WO2017104764A1

WO2017104764A1 - Transmission device

Info

Publication number: WO2017104764A1
Application number: PCT/JP2016/087431
Authority: WO
Inventors: 隆憲野口; 慎弥松岡
Original assignee: 武蔵精密工業株式会社
Priority date: 2015-12-18
Filing date: 2016-12-15
Publication date: 2017-06-22
Also published as: JP2017110791A

Abstract

A transmission device provided, in a transmission case, with: a first transmission member having a first axis as the center axis; an eccentric rotation member in which a main shaft part capable of rotating about the first axis and an eccentric shaft part are integrally linked, the eccentric shaft part having a second axis which is eccentric in relation to the first axis as the center axis; a second transmission member disposed so as to face the first transmission member and rotatably supported by the eccentric shaft part; a third transmission member disposed so as to face the second transmission member, the third transmission member being capable of rotating about the first axis; a first gear shift mechanism capable of transmitting a torque between the first and second transmission members; and a second gear shift mechanism capable of transmitting a torque between the second and third transmission members, wherein the second transmission member (8) has a hollow part (SP) communicating to an internal space (IC) of the transmission case (C), and is disposed so that a bearing (7) for rotatably supporting the second transmission member (8) on the eccentric shaft part (6e) faces the hollow part (SP). The first gear shift mechanism and the bearing on the eccentric shaft part are thereby efficiently lubricated.

Description

Transmission

The present invention centers on a first transmission member having a first axis as a central axis, a main shaft portion rotatable around the first axis, and a second axis eccentric from the first axis, in a transmission device, particularly in a transmission case. An eccentric rotating member integrally connected to an eccentric shaft portion serving as an axis, a second transmission member disposed opposite to the first transmission member and rotatably supported by the eccentric shaft portion, and opposed to the second transmission member A third transmission member arranged and rotatable around the first axis, a first transmission mechanism capable of transmitting torque while shifting between the first and second transmission members, and a transmission between the second and third transmission members. The present invention relates to a transmission device including a second speed change mechanism capable of transmitting torque.

In the transmission device as described above, lubricating oil is normally supplied into the transmission case during operation, and the internal mechanism of the transmission case, that is, the first to third transmission members, is supplied by this lubricating oil. Lubrication is possible. Further, a bearing is interposed between the second transmission member and the eccentric shaft portion of the eccentric rotating member in order to facilitate relative rotation therebetween (see Patent Document 1 below).

Japanese Patent No. 4814351

However, in the transmission device of Patent Document 1, since the bearing interposed between the second transmission member and the eccentric shaft portion is surrounded by the first to third transmission members, it is difficult for the lubricating oil to reach the bearings. There is a risk of insufficient lubrication.

The present invention has been made in view of such circumstances, and an object thereof is to provide a transmission device that can solve the above problem with a simple structure.

In order to achieve the above object, the present invention provides a first transmission member having a first axis as a central axis, a main shaft portion rotatable around the first axis, and a second axis eccentric from the first axis. An eccentric rotating member integrally connected to the eccentric shaft portion, a second transmission member disposed opposite to the first transmission member and rotatably supported by the eccentric shaft portion via a bearing, A third transmission member disposed opposite to the transmission member and capable of rotating about a first axis; a first transmission mechanism capable of transmitting torque while shifting between the first and second transmission members; and the second and second transmission members. 3. A transmission device including a second transmission mechanism capable of transmitting torque while shifting between the transmission members in the transmission case, wherein the second transmission member has a hollow portion communicating with the internal space of the transmission case. And the bearing is disposed to face the hollow portion. The first feature and.

Further, in addition to the first feature, the present invention has a second feature that the hollow portion is communicated with an inner peripheral side of the second transmission mechanism.

According to the present invention, in addition to the first or second feature, the second transmission member is supported by the eccentric shaft portion via the bearing and is opposed to the first transmission member. And a second half facing the first half with a gap, and a connecting member integrally connecting the first and second halves, the first and second halves. The hollow portion is defined between the connecting member and the connecting member, and the connecting member is provided with a first oil circulation hole for communicating between the internal space of the transmission case and the hollow portion, and the first half A third feature is that the first transmission mechanism is provided between the body and the first transmission member, and the second transmission mechanism is provided between the second half and the third transmission member. To do.

According to the fourth aspect of the present invention, in addition to the third feature, the second half is provided with a second oil circulation hole that communicates the hollow portion with the inner peripheral side of the second transmission mechanism. It is characterized by.

According to the present invention, in addition to the third or fourth feature, the first half and the second half are respectively fitted in one end and the other end of the connecting member which is cylindrical. The fifth feature is that it is fixed.

According to the first feature of the present invention, the second transmission member has a hollow portion communicating with the internal space of the transmission case, and is interposed between the second transmission member and the eccentric shaft portion of the eccentric rotation member. Since the bearing is arranged so as to face the hollow portion, during operation of the transmission device, the lubricating oil flowing between the inside of the transmission case and the hollow portion of the second transmission member is used to It is possible to effectively lubricate the bearing that has been exposed. In addition, since the lubricating oil that flows from the hollow portion and passes through the bearing can be supplied to the inner peripheral side of the first transmission mechanism between the first and second transmission members, the first transmission mechanism is efficiently lubricated. It becomes possible.

In particular, according to the second feature, since the hollow portion of the second transmission member is communicated with the inner peripheral side of the second transmission mechanism, the lubricating oil that has flowed into the hollow portion of the second transmission member is absorbed by the second transmission mechanism. Also supplied to the inner peripheral side, the second speed change mechanism can be efficiently lubricated.

In particular, according to the third feature, the second transmission member is supported by the eccentric shaft portion via a bearing and is opposed to the first transmission member, and the first half is spaced from the first half. A second half that faces each other and a connecting member that integrally connects the first and second halves; a hollow portion is defined between the two halves and the connecting member; The member is provided with a first oil circulation hole that allows communication between the internal space of the transmission case and the hollow portion, and the first transmission mechanism is provided between the first half and the first transmission member, and the second half is provided. Since the second transmission mechanism is provided between the body and the third transmission member, the second transmission member is divided so that the processing of the first and second transmission mechanisms for the second transmission member is performed for each half body. Can be performed individually, and the processing is facilitated to improve productivity. In addition, since the lubricating oil in the transmission case can flow into the hollow portion through the first oil circulation hole, and the first oil circulation hole can be processed into the connecting member between both halves, the workability is good. In addition, the weight of the connecting member can be reduced.

In particular, according to the fourth feature, the second half body is provided with a second oil circulation hole for communicating the hollow portion with the inner peripheral side of the second speed change mechanism. The inflowing lubricating oil is also supplied to the inner peripheral side of the second transmission mechanism, so that the second transmission mechanism can also be efficiently lubricated, and the second half body is lightened by the special provision of the second oil circulation hole. .

In particular, according to the fifth feature, since the first half and the second half are respectively fitted and fixed to one end and the other end of the cylindrical connecting member, both ends of the cylindrical connecting member are fixed. The first and second halves can be accurately and easily positioned and fixed coaxially to the portion, which can contribute to improvement in assembling workability and assembling accuracy.

FIG. 1 is a longitudinal front view of a differential gear as a transmission device according to an embodiment of the present invention. (First embodiment) FIG. 2 is an exploded perspective view of a main part (differential mechanism) of the differential device. (First embodiment) FIG. 3 is a cross-sectional view taken along arrow 3-3 in FIG. (First embodiment) 4 is a cross-sectional view taken along arrow 4-4 of FIG. (First embodiment) FIG. 5 is a cross-sectional view taken along line 5-5 in FIG. (First embodiment) FIG. 6 is an enlarged longitudinal sectional view showing the main part (differential mechanism) of the differential device together with the flow of the lubricating oil. (First embodiment)

C ... Differential case as transmission case D ... Differential device HB1, HB2 as transmission device ... First and second hub ICs ... Inside of differential case as transmission case Space SP... Hollow portions T1, T2,..., First and second transmission mechanisms X1, X2 .. first and

second axes

5, 8, 9,. ... Eccentric rotating member 6j... Main shaft portion 6e...

Eccentric shaft portions

8a and 8b... First and second

oil flow holes

21, 22... First and second transmission grooves 23... First rolling

balls

24, 25 as first rolling elements. 26... 2nd rolling ball as second rolling element

Embodiments of the present invention will be described below with reference to the accompanying drawings.

First embodiment

First, an embodiment of the present invention shown in FIGS. 1 to 6 will be described. In FIG. 1, a differential device D as a transmission device is housed in a transmission case 1 of an automobile together with a transmission.

In the differential device D, the left and right drive axles S1, S2 (in which the rotation of the ring gear Cg that rotates in conjunction with the output side of the transmission is aligned on the central axis of the differential device D, that is, the first axis X1, are relatively rotatable. That is, the first and second drive shafts) are distributed while allowing differential rotation between the drive axles S1 and S2. The drive axles S1, S2 and the transmission case 1 are sealed with seal members 4, 4 '.

The bottom of the mission case 1 is configured as an oil pan (not shown) that can store a predetermined amount of lubricating oil. The stored lubricating oil in the oil pan is vigorously stirred by rotating a rotating portion in the mission case 1, for example, a differential case C described later, and scattered widely in the internal space of the case 1, and the scattered lubricating oil makes the case Each part in 1, that is, a lubricated part can be lubricated. In addition to (or instead of) the above-described lubrication structure, the lubricating oil pumped by pump means such as an oil pump may be forcibly fed to each part in the mission case 1.

The differential device D includes a differential case C as a transmission case that is supported by the transmission case 1 so as to be rotatable about the first axis X1, and a differential mechanism 3 to be described later housed in the differential case C. The differential case C includes a ring gear Cg made of a helical gear having oblique teeth Cga provided on the outer periphery of a short cylindrical gear body, and a pair of left and right first and first pairs whose outer peripheral ends are joined to both axial ends of the ring gear Cg. Two side wall plate portions Ca and Cb are provided. At least one of the side wall plate portions Ca and Cb is provided with a drain hole (not shown) capable of appropriately discharging excess lubricating oil in the differential case C by centrifugal force or the like in the vicinity of the outer peripheral end thereof.

The first and second side wall plate portions Ca and Cb integrally have cylindrical first and second hubs HB1 and HB2 arranged on the first axis X1 at their inner peripheral end portions, respectively. The outer peripheral portions of the hubs HB1 and HB2 are rotatably supported by the mission case 1 via bearings 2 and 2 '. The first and second drive axles S1 and S2 are fitted and supported on the inner peripheral portions of the first and second hubs HB1 and HB2 so as to be rotatable about the first axis X1, respectively. At least one of the fitting surfaces (in the illustrated example, the inner peripheral surfaces of the hubs HB1 and HB2) includes at least the hubs HB1 and HB2 and the drive axles S1 when the vehicle is moving forward (ie, when the drive axles S1 and S2 are rotating forward). The first and

second spiral grooves

18 and 19 for drawing the scattered lubricating oil in the mission case 1 into the differential case C are formed along with the relative rotation with S2. The outer ends of the

spiral grooves

18 and 19 are opened in the mission case 1 and the inner ends thereof are opened in the differential case C, respectively. On the outer end surfaces of the hubs HB1 and HB2, guide portions HB1a and HB2a that can efficiently guide and guide the inflow of lubricating oil from the inside of the transmission case 1 to the outer end openings (that is, the inlets) of the

spiral grooves

18 and 19 protrude. Established.

In the present embodiment, the

spiral grooves

18 and 19 are exemplified as the lubricating oil supply means for supplying the lubricating oil in the mission case 1 into the differential case C. In addition to the

spiral grooves

18 and 19, (Or instead), as another lubricating oil supply means, for example, an oil passage (not shown) provided with lubricating oil pumped by pump means such as an oil pump in the drive axles S1, S2 and / or the differential case C It may be supplied into the differential case C via Alternatively, as still another lubricating oil supply means, a through hole that directly communicates the inside and the outside may be formed in at least one of the side wall plates Ca and Cb of the differential case C. The

spiral grooves

18 and 19 may be formed on the outer peripheral surfaces of the drive axles S1 and S2.

Next, the structure of the differential mechanism 3 in the differential case C will be described. The differential mechanism 3 is provided integrally with the first side wall plate portion Ca and can be rotated around the first axis X1 and is spline-fitted 16 to the first drive axle S1 to be coupled to the first axis. A main shaft portion 6j including a cylindrical first spline boss SB1 rotatable around X1 and an eccentric shaft portion 6e having a second axis line X2 eccentric from the first axis line X1 by a predetermined amount of eccentricity e as a central axis line are integrally coupled. The eccentric eccentric member 6 and the annular second transmission member, one side of which is opposed to the first transmission member 5 and rotatably supported by the eccentric shaft portion 6e via a bearing 7 made of a ball bearing. 8, an annular third transmission member 9 that is disposed opposite to the other side of the second transmission member 8 and is spline-fitted 17 to the second drive axle S2 and rotatable about the first axis X1, Torque can be transmitted while shifting between the first and

second transmission members

5 and 8 It comprises a first transmission mechanism T1, and a second transmission mechanism that transmit the torque T2 while shifting between the second and

third transmission members

8,9.

Thus, the second transmission member 8 is rotatably supported around the second axis X2 by the second transmission member 8 being rotatably supported on the eccentric shaft portion 6e of the eccentric rotation member 6 that rotates about the first axis X1. Can revolve around the first axis X1 relative to the main axis 6j while rotating around the second axis X2 relative to the eccentric axis 6e of the eccentric rotating member 6 around the first axis X1. .

The second transmission member 8 has an annular first half 8a that is rotatably supported by the eccentric shaft portion 6e of the eccentric rotating member 6 via a bearing 7, and an interval between the first half 8a. An opposed annular second half 8b and a basically cylindrical connecting member 8c for integrally connecting the two

halves

8a, 8b are provided. The first transmission mechanism T1 is provided between the first half 8a and the first transmission member 5, and the second transmission mechanism T2 is provided between the second half 8b and the third transmission member 9. It is done. A hollow portion SP of the second transmission member 8 is defined between the first and

second half bodies

8a and 8b and the connecting member 8c.

The connecting member 8c is provided with a plurality of first oil circulation holes 11 that communicate between the internal space IC of the differential case C and the hollow portion SP of the second transmission member 8 at equal intervals in the circumferential direction. Lubricating oil scattered in the internal space IC can be introduced into the hollow portion SP through the first oil circulation hole 11. Further, the second half body 8b is formed with a second oil circulation hole 12 that communicates the hollow portion SP with the inner peripheral side of the second transmission mechanism T2 in a circular shape with the second axis X2 as the center.

The third transmission member 9 includes a main shaft portion 6j including a cylindrical second spline boss SB2 that is spline-fitted 17 to the second drive axle S2 and is rotatable about the first axis X1, and the main shaft portion 6j. A disc portion 9c provided coaxially with the inner end portion 6ja is coupled and integrated.

In addition, annular step portions 8c1 and 8c2 for fitting the first half body 8a and the second half body 8b respectively into the spigot are formed on the inner peripheral surfaces of the one end and the other end of the connecting member 8c. The fitting portion is fixed by appropriate fixing means such as welding or caulking. According to the above-described inlay fitting, the first and

second halves

8a and 8b can be accurately and easily positioned and fixed coaxially at both ends of the connecting member 8c. This is advantageous in improving the assembly workability and assembly accuracy of the transmission member 8.

A first thrust washer TH1 that allows relative rotation between the inner surface of the first side wall plate portion Ca of the differential case C and the opposed surface of the eccentric rotating member 6 is interposed. Further, a second thrust washer TH2 that allows relative rotation between the inner side surface of the second side wall plate portion Cb of the differential case C and the third transmission member 9 is interposed.

Further, the differential mechanism 3 is opposite in phase to the eccentric shaft portion 6e of the eccentric rotating member 6 and the total center of gravity G of the second transmission member 8 across the first axis X1, and larger than the rotational radius of the total center of gravity G. And a balance weight W attached to the main shaft portion 6j of the eccentric rotating member 6. This balance weight W is comprised from the cyclic | annular attachment base Wm and the weight part Ww fixedly provided in the circumferential direction specific area | region of the attachment base Wm.

The hollow portion SP of the second transmission member 8 (the connecting member 8c) is used as an accommodation space for accommodating the balance weight W. That is, the main shaft portion 6j of the eccentric rotating member 6, especially the first spline boss SB1, has an inner end portion 6ja extending to the hollow portion SP, and an outer periphery of the extending end portion (the inner end portion 6ja). A balance weight W is attached to the. For fixing the balance weight W to the main shaft portion 6j, a retaining ring 10 such as a circlip as a retaining member for preventing the attachment base portion Wm from being detached from the main shaft portion 6j is detachably attached to the inner end portion 6ja. Is done. For the mounting, a locking groove in which the retaining ring 10 can be resiliently locked is formed in the outer periphery of the inner end 6ja.

As shown in FIGS. 1 to 3, the inner surface of the first transmission member 5 facing the one side portion (first half 8a) of the second transmission member 8 has a waveform centered on the first axis X1. An annular first transmission groove 21 is formed, and the first transmission groove 21 extends in the circumferential direction along a hypotrochoid curve having a virtual circle centered on the first axis X1 in the illustrated example. On the other hand, a corrugated annular second transmission groove 22 centering on the second axis X2 is formed on one side portion (first half 8a) of the second transmission member 8 facing the first transmission member 5. . In the illustrated example, the second transmission groove 22 extends in the circumferential direction along an epitrochoid curve having a virtual circle centered on the second axis X2 as a base circle, and is smaller than the wave number of the first transmission groove 21. It has a wave number and intersects the first transmission groove 21 at a plurality of locations. A plurality of first rolling balls 23 as first rolling elements are interposed at intersections (that is, overlapping portions) of the first transmission groove 21 and the second transmission groove 22, and each first rolling groove is provided. The ball 23 can roll on the inner surfaces of the first and

second transmission grooves

21 and 22.

Between the opposing surfaces of the first transmission member 5 and the second transmission member 8 (first half 8a), an annular flat first holding member H1 is interposed. The first holding member H1 can maintain the engagement state of the plurality of first rolling balls 23 with both the

transmission grooves

21 and 22 at the intersections of the first and

second transmission grooves

21 and 22. In addition, a plurality of circular first holding holes 31 that hold the plurality of first rolling balls 23 in a freely rotating manner while keeping their mutual spacing constant are provided at equal intervals in the circumferential direction.

As shown in FIGS. 1, 2, and 4, a corrugated annular third transmission groove 24 centering on the second axis X <b> 2 is formed on the other side portion (second half body 8 b) of the second transmission member 8. In the illustrated example, the third transmission groove 24 extends in the circumferential direction along a hypotrochoidal curve having a virtual circle centered on the second axis X2 as a base circle. On the other hand, on the surface of the third transmission member 9 facing the second transmission member 8, that is, on the inner side surface of the disc portion 9c, a corrugated annular fourth transmission groove 25 centering on the first axis X1 is formed. In the illustrated example, the fourth transmission groove 25 extends in the circumferential direction along an epitrochoidal curve having a virtual circle centered on the first axis X1 as a base circle, and is smaller than the wave number of the third transmission groove 24. It has a wave number and intersects with the third transmission groove 24 at a plurality of locations. A plurality of second rolling balls 26 as second rolling elements are interposed at intersections (overlapping portions) of the third transmission groove 24 and the fourth transmission groove 25, and each second rolling ball is disposed. 26 can roll on the inner surfaces of the third and

fourth transmission grooves

24 and 25. In the present embodiment, the trochoidal coefficients of the first and

second transmission grooves

21 and 22 and the trochoidal coefficients of the third and

fourth transmission grooves

24 and 25 are set to different values.

Between the opposing surfaces of the third transmission member 9 and the second transmission member 8 (second half 8b), an annular flat second holding member H2 is interposed. The second holding member H2 can maintain the engaged state of the plurality of second rolling balls 26 in both the

transmission grooves

24 and 25 at the intersections of the third and

fourth transmission grooves

24 and 25. In addition, a plurality of circular second holding holes 32 for holding the plurality of second rolling balls 26 rotatably while restricting the mutual interval between them are provided at equal intervals in the circumferential direction.

In the present embodiment described above, the wave number of the first transmission groove 21 is Z1, the wave number of the second transmission groove 22 is Z2, the wave number of the third transmission groove 24 is Z3, and the wave number of the fourth transmission groove 25 is Z4. The first to

fourth transmission grooves

21, 22, 24, 25 are formed so that the following formula is established.
(Z1 / Z2) × (Z3 / Z4) = 2
Desirably, Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or Z1 = 6, Z2 = 4, Z3 = 8, and Z4 = 6 as shown in the illustrated example.

In the illustrated example, the eight-wave first transmission groove 21 and the six-wave second transmission groove 22 intersect at seven locations, and seven first rolling balls are formed at the seven intersections (overlapping portions). 23, and the 6-wave third transmission groove 24 and the 4-wave fourth transmission groove 25 intersect at five locations, and five second rolling motions at the five intersections (overlapping portions). A ball 26 is interposed.

Thus, the first transmission groove 21, the second transmission groove 22, and the first rolling ball 23 cooperate with each other and can transmit torque while shifting between the first transmission member 5 and the second transmission member 8. The first transmission mechanism T1 is configured, and the third transmission groove 24, the fourth transmission groove 25, and the second rolling ball 26 cooperate with each other while shifting between the second transmission member 8 and the third transmission member 9. A second transmission mechanism T2 capable of transmitting torque is configured.

Next, the operation of the embodiment will be described.

Now, for example, in a state where the eccentric rotary member 6 (and hence the eccentric shaft portion 6e) is fixed by fixing the right first drive axle S1, the ring gear Cg is driven by the power from the engine, and the differential case C and therefore the first When the transmission member 5 is rotated about the first axis X 1, the eight-wave first transmission groove 21 of the first transmission member 5 passes through the six-wave second transmission groove 22 of the second transmission member 8 to the first rolling ball 23. Therefore, the first transmission member 5 drives the second transmission member 8 with a speed increasing ratio of 8/6. According to the rotation of the second transmission member 8, the six-wave third transmission groove 24 of the second transmission member 8 replaces the four-wave fourth transmission groove 25 of the disk portion 9 c of the third transmission member 9. Since it is driven via the two rolling balls 26, the second transmission member 8 drives the third transmission member 9 with a speed increasing ratio of 6/4.

After all, the first transmission member 5 is
(Z1 / Z2) × (Z3 / Z4) = (8/6) × (6/4) = 2
The third transmission member 9 is driven with the speed increasing ratio.

On the other hand, when the differential case (and hence the first transmission member 5) is rotated in the state where the third transmission member 9 is fixed by fixing the left second driving axle S2, the rotational driving force of the first transmission member 5 Due to the driving reaction force of the second transmission member 8 against the stationary third transmission member 9, the second transmission member 8 rotates while rotating about the eccentric shaft portion 6 e (second axis X 2) of the eccentric rotation member 6. Revolving around one axis line X1 drives the eccentric shaft portion 6e around the first axis line X1. As a result, the first transmission member 5 drives the eccentric rotating member 6 with a double speed increasing ratio.

Thus, when the loads of the eccentric rotating member 6 and the third transmission member 9 are balanced with each other or change with each other, the amount of rotation and the amount of revolution of the second transmission member 8 change steplessly, and the eccentric rotation The average value of the rotational speeds of the member 6 and the third transmission member 9 is equal to the rotational speed of the first transmission member 5. Thus, the rotation of the first transmission member 5 is distributed to the eccentric rotation member 6 and the third transmission member 9, so that the rotational force transmitted from the ring gear Cg to the differential case C can be distributed to the left and right drive axles S1, S2. it can.

At that time, Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or Z1 = 6, Z2 = 4, Z3 = 8, Z4 = 6 to ensure the differential function. Simplification of the eaves structure can be achieved.

By the way, in this differential device D, the rotational torque of the first transmission member 5 is applied to the second transmission member 8 via the first transmission groove 21, the plurality of first rolling balls 23 and the second transmission groove 22, and The rotational torque of the second transmission member 8 is transmitted to the third transmission member 9 via the third transmission groove 24, the plurality of second rolling balls 26 and the fourth transmission groove 25, respectively. Torque transmission between the second transmission member 8 and the second transmission member 8 and the third transmission member 9 is performed at a plurality of locations where the first and second rolling

balls

23 and 26 exist. Thus, the strength and weight of each transmission element such as the first to

third transmission members

5, 8, 9 and the first and second rolling

balls

23, 26 can be increased.

In the above-described torque transmission process of the differential device D, the stored lubricating oil at the bottom of the transmission case 1 is stirred by the differential case C or the like and scattered in the transmission case 1 over a wide range as described above. As shown in FIG. 6, a part of the scattered lubricating oil is brought into the differential case C by the pulling action of the

spiral grooves

18 and 19 accompanying the relative rotation between the hubs HB1 and HB2 of the differential case C and the drive axles S1 and S2. Then, the air is actively supplied, and is further introduced into the internal space of the differential mechanism 3, that is, the hollow portion SP of the second transmission member 8 through the spline

fitting portions

16 and 17. The introduced lubricating oil flows radially outward by centrifugal force in the hollow portion SP and flows toward the inner peripheral side of the second transmission mechanism T2 and the bearing 7 on the eccentric shaft portion 6e, and lubricates them. To do. Then, the oil that has passed through the second speed change mechanism T2 flows into the internal space IC of the differential case C (around the outer periphery of the second mechanism T2). The oil that has passed through the bearing 7 reaches the inner peripheral side of the first transmission mechanism T1, lubricates the mechanism T1, and flows into the internal space IC of the differential case C from the outer peripheral side.

Further, since the plurality of first oil circulation holes 11 provided in the second transmission member 8 (the connecting member 8 c) are widely opened in the internal space IC of the differential case C, the internal space of the differential case C through the first oil circulation hole 11. The lubricating oil can smoothly flow, that is, enter and exit between the IC and the hollow portion SP of the second transmission member 8. The second oil circulation hole 12 provided in the second transmission member 8 (second half 8b) communicates the hollow portion SP of the second transmission member 8 with the inner peripheral side of the second transmission mechanism T2. The second transmission mechanism T2 can be more effectively lubricated with the lubricating oil that goes from the hollow portion SP to the inner peripheral side of the second transmission mechanism T2 through the second oil circulation hole 12.

In addition, in the present embodiment, the second transmission member 8 is divided into the connecting member 8c and the first and

second halves

8a and 8b sandwiching the connecting member 8c. The processing of the two speed change mechanisms T1 and T2 can be performed individually for each of the

half bodies

8a and 8b, so that the processing is easy and the productivity is improved. Further, the lubricating oil enters and exits between the hollow portion SP of the second transmission member 8 and the internal space IC of the differential case C through the first oil circulation hole 11 provided in the connecting member 8c. Since the oil circulation hole 11 is formed in the connecting member 8c between the two

halves

8a and 8b, the workability is good and the weight of the connecting member 8c is reduced. Furthermore, the second half body 8b is provided with a second oil circulation hole 12 that allows the hollow portion SP to communicate with the inner peripheral side of the second transmission mechanism T2, so that the lubricating oil that has flowed into the hollow portion SP can be contained in the second transmission mechanism T2. The second transmission mechanism T2 can be sufficiently lubricated more efficiently, and the second oil circulation hole 12 contributes to the weight reduction of the second half 8b.

The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

For example, in the above-described embodiment, the differential device D is exemplified as the transmission device, and the power input from the power source to the differential case C is decentered via the second transmission member 8 and the first and second transmission mechanisms T1 and T2. Although the rotation member 6 and the third transmission member 9 are distributed while allowing differential rotation, the present invention can be applied to various transmission devices other than the differential device.

Further, a casing corresponding to the differential case C of the above embodiment is a fixed mission case, and either one of the eccentric rotating member 6 or the third transmission member 9 is an input shaft, and one of the other is an output shaft. The differential device D of the embodiment can be diverted as a transmission (decelerator or speed increaser) that can change (decelerate or increase speed) the rotational torque input to the input shaft and transmit it to the output shaft. In such a case, such a transmission (reduction gear or speed increaser) is the transmission device of the present invention.

Moreover, in the said embodiment, although the differential device D as a transmission device is accommodated in the mission case 1 of a motor vehicle, the differential device D is not limited to the differential device for motor vehicles, Various It can be implemented as a differential for a mechanical device.

In the above embodiment, the differential device D as a transmission device is applied to the left / right wheel transmission system to distribute power while allowing differential rotation to the left and right drive axles S1, S2. Although shown in the present invention, the differential device as a transmission device is applied to the front / rear wheel transmission system in the front / rear wheel drive vehicle to allow power to be driven while allowing differential rotation with respect to the front and rear drive wheels. You may make it distribute.

Moreover, although the 2nd transmission member 8 of the said embodiment was comprised from the 1st,

2nd half bodies

8a and 8b, and the connection member 8c, the 2nd transmission member 8 is the 1st on one surface of one member. The second transmission groove 22 may be provided, and the third transmission groove 24 may be provided on the other surface.

In the above-described embodiment, the first and second transmission mechanisms T1, T2 both use rolling ball type transmission mechanisms, but are not limited to the structure of the above-described embodiment. That is, various speed change mechanisms including at least an eccentric rotating member and a second transmission member capable of rotating around the second axis and revolving around the first axis in conjunction with the rotation thereof, such as an inscribed planetary gear mechanism Alternatively, a cycloid speed reducer (speed increaser) or a trochoid speed reducer (speed increaser) having various structures may be applied to one or both of the first and second speed change mechanisms T1 and T2.

Moreover, in the said embodiment, although each

transmission groove

21,22; 24,25 of 1st, 2nd transmission mechanism T1, T2 is made into the corrugated cyclic | annular wave groove along a trochoid curve, these transmission grooves are embodiment. For example, it may be a wave-shaped wave groove along a cycloid curve.

Moreover, in the said embodiment, 1st and 2nd as a rolling element between the 1st and

2nd transmission grooves

21 and 22 of the 1st, 2nd transmission mechanisms T1 and T2, and the 3rd and

4th transmission grooves

24 and 25 are used. Although two rolling

balls

23 and 26 are interposed, the rolling elements may be in the form of rollers or pins. In this case, the first and

second transmission grooves

21 and 22, and the third and second The four

transmission grooves

24 and 25 are formed in an inner surface shape such that a roller-shaped or pin-shaped rolling element can roll.

In the above-described embodiment, the eccentric rotating member 6 and the third transmission member 9 are connected to the drive axles S1 and S2 supported by the differential case C (spline fittings 16 and 17), and the drive axles S1 and S2 are interposed therebetween. In the present invention, the eccentric rotation member 6 and the third transmission member 9 may be directly supported by the differential case C.

In the above-described embodiment, the first and second holding members H1 and H2 are configured by circular rings having inner and outer peripheral surfaces each having a perfect circle. The shape is not limited to the above-described embodiment, and may be any annular body that can hold at least a plurality of first and second rolling

balls

23 and 26 at regular intervals, for example, an elliptical annular body or a waveform. A curved annular body may be used.

If the first and second rolling

balls

23 and 26 can smoothly roll without the first and second holding members H1 and H2, the first and second holding members H1 and H2 are omitted. Also good.

Claims

A first transmission member (5) having a first axis (X1) as a central axis;
A main shaft portion (6j) rotatable around the first axis (X1) and an eccentric shaft portion (6e) having a second axis (X2) eccentric from the first axis (X1) as a central axis are integrally connected. An eccentric rotating member (6),
A second transmission member (8) disposed opposite to the first transmission member (5) and rotatably supported by the eccentric shaft portion (6e) via a bearing (7);
A third transmission member (9) disposed opposite to the second transmission member (8) and rotatable about the first axis (X1);
A first transmission mechanism (T1) capable of transmitting torque while shifting between the first and second transmission members (5, 8);
A transmission device including a second transmission mechanism (T2) capable of transmitting torque while shifting between the second and third transmission members (8, 9) in a transmission case (C),
The second transmission member (8) has a hollow portion (SP) communicating with the internal space (IC) of the transmission case (C),
The said bearing (7) is arrange | positioned so that the said hollow part (SP) may be faced, The transmission device characterized by the above-mentioned.
The transmission device according to claim 1, wherein the hollow portion (SP) communicates with an inner peripheral side of the second transmission mechanism (T2).
The second transmission member (8) is supported by the eccentric shaft portion (6e) via the bearing (7) and is opposed to the first transmission member (5), and the first half (8a), A second half (8b) opposed to the first half (8a) with an interval, and a connecting member (8c) for integrally connecting the first and second halves (8a, 8b). The hollow portion (SP) is defined between the first and second halves (8a, 8b) and the connecting member (8c),
The connecting member (8c) is provided with a first oil circulation hole (11) for communicating between the internal space (IC) of the transmission case (C) and the hollow portion (SP),
The first transmission mechanism (T1) is disposed between the first half (8a) and the first transmission member (5), and the second half (8b) and the third transmission member (9). The transmission device according to claim 1, wherein the second speed change mechanism (T2) is provided between each of the transmission devices.
The second half (8b) is provided with a second oil circulation hole (12) that allows the hollow portion (SP) to communicate with the inner peripheral side of the second transmission mechanism (T2). The transmission device according to claim 3.
The first half (8a) and the second half (8b) are respectively fitted in and fixed to one end and the other end of the cylindrical connecting member (8c). The transmission device according to claim 3 or 4.