WO2023112801A1 - 駆動装置 - Google Patents
駆動装置 Download PDFInfo
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- WO2023112801A1 WO2023112801A1 PCT/JP2022/045184 JP2022045184W WO2023112801A1 WO 2023112801 A1 WO2023112801 A1 WO 2023112801A1 JP 2022045184 W JP2022045184 W JP 2022045184W WO 2023112801 A1 WO2023112801 A1 WO 2023112801A1
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- Prior art keywords
- bearing
- groove
- case
- oil
- grooves
- Prior art date
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- 238000010586 diagram Methods 0.000 description 30
- 230000007246 mechanism Effects 0.000 description 30
- 230000002093 peripheral effect Effects 0.000 description 17
- 230000004048 modification Effects 0.000 description 15
- 238000012986 modification Methods 0.000 description 15
- 230000005540 biological transmission Effects 0.000 description 13
- 230000000052 comparative effect Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 239000007787 solid Substances 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/067—Fixing them in a housing
-
- 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
-
- 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
Definitions
- the present disclosure relates to a driving device.
- a lubricating circuit in which oil stored in a case is pumped up by an oil pump, and the pumped oil is supplied to a power transmission mechanism to lubricate the power transmission mechanism (including bearings).
- the surface of the bearing that faces the case in the radial direction and is the surface on the side where the bearing can slide against the case for example, in the case of a clearance fit, the surface on the side of the clearance fit.
- the present disclosure aims to reduce wear of the case caused by creep by providing a mechanism for appropriately supplying oil from the oil pump to the surface of the bearing.
- a stationary member In one aspect, a stationary member; a bearing; a rotary-side member that is drivingly connected to a drive source and supported by the fixed-side member via the bearing so as to be rotatable about an axis;
- the bearing is press-fitted with the rotating member and fitted with the stationary member,
- One or more grooves through which oil passes are formed on a surface of the bearing radially facing the fixed member or a surface of the fixed member radially facing the bearing,
- a drive is provided wherein the groove extends axially and circumferentially about the axis and is open on at least one of the axial sides of the bearing.
- FIG. 1 is a skeleton diagram of a vehicle drive system including a rotating electric machine and a power transmission mechanism
- FIG. FIG. 2 is an explanatory diagram of a bearing structure suitable for the vehicle drive system according to the present embodiment
- FIG. 4 is an explanatory diagram of grooves formed on the outer peripheral surface of the outer race; It is explanatory drawing of the variation of R shape of the bottom part of a groove
- FIG. 4 is an explanatory diagram of a mode of conveying oil by the grooves of the present embodiment
- FIG. 5 is a diagram showing each state when creep occurs in which the bearing rotates with respect to the case.
- FIG. 5 is an explanatory diagram of the relationship between torque generated in a direction to rotate the outer race relative to the case and torque generated in a direction to stop the rotation of the outer race relative to the case;
- FIG. 5 is an explanatory diagram of fluctuation characteristics of each torque according to a comparative example;
- FIG. 4 is an explanatory diagram of fluctuation characteristics of each torque according to the present embodiment; It is explanatory drawing of preferable arrangement
- FIG. 13 is a cross-sectional view along line Q3-Q3 of FIG. 12;
- FIG. 13 is a diagram corresponding to FIG. 12 in the case of a configuration without an oil reservoir;
- FIG. 12 is an explanatory diagram of grooves formed in the outer peripheral surface of the outer race of the bearing according to the fourth modification;
- FIG. 12 is an explanatory diagram of grooves formed in the outer peripheral surface of the outer race of the bearing according to the fifth modified example;
- FIG. 12 is an explanatory diagram of grooves formed in the inner peripheral surface of the case (the surface facing the outer race in the radial direction) according to the sixth modification;
- the vehicle drive system 100 to which the vehicle drive device 17 according to the present embodiment can be suitably applied will be described, and then the bearing structure in the vehicle drive device 17 according to the present embodiment will be described.
- FIG. 1 is a skeleton diagram of a vehicle drive system 100 including a rotating electrical machine 1 and a power transmission mechanism 7.
- FIG. 1 is a skeleton diagram of a vehicle drive system 100 including a rotating electrical machine 1 and a power transmission mechanism 7.
- the vehicle drive system 100 includes a rotating electrical machine 1 that serves as a vehicle drive source, and a power transmission mechanism 7 provided in a power transmission path that connects the rotating electrical machine 1 and wheels W.
- the power transmission mechanism 7 includes an input member 3, a counter gear mechanism 4, a differential gear mechanism 5, and left and right output members 6A and 6B.
- the input member 3 has an input shaft 31 and an input gear 32 .
- the input shaft 31 is a rotating member that rotates around the first axis A1.
- the input gear 32 is a gear that transmits rotational torque (driving force) from the rotary electric machine 1 to the counter gear mechanism 4 .
- the input gear 32 is provided on the input shaft 31 of the input member 3 so as to rotate together with the input shaft 31 of the input member 3 .
- the counter gear mechanism 4 is arranged between the input member 3 and the differential gear mechanism 5 in the power transmission path.
- the counter gear mechanism 4 has a counter shaft 41 , a first counter gear 42 and a second counter gear 43 .
- the counter shaft 41 is a rotating member that rotates around the second axis A2.
- the second axis A2 extends parallel to the first axis A1.
- the first counter gear 42 is an input element of the counter gear mechanism 4 .
- the first counter gear 42 meshes with the input gear 32 of the input member 3 .
- the first counter gear 42 is connected to the counter shaft 41 so as to rotate together with the counter shaft 41 .
- the second counter gear 43 is an output element of the counter gear mechanism 4.
- the second counter gear 43 is formed to have a smaller diameter than the first counter gear 42 .
- the second counter gear 43 is provided on the counter shaft 41 so as to rotate together with the counter shaft 41 .
- the differential gear mechanism 5 is arranged on the third axis A3 as its rotation axis.
- a third axis A3 extends parallel to the first axis A1.
- the differential gear mechanism 5 distributes the driving force transmitted from the rotary electric machine 1 side to the left and right output members 6A and 6B.
- the differential gear mechanism 5 has a differential input gear 51 that meshes with the second counter gear 43 of the counter gear mechanism 4 .
- the differential gear mechanism 5 also includes a differential case 52, in which a pinion shaft, pinion gears, left and right side gears, and the like are accommodated.
- the left and right side gears are connected to the left and right output members 6A, 6B so as to rotate together.
- the left and right output members 6A, 6B are drivingly connected to the left and right wheels W, respectively.
- the left and right output members 6A and 6B transmit driving force distributed by the differential gear mechanism 5 to the wheels W, respectively.
- the left and right output members 6A and 6B may be composed of two or more members.
- the rotating electric machine 1 drives the wheels W via the power transmission mechanism 7.
- other reduction mechanisms such as planetary gear mechanisms may be utilized.
- the vehicle drive device 17 in the vehicle drive system 100 shown in FIG. 1, together with the case 2, various components within the case 2 form the vehicle drive device 17 according to this embodiment.
- One or both of the left and right output members 6 ⁇ /b>A and 6 ⁇ /b>B may be partially or wholly not housed in the case 2 .
- the vehicle drive system 17 is applicable not only to the vehicle drive system 100 having the specific configuration shown in FIG. 1, but also to various vehicle drive systems.
- the vehicle drive device 17 is arbitrary as long as it has at least one rotating member that is drivingly connected to the wheels W in a manner that can transmit power from a drive source (for example, the rotary electric machine 1 or the engine) to the wheels W. of vehicle drive systems.
- a drive source for example, the rotary electric machine 1 or the engine
- FIG. 2 is an explanatory diagram of the bearing structure 9 suitable for the vehicle drive device 17 according to this embodiment, and is a schematic diagram viewed in the axial direction.
- the X direction and the X1 side and the X2 side along the X direction are defined as directions perpendicular to the first axis A1.
- the X direction may substantially correspond to the horizontal direction, for example.
- bearing structure 9 will be described with an example applied to the bearing 90 that rotatably supports the input shaft 31 shown in FIG. It may be applied to other possible supporting bearings (not shown).
- the bearing 90 is press-fitted (interference-fitted) with the input shaft 31, which is a member on the rotating side, and is loosely fitted to the case 2, which is a member on the stationary side. That is, the outer race 91 of the bearing 90 is loosely fitted into the shaft hole of the case 2 , and the input shaft 31 is press-fitted radially inward of the inner race 92 .
- the bearing 90 is a ball bearing in the example shown in FIG. 2, it may be another type of rolling bearing using rollers or the like.
- the surface of the bearing 90 that faces the case 2 in the radial direction is also referred to as "the outer peripheral surface of the outer race 91".
- FIG. 3 is an explanatory view of the groove 96 formed on the outer peripheral surface of the outer race 91.
- a part of the case 2 in FIG. 90 is a side view (viewed in the X direction from the X2 side).
- FIG. 3 schematically shows another part of case 2 in FIG. 2 (X1 side with respect to line L200 in FIG. 2).
- the Y direction and the Y1 side and Y2 side along the Y direction are defined as directions parallel to the first axis A1.
- the oil is schematically indicated by a hatched area 80 .
- FIG. 4 is an explanatory diagram of variations of the R shape of the bottom of the groove 96, and is a cross-sectional view along the line Q1-Q1 in FIG.
- a groove 96 through which oil passes is formed on the outer peripheral surface of the outer race 91 of the bearing 90 (the surface facing the case 2 in the radial direction).
- the grooves 96 may have a cross-sectional shape with corners R at the bottoms 960A, 960B, 960C as shown in FIG.
- FIG. 4 schematically shows the cross-sectional shape of the groove 96.
- FIG. 4 schematically shows three types of bottoms 960A, 960B, and 960C in the groove 96.
- stress concentration at the bottom portion of the groove 96 can be prevented, and the size of the bearing 90 having the groove 96 can be reduced.
- the groove 96 has a spiral shape around an axis extending from one axial end to the other axial end of the bearing 90 and is axially open at both axial ends of the bearing 90 .
- the groove 96 is schematically indicated by a single line (dotted line on the X1 side, which is the back side).
- FIG. 5 is an explanatory diagram of the manner in which oil is conveyed by the grooves 96 of this embodiment, and is a diagram corresponding to FIG. 3 for explaining the flow of oil by the grooves 96 .
- the state of the groove 96 when the outer race 91 of the bearing 90 rotates with respect to the case 2 is indicated by reference numerals 96(1) to 96(4).
- 96(1) to 96(4) correspond in chronological order.
- the oil flows from one side in the axial direction (Y2 side in FIG. 5). It is conveyed to the other side (the Y1 side in FIG. 5) by the groove 96 (see arrow 300 in FIG. 5).
- the helical direction of the groove 96 is such that when the input shaft 31 rotates in the rotational direction corresponding to the forward movement of the vehicle, the oil in the space SP1 on one axial side (the Y2 side in FIG. 5) of the bearing 90 It is set to send to the other side of the bearing 90 (the Y1 side in FIG. 5). Due to the axial flow of oil by the grooves 96, the oil can be appropriately supplied between the outer race 91 of the bearing 90 and the case 2 in the radial direction. can effectively reduce the coefficient of friction between Further effects associated with this will be described later with reference to FIGS. 6 to 8. FIG.
- an oil passage 36 is provided for supplying oil from the Y2 side) to the adjacent space SP1.
- the oil supplied to the space SP1 can be efficiently supplied between the outer race 91 of the bearing 90 and the case 2 in the radial direction.
- Part or all of the oil passage 36 may be formed in the case 2 or may be formed by a tubular member separate from the case 2 .
- the oil can be conveyed from one side (Y2 side in FIG. 5) of the bearing 90 to the other side (Y1 side in FIG. 5) through the groove 96. It is possible to eliminate the oil passage with For example, in a configuration in which a rotor shaft (not shown) of the rotary electric machine 1 is hollow to form an axial oil passage, oil from the axial oil passage is supplied to the power transmission mechanism 7 side (for example, the case 2 ) via a bearing 90 . can be supplied to various lubrication target elements arranged in the space on the power transmission mechanism 7 side in .
- FIG. 6 is a diagram showing states S400 to S404 when creep occurs in which the bearing 90 rotates with respect to the case 2.
- arrows R91 and R92 represent the rotation state and rotation direction.
- FIG. 7 shows a torque T1 generated in a direction that rotates the outer race 91 relative to the case 2 (here, clockwise rotation) and a torque T1 that stops the rotation of the outer race 91 relative to the case 2 (here, clockwise rotation).
- FIG. 4 is an explanatory diagram of a relationship with a torque T2 generated in a direction;
- FIG. 8 is a characteristic diagram according to a comparative example, and FIG.
- FIGS. 8 and 9 are characteristic diagram according to this embodiment.
- the horizontal axis represents the rotational speed of the inner race 92 of the bearing 90
- the vertical axis represents the torque. ing.
- the comparative example differs from the bearing 90 of this embodiment in that it does not have the groove 96 .
- state S402 and subsequent state S404 occur when torque T1 (see FIG. 7) falls below torque T2 (see FIG. 7). That is, when torque T1>torque T2, the outer race 91 continues to rotate (that is, so-called co-rotation creep occurs). Note that if the coefficient of friction that contributes to the torque T2 (the coefficient of friction between the case 2 and the outer race 91) can be reduced, the torque T2 can be reduced and the relationship of torque T1>torque T2 can easily be realized.
- the oil flowing through the groove 96 as described above can reduce the coefficient of friction (the coefficient of friction between the case 2 and the outer race 91) that contributes to the torque T2. Therefore, as shown in FIG. 9, it is easy to maintain the relationship of torque T1>torque T2 even in the low speed range.
- the oil flowing through the groove 96 maintains the relationship of torque T1>torque T2, thereby effectively reducing wear of the case 2.
- FIG. 10 is an explanatory diagram of a preferred arrangement of grooves.
- FIG. 10 shows two variations (grooves 96A, 96B) as modifications to the groove 96.
- the groove 96A is formed on the outer peripheral surface of the outer race 91A of the bearing 90A according to the first modified example
- the groove 96B is formed on the outer peripheral surface of the outer race 91B of the bearing 90B according to the second modified example.
- Both of the grooves 96A and 96B are provided with a plurality of grooves, unlike the groove 96 of the above-described embodiment.
- Each of the grooves 96A, 96B has a similar helical configuration, albeit with a significantly narrower circumferential extent than the groove 96 of the previous embodiment.
- grooves 96A and 96B similarly to the groove 96 according to the above-described embodiment, when the input shaft 31 rotates in the rotational direction corresponding to the forward movement of the vehicle, the oil in the space SP1 is pushed to the other side of the bearings 90A and 90B ( Y1 side in FIG. 10). Due to the axial oil flow by the grooves 96A and 96B, the oil can be appropriately supplied between the outer races 91A and 91B of the bearings 90A and 90B and the case 2 in the radial direction. The coefficient of friction between the outer races 91A, 91B and the case 2 can be effectively reduced.
- the configuration in which the grooves 96B are formed with a relatively high density can be advantageous in that the amount of oil that can be supplied can be increased (and the coefficient of friction can be reduced accordingly).
- the contact area between the outer race 91B and the case 2 is reduced, which is disadvantageous in that the contact pressure increases.
- the grooves on the outer circumferential surface of the outer race preferably, like the grooves 96A of the bearing 90A, intersect an imaginary line on the outer circumferential surface of the outer race that is parallel to the axial direction at each circumferential position. is formed so that is less than or equal to 1 time.
- FIG. 10 shows an imaginary line L800 for one circumferential position. In this case, imaginary line L800 intersects groove 96A of bearing 90A only once, but intersects groove 96B of bearing 90B twice.
- the term "intersection” here means a cross-shaped manner. Therefore, in the case of the imaginary line L801 illustrated for the bearing 90A in FIG. 10 (an imaginary line L801 for another circumferential position), the imaginary line L801 is the axial end (Y1 side) of the groove 96A of the bearing 90A. end), but does not "cross" groove 96A. In this respect, also in the case of the groove 96 according to the above-described embodiment, an imaginary line (not shown) that intersects one axial end of the groove 96 intersects the other axial end of the groove 96 . The number of times is one or less.
- FIG. 11 is an explanatory diagram of a groove 96D formed in the outer peripheral surface of an outer race 91D of a bearing 90D according to a third modification, and is a side view (X direction view from the X2 side) similar to FIG. .
- 12 is an enlarged view of the Q2 portion of FIG. 11.
- FIG. 13 is a cross-sectional view along line Q3-Q3 of FIG. 12.
- FIG. 14 is a diagram corresponding to FIG. 12 in the case of a configuration without the oil reservoir 961D.
- the width of the groove 96D in the direction perpendicular to the longitudinal direction increases at both axial end portions.
- the groove 96D is shown in black in the portion on the front side.
- the groove width in the direction perpendicular to the longitudinal direction of the groove 96D is w0 in the normal section, whereas it is wider than w0 in the end portion. also has a significantly larger width w1.
- the portion of the end portion of the outer race 91D adjacent to the groove 96D can function as the oil reservoir 961D. It is possible to reduce wear on the case 2 side that may occur in the case.
- a portion 912 of the axial end of the outer race 91D adjacent to the groove 96 tapers at the circumferential end. , so that a relatively high surface pressure can be applied to the case 2 that contacts the portion 912 . Such relatively high surface pressure can accelerate wear of the case 2 .
- an oil reservoir 961D that does not come into contact with the case 2 is formed.
- the oil reservoir 961D may be formed by cutting the portion 912 or the like.
- the bottom portion 960D of the groove 96D has the form of the bottom portion 960A described above with reference to FIG. 960C form.
- the oil reservoir 961D is formed at both ends in the axial direction with respect to one groove 96D. ) may be formed only.
- the width w0 of the groove 96D is changed from the width w1 to w1 gradually, but it may be changed stepwise. That is, the angle ⁇ shown in FIG. 12 may be approximately 90 degrees. Also, the corner portion related to the angle ⁇ shown in FIG. 12 may be given an angle R. FIG. Also, similarly, the corner portion related to the angle ⁇ shown in FIG. 12 may be given an angle R. Also, although one groove 96D is formed in the example shown in FIGS. 11 to 13, a plurality of similar grooves 96D may be formed as described above with reference to FIG.
- an oil reservoir like the oil reservoir 961D described above with reference to FIGS. 11 to 13 may be formed.
- an oil reservoir portion may be formed for each of the plurality of grooves 96D, or may be formed in common for two or more of the plurality of grooves 96D. good.
- FIG. 15 is an explanatory diagram of a groove 96E formed in the outer peripheral surface of the outer race 91E of the bearing 90E according to the fourth modification, and is a side view (X direction view from the X2 side) similar to FIG. .
- the groove 96E according to this modified example differs from the groove 96 according to the above-described embodiment in that it opens only on one end side (Y2 side) in the axial direction. Specifically, although the groove 96E extends in the axial direction and in the circumferential direction around the axis, the groove 96E does not open in the axial direction at the end surface of the outer race 91E on the Y1 side, returns to the Y2 side, and returns to the Y2 side of the outer race 91E. is axially open at the end face of the
- the groove 96E according to this modified example has a form in which it makes one reciprocation from the opening (entrance) on the Y2 side toward the Y1 side and then returns to the Y2 side and opens, but it may also have a form in which it makes two or more reciprocations. .
- a plurality of grooves 96E may be formed in such a manner that a plurality of sets of inlets and outlets are formed on the Y2 side.
- an oil reservoir like the oil reservoir 961D described above with reference to FIGS. 11 to 13 may be formed.
- an oil reservoir portion may be formed for each of the plurality of grooves 96E, or may be formed commonly for two or more of the plurality of grooves 96E. good.
- FIG. 16 is an explanatory diagram of a groove 96F formed in the outer peripheral surface of the outer race 91F of the bearing 90F according to the fifth modification, and is a side view (X direction view from the X2 side) similar to FIG. .
- the outer race 91F according to this modified example differs from the outer race 91 according to the embodiment described above in that a groove 96F is added.
- the groove 96F allows oil to be transported in the opposite direction to the groove 96. Specifically, the groove 96F can send the oil from the Y1 side to the Y2 side when the input shaft 31 rotates in the rotational direction corresponding to when the vehicle moves forward.
- a plurality of grooves 96F according to this modified example may be formed as described above with reference to FIG. Also in this modified example, an oil reservoir like the oil reservoir 961D described above with reference to FIGS. 11 to 13 may be formed. When a plurality of grooves 96F are formed, an oil reservoir portion may be formed for each of the plurality of grooves 96F, or may be formed commonly for two or more of the plurality of grooves 96F. good.
- FIG. 17 is an explanatory diagram of a groove 96G formed in the inner peripheral surface of the case 2G (the surface facing the outer race 91 in the radial direction) according to the sixth modification, and is a schematic diagram showing the inner peripheral surface of the case 2G. It is a top view.
- the L direction shown in FIG. 17 corresponds to the circumferential direction.
- FIG. 17 shows an explanatory dotted line representing the connection of the grooves 96G, but the dotted line does not represent the groove 96G itself.
- a range SC1 shown in FIG. 17 schematically indicates an axial range over which the bearing 90 extends.
- the groove 96G is in the form of a single spiral, and is formed in the axial range (see range SC1) in which the bearing 90 extends. That is, the spiral-shaped groove 96G faces the outer race 91 of the bearing 90 over the entire axial length of the outer race 91 . In FIG. 17, the groove 96G extends beyond the bearing 90 on both axial sides of the bearing 90 so that it is open on both axial sides of the bearing 90 . Also in this modification, when the bearing 90 rotates with the rotation of the input shaft 31 (see S400) as described above with reference to FIG. 6, the outer race 91 rotates with respect to the case 2G.
- the spiral direction of the groove 96G is such that the oil in the space SP1 (see FIG. 3) is sent to the Y1 side when the input shaft 31 rotates in the rotational direction corresponding to the forward movement of the vehicle.
- this modification relates to the case 2G that may be used with the bearing 90 having the grooves 96 described above, but the case 2G can be suitably combined with bearings that do not have the grooves 96 described above. That is, in the case of this modification, the groove 96 in the bearing 90 may be omitted.
- the grooves 96G are open on both axial sides of the bearing 90 by extending beyond the bearing 90 on both axial sides of the bearing 90, but this is not the only option. That is, the groove 96G may be formed so as to open only on the Y2 side in the same way as the groove 96E described above with reference to FIG.
- the present invention is not limited to this. That is, in the above-described embodiment, the outer race 91 is loosely fitted to the stationary member, but the inner race 92 may be loosely fitted to the stationary member.
- grooves similar to the grooves 96 described above may be formed on the inner peripheral surface of the inner race 92 (the surface facing the stationary member in the radial direction).
- the outer race 91 is loosely fitted to the case 2, but it is not limited to this.
- the outer race 91 may be an intermediate fit or an interference fit to the case 2 .
- the wear of the case 2 can be reduced by forming a similar groove 96 in the outer race 91 .
- the present invention is applied to a vehicle driving device that drives wheels, but it is also applicable to a vehicle driving device that transmits driving force to vehicle-mounted parts other than wheels, and to a driving device that is used for purposes other than vehicles.
- a vehicle driving device that transmits driving force to vehicle-mounted parts other than wheels
- a driving device that is used for purposes other than vehicles.
- the present invention may be applied to a bearing structure related to a rotating member drivingly connected to an actuator.
- the applicable power transmission mechanism is arbitrary as described above, and may be applied to AMT (Automated Manual Transmission).
- Vehicle driving device driving device
- 2 Case (fixed side member), 90, 90A to 90F... Bearing, 31
- Input shaft rotating side member
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- General Engineering & Computer Science (AREA)
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- Rolling Contact Bearings (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
ベアリングと、
駆動源に駆動連結され、前記固定側部材に前記ベアリングを介して軸まわりに回転可能に支持される回転側部材と、を備え、
前記ベアリングは、前記回転側部材が圧入されるとともに、前記固定側部材に嵌合され、
前記ベアリングにおける前記固定側部材に径方向で対向する表面、又は、前記固定側部材における前記ベアリングに径方向で対向する表面には、油が通る1本以上の溝が形成され、
前記溝は、軸方向にかつ軸まわりの周方向に延在し、かつ、前記ベアリングの軸方向の両側のうちの少なくとも一方側において、開口する、駆動装置が提供される。
また、図11から図13に示す例では、1本の溝96Dが形成されているが、図10を参照して上述したように、複数の同様の溝96Dが形成されてもよい。また、複数の同様の溝96Dが形成される場合においても、図11から図13を参照して上述した油溜め部961Dのような油溜め部が形成されてもよい。溝96Dが複数本形成される場合、油溜め部は、複数の溝96Dのそれぞれごとに形成されてもよいし、複数の溝96Dの2つ以上の一部又は全部に共通に形成されてもよい。
Claims (6)
- 固定側部材と、
ベアリングと、
駆動源に駆動連結され、前記固定側部材に前記ベアリングを介して軸まわりに回転可能に支持される回転側部材と、を備え、
前記ベアリングは、前記回転側部材が圧入されるとともに、前記固定側部材に嵌合され、
前記ベアリングにおける前記固定側部材に径方向で対向する表面、又は、前記固定側部材における前記ベアリングに径方向で対向する表面には、油が通る1本以上の溝が形成され、
前記溝は、軸方向にかつ軸まわりの周方向に延在し、かつ、前記ベアリングの軸方向の両側のうちの少なくとも一方側において、開口する、駆動装置。 - 前記回転側部材は、前記駆動源からの動力を車輪に伝達可能な態様で車輪に駆動連結され、
前記ベアリングの軸方向の前記一方側から隣接する空間部に油を供給する油路を更に備え、
前記溝は、前記空間部に連通する態様で前記ベアリングの軸方向の前記一方側において開口するとともに、軸方向の他方側で開口し、かつ、
前記溝は、車両前進時に対応する前記回転側部材の回転方向の回転時に、前記空間部に供給される油を、前記ベアリングの前記一方側から軸方向の他方側に送るように、形成される、請求項1に記載の駆動装置。 - 前記溝は、底部に角Rを有する断面形状である、請求項1又は2に記載の駆動装置。
- 前記溝は、軸まわりの各周方向位置において、前記表面上の仮想ラインであって軸方向に平行な仮想ラインに対する交差回数が1回以下となるように、形成される、請求項1から3のうちのいずれか1項に記載の駆動装置。
- 前記溝は、前記ベアリングに形成され、前記ベアリングの軸方向の一端から他端まで延在する軸まわりの螺旋状の形態であり、かつ、前記ベアリングの軸方向の両側の端面で軸方向に開口する、請求項1から4のうちのいずれか1項に記載の駆動装置。
- 前記溝は、前記ベアリングに形成され、前記ベアリングの軸方向の両側のうちの前記少なくとも一方側の端部において、長手方向に対して垂直方向の溝幅が拡大する、請求項1から5のうちのいずれか1項に記載の駆動装置。
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06133488A (ja) * | 1992-10-13 | 1994-05-13 | Mitsubishi Electric Corp | 回転機の軸受装置 |
JP2017053420A (ja) * | 2015-09-09 | 2017-03-16 | 株式会社ジェイテクト | 転がり軸受 |
JP2019129608A (ja) | 2018-01-24 | 2019-08-01 | トヨタ自動車株式会社 | 車両用駆動装置 |
JP2020034076A (ja) * | 2018-08-29 | 2020-03-05 | トヨタ自動車株式会社 | 車両用動力伝達装置 |
US20200208682A1 (en) * | 2018-08-13 | 2020-07-02 | Schaeffler Technologies AG & Co. KG | Lubrication groove for deep groove ball bearing |
-
2022
- 2022-12-07 WO PCT/JP2022/045184 patent/WO2023112801A1/ja active Application Filing
- 2022-12-07 JP JP2023567728A patent/JPWO2023112801A1/ja active Pending
- 2022-12-07 CN CN202280077860.8A patent/CN118302618A/zh active Pending
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Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06133488A (ja) * | 1992-10-13 | 1994-05-13 | Mitsubishi Electric Corp | 回転機の軸受装置 |
JP2017053420A (ja) * | 2015-09-09 | 2017-03-16 | 株式会社ジェイテクト | 転がり軸受 |
JP2019129608A (ja) | 2018-01-24 | 2019-08-01 | トヨタ自動車株式会社 | 車両用駆動装置 |
US20200208682A1 (en) * | 2018-08-13 | 2020-07-02 | Schaeffler Technologies AG & Co. KG | Lubrication groove for deep groove ball bearing |
JP2020034076A (ja) * | 2018-08-29 | 2020-03-05 | トヨタ自動車株式会社 | 車両用動力伝達装置 |
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