JP2006336718A - Oil feeder - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an oil feeder capable of reducing cost for arranging a discharge passage connected to an oil pump while securing the degree of freedom of the arrangement of the oil pump installed in a gear storage case. <P>SOLUTION: This oil feeder A comprises the oil pump 21 installed in a transmission casing 16 having side walls on which an input shaft 4 disposed in a drive force transmission system D and output shafts 6, 7 connected coaxially with the input shaft 4 through a gear train are pivotally supported and driven by receiving the rotation of the input shaft 4 through a pump shaft 22 disposed oppositely to the input shaft. A pressure oil from the oil pump 21 is fed to the gear train in the transmission casing 16 after being passed through a shaft oil passage 69 formed in the pump shaft 22. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an oil supply device mounted on a gear housing case such as a transmission provided in a power transmission system of a vehicle.

  The power transmission system of the vehicle transmits the driving force of the engine, which is a driving source, to the driving wheels via a clutch, a transmission, a differential, a transfer, an axle shaft, and the like. The gear train which comprises is accommodated in the gear accommodation case. Such a gear housing case such as a transmission is equipped with an oil supply device having an oil pump, and by driving the oil pump, the oil in the internal oil sump is sucked and supplied to the gear train to perform lubrication. Yes.

  By the way, in such an oil pump, for example, a trochoid pump or a gear pump, the pump shaft that receives the rotational force directly or indirectly from the input shaft on the engine side rotationally drives the driving rotating body and the driven rotating body, and both tooth surfaces thereof. The oil in the oil reservoir in the transmission casing is sucked through the suction passage in accordance with the meshing disengagement displacement, and the discharged oil is supplied to the gear train and the transmission element side.

  An example of such an oil supply device is disclosed in JP-A-8-68456 (Patent Document 1). Here, the oil supply device is a part where the torque converter casing and the transmission casing overlap and are integrally joined, and an oil pump is attached to a part away from the input shaft extending from the torque converter side. The rotational force on the side is transmitted to the oil pump through the chain-type rotation transmission means and is driven. In such an oil pump, the pump is driven in conjunction with the drive on the torque converter side, sucks oil through a suction passage extending from a lower oil sump in the transmission casing, and supplies discharged oil to the torque converter and transmission side. ing.

JP-A-8-68456

  By the way, the oil pump sucks oil from the oil reservoir through the suction passage formed in the transmission casing, and changes the speed of the discharge oil through the discharge passage formed in the transmission casing and through the oil passage provided on the input shaft and the output shaft that can be interlocked with it. It is supplied to gears, gear change elements, etc. In the oil supply device of Patent Document 1, a suction path and a discharge path are formed in the 2ND brake holder on the transmission casing side of the oil pump offset from the input shaft.

  As described above, in the conventional oil supply apparatus, all of the suction path and the discharge path are formed on the transmission casing side by drilling or the like, and the relatively long discharge oil becomes one of the factors that increase the processing cost. Yes. In particular, when it is necessary to guide the discharge oil to the side wall on the opposite side to the side wall on the oil pump mounting side, the discharge path is continuously formed relatively long along the inner wall of the transmission casing. This is one of the factors that increase costs.

  The present invention has been made by paying attention to the above-mentioned problems, and it is possible to reduce the cost of disposing the discharge passage connected to the oil pump while ensuring the degree of freedom of the arrangement of the oil pump attached to the gear housing case. An object of the present invention is to provide an oil supply device that can be reduced.

  In order to achieve the above object, the invention according to claim 1 is a gear in which an input shaft disposed in a driving force transmission system and an output shaft connected coaxially with the input shaft via a gear train are pivotally supported. In an oil supply apparatus equipped with an oil pump mounted on a side wall of a storage case and transmitting rotation of the input shaft to a pump shaft disposed opposite to the input shaft and driven by the pump shaft, pressure from the oil pump Oil is supplied to the gear train in the gear housing case through an in-shaft oil passage formed in the pump shaft.

  According to a second aspect of the present invention, in the oil supply device according to the first aspect, the pump shaft is arranged in parallel to the input shaft and is transmitted to rotate through a gear train.

  According to a third aspect of the present invention, in the oil supply device according to the first or second aspect, both ends of the pump shaft are pivotally supported by a pair of opposing side walls of the gear housing case.

  According to a fourth aspect of the present invention, in the oil supply device according to any one of the first to third aspects, the oil pump includes a driving rotary body that rotates by receiving a driving force via a pump shaft, and the driving rotary body. A discharge chamber located in a side where both tooth surfaces of the drive rotor and the driven rotor are engaged with each other is accommodated in the shaft oil passage, and the tooth surfaces are disengaged. The suction chamber located on the side communicates with the oil sump of the gear housing case through a suction path.

  According to a fifth aspect of the present invention, in the oil supply device according to any one of the first to fourth aspects, the gear housing case is coaxially connected to the input shaft on the engine side of the driving force transmission system via a transmission gear train. A transmission casing that pivotally supports a connected output shaft.

  According to the first aspect of the present invention, an oil pump is provided that is driven via a pump shaft disposed opposite to an input shaft in the driving force transmission system, and the pressure oil from the oil pump is supplied to the in-shaft oil passage of the pump shaft. Since the oil pump is supplied to the gear train in the gear housing case, the degree of freedom at the position where the oil pump is disposed is increased, and the portion corresponding to the oil passage in the shaft is formed along the wall portion of the gear housing case. Therefore, it is possible to shorten the discharge oil passage along the wall portion of the gear housing case, thereby reducing the cost.

  According to the invention of claim 2, since the pump shaft is arranged in parallel with the input shaft, the oil pump can be offset from the axial direction of the input shaft, the axial length of the gear housing case can be shortened, and the size can be reduced. .

  According to the invention of claim 3, since both side ends of the pump shaft are pivotally supported by the pair of side walls of the gear housing case, the pressure oil discharged from the oil pump on the one side wall side can be easily Can be supplied to the gear train in the gear housing case and the oil passage in the shaft forms a short-circuit path, so that the discharge oil passage can be shortened reliably and the cost can be reduced.

  According to the invention of claim 4, the oil in the oil reservoir of the gear housing case is guided to the suction chamber by driving the driving rotating body that rotates by receiving the driving force through the pump shaft and the driven rotating body that meshes with the driving rotating body, The pressure oil in the discharge chamber can be reliably supplied to the gear train in the gear housing case through the in-shaft oil passage.

  According to the invention of claim 5, even when the gear housing case is a transmission casing, oil can be supplied to the transmission gear train through a relatively short discharge oil passage including the in-shaft oil passage, and the transmission gear train is reliably lubricated. The cost can be reduced.

FIG. 1 shows a transmission equipped with an oil supply apparatus as an embodiment of the present invention.
Here, prior to the description of the oil supply device A, the driving force transmission system D including the automatic transmission 5 to which the oil supply device A is mounted will be described first. The driving force transmission system D is mounted on a hybrid vehicle that runs on the engine E and the in-wheel motor 13 of the left and right driving wheels W.

  The driving force transmission system D includes a reciprocating gasoline engine (hereinafter simply referred to as engine E), a flywheel 2 integrally coupled to the crankshaft 1, a clutch 3 attached to the flywheel 2, and the clutch 3 is engine E. A planetary gear type automatic transmission 5 that receives the rotational force received through the input shaft 4, a generator G connected to the protruding end side of the internal output shaft 6 of the automatic transmission 5, an internal / external output shaft 6, which will be described later. 7, a countershaft 8 connected in parallel at a predetermined interval, a differential case 9 that receives the rotation of the external output shaft 7 via the countershaft 8, and left and right each receiving a left-right rotational force branched by the differential case 9 Axle shafts 11, 12 and in-wheel motors 13 to which the left and right ends of the left and right axle shafts 11, 12 are connected are provided.

  The clutch 3 includes an input shaft 4 concentrically connected to the flywheel 2 so as to be relatively rotatable, a clutch plate 14 that is spline-fitted so as to be relatively movable in the axial direction with respect to the input shaft 4, and an elastic force to the clutch plate 14. And a clutch connection / disconnection means 15 for releasing the pressure contact when the release mechanism (not shown) is operated.

  The automatic transmission 5 has an input shaft 4 pivotally supported on one side wall 161 (right side wall in FIG. 1) of the transmission casing 16 via a main bearing 17 and a main bearing 18 on the other side wall 162 (left side wall in FIG. 1). The inner and outer output shafts 6 and 7 that are pivotally supported are arranged on the same center line, and a planetary gear type transmission gear mechanism 19 is attached over them. An oil pump 21 used in the oil supply device A is mounted in the vicinity of the transmission gear mechanism 19.

  As shown in FIGS. 1 and 2, the input shaft 4 includes a front portion 401 that opposes the clutch 3, a rear portion 402 that opposes the transmission chamber R, and an intermediate large-diameter portion 23 therebetween. The portion 23 is pivotally attached to the central boss portion 163 of the one side wall 161 via the main bearing 17. As shown in FIG. 2, the intermediate large-diameter portion 23 has a sliding bearing portion 24 formed continuously next to the main bearing 17, and is formed so as to pivotally support the intermediate large-diameter portion 23. As will be described later, a casing-side outlet 26 that is a part of the discharge passage 25 is formed in the sliding bearing portion 24. An annular groove portion 27 is formed in the intermediate large diameter portion 23 of the input shaft 4 so as to face the casing-side outlet 26, and the annular groove portion 27 is communicated with the central oil passage 28 of the input shaft 4 through the introduction passage 29.

The central oil passage 28 of the input shaft 4 is continuously formed in a straight line from the introduction passage 29 side to the output shaft side opening 31, and first and second branch passages 32 and 33 are formed at appropriate positions.
A rear portion 402 (left side in FIG. 2) of the input shaft 4 is fitted into a center hole 35 of the inner output shaft 6 described later so as to be relatively rotatable, and a cylindrical outer output shaft 7 is fitted on the inner output shaft 6. The outer output shaft 7 is pivotally attached to the central boss portion 164 of the other side wall 162 via a main bearing 18.

A pump gear 36 that transmits rotational force to an oil pump 21 (described later) is integrally attached to a portion of the intermediate large diameter portion 23 of the input shaft 4 on the transmission inner chamber R side, and a mounting flange 37 is overlapped with the pump gear 36. Projected. The center portion of the carrier 38 is integrally coupled to the other side surface of the mounting flange 37, and three planetary gears 39 are attached to the peripheral side of the carrier 38 at equal intervals in the circumferential direction. The planetary gear 39 meshes with a ring gear 45 and a sun gear 42, which will be described later, and can transmit rotational force.
Of the inner and outer output shafts 6 and 7, the rear end side of the inner output shaft 6 is connected to the generator G, and the sun gear 42 is integrally coupled to the cylindrical front portion 601 on the front end side. The sun gear 42 is formed so that the planetary gear 39 on the carrier 38 side meshes.

  The cylindrical outer output shaft 7 is externally fitted to the cylindrical front portion 601 through a gap t, and a drive gear 43 and a ring gear case 44 attached to the end are located on the transmission inner chamber R side. Connected together. The ring gear case 44 is disposed to face the carrier 38 with a predetermined interval, and an outer peripheral end thereof is bent in the axial direction to project an annular flange portion 441. A ring gear 45 is formed on an inner peripheral wall surface of the annular flange portion 441. The The ring gear 45 meshes with the planetary gear 39 on the carrier 38 side.

In FIG. 2, reference numeral 51 denotes a thrust bearing provided between the left and right side walls of the sun gear 42 and the ring gear case 44 and the annular flange portion 37, and reference numeral 52 denotes a rotating shaft 46 and a planetary gear pivotally supported. 39 shows an annular seal for reliably guiding the oil.
Such an automatic transmission 5 is a planetary gear type automatic transmission, and when a carrier 38 integral with the input shaft 4 rotates around the input shaft 4 together with a plurality of planetary gears 39, the ring gear 45 is in a low rotation or stopped state. Each planetary gear 39 rotates around its central axis 46 and can transmit the rotational force to the ring gear case 44, that is, the driving wheel W side on the outer output shaft 7 side. The rotational force can be increased and transmitted to the generator G side of the shaft 6.

The rotation of the external output shaft 7 of the automatic transmission 5 is transmitted from the drive gear 43 to the counter shaft 8 through the driven gear 53. The countershaft 8 is provided with a driven gear 53 and a reduction gear 54. The reduction gear 54 has fewer teeth than the driven gear 53, and can transmit the rotation by decelerating to the differential gear 55 meshing therewith. Further, the number of teeth of the differential gear 55 that meshes with the reduction gear 54 is large, and thus the differential case 9 is formed to rotate at a reduced speed.
A pair of pinion gears 57 are pivotally supported in the differential case 9, and a pair of side gears 58 meshing with the pinion gears 57 are connected to the left and right axle shafts 11 and 12, so that the driving force received by the differential case 9 can be relatively rotated. It is branched to the left and right and can be transmitted to the left and right drive wheels W.

The ends of the left and right axle shafts 11 and 12 are connected to a one-way clutch (not shown) in the in-wheel motor 13. The in-wheel motor 13 can be driven only by electric power from a battery (not shown) charged by the generator G, and is also driven by receiving driving force from the left and right axle shafts 11 and 12 via a one-way clutch (not shown). Alternatively, the drive wheel W can be driven by the engine E with a single driving force.
By the way, an oil pump 21 constituting the main part of the oil supply device A is disposed in the transmission chamber R in the vicinity of the transmission gear mechanism 19.

  The oil pump 21 is recessed in the other side wall 162 of the transmission casing 16 and has a pump chamber 61 formed by overlapping and integrally coupling the pump casing 59, and an outer that is rotatably fitted in the pump chamber 61. A rotor 62, an inner rotor 63 loosely fitted in the outer rotor 62, a pump shaft 22 with one end integrally coupled to the inner rotor 63 and an axial oil passage 69 continuously formed in the axial direction, At the suction position formed by the outer rotor 62 and the inner rotor 63 provided in the pump casing 59, the pump gear 67 integrally coupled from the center of the pump shaft 22, and the bearing portion 41 of the one side wall 161 pivotally supporting the other end. A suction port 64 (suction chamber) formed to face each other and a discharge port 65 (discharge chamber) facing the discharge position; Obtain.

As shown in FIG. 3, the other side wall 162 is formed with a through-hole-like suction passage 66 extending vertically, with its upper end communicating with the suction port 64, and the lower suction port 68 at the lower portion of the transmission casing 16. It is formed so as to be positioned below the surface Fs.
As shown in FIG. 2, the bearing portion 41 of the one side wall 161 is formed with a discharge path 25 that guides oil from the other end of the pump shaft 22 to the sliding bearing portion 24 of the central boss portion 163 below the bearing portion 41. The lower end of the discharge passage 25 is formed as a casing side outlet 26 in the sliding bearing portion 24, and the casing side outlet 26 communicates with an annular groove portion 27 (see FIG. 2) of the intermediate large diameter portion 23 of the input shaft 4. The oil from the oil pump 21 is allowed to flow into the central oil passage 28 of the input shaft 4.

The operation of the transmission equipped with such an oil supply device will be described along the operation of the driving force transmission system D.
The hybrid vehicle (not shown) travels while driving the left and right drive wheels W by the left and right in-wheel motors 13 while the battery satisfies the set charging condition. If the battery does not satisfy the set charging condition, the vehicle is driven and charged. In the mode, start running with generator charging and engine driving force.

  In this case, the clutch 3 is kept in contact, the rotation of the engine E is always transmitted to the input shaft 4, and the automatic transmission according to the load of the generator G and the running resistance from the drive wheels W is performed in the automatic transmission 5. The rotational force increased from the internal output shaft 6 is supplied to the generator G, and the rotational force decelerated from the external output shaft 7 is applied to the countershaft 8, the differential case 9, the left and right axle shafts 11, 12, The vehicle is transmitted to the drive wheels W via a one-way clutch (not shown) in the wheel motor 13 and the vehicle is driven by driving the engine.

If the battery does not satisfy the set charging condition and is stopped, the ring gear case 44 stops and the generator G on the side of the sun gear 42 and the internal output shaft 6 can be rotated at the maximum speed increasing ratio. Can drive well.
It is assumed that the engine E is driven in such traveling of the vehicle and the battery charging mode or the power generation dedicated mode.
At this time, the oil pump 21 of the oil supply device A is driven in conjunction with the input shaft 4.

  In this case, the pump shaft 22 interlocked with the input shaft 4 rotates the inner rotor 63 that is a driving rotating body of the oil pump 21 and the outer rotor 62 that is a driven rotating body that meshes with the inner rotor 63. As a result, the suction port 64 (suction chamber) on the side where the tooth surfaces of both rotors are disengaged sucks oil from the inside of the oil reservoir below the oil surface Fs through the suction passage 66, and both tooth surfaces of both rotors mesh. The pressure oil that reaches the discharge port 65 (discharge chamber) on the side is supplied to the central oil passage 28 of the input shaft 4 through the discharge passage 25. Furthermore, of the pressure oil that has reached the central oil passage 28, the oil that passes through the output shaft side opening 31 of the central oil passage 28 passes through the outlet communication passage 47 of the inner output shaft 6 and is a gap on the inner wall side of the outer output shaft 7. Guide oil to part t. The oil that has reached here is supplied to the main bearing 18 via the bearing oil passage 48 of the outer output shaft 7. Further, the oil that has passed through the first branch path 32 of the input shaft 4 passes through the first communication path 34 of the inner output shaft 6 and reaches the sun gear 42 in the ring gear case 44 and can be lubricated. Further, the oil that has passed through the second branch 33 of the input shaft 4 passes through the radial path r of the annular flange portion 37 from the end opening of the inner output shaft 6, and is pivotally supported coaxially with the rotating shaft 46 of the planetary gear 39. The planetary gear 39 can be supplied with oil. As described above, the pressure oil in the central oil passage 28 is supplied to each gear meshing surface and each sliding contact surface constituting the planetary gear type automatic transmission, and the lubrication and cooling of these gears can be performed accurately and durable. Can be secured.

  In particular, in the oil supply apparatus A of FIG. 1, the main part of the discharge passage 25 is formed by the in-shaft oil passage 69 of the pump shaft 22. For this reason, as shown in FIG. 1, compared with the conventional case (shown by a two-point difference line with reference symbol OL) in which all the discharge passages are formed on the side wall side of the transmission casing 16, the in-shaft oil passage 69 is a short circuit. In the oil supply apparatus A in FIG. 1, the length LH of the portion formed on the side wall side of the discharge path 25 can be sufficiently shortened, and the discharge path 25 can be reliably shortened and the cost can be reduced.

Moreover, since both side ends of the pump shaft 22 are pivotally supported across the pair of one side wall 161 and the other side wall 162 of the transmission casing 16, the pressure oil discharged by the oil pump 21 on the other side wall 162 side is used as the in-shaft oil passage. The degree of freedom at the position where the oil pump is disposed is increased from the point that it is easily guided to the one side wall 161 by 69.
Further, since the pump shaft 22 is arranged in parallel with the input shaft 4, the oil pump 21 can be offset from the axial direction of the input shaft, the axial length of the transmission casing 16 can be shortened, and the size can be reduced.

  In the above description, the oil pump has been described as a trochoid pump. However, the oil pump may be a gear pump in which the external teeth mesh with each other, or a turbine pump. In these cases, the same effect as the oil supply device A in FIG. can get. Further, in the above description, the gear housing case is a transmission casing. However, an oil supply device may be attached to a transfer or the like provided in a driving force transmission system and including a transmission gear train. Lubrication can be performed reliably and cost reduction can be achieved.

1 is a skeleton diagram of a driving force transmission system including a transmission equipped with an oil supply device as one embodiment of the present invention. FIG. It is a notch sectional view of the transmission equipped with the oil supply apparatus of FIG. It is a partial notch perspective view of the other side wall of the transmission casing of the transmission equipped with the oil supply apparatus of FIG.

Explanation of symbols

3 Clutch 4 Input shaft 5 Transmission 6 Inner output shaft 7 Outer output shaft 16 Shift casing (gear housing case)
21 Oil pump 22 Pump shaft 64 Oil path in shaft A Oil supply device D Driving force transmission system

Claims (5)

The input shaft arranged in the driving force transmission system and the output shaft connected coaxially with the input shaft via a gear train are mounted on the side wall of the gear housing case, and the rotation of the input shaft is controlled by the input shaft. In an oil supply device including an oil pump that is transmitted to a pump shaft that is disposed opposite to and driven by the pump shaft,
An oil supply apparatus characterized in that the pressure oil from the oil pump is supplied to a gear train in the gear housing case after passing through an in-shaft oil passage formed in the pump shaft. The oil supply device according to claim 1,
An oil supply apparatus, wherein the pump shaft is arranged in parallel with the input shaft and is transmitted to rotate through a gear train. The oil supply device according to claim 1 or 2,
An oil supply device, wherein both ends of the pump shaft are pivotally supported by a pair of opposite side walls of the gear housing case. In the oil supply device according to any one of claims 1 to 3,
The oil pump accommodates a driven rotating body that rotates by receiving a driving force via a pump shaft, a driven rotating body that meshes with the driving rotating body, and a side where both tooth surfaces of the driving rotating body and the driven rotating body mesh with each other. The discharge chamber located in the shaft communicates with the oil passage in the shaft, and the suction chamber located on the side where the both tooth surfaces are disengaged communicates with the oil reservoir of the gear housing case through the suction passage. Oil supply device. In the oil supply device according to any one of claims 1 to 4,
The oil supply device according to claim 1, wherein the gear housing case is a transmission casing that pivotally supports an input shaft on the engine side and an output shaft connected coaxially via a transmission gear train.

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