation (7) is shown by L4 in fig. 9, and it is understood that as the pitch PCD increases, the gear strength increases due to the increase in the modulus.
When the pitch PCD is increased as compared with the pitch PCD1 of the reference differential device D', the transmission load FO is reduced, but the rate of change in the gear strength due to this is reduced as described above with respect to the pitch diameter PD 1 Is equal. And the pitch diameter PD of the side gear S 1 And pitch PCD are in proportional relationship. Thus, the first and second substrates are bonded together,
rate of change in gear strength due to reduction in transmission load=pcd 2/PCD1 … (8)
As shown in L5 of fig. 9, the equation (8) shows that as the pitch PCD increases, the gear strength increases due to a decrease in the transmission load.
The rate of change of the gear strength due to an increase in the modulus MO (the right term of the equation (7)) is multiplied by the rate of change of the gear strength due to a decrease in the transmission load with an increase in the pitch diameter PD (the right term of the equation (8)), and the rate of change of the gear strength with an increase in the pitch cone distance PCD is expressed by the following equation (9).
Gear strength change rate caused by increase of pitch cone distance= (PCD 2/PCD 1) 3· (9)
As shown in L6 of fig. 9, the equation (9) shows that the gear strength greatly increases as the pitch PCD increases.
Further, the combination of the gear ratio Z1/Z2 and the pitch PCD is determined as: the increase in gear strength by the method of [2] (increase in pitch cone) is sufficient to compensate for the decrease in gear strength by the method of [1] (increase in gear ratio), so that the gear strength of the differential device as a whole is equal to or greater than the gear strength of the conventional differential device.
For example, in the case where the gear strength of the side gear S of the reference differential device D' is maintained at 100%, the value obtained by multiplying the rate of change in the gear strength (the right term of the above equation (6)) due to the increase in the gear ratio obtained by [1] by the rate of change in the gear strength (the right term of the above equation (9)) due to the increase in the pitch cone obtained by [2] may be set to 100%. Thus, the relationship between the gear ratio Z1/Z2 and the rate of change of the pitch cone PCD in the case where the gear strength of the reference differential device D' is maintained at 100% can be obtained by the following equation (10). Equation (10) is shown by L7 of fig. 10 when the number of teeth Z2 of the pinion P is 10.
[ formula 5 ]
In this way, the equation (10) shows the relationship between the gear ratio Z1/Z2 and the rate of change of the pitch cone PCD when the gear strength of the reference differential device D' with the gear ratio Z1/z2=14/10 is maintained at 100% (see fig. 10), but when the shaft diameter of the pinion shaft PS (i.e., the pinion supporting portion) supporting the pinion P is D2, the rate of change of the pitch cone PCD on the vertical axis of fig. 10 can be converted into the rate of D2/PCD.
[ Table 1 ]
| PCD | Shaft diameter (d 2) | d2/PCD |
| 31 | 13 | 42％ |
| 35 | 15 | 43％ |
| 38 | 17 | 45％ |
| 39 | 17 | 44％ |
| 41 | 18 | 44％ |
| 45 | 18 | 40％ |
That is, in the conventional differential device, the increase change of the pitch PCD is correlated with the increase change of d2 as in table 1, and can be expressed as a decrease in the ratio of d2/PCD when d2 is constant. Further, in the conventional differential device, as shown in table 1, since the relationship between D2/PCD accommodated in the range of 40% to 45% when the differential device D ' is the reference differential device and the gear strength increases when PCD increases, the gear strength can be made equal to or higher than that of the conventional differential device by determining the shaft diameter D2 and pitch PCD of the pinion shaft PS to be at least 45% or less when the differential device D ' is the reference differential device D '. That is, in the case of the reference differential device D', D2/PCD is not more than 0.45. In this case, if PCD after the increase/decrease change is PCD2 with respect to the pitch PCD1 of the reference differential device D', the following relationship may be satisfied:
d2/PCD2≤0.45/(PCD2/PCD1)…(11)。
Further, if the expression (11) is substituted into the above expression (10), the relationship of d2/PCD and the gear ratio Z1/Z2 can be converted into the following expression (12).
[ formula 6 ]
When the equal sign of the equation (12) is established, the number of teeth Z2 of the pinion P is 10, which can be expressed as L8 in fig. 11. When the equivalent of the equation (12) is established, the relationship between D2/PCD and the gear ratio Z1/Z2 is maintained at 100% for the gear strength of the reference differential device D'.
In the conventional differential device, as described above, not only the gear ratio Z1/Z2 is set to 1.4 as in the reference differential device D', but also a gear ratio Z1/Z2 is set to 1.6 or a gear ratio Z1/Z2 is set to 1.44 is generally used. Based on this fact, in the case where it is assumed that a sufficient gear strength, that is, 100% of that required for the reference differential device D '(the gear ratio Z1/z2=1.4) is obtained, in the differential device of the conventional prior art, the gear strength is reduced to 87% compared with the reference differential device D' in the differential device having the gear ratio Z1/Z2 of 16/10, as is clear from fig. 8. However, in the conventional differential device, the gear strength reduced to this level is allowed to be used as a practical strength. Therefore, even in the differential device flattened in the axial direction, it is considered that the gear strength can be sufficiently ensured and allowed as long as the gear strength is at least 87% with respect to the reference differential device D'.
From such a point of view, if the relationship between the gear ratio Z1/Z2 and the change rate of the pitch cone distance PCD in the case where the gear strength of the reference differential device D 'is maintained at 87% is first obtained, the relationship can be expressed by the following equation (10') by performing the calculation by simulating the process of deriving the equation (10) (that is, by multiplying the change rate of the gear strength (the right term of the equation (6)) associated with the increase in the gear ratio by the change rate of the gear strength (the right term of the equation (9)) caused by the increase in the pitch cone distance.
[ formula 7 ]
If the above expression (11) is substituted into the above expression (10 '), the relationship between D2/PCD and the gear ratio Z1/Z2 in the case where the gear strength of the reference differential device D' is maintained at 87% or more can be converted into the following expression (13). However, in the calculation, the term expressed by the variable is used, the term is calculated by using a three-significant digit, and the number of digits is omitted, and in accordance with this, when the term is substantially equal in practice due to calculation errors, the term is expressed by using an equal sign in the expression.
[ math figure 8 ]
When the equal sign of the equation (13) is established, the number Z2 of teeth of the pinion P is 10, which can be expressed as shown in fig. 11 (more specifically, as shown by a line L9 in fig. 11), and in this case, the region corresponding to the equation (13) is a region on the line L9 and below the line L9 in fig. 11. In particular, in the differential device in which the number of teeth Z2 of the pinion gear P is 10 and the gear ratio Z1/Z2 exceeds 2.0, the specific region (hatched region in fig. 11) satisfying the gear ratio Z1/Z2 exceeding 2.0 on the right side of the line L10 in fig. 11 satisfies the equation (13), and is a set region of Z1/Z2 and D2/PCD capable of securing a gear strength of at least 87% with respect to the reference differential device D'. For reference, if an embodiment in which the gear ratio Z1/Z2 is set to 40/10 and the d2/PCD is set to 20.00% is exemplified in FIG. 11, as in diamond points, and if an embodiment in which the gear ratio Z1/Z2 is set to 58/10 and the d2/PCD is set to 16.67% is exemplified in FIG. 11, as in the triangular points, they are all accommodated in the above-described specific region. As a result of the simulation-based intensity analysis, it was confirmed that the gear intensity equal to or higher than the conventional one (more specifically, the gear intensity of 87% or higher relative to the reference differential device D') was obtained.
Thus, the flat differential device located in the specific region has the following structure: the differential device which can ensure the same degree of gear strength (for example, static torsional load strength) and maximum torque transmission amount as the conventional non-flat differential device and is sufficiently narrowed in the axial direction of the output shaft as a whole can achieve the following effects: even in the transmission system in which there are many restrictions in layout around the differential device, the differential device can be assembled easily with a high degree of freedom without effort, and the transmission system is advantageously miniaturized.
Further, for example, in the case where the flat differential device located in the specific region is configured as in the above-described embodiment (more specifically, the configuration shown in fig. 1 to 6), the flat differential device located in the specific region can also obtain the effects accompanying the configuration shown in the above-described embodiment.
The description above (in particular, the description relating to fig. 8, 10, and 11) is made for the differential device in which the number of teeth Z2 of the pinion P is 10, but the present invention is not limited thereto. For example, a flat differential device capable of achieving the above-described effects even when the number of teeth Z2 of the pinion gear P is 6, 12, or 20 can be represented by the expression (13) as shown by hatching in fig. 12, 13, or 14. That is, the equation (13) derived as described above can be applied regardless of the change in the number of teeth Z2 of the pinion P, and for example, even when the number of teeth Z2 of the pinion P is 6, 12, or 20, the same as when the number of teeth Z2 of the pinion P is 10, the above-described effects can be obtained by setting the number of teeth Z1 of the side gear S, the number of teeth Z2 of the pinion P, the shaft diameter d2 of the pinion shaft PS, and the pitch PCD so as to satisfy the equation (13).
For reference, when the number of teeth Z2 of the pinion P is 12, an example in which the number of teeth Z1/Z2 is 48/12 and d2/PCD is 20.00% is illustrated by diamond points in fig. 13, and an example in which the number of teeth Z1/Z2 is 70/12 and d2/PCD is 16.67% is illustrated by triangle points in fig. 13. As a result of the simulation-based strength analysis, it was confirmed that the gear strength equal to or higher than the conventional one (more specifically, the gear strength of 87% or higher relative to the reference differential device D') was obtained. Further, these embodiments are accommodated in the specific region as shown in fig. 13.
As a comparative example, for the embodiment not accommodated in the above specific region, for example, the embodiment in which the gear ratio Z1/Z2 is set to 58/10, the embodiment in which d2/PCD is set to 27.50% is exemplified by the star point in fig. 11 in the case where the gear number Z2 of the pinion P is set to 10, the embodiment in which the gear ratio Z1/Z2 is set to 40/10, the d2/PCD is set to 34.29% is exemplified by the dot in fig. 11, the embodiment in which the gear ratio Z1/Z2 is set to 70/12, the embodiment in which d2/PCD is set to 27.50% is exemplified by the star point in fig. 13 in the case where the gear number Z2 of the pinion P is set to 12, the embodiment in which the gear ratio Z1/Z2 is set to 48/12, and the dot in fig. 13 in which d2/PCD is set to 34.29% is exemplified by the star point in the case where the gear number Z2 of the pinion P is set to 12. As a result of the simulation-based intensity analysis, it was confirmed that the gear intensity equal to or higher than the conventional one (more specifically, the gear intensity of 87% or higher than the reference differential device D') could not be obtained. That is, it can be confirmed that the above-described effects cannot be obtained in the embodiment not accommodated in the above-described specific region.
The embodiments of the present invention have been described above, but the present invention is not limited to the above embodiments, and various design changes may be made without departing from the gist thereof.
For example, the following structure is shown in the above embodiment: the reduction gear mechanism RG constituted by the planetary gear mechanism is disposed adjacently on the side of the differential case DC as the input member, and the output side element (carrier 23) is coupled to the differential case DC (cover C'), so that the power of the power source is transmitted to the differential case DC via the reduction gear mechanism RG, but the output side element of the reduction gear mechanism other than the planetary gear mechanism may be coupled to the differential case DC.
And, it is also possible to: instead of such a reduction gear mechanism, an input gear portion (final driven gear, final gear) that receives power from the power source is integrally formed on the outer peripheral portion of the differential case DC, or is fixed to the outer peripheral portion of the differential case DC by post-attachment, and power from the power source is transmitted to the differential case DC via the input gear portion.
Also in the above-described embodiment, the structure is shown as follows: the grooves 8, 8 'in the inner periphery of the boss portion Cb of the cover portion C, C' can supply the lubricating oil present in the outer periphery of the boss portion Cb in the transmission case M to the oil storage portion T on the inner end side of the boss portion Cb and further to the oil groove G, but an oil supply path that guides the lubricating oil scattered in the transmission case M to the inner end portion of the oil storage portion T or the oil groove G (for example, the side wall portion Cs or the boss portion Cb) may be provided at an appropriate position of the differential case DC instead of the grooves 8, 8 'or while retaining the grooves 8, 8'. In this case, the lubricating oil scattered in the transmission case M may naturally flow into the oil supply passage, or the lubricating oil may be positively supplied to the oil supply passage by an oil pump, not shown.
In the above-described embodiment, the radially inner end of the washer W is radially outward of the radially inner end of the back surface portion fg of the tooth portion Sg of the side gear S, but the invention is not limited thereto. For example, the radially inner end portion of the washer W may extend to the same position as the radially inner end of the back surface portion fg of the tooth portion Sg of the side gear S. This can more effectively suppress the decrease in the support rigidity of the back surface fg of the tooth Sg of the side gear S with a large load.
In the above embodiment, the following configuration is shown: the rear surfaces of the pair of side gears S are covered with a pair of exclusive cover portions C, C' of the differential case DC, respectively, but in the present invention, exclusive cover portions may be provided only on the rear surface of one side gear S. In this case, for example, a driving member (for example, the carrier 23 of the reduction gear mechanism RG) located on the upstream side of the power transmission path may be disposed on the side of the differential case DC where the dedicated cover portion is not provided, and the driving member and the differential case DC may be coupled. In this case, the driving member doubles as the cover portion C', and the driving member and the differential case DC constitute the input member of the present invention.
In the above-described embodiment, the differential device D allows the rotational speed difference between the left and right axles, but the differential device of the present invention may be implemented in a center differential that absorbs the rotational speed difference between the front wheels and the rear wheels.
Claims (8)
1. A differential device, characterized in that the differential device comprises:
an input member (DC) to which a driving force is input;
a differential gear (P) supported by the input member (DC), capable of rotating relative to the input member (DC), and capable of revolving around a rotation center of the input member (DC) in association with rotation of the input member (DC);
a pair of output gears (S) having a tooth portion (Sg) meshing with the differential gear (P) and a shaft portion (Sj) located radially inward of the tooth portion (Sg);
a washer (W) interposed between the back surface of the tooth portion (Sg) of each of the output gears (S) and the input member (DC); and
an oil groove (G) recessed in an opposing surface of the input member (DC) opposing the rear surface (f) of the output gear (S), the oil groove extending from the periphery of the shaft portion (Sj) of the output gear (S) to the rear surface of the washer (W),
the oil groove (G) is arranged offset in the circumferential direction of the output gear (S) with respect to the meshing part (I) between the tooth part (Sg) and the differential gear (P),
The input member (DC) has a side wall (Cs) facing the rear surface (f) of the output gear (S),
the side wall (Cs) has a plurality of through holes (H) arranged at intervals in the circumferential direction,
the oil groove (G) is configured to pass between 2 adjacent through holes (H) in the circumferential direction,
the oil groove (G) is arranged at a position which does not overlap with the differential gear (P) in the circumferential direction, as viewed in a projection plane perpendicular to the rotation axis (L) of the output gear (S).
2. A differential device according to claim 1, wherein,
an oil reservoir (T) facing the outer periphery of the shaft (Sj) of the output gear (S) is recessed in the inner periphery of the facing surface of the input member (DC) facing the output gear (S).
3. A differential device according to claim 1, wherein,
the oil groove (G) is arranged near the meshing part (I) in the circumferential direction of the output gear (S).
4. A differential device according to claim 2, wherein,
the oil groove (G) is arranged near the meshing part (I) in the circumferential direction of the output gear (S).
5. A differential device according to claim 1, wherein,
the oil grooves (G) are arranged in pairs with the meshing portions (I) therebetween, as viewed in a projection plane perpendicular to the rotation axis of the output gear (S).
6. A differential device according to claim 2, wherein,
the oil grooves (G) are arranged in pairs with the meshing portions (I) therebetween, as viewed in a projection plane perpendicular to the rotation axis of the output gear (S).
7. A differential device as claimed in claim 3, wherein,
the oil grooves (G) are arranged in pairs with the meshing portions (I) therebetween, as viewed in a projection plane perpendicular to the rotation axis of the output gear (S).
8. The differential device according to claim 4, wherein,
the oil grooves (G) are arranged in pairs with the meshing portions (I) therebetween, as viewed in a projection plane perpendicular to the rotation axis of the output gear (S).
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| JP2015123201 | 2015-06-18 | ||
| JP2015199797A JP6612577B2 (en) | 2014-10-22 | 2015-10-07 | Differential |
| JP2015-199797 | 2015-10-07 | ||
| JP2015-232392 | 2015-11-27 | ||
| JP2015232392A JP6742715B2 (en) | 2015-06-18 | 2015-11-27 | Differential |
| CN201610436532.9A CN106337922B (en) | 2015-06-18 | 2016-06-17 | Differential gear |
| CN202010417669.6A CN111577855B (en) | 2015-06-18 | 2016-06-17 | Differential device |
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| CN104405850A (en) * | 2014-09-18 | 2015-03-11 | 广西柳工机械股份有限公司 | Differential |
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| JPH0635726U (en) * | 1992-10-16 | 1994-05-13 | ダイハツ工業株式会社 | Lubrication structure of differential gear |
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