WO2007043334A1 - ケーシングのシール構造 - Google Patents
ケーシングのシール構造 Download PDFInfo
- Publication number
- WO2007043334A1 WO2007043334A1 PCT/JP2006/319099 JP2006319099W WO2007043334A1 WO 2007043334 A1 WO2007043334 A1 WO 2007043334A1 JP 2006319099 W JP2006319099 W JP 2006319099W WO 2007043334 A1 WO2007043334 A1 WO 2007043334A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- case
- seal
- cylindrical member
- cylindrical
- sealing
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/062—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces characterised by the geometry of the seat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
-
- 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
-
- 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
- F16H2057/02013—Extension units for gearboxes, e.g. additional units attached to a main gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H2061/0046—Details of fluid supply channels, e.g. within shafts, for supplying friction devices or transmission actuators with control fluid
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
- F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
Definitions
- the present invention relates to a seal structure for a case sink, and more particularly to a seal structure for a casing that seals a flow path that passes through a joint portion between first and second case components.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2000-0 1 1 6 7 3 5 (Patent Document 1), a passage through which a fluid passes is formed in each of the divided cases, and these cases are combined.
- a drive device is disclosed in which a passage formed in each of them is sometimes communicated.
- Patent Document 2 Japanese Patent Laid-Open No. 2 0 3-1 6 6 4 0 7 (Patent Document 2), a hollow knock pin for positioning crosses the joint surface between the oil pump body and the oil pump cover, and the oil drain discharge hole And a cover positioning structure that is press-fitted into the oil supply path. '
- Patent Document 1 when a plurality of casings are combined to connect the flow paths provided in each case, it is necessary to provide a sealing portion that suppresses fluid leakage on the joint surface of the casing. is there.
- the seal portion when a seal portion is provided at a position exposed to the flow path, the seal portion may be washed away by the fluid flow, and the sealing performance may be deteriorated.
- An object of the present invention is to provide a case sink sealing structure having high sealing performance.
- the casing sealing structure according to the present invention includes a first case component having a first fluid path, and a second fluid that communicates with the first fluid path when combined with the first case component.
- a second case constituent member having a path and a joint portion between the first and second case constituent members are fitted to the first and second case constituent members to surround the first and second fluid paths And a seal member provided on the outer peripheral side of the cylindrical member.
- the seal portion is provided on the outer peripheral side of the cylindrical member, the seal portion is not exposed to the fluid flowing through the fluid path, and the seal portion is caused to flow by the fluid flow. Can be suppressed. As a result, it is possible to suppress a decrease in sealing performance.
- the cylindrical member includes a member that fits into both the first and second case constituent members.
- the tubular member can function as a knock pin by fitting the tubular member to both the first and second case constituent members, the number of holes for providing the knock pin is reduced. be able to. As a result, manufacturing costs are reduced.
- a seal portion is provided so as to be in contact with the outer peripheral surface of the cylindrical member.
- the seal portion is held between the tubular ⁇ member and the case constituent member. Therefore, it is possible to simplify the processing for forming the space for the seal portion and further reduce the manufacturing cost.
- a recess is formed by retreating at least one joint surface of the first and second case constituent members at a position adjacent to the outer peripheral surface of the cylindrical member, Is provided with a seal portion.
- the recess can be formed by processing only the corner of the case component.
- the seal structure of the case sink can be configured by providing the seal portion only at one place. As a result, the manufacturing cost can be reduced.
- the seal portion is an O-ring. Or a liquid gasket. As a result, high sealing performance can be obtained while reducing the manufacturing cost.
- the seal portion includes first and second seal members provided between the first and second case constituent members and the cylindrical member, respectively.
- the followability to the opening of the joint surfaces of the first and second seal constituent members can be improved.
- a seal structure having high sealing properties can be obtained.
- an inner diameter of a portion that receives the cylindrical member in the first and second case constituent members is larger than an outer diameter of the cylindrical member, and the first and second case constituent members The total depth of the portion that receives the cylindrical member is larger than the axial length of the cylindrical member.
- the tubular member is allowed to move, so that high sealing performance is ensured.
- the cylindrical member or the seal portion expands by coming into contact with the fluid flowing through the first and second fluid paths.
- the tubular member expands the seal portion in the radial direction by being fitted into the seal portion.
- a scenery structure having high sealing performance can be obtained while suppressing an increase in cost.
- FIG. 1 is a cross-sectional view of a power transmission device to which a case sink sealing structure according to Embodiment 1 of the present invention is applied.
- FIG. 2 is a diagram showing details of the structure of part A of the power transmission device shown in FIG.
- FIG. 3 is a cross-sectional view showing a case sink sealing structure according to Embodiment 1 of the present invention.
- FIG. 4 is a cross-sectional view showing a modification of the seal structure of the case sink according to Embodiment 1 of the present invention.
- FIG. 5 is a cross-sectional view showing another modification of the case sink sealing structure according to Embodiment 1 of the present invention.
- FIG. 6 is a cross-sectional view showing still another modification of the case sink sealing structure according to Embodiment 1 of the present invention.
- FIG. 7 is a cross-sectional view showing still another modified example of the seal structure of the case sink according to Embodiment 1 of the present invention.
- FIG. 8 is a cross-sectional view showing still another modified example of the seal structure of the case sink according to Embodiment 1 of the present invention.
- FIG. 9 is a cross-sectional view showing still another modified example of the casing seal structure according to Embodiment 1 of the present invention.
- FIG. 10 is a cross-sectional view showing still another modification of the casing sealing structure according to Embodiment 1 of the present invention.
- FIG. 11 is a sectional view showing still another modified example of the casing structure of the casing according to Embodiment 1 of the present invention.
- FIG. 12 is a cross-sectional view showing still another modification of the sealing structure for the casing according to Embodiment 1 of the present invention.
- FIG. 13 is a cross-sectional view showing still another modified example of the seal structure of the case sink according to Embodiment 1 of the present invention.
- FIG. 14 is a cross-sectional view showing still another modification of the case sink sealing structure according to Embodiment 1 of the present invention.
- FIG. 15 is a cross-sectional view showing a case sink scenery structure according to Reference Example 1.
- FIG. 16 is a cross-sectional view showing the seal structure of the case sink according to Reference Example 2.
- FIG. 17 is a cross-sectional view of a power transmission device to which the casing seal structure according to Embodiment 2 of the present invention is applied.
- FIG. 18 is a cross-sectional view showing the sealing structure of the casing according to the second embodiment of the present invention.
- FIG. 19 is a cross-sectional view showing the seal structure of the game sink according to Embodiment 3 of the present invention.
- FIG. 20 is a cross-sectional view showing a modification of the case structure of the case sink according to Embodiment 3 of the present invention.
- FIG. 21 is a cross-sectional view showing another modified example of the case structure of the case sink according to Embodiment 3 of the present invention.
- FIG. 22 is a diagram illustrating a mechanism in which the barrel-shaped member expands the sealing material in the structure shown in FIG.
- FIG. 23 is a cross-sectional view showing still another modified example of the seal structure of the case sink according to Embodiment 3 of the present invention.
- FIG. 24 is a cross-sectional view showing still another modification of the casing structure of the casing according to Embodiment 3 of the present invention.
- FIG. 1 is a cross-sectional view of a power transmission device to which a case sink sealing structure according to Embodiment 1 of the present invention is applied.
- drive unit 1 which is a power transmission device mounted on a hybrid vehicle, includes rotating electric machines 1 0 0, 2 0 0, a planetary gear mechanism 3 0 0, and a speed reduction mechanism 4 0 0 And a differential tone mechanism 500 and a drive shaft receiving portion 600.
- the rotating electrical machines 100, 20 0, the planetary gear mechanism 30 0, the deceleration mechanism 4 0 0 and the differential mechanism 5 0 0 are provided in the casing 700.
- the rotating electrical machines 10 0, 2 0 0 are motor generators having a function as an electric motor or a generator.
- the rotating electrical machines 1 0 0 and 2 0 0 are respectively connected to rotating shafts 1 1 0 and 2 1 0 that are rotatably mounted on the casing 7 0 0 through bearings 1 2 0 and 2 2 0.
- Each of rotors 1 3 0 and 2 3 0 has a rotor core and a magnet embedded in the rotor core.
- the rotor core is configured by laminating plate-like magnetic bodies such as iron or iron alloy.
- the magnets are arranged at almost equal intervals in the vicinity of the outer periphery of the rotor core.
- the stators 1 4 0 and 2 4 0 have ring-shaped stator cores 1 4 1 and 2 4 1 and stator coils 1 4 2 and 2 4 2 wound around the stator cores 1 4 1 and 2 4 1, respectively. .
- Stator coils 1 4 2 and 2 4 2 are each electrically connected to the battery via a cape nore. '
- Stator cores 14 1 and 2 4 1 are configured by laminating plate-like magnetic bodies such as iron or iron alloys.
- a plurality of teeth portions (not shown) and slot portions (not shown) as recesses formed between the teeth portions are formed on the inner peripheral surfaces of the stator cores 14 1 and 2 41.
- the slot portion is provided so as to open to the inner peripheral side of the stator cores 14 1 and 2 4 1.
- Stator coils 1 4 2 and 2 4 2 including three winding phases U phase, V phase and W phase are wound around the teeth portion so as to fit into the slot portion.
- the U phase, V phase, and W phase of the coils 1 4 2 and 2 4 2 are wound so as to be shifted on the circumference.
- Planetary gear mechanism 300 is constituted by a plurality of planetary gears, for example, and has a power split function and a speed reduction function.
- the ring gear in the plurality of planetary gears may be constituted by one cylindrical member.
- the power output from the engine (not shown) is transmitted to the shaft 2 and divided into two paths by the planetary gear mechanism 300.
- One of the two paths is a path that is transmitted from the speed reduction mechanism 400 to the drive shaft receiving portion 600 via the differential mechanism 500.
- the driving force transmitted to the drive shaft receiving portion 60 is transmitted as a rotational force to a wheel (not shown) via a drive shaft (not shown), thereby causing the vehicle to travel.
- the other is a path for generating electric power by driving the rotating electrical machine 100.
- the rotating electrical machine 1 0 0 generates power by the engine power distributed and distributed by the planetary gear mechanism 3 0 0.
- the electric power generated by the rotating electrical machine 100 is selectively used according to the vehicle ⁇ traveling state and the state of the battery (not shown). For example, during normal travel and sudden acceleration of the vehicle, the electric power generated by the rotating electrical machine 100 becomes the power for driving the rotating electrical machine 200 as it is. On the other hand, under the conditions determined for the battery, the electric power generated by the rotating electrical machine 100 is stored in the battery via an inverter and a comparator (not shown).
- the rotary electric machine 200 is driven by at least one of the electric power stored in the battery and the electric power generated by the rotary electric machine 100.
- the driving force of the rotating electrical machine 2 0 0 is transmitted from the speed reduction mechanism 4 0 0 to the drive shaft receiving portion 6 0 0 via the differential chanel mechanism 5 0 0. In this way, the driving force of the engine can be assisted by the drive and power from the rotating electrical machine, or the vehicle can be driven only by the driving force from the rotating electrical machine 200.
- the wheels are rotated by the poorness of the vehicle body.
- the rotating electrical machine 2 0 0 is driven through the drive shaft receiving portion 60 0, the differential mechanism 5 0 0, and the reverse speed mechanism 4 0 0 by the rotational force from the wheels.
- the rotating electrical machine 200 operates as a generator.
- the rotating electrical machine 200 acts as a regenerative brake that converts braking energy into electric power.
- the electric power generated by the rotating electrical machine 200 is stored in the battery via the inverter.
- the rotating electrical machines 100 and 20 generate heat when driving force is generated and when power is generated.
- heat is generated in the planetary gear mechanism 300 by driving.
- the heat generated in the rotating electrical machines 100, 200 or the planetary gear mechanism 300 is released to the casing 70 through oil or the like.
- the components of the drive unit 1 in the casing 700 are affected by heat.
- a water jacket 800 as a “cooling device” is provided in the case sink 700.
- a cooling medium passage for circulating the cooling medium is formed.
- the cooling medium in the cooling medium passage is circulated through the radiator 3 by the pump 4.
- the rotating electrical machines 1 0 0 and 2 0 0 are cooled via the casing 7 0 0.
- Cold For example, LLC (Long Life Coolant) is used as the rejection medium, but cooling water and antifreeze can also be used.
- the cooling medium passage is set so that the cooling medium flows in the direction (in the direction of arrow D R 1) from the rotating electrical machine 200 side toward the rotating electrical machine 100 side.
- the rotating electrical machines 1 0 0 and 2 0 0 are respectively housed in a housing 7 10 and a case 7 20 which are separate casings.
- the water jacket 800 has a first portion 8 10 located on the rotating electrical machine 10 0 side and a second portion 8 2 0 located on the rotating electrical machine 2 0 0 side.
- the side surface of the first portion 8 1 0 of the water jacket 8 0 0 is formed integrally with the housing 7 1 0, and the side surface of the second portion 8 2 0 of the water jacket 8 0 0 is formed integrally with the case 7 2 0. Is done.
- the first and second parts 8 10 and 8 2 0 are provided with openings serving as cooling medium passages. Then, by combining the nose zinc 7 10 and the case 7 20, the cooling medium passage in the first portion 8 10 and the cooling medium passage in the second portion 8 2 0 are communicated.
- the cooling medium is formed between the housing 7 1 0 (first portion 8 1 0 of the water jacket 8 0 0) and the case 7 2 0 (second portion 8 2 0 of the water jacket 8 0 0). Pass through the joint surface. Therefore, it is necessary to provide a seal structure that suppresses the leakage of the cooling medium from the joint surface between the housing 7 10 and the case 7 2 0.
- Figures 15 and 16 are cross-sectional views showing the seal structures of case sinks according to Reference Example 1 and Reference Example 2, respectively.
- FIG. 2 is a diagram showing details of the structure of part A in FIG.
- FIG. 3 is a cross-sectional view showing a sealing structure of the casing according to the present embodiment, and schematically shows the structure shown in FIG.
- a flow path 7 11 is formed in the housing 7 1 0 constituting the first portion 8 10 of the water jacket, and the second portion 8 2 0 of the water jacket is formed.
- a flow path 7 2 1 is formed in the case 7 20 that is configured.
- a knock pin 7 30 having a cylindrical shape is provided on a joint surface between the housing 7 10 and the case 7 20.
- a FIPG reservoir 7 4 0 is provided on the outer peripheral surface of the knock pin 7 3 0.
- the FI P G reservoir 7 40 is provided in a recess formed by chamfering the corner of the joint surface between the housing 7 10 and the case 7 20.
- the FIPG pool 7 4 0 is not exposed to the flow of the cooling medium, and the FIPG pool 7 4 0 is allowed to flow. Can be suppressed. As a result, it is possible to suppress a decrease in sealing performance. Further, the chamfering process for forming the space for the FI P G pool 740 can be easily performed as compared with the formation of the groove, so that an increase in cost is suppressed. Further, since the knock pins 7 30 can be used as positioning means when the housing 7 10 and the case 7 20 are assembled, the number of knock pins can be reduced. As a result, the number of parts can be reduced and costs can be reduced.
- FIG. 4 to FIG. 14 are diagrams showing modified examples of the seal structure.
- Fig. 4 and Fig. 5 As described above, the chamfering process for forming the FIPG reservoir 7 4 0 installation space (recess) may be provided only on one of the housing 7 1 0 and the case 7 2 0. Further, as shown in FIG. 6, the FIPG reservoir 74 0 is provided in a recess formed by countersinking the corner of the joint surface between the housing 7 1 0 and the case 7 2 °. May be. Further, as shown in FIGS. 7 and 8, the spot facing may be applied only to one of the housing 7 10 and the case rim 20.
- an O-ring 7 5 0 is provided instead of the FI P G pool 7 4 0.
- the housing 71 1 ⁇ is formed by chamfering, and the recess is provided with a ⁇ link 7 5 0, and in the example of FIG. 10, the case 7 2 0 is chamfered.
- an O link 7 5 0 is provided in the recess formed by countersinking the housing 7 10.
- an O-ring 7 5 0 is provided in a recess formed by countersinking the case 7 2 0.
- FIPG pool 7 4 0 or O link 7 5 0 is provided in a position adjacent to the outer peripheral surface of the knock pin 7 30, a recess formed by retreating at least one of the joint surfaces of the housing 7 10 and the case 7 20.
- the FIPG pool 7 4 0 and the O-ring 7 5 ° force are provided so as to contact the outer peripheral surface of the knock pin 7 3 0 at the joint portion of the housing 7 10 and the case 7 20. It has been.
- the outer peripheral surface of the knock pin 7 3 0 and the O-ring 7 5 0 can be provided apart from each other at the joint between the housing 7 1 0 and the case 7 2 0.
- the housing 7 It is necessary to perform a process of providing a groove on the joint surface of 10 or case 7 20.
- the FIPG pool 7 4 0 0 link 7 5 0 is not provided by simply cutting the corner of the housing 7 1 0 case 7 2 0. Can be formed.
- the manufacturing cost is reduced by simplifying the processing of the housing 7 10 and the case 7 20.
- the seal structure can be formed by providing the FIPG pool 7 4 0 or the 0 link 7 5 0 at one place. As a result, an increase in manufacturing costs can be suppressed.
- processing for forming a space for installation of FIPG pool 7 4 0 may be performed on knock pin 7 3 0.
- the FIPG pool 7 4 0 is provided so as to contact the outer peripheral surface of the knock pin 7 3 0.
- the FIPG pool 7 40 may be provided over substantially the entire axial direction of the knock pin 73 30.
- the case structure of the case sink according to the present embodiment includes a housing 7 10 as a “first case component” having a flow path 7 11 as a “first fluid path”, and a housing 7 Case 7 2 0 as “second case component” having flow path 7 2 1 as “second fluid path” communicating with flow path 7 1 1 when combined with 1 0 and housing 7
- a “cylindrical member” that is fitted to both the housing 7 1 0 and the case 7 2 0 at the joint between the 1 0 and the case 7 2 0 and is provided so as to surround the flow paths 7 1 1 and 7 2 1
- a FIPG pool 7 4 0 or 0 ring 7 5 0 as a “seal part” provided on the outer peripheral side of the knock pin 7 3 0.
- the knock pin 7 30 can be used as a positioning means when the housing 7 10 and the case 7 20 are assembled. As a result, it is possible to reduce the manufacturing cost of the casing 70 for providing the knock pin by reducing the number of processing steps.
- the “seal part” is provided on the outer peripheral side of the knock pin 7 30, the “seal part” is not exposed to the fluid flowing through the flow paths 7 1 1, 7 2 1, and the flow of the fluid The “seal part” can be prevented from flowing. As a result, it is possible to suppress a decrease in sealing performance. Furthermore, manufacturing costs can be further reduced by configuring the “seal” with an O-ring or liquid gasket (FIPG).
- FIPG liquid gasket
- knock pin 7 30 is not limited to a cylindrical shape, and may be, for example, a cylindrical shape having a polygonal cross section in the axial direction.
- FIG. 17 is a cross-sectional view of a power transmission device to which the case sink sealing structure according to the second embodiment is applied.
- the power transmission device according to the present embodiment is an automatic transmission 100 0 ° mounted on a vehicle.
- Case sink 7 0 0 B which accommodates each device of automatic transmission 1 0 0 0 is a lid-like case 7 1 0 B as a “first case component” and a cylinder as a “second case component” The case is divided into 7 2 0 B.
- the lid-shaped case 7 1 0 B and the cylindrical case 7 2 0 B protrude outward in the radial direction from the lid-shaped case 7 10 0 B and the cylindrical case 7 2 0 B in a state in which the end surfaces thereof are in close contact with each other.
- Each has a protruding flange.
- the rotating shaft 10 0 20 is supported rotatably with respect to the case sink 7 0 0 B by a bearing 1 0 2 2 provided on the lid-like case 7 1 0 B. Note that engine power (not shown) is transmitted to the rotating shaft 10 0 2 0 via a torque converter. As a result, the rotary shaft 100 ° is always driven to rotate.
- Planetary gears 10 2 4, 1 0 2 6 are arranged in the axial direction on the outer peripheral side of the rotary shaft 10 20.
- the planetary gears 10 2 4 and 1 0 26 constitute a so-called Ravigne type gear train in which a link gear and a planetary carrier are formed as a body.
- the planetary gear 1 0 2 4 is a single pinion type planetary gear.
- the planetary gear 1 0 2 6 is a double pinion type planetary gear.
- a sun gear 1 0 2 8 of a planetary gear 1 0 26 is supported on the outer peripheral side of the rotary shaft 1 0 2 0 via a plurality of bushes so as to be rotatable relative to the rotary shaft 1 0 2 0.
- the sun gear 1 0 2 0 of the planetary gear 1 0 2 4 S is rotated relative to the rotary shaft 1 0 2 0 and the sun gear 1 0 2 8 via a plurality of bushes Supported as possible.
- the sun gears 1 0 2 8 and 1 0 3 0 are respectively injected into pinion gears that are instructed to rotate on a common carrier pin 1 0 3 2.
- one pinion gear 1 0 3 4 in the pinion gear 1 0 2 6 which is a double pinion type pinion gear is shown.
- the other pinion gear functions as a pinion gear common to the pinion gears 10 2 4.
- the other pinion gear (not shown) is meshed with the link gear 1 0 3 6, and the output of the link gear 1 0 3 6 is transmitted to the output gear 1 0 3 8, the carrier pin 1 0 3 2
- a hub member 10 0 40 whose outer peripheral part is formed in a cylindrical shape is connected to the end on the lid-like case 7 10 B side by press-fitting.
- the friction engagement element 1 0 4 2 is included in a clutch device 1 0 4 8 that selectively transmits the rotation of the rotary shaft 1 0 2 0 to the hub member 1 0 4 0.
- the clutch device 1 0 4 8 is connected to the frictional engagement element 1 0 4 2 and the rotary shaft 1 0 2 0 and is rotated together with the friction engagement element 1 0 4 2.
- One friction plate is spline-fitted with a clutch drum 1 0 50 and a clutch drum 1 0 5 0 so that the friction engagement element 1 0 4 2 Clutch piston 10 0 2 that presses the clutch, and a piston piston 1 0 5 2 and a hub member 1 0 40 0, and a space in which the axial movement of the inner periphery is blocked by the snap ring Spring 1 0 5 4 which is interposed between the wall 1 0 5 4 and the clutch piston 1 0 5 2 and the partition wall 1 0 5 4 and biases the clutch piston 1 0 5 2 to the clutch drum 1 0 5 0 side And 6.
- a hydraulic chamber 1058 which is an oil-tight space, is formed between the clutch drum 10500 and the clutch piston 1052.
- a centrifugal hydraulic canceller for canceling the thrust of clutch piston 1 0 5 2 based on the centrifugal hydraulic pressure generated in the hydraulic chamber 1 0 5 8.
- a chamber 1 0 6 0 is formed.
- the one-way clutch 1 ⁇ 4 6 is used to restrict the rotation of the hub member 1 0 4 0 in one direction. belongs to.
- the one-way clutch 10 0 4 6 is arranged on the outer peripheral side and is arranged on the cylindrical case 7 20 B. It has an inner race that is fixed, and a sprag that is interposed between the outer race and the inner race. Here, the sprag prevents rotation in one direction.
- the friction engagement element 10 46 is a component member of the brake device 10 62 for selectively stopping the rotation of the hub member 10 40.
- the brake device 1 0 6 2 includes a friction engagement element 1 0 4 6, a brake piston 1 0 6 4, a sprink receiving plate 1 0 6 6 fixed to the cylindrical case 7 2 0 B, and a brake piston 1 And a spring (not shown) that is interposed between the 0 6 4 and the sprink receiving plate 1 0 6 6 and urges the brake piston 1 0 6 4 in a direction to isolate it from the friction engagement element 1 0 4 6.
- a hydraulic chamber 1 0 6 8 is formed between the brake piston 10 6 4 and the cylindrical case 7 2 0 B.
- the working oil is supplied through the connected flow path 7 2 2.
- the oil passage 7 11 is connected to a hydraulic oil supply hole connected to a valve body (not shown).
- the flow paths 7 2 1, 7 2 2 (oil passages) formed in the cylindrical case 7 2 0 B are formed so as to penetrate a part of the cylindrical case 7 2 0 B, and the cylindrical shape
- the openings formed on the outer wall side of the case 7 20 B are each sealed with a sealing member 1 0 70.
- FIG. 18 is a cross-sectional view showing the sealing structure of the case sink (part B in FIG. 17) according to the present embodiment. Referring to FIG.
- the opening 7 1 2 of the flow path 7 1 1 formed in the lid-like case 7 10 B and the opening 7 22 of the flow path 721 formed in the cylindrical case 720 B are: It has a larger diameter than channels 71 1 and 721.
- the openings 71 2 and 722 are formed by, for example, spot facing.
- a cylindrical member 731 is inserted into the openings 71 2 and 722.
- the cylindrical member 73 1 includes, for example, a metal material such as iron or copper, or a relatively hard elastic body such as synthetic resin.
- the cylindrical member 731 is provided in a state straddling the lid-like case 710B and the cylindrical case 720B.
- a gap is formed between the inner peripheral surface of the openings 71 2 and 722 and the outer peripheral surface of the cylindrical member 731.
- the diameter of the inner periphery of the cylindrical member 731 is formed to be equal to or larger than the diameter of the flow paths 71 1, 721.
- the axial distance between the bottom surface of the opening 71 2 and the bottom surface of the opening 722, that is, the total depth of the openings 7 1 2 and 72 2 is the length of the cylindrical member 731 in the axial direction ( It is longer than (axis length). Therefore, the cylindrical member 73 1 can move in the axial direction, and when a radial axial deviation (A) occurs in the flow paths 71 1 and 721, the movable gap (B) Inclination to accommodate the deviation (A) is possible.
- the outer peripheral surface of the cylindrical member 73 1 is used as a “first and second seal member” for liquid-tightly sealing the inner peripheral surface of the openings '71 1 and 721 and the outer peripheral surface of the cylindrical member 73 1.
- the sheath members 741A and 741B (for example, rubber seals) are bonded (for example, vulcanized). Note that the mounting positions of the sealing members 741 A and 741 B are such that the outer periphery of the sealing members 741A and 741 B is maintained even if the cylindrical member 731 is moved in the axial direction to a position where the cylindrical member 731 contacts the bottom of the openings 712 and 722.
- the part is set so as to be pressed by the inner peripheral surfaces of the openings 712 and 722.
- the cylindrical member 731 is inclined by substantially the same amount as the axial deviation (A). In this way, even if the shaft misalignment (A) occurs between the two cases 71 OB and 72 OB, the cylindrical member 731 is inclined, so that leakage of hydraulic oil due to the shaft misalignment (A) is suppressed.
- this gap (C) is always kept at the seal member 741 A , 741 B, the leakage of hydraulic fluid from the gap (C) is suppressed by the sleeve members 741 A, 741 B.
- the spacing between the sleeve members 741 A and 741 B is set to be sufficiently larger than the assumed maximum value of the gap (C), and the cylindrical member 731 contacts the bottom of the openings 712 and 722. Even in this state, the gap (C) is always within the interval between the seal members 741 A and 74 IB.
- the cylindrical member 73 1 is movable in the openings 712 and 722 by the axial center and radial gaps, and is free from axial misalignment (A) in various directions of the flow paths 71 1 and 721. However, it is possible to seal the flow paths 7 1, 1 and 721 in a liquid-tight manner. Furthermore, even when these shaft misalignments (A) and axial center gaps (C) occur in combination, the spacing between the seal members 741 A and 741 B bonded to the cylindrical member 731 is sufficient.
- the seal members 741 A and 74 IB are pressed against the inner peripheral surfaces of the openings 71 2 and 722, and the flow path 71 1 , 721 is sealed in a liquid-tight manner to suppress hydraulic fluid leakage.
- the sealing cases 741 A and 741 B connect the lid-like cases 7 and 10 B and the cylindrical case 720 B to each other.
- the leakage of hydraulic fluid from the mating surface is suppressed, and the specified dimensional error of the circle f member 7 3 1 can be tolerated, so that extremely accurate machining is not required, resulting in automatic
- the manufacturing cost of the transmission 10 can be reduced.
- the cylindrical member 7 3 1 is made of an elastic body, so that the respective flow paths 7 1 1, 7 are formed by the elastic force of the cylindrical member 7 3 1. 2 Dimensional error of 1 can be tolerated.
- the cylindrical member 7 10 has a gap (C) in the axial direction between the lid-like case 7 10 0 B and the cylindrical case 7 2 0 B. 3 1 slides in the openings 7 1 2 and 7 2 2 in the axial direction, so that the liquid-tightness of the flow paths 7 1 1 and 7 2 1 is maintained, and against the axial misalignment (A) Accordingly, the liquid-tightness of the flow paths 7 11 1 and 7 2 1 is maintained by the inclination of the cylindrical member 7 31.
- the leakage of the fluid from the flow paths 7 1 1 and 7 2 1 is suppressed by the cylindrical member 7 3 1 appropriately moving in the openings 7 1 2 and 7 2 2.
- the gap formed between the seal members 7 4 1 A and 7 4 1 B is sufficiently larger than the assumed gap (C) in the axial direction. Therefore, even for the gap (C) in the axial direction, the pair of seal members 7 4 1 A and 7 4 1 B make the flow paths 7 1 1 and 7 2 1 liquid-tight. Can be sealed.
- the openings 7 1 2 and 7 2 2 are formed by counterbore processing, so that the processing becomes relatively easy and the manufacturing cost can be reduced. . ,
- the cylindrical member 731 may be made of, for example, aluminum other than the materials described above, or may be an elastic member such as a resin material resistant to fluid such as hydraulic oil. '
- sealing members 7 4 1 A and 7 4 1 B may be constituted by other elastic members such as a resin material.
- cylindrical member 7 3 1 and the seal members 7 4 1 A and 7 4 1 B may be configured separately as described above.
- Seal member 7 4 1, 7 4 1 B can be molded with member 7 3 1 inserted,
- the circular member 7 3 1 and the seal member 7 4 1 A, 7 4 1 B may be integrally molded with a resin material.
- the lid-like case 7 10 B and the cylindrical case 7 2 0 B and the cylindrical member 7 3 1 as the “cylindrical member” are used. Between them, seal members 7 4 1 A and 7 4 1 B are provided as “seal portions”, respectively.
- the opening 7 1 2, 7 2 which is a portion for receiving the cylindrical member 7 3 1 in the lid case 7 10 B and the cylindrical case 7 2 0 B
- the inner diameter of 2 is larger than the outer diameter of the cylindrical member 7 3 1
- the total depth of the openings 7 1 2 and 7 2 2 is larger than the axial length of the cylindrical member 7 3 1.
- FIG. 19 is a cross-sectional view showing a case sink sealing structure according to Embodiment 3 of the present invention.
- the seal structure of the casing according to the present embodiment is a modification of the seal structure according to the second embodiment.
- the automatic seal shown in FIG. This is provided in the case 1 of the transmission 100 °.
- a hole having a diameter larger than the diameter of the flow channel 7 11 is formed in the opening of the flow channel 7 11 formed in the lid-like case 7 10 B.
- the opening of the flow path 7 2 1 formed in the cylindrical case 7 20 B is a hole having a diameter larger than the diameter of the flow path 7 21, and the opening of the flow path 7 11 1 A hole having the same diameter as the formed hole is formed.
- one end is inserted into the hole formed in the lid-like case 7 10 B, and the other end is formed in the cylindrical case 72 B
- a cylindrical member 7 3 2 inserted into the hole is disposed so as to straddle the flow paths 7 11 1 and 7 2 1.
- the holes formed in the lid-like case 7 10 B and the cylindrical case 7 20 B are formed by, for example, spot facing, and the lid-like case 7 10 B and the cylindrical case 7 2 0 are formed. It has a function to prevent the axial displacement of the cylindrical member 7 3 2 when B is assembled.
- Cylindrical member 7 3 2 is composed of, for example, a water-absorbing resin made of a crosslinked polymer of a hydrophilic polymer such as an anionic cellulose derivative, starch-polyacrylamide, polyvinylpyrrolidone, maleic acid, or an acrylic polymer. It is composed of a so-called swelling member that expands by contact with a fluid.
- the cylindrical member 7 3 2 that is a swelling member expands due to contact with the hydraulic oil, and the sealing material 7 4 2 is The diameter is expanded and pressed toward the inner peripheral surface of the opening of the flow paths 7 1 1 and 7 2 1.
- the sealing material 7 4 2 is suitably deformed by the cylindrical member 7 3 2, The sealing performance by the sealing material 7 4 2 is maintained.
- the cylindrical member 7 3 2 and the sheath material 7 4 2 have such relative strength that when the cylindrical member 7 3 2 is swollen, the sealing material 7 4 2 is deformed by the swelling of the cylindrical member. As shown, each material is set.
- a cylindrical member 7 3 2 located on the inner peripheral side is replaced with a cylinder made of a metal material or a rigid resin material having a relatively high rigidity such as an iron material or a copper material.
- the sealing material 7 4 2 constituted by a rigid member having a shape and located on the outer peripheral side is made of the same material as the swelling member described above.
- FIG. 20 is a cross-sectional view showing a modification of the case structure of the case sink according to the present embodiment. Referring to FIG.
- a wedge-shaped member 7 3 3 made of a metal material such as iron or copper, and an elastically deformable cylindrical seal material 7 4 made of rubber or the like 7 4 3 is a seal structure. Note that the wedge-shaped member 7 3 3 has higher rigidity than the seal material 7 4 3.
- the sealing material 7 4 3 is originally formed in a cylindrical shape having a uniform cross section in the axial direction.
- the sealing material 7 4 3 is pressed in the outer diameter direction by the outer peripheral surface of the wedge-shaped member 7 3 3, and the flow paths 7 1 1, 7 2
- the diameter is increased so as to be in close contact with the inner peripheral surface of the opening of 1.
- Hydraulic oil leakage is prevented.
- radial and axial deformations are caused by misalignment or external force of the flow paths 7 1 1 and 7 2 1, and the sealing material 7 4 3 is deformed in response to the deviations and deformations. The sealing performance by the sealing material 7 4 3 is maintained.
- FIG. 21 is a cross-sectional view showing another modified example of the seal structure of the case sink according to the present embodiment.
- a barrel-shaped member 7 3 4 made of a metal material such as iron or copper, and an elastically deformable cylindrical seal made of, for example, a comb material It is characterized in that a seal structure is formed by the material 7 4 4.
- the barrel-shaped member 7 3 4 has a length in the axial direction before the combination of the lid-like case 7 1 0 B and the cylindrical case 1 2 0 B.
- the lid-like case 7 1 0 B and the cylindrical case It is formed longer than the axial length between the bottoms of the openings formed in 7 20 B.
- the middle part of the barrel-shaped member 7 3 4 expands radially outward, and the sealing material 7 4 4 is pressed in the outer radial direction, and the lid-like case 7 1 0 B and cylindrical case 7 2 0
- the diameter is expanded so as to be in close contact with the inner peripheral surface of B. This improves the sealing performance of the joint between the lid-like case 7 10 B and the cylindrical case 7 20 B, and hydraulic oil from the joint surface between the lid-like case 7 10 B and the cylindrical case 7 2 B Leakage is prevented.
- the flow path 7 1 1, 7 2 1 Even if radial and axial deformations occur due to misalignment or external force, the sealing material 7 4 4 is deformed in response to the displacement or deformation, and the sealing material 7 4 The sealing performance by 4 is maintained.
- FIG. 23 is a cross-sectional view showing still another modified example of the sealing structure of the casing according to the present embodiment.
- FIG. 23 a state before the combination of the lid-like case 7 10 0 B and the cylindrical case 7 2 0 B is shown.
- the sealing structure on the lid case 7 10 B side and the sealing structure on the cylindrical case 7 2 0 B side are formed by separate members.
- Lid case 7 10 B The seal structure on the B side is a water-absorbing material composed of a cross-linked hydrophilic polymer such as an anionic cellulose derivative, nylon-polyacrylamide, polyvinylpyrrolidone, maleic acid, or an acrylic polymer.
- a cylindrical member 7 3 5 A made of a so-called swelling member that expands when it comes into contact with a fluid, and made of an elastically deformable sealing material 7 4 5 A made of, for example, a rubber material .
- the sealing structure on the cylindrical case 7 2 0 B side is made up of, for example, the cylindrical member 7 3 5 B made of the above-described swelling member and the inertia material 7 4 5 B made of, for example, rubber material that can be deformed by inertia. It is formed.
- Sealing materials 7 4 5 A and 7 4 5 B respectively have flange portions 7 4 5 OA and 7 4 5 0 B extending on the joint surfaces of the lid-like case 7 1 0 B and the cylindrical case 7 2 0 B .
- the sealing materials 7 4 5 A and 7 4 5 B become cylindrical parts 7 3 5 A, By being suitably deformed by 7 3 5 B, sealing performance by the sheet / leather material 7 4 5 A, 7 4 5 B is secured.
- Cylindrical members 7 3 5 A and 7 3 5 B and seal material 7 4 5 A and 7 4 5 B are used when cylindrical members 7 3 5 A and 7 3 5 B are swollen.
- the respective materials are set so that the sealing materials 745 A and 745 B have a relative strength that can be deformed by swelling of the cylindrical member.
- FIG. 24 is a cross-sectional view showing still another modified example of the seal structure of the case sink according to the present embodiment.
- FIG. 24 shows a state before the combination of the lid-like case 710 B and the cylindrical case 720 B.
- the sealing structure on the lid-like case 710 B side and the sealing structure on the cylindrical case 720 B side are formed by separate members.
- the seal structure on the side of the lid-like case 710 B consists of a wedge-shaped member 736 A made of a metal material such as iron or copper, and an elastically deformable cylindrical thin material 746 A made of a rubber material, for example. It is formed by.
- the seal structure on the cylindrical case 720 B side includes a wedge-shaped member 736 B made of a metal material such as iron or copper, and an elastically deformable cylindrical sheath material 746B made of a comb material or the like. And is formed. Sealing materials 746 A and 746 B have flange portions 7460A and 7460B extending on the joint surfaces of the lid-like case 710B and the cylindrical case 720B, respectively.
- the wedge-shaped members 736 A and 736 B have higher rigidity than the sealing materials 746 A and 746 B.
- the sealing materials 746 A and 746 B are originally formed in a cylindrical shape having a uniform cross section in the axial direction.
- the sealing materials 746 A and 746 B are pressed in the outer diameter direction by the outer peripheral surfaces of the wedge-shaped members 736 A and 736 B.
- the diameter is increased so as to be in close contact with the inner peripheral surfaces of the lid-like case 7 10 B and the cylindrical case 720 B.
- the sealing performance of the joint between the lid-like case 710B and the cylindrical case 720B is improved, and leakage of hydraulic oil from the joint surface of the lid-like case 710B and the cylindrical case 720B is prevented.
- the sealing materials 746 A, 746 B are deformed in response to the deviations and deformations. The sealing performance by the seal materials 746 A and 746 B is maintained.
- the idea of the present invention can be applied to aspects other than the above-described configuration.
- the flow paths 7 1 1 and 7 2 1 are not limited to the refrigerant passage and the hydraulic oil supply flow path, and the present invention can be applied to any flow path that communicates between different members. Is possible.
- the liquid flowing through the channel is not limited to water or oil, and the present invention can be applied to other fluids. In this case, a material suitable for the fluid is selected as the swelling member.
- cylindrical members 7 3 2, 7 3 5 A, 7 3 5 B, wedge wedge members 7 3 3, 7 3 6 A, 7 3 6 B and barrel-shaped members 7 3 4, and the sealing material 7 4 2 to 7 4 4, 7 4 5 A, 7 4 5 B, 7 4 6 A, 7 4 6 B are configured separately from each other, but the lid-like case 7 10 0 B and the cylindrical case Prior to the combination of 7 20 B, these members may be integrated by bonding or the like.
- the rubber material described above for example, a synthetic resin or the like may be used.
- a wedge-shaped member and a barrel-shaped member are used as the expanding member.
- the mode of the expanding member is not limited to these, and for example, a retaining ring formed in a cylindrical shape in the radial direction. Any member that generates force can be used freely as an expanding member.
- the present invention can be applied to, for example, a casing seal structure in a power transmission device or the like.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Gasket Seals (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007539859A JPWO2007043334A1 (ja) | 2005-10-07 | 2006-09-20 | ケーシングのシール構造 |
US11/991,959 US20080217867A1 (en) | 2005-10-07 | 2006-09-20 | Sealing Structure of Casing |
DE112006002639T DE112006002639T5 (de) | 2005-10-07 | 2006-09-20 | Dichtungsstruktur für eine Umhausung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005295212 | 2005-10-07 | ||
JP2005-295212 | 2005-10-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007043334A1 true WO2007043334A1 (ja) | 2007-04-19 |
Family
ID=37942584
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/319099 WO2007043334A1 (ja) | 2005-10-07 | 2006-09-20 | ケーシングのシール構造 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20080217867A1 (ja) |
JP (1) | JPWO2007043334A1 (ja) |
CN (1) | CN101283206A (ja) |
DE (1) | DE112006002639T5 (ja) |
WO (1) | WO2007043334A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20150107620A (ko) | 2014-03-13 | 2015-09-23 | 쟈트코 가부시키가이샤 | 케이스 유닛 및 그 조립 방법 |
JP2017020582A (ja) * | 2015-07-10 | 2017-01-26 | ジヤトコ株式会社 | 油路接続構造 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6189640B2 (ja) * | 2013-05-29 | 2017-08-30 | Ntn株式会社 | 電動リニアアクチュエータ |
US11162588B2 (en) * | 2017-01-16 | 2021-11-02 | Aisin Aw Co., Ltd. | Seal structure and transmission including the same |
US11433704B2 (en) * | 2018-09-21 | 2022-09-06 | Dana Heavy Vehicle Systems Group, Llc | Axle assembly and the tire inflation system made therewith |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62191985U (ja) * | 1986-05-27 | 1987-12-07 | ||
JPH05133474A (ja) * | 1991-11-07 | 1993-05-28 | Nippon Pillar Packing Co Ltd | 耐熱ガスケツトおよびそれを用いた継手構造 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1216317A (en) * | 1916-02-05 | 1917-02-20 | Lock Joint Pipe Co | Joint for concrete pipes. |
US1206111A (en) * | 1916-02-05 | 1916-11-28 | Allan M Hirsh | Joint for concrete pipes. |
US1385606A (en) * | 1916-10-16 | 1921-07-26 | Christensen Jorgen An Frederik | Device for joining concrete blocks disposed in a pillar or in series |
US2340926A (en) * | 1940-09-05 | 1944-02-08 | Detroit Macoid Corp | Plastic conduit |
US4669760A (en) * | 1986-02-05 | 1987-06-02 | Flow Industries, Inc. | Swivel fitting arrangement for use in a pressurized fluid line |
JP3802800B2 (ja) | 2001-11-30 | 2006-07-26 | 本田技研工業株式会社 | エンジンのオイルポンプカバー位置決め構造 |
JP2004116735A (ja) | 2002-09-27 | 2004-04-15 | Toyota Motor Corp | 駆動装置 |
-
2006
- 2006-09-20 WO PCT/JP2006/319099 patent/WO2007043334A1/ja active Application Filing
- 2006-09-20 US US11/991,959 patent/US20080217867A1/en not_active Abandoned
- 2006-09-20 JP JP2007539859A patent/JPWO2007043334A1/ja not_active Withdrawn
- 2006-09-20 CN CN200680037345.8A patent/CN101283206A/zh active Pending
- 2006-09-20 DE DE112006002639T patent/DE112006002639T5/de not_active Withdrawn
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62191985U (ja) * | 1986-05-27 | 1987-12-07 | ||
JPH05133474A (ja) * | 1991-11-07 | 1993-05-28 | Nippon Pillar Packing Co Ltd | 耐熱ガスケツトおよびそれを用いた継手構造 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20150107620A (ko) | 2014-03-13 | 2015-09-23 | 쟈트코 가부시키가이샤 | 케이스 유닛 및 그 조립 방법 |
JP2015175398A (ja) * | 2014-03-13 | 2015-10-05 | ジヤトコ株式会社 | ケースユニット、及びその組み立て方法 |
JP2017020582A (ja) * | 2015-07-10 | 2017-01-26 | ジヤトコ株式会社 | 油路接続構造 |
Also Published As
Publication number | Publication date |
---|---|
US20080217867A1 (en) | 2008-09-11 |
CN101283206A (zh) | 2008-10-08 |
DE112006002639T5 (de) | 2008-08-21 |
JPWO2007043334A1 (ja) | 2009-04-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8736119B2 (en) | External cover-cooled rotary electric machine and casing used therein | |
EP2778460B1 (en) | Drive force transmission device | |
US20140239757A1 (en) | Housing Arrangement for an Electrical Machine | |
US9085295B2 (en) | Drive system for hybrid vehicle | |
JP2013154872A (ja) | パワートレインモジュール | |
WO2007043334A1 (ja) | ケーシングのシール構造 | |
JP2015174561A (ja) | 車両用駆動装置とその組付方法 | |
JP2013072371A (ja) | オイルポンプ装置 | |
US7683520B2 (en) | Electric motor and rotating device that changes relative phase of rotors | |
JP2018038099A (ja) | 電動モータ | |
US9421857B2 (en) | Modular powertrain component for hybrid electric vehicles | |
JP6967994B2 (ja) | 潤滑油供給装置 | |
US7926819B2 (en) | Seals for transmission drive motors | |
JP5310783B2 (ja) | 動力伝達装置 | |
JP2010007516A (ja) | 電動オイルポンプ | |
JP5682352B2 (ja) | 動力伝達装置 | |
JP5402001B2 (ja) | 回転電機の冷却構造およびその製造方法 | |
JP2009201216A (ja) | 電動機の冷却構造 | |
WO2012018027A1 (ja) | ハイブリッド駆動装置 | |
JP2019017187A (ja) | 回転電動機、この回転電動機を備えたインホイールモータ駆動装置および回転電動機の製造方法 | |
JP2012016240A (ja) | 回転電機及び回転電機冷却システム | |
JP5261461B2 (ja) | 車両用駆動装置 | |
JP2009185912A (ja) | トルクコンバータ | |
JP4961257B2 (ja) | 電動機 | |
US20210095766A1 (en) | A sealing arrangement for a hydrodynamic machine for a vehicle |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200680037345.8 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
DPE1 | Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 11991959 Country of ref document: US |
|
ENP | Entry into the national phase |
Ref document number: 2007539859 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120060026399 Country of ref document: DE |
|
RET | De translation (de og part 6b) |
Ref document number: 112006002639 Country of ref document: DE Date of ref document: 20080821 Kind code of ref document: P |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 06798357 Country of ref document: EP Kind code of ref document: A1 |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: 8607 |