JP2017053378A - Transmission device and differential device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a compact-sized and light-weight transmission device comprising an eccentric rotating member in which a main shaft part rotatably supported around a first axis line and an eccentric shaft part positioned on a second axis line eccentric from the first axis line are integrally connected to each other at a casing having integrally a first transmission member; a second transmission member arranged to be adjacent to the first transmission member and rotatably supported at the eccentric shaft part; a third transmission member arranged to be adjacent to the second transmission member and rotatably supported around the first axis line at the casing; a first speed change mechanism between the first and second transmission members; and a second speed change mechanism between the second and third transmission members even if there is provided a balance weight for reducing a rotational unbalanced state in respect to an eccentric rotating system including the eccentric shaft part and the eccentric rotating member.SOLUTION: A transmission device D includes a balance weight W arranged outside in a radial direction of a second transmission member 8 and a synchronous rotation mechanism I for performing a synchronous rotation with an eccentric rotating member 6 while holding it at a position of inverse phase to that of an eccentric shaft part 6e.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a transmission device, in particular, a casing integrally including a first transmission member having a first axis as a central axis, a main shaft portion rotatably supported around the first axis, and an eccentricity from the first axis. An eccentric rotating member formed by integrally connecting the eccentric shaft portions positioned on the second axis, a second transmission member disposed adjacent to the first transmission member and rotatably supported by the eccentric shaft portion, and A third transmission member disposed adjacent to the second transmission member and rotatably supported on the casing around the first axis; a first transmission mechanism capable of transmitting torque while shifting between the first and second transmission members; The present invention relates to a transmission device including a second transmission mechanism capable of transmitting torque while shifting between second and third transmission members, and a differential device using the transmission device.

  The transmission device is conventionally known as disclosed in, for example, Patent Document 1. In this device, the position of the center of gravity of the eccentric rotation system including the eccentric shaft portion of the eccentric rotation member and the second transmission member is changed from the first axis. It is unevenly distributed at positions separated in the direction of the two axes. Therefore, when the second transmission member revolves around the first axis with respect to the main shaft portion while rotating around the second axis with respect to the eccentric shaft portion of the eccentric rotation member as the eccentric rotation member rotates about the first axis. Since the centrifugal force of the eccentric rotation system acts largely in a specific direction with respect to the first axis (that is, the offset side of the second axis), the rotation of the eccentric rotation system becomes an unbalanced state, which is the vibration of the device. It becomes a generation factor.

  Therefore, in the transmission device of Patent Document 1, a balance weight for reducing the unbalanced state of the rotation is provided in the eccentric rotation system.

Japanese Patent No. 4814351

  However, in the transmission device of Patent Document 1, the balance weight 12c is integrated with a rotating shaft (eccentric shaft 12) integrally including an eccentric rotating member (eccentric portion 12d) at a position shifted in the axial direction with respect to the eccentric rotating member 12d. Provided. For this reason, the rotation shaft 12 is elongated in the axial direction by the provision of the balance weight 12c. Since the balance weight 12c is located on the first axis, the balance weight 12c requires the weight 12c to extend radially outward from the first axis in order to enhance the balancer effect of the weight 12c. There is an increase in weight weight.

  Further, since the balance weight 12c and the eccentric rotating member 12d are disposed so as to be shifted in the axial direction, the centrifugal force in the reverse direction acting on the center of gravity of the both generates a couple of forces on the rotating shaft 12. Therefore, the couple becomes a cause of vibration.

  In the casing, a dead space is generated around the second transmission member (eccentric plate 4) to allow the eccentric rotation of the second transmission member (eccentric plate 4). There is no particular contrivance to effectively use it as an installation space for functional parts.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a transmission device and a differential device that have a simple structure and can solve the above problems at once.

  In order to achieve the above object, the present invention provides a casing integrally including a first transmission member having a first axis as a central axis, a main shaft portion rotatably supported by the casing around the first axis, and An eccentric rotating member formed by integrally connecting eccentric shaft portions positioned on a second axis that is eccentric from the first axis, and adjacent to the first transmission member, and rotatably supported by the eccentric shaft portion. A second transmission member, a third transmission member disposed adjacent to the second transmission member and supported by the casing so as to be rotatable around the first axis, and a speed change between the first and second transmission members. And a second transmission mechanism capable of transmitting torque while shifting between the second transmission member and the third transmission member, wherein the second transmission member is radially outward. Balance weight placed on , The balance weight, the first; and a synchronous rotating mechanism for the rotating eccentric rotating member and synchronously while maintaining the position of the opposite phase from that of the eccentric shaft portion with respect to said first axis.

  According to the present invention, in addition to the first feature, the synchronous rotation mechanism includes a first support portion rotatably supported around the second axis on the outer periphery of the second transmission member, and the casing or the first 3 a second support portion that is rotatably supported by the transmission member around the first axis, and a connecting portion that integrally connects the first and second support portions; A second feature is that the balance weight is held at the position of the opposite phase in the portion or the connecting portion.

  Further, according to the present invention, in addition to the first or second feature, the first speed change mechanism is a corrugated ring formed around a first axis on a surface of the first transmission member facing the second transmission member. A first transmission groove and a second transmission groove of the second transmission member, the second transmission groove having a wave number different from the first transmission groove and having a wave number formed around the second axis on the surface facing the first transmission member, A plurality of first rolling elements that are interposed in a plurality of overlapping portions of the first and second transmission grooves and that perform variable speed transmission between the first and second transmission members while rolling the first and second transmission grooves; The second transmission mechanism includes a wavy annular third transmission groove formed around the second axis on a surface of the second transmission member facing the third transmission member, and a third transmission member, A fourth transmission groove having a wave shape and a wave number different from the third transmission groove formed on the surface facing the two transmission members around the first axis; And a plurality of second rolling elements interposed between a plurality of overlapping portions of the fourth transmission groove and performing transmission transmission between the second and third transmission members while rolling on the third and fourth transmission grooves. This is the third feature.

Further, the present invention is a differential device using the transmission device having the third feature,
The casing is a differential case that integrally has a first transmission member and receives power. The differential case is connected to a first drive shaft connected to the main shaft portion and a third transmission member. When the second drive shaft is rotatably supported, the wave number of the first transmission groove is Z1, the wave number of the second transmission groove is Z2, the wave number of the third transmission groove is Z3, and the wave number of the fourth transmission groove is Z4. The fourth feature is that the following expression (Z1 / Z2) × (Z3 / Z4) = 2 holds.

  According to the first feature of the present invention, the balance weight disposed radially outward of the second transmission member, and the balance weight is positioned in a phase opposite to the eccentric shaft portion of the eccentric rotation member with respect to the first axis. The center of gravity of the eccentric rotating system including the eccentric shaft portion of the eccentric rotating member and the second transmission member is in the direction from the first axis to the second axis. If the second transmission member revolves around the first axis while rotating around the second axis along with the rotation of the eccentric rotation member around the first axis, the eccentric rotation system is centrifugally The force can be balanced as much as possible with the centrifugal force of the balancer rotation system including the balance weight and the rotation synchronization mechanism. Thereby, since the unbalanced state of rotation due to the former bias of the centrifugal force can be eliminated or reduced, it is possible to effectively prevent the occurrence of vibration of the device due to the unbalanced state of rotation.

  In particular, since the balance weight is disposed radially outward of the second transmission member, there is no possibility that the apparatus will be lengthened in the axial direction due to the installation of the balance weight, so that the apparatus can be reduced in the axial direction. It will be advantageous. In addition, since the rotation radius of the center of gravity of the balancer rotation system including this balance weight can be set sufficiently larger than the rotation radius of the center of gravity of the eccentric rotation system, it contributes to the weight reduction of the balance weight and hence the weight of the device. can do. Moreover, since the axial shift amount of both centroids can be set to zero or slightly, generation of couples due to centrifugal force acting on both centroids can be effectively suppressed. It is possible to effectively prevent the vibration of the apparatus. In addition, since the dead space generated around the second transmission member in order to allow the eccentric transmission of the second transmission member can be effectively utilized as the installation space for the balance weight, it can contribute to the downsizing of the device as much. .

  Further, according to the second feature of the present invention, the synchronous rotation mechanism includes a first support portion that is rotatably supported around the second axis on the outer periphery of the second transmission member, and the casing or the third transmission member. A second support portion rotatably supported about the axis, and a connecting portion that integrally connects the first and second support portions, and a balance weight is provided to the first support portion or the connecting portion. Since it is held at the position of the opposite phase, the balance weight is made eccentric with respect to the first axis by the simple synchronous rotation mechanism straddling the outer periphery of the second transmission member and the casing or the third transmission member. It can be reliably rotated synchronously with the eccentric rotating member while being held at a position opposite to the position of the unit, thereby contributing to simplification of the structure of the device and further cost reduction.

  Further, according to the third feature of the present invention, a plurality of first rolling elements interposed between a plurality of overlapping portions of corrugated annular first and second transmission grooves having different wave numbers between the first and second transmission members. (Ie, distributed in a plurality of locations in the circumferential direction) to transmit torque, and between the second and third transmission members, a plurality of wave-shaped annular third and fourth transmission grooves having different wave numbers Torque is transmitted via a plurality of second rolling elements interposed in the overlapping portion (that is, distributed in a plurality of locations in the circumferential direction), so that the load burden on each transmission element is reduced and the strength is increased and the weight is reduced. Therefore, a high-performance transmission device can be provided.

  According to the fourth aspect of the present invention, the transmission can be used as a differential device.

1 is a longitudinal front view of a differential gear according to a first embodiment of the present invention. The exploded perspective view of the principal part of the differential 3-3 arrow sectional view of FIG. 4-4 cross-sectional view of FIG. Sectional view along arrow 5-5 in FIG. Longitudinal front view of the differential according to the second embodiment of the present invention (corresponding to FIG. 1) 7-7 sectional view of FIG. A longitudinal front view of a differential gear according to a third embodiment of the present invention (corresponding to FIGS. 1 and 6).

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

  First, the description starts with the description of the first embodiment of the present invention shown in FIGS. In FIG. 1, a differential device D is housed in a transmission case 1 of an automobile together with a transmission, and this differential device D constitutes a transmission device of the present invention.

  This differential device D is a left-right drive in which the rotation of the driven gear 3 composed of an inclined gear that rotates in conjunction with the output side of the transmission is arranged on the central axis of the differential device D, that is, the first axis X1 so as to be relatively rotatable. Distributing the axles S1 and S2 while allowing differential rotation between the drive axles S1 and S2.

  As clearly shown in FIG. 1, the differential device D includes a differential case C that is rotatably supported by the transmission case 1 via the first and second bearings 11 and 12 on the first axis X1. The differential case C includes a first case half C1 and a second case half C2 welded or bolted to the first case half C1.

  The second case half C2 is formed in a bowl shape, and the central boss portion of the small diameter end portion thereof is rotatably supported by the transmission case 1 via the second bearing 12. On the other hand, the first case half C1 is formed flat so as to close the large-diameter end face of the second case half C2, and the outer peripheral end is welded or bolted to the open end of the second case half C2. The central boss portion of the first case half C1 is rotatably supported by the transmission case 1 via the first bearing 11. Thus, the differential case C constitutes the casing of the present invention, and the first case half C1 constitutes the first transmission member of the present invention.

  A first output shaft 6 disposed in the differential case C of the differential device D is rotatably supported by the first case half body C1 via a third bearing 13 on the first axis X1, and this first output The right driving axle S1 is splined to the shaft 6. The second case half C2 is rotatably supported by a second output shaft 7 of the differential device D disposed in the differential case C via a fourth bearing 14 on the first axis X1. The left drive axle S2 is splined to the output shaft 7. Thus, the right drive axle S1 constitutes the first drive shaft, and the left drive axle S2 constitutes the second drive shaft.

  The first output shaft 6 is rotatably supported via a third bearing 13 on the first axis X1, and a main shaft portion 6j to which the right drive axle S1 is splined, and a fixed distance e from the first axis X1. An eccentric shaft member 6e disposed on the second axis line X2 that is eccentric as much as possible is combined and integrated, and constitutes an eccentric rotating member of the present invention.

  The eccentric shaft portion 6e of the first output shaft 6 is disposed in the differential case C (particularly, the second case half C2) and is formed in an annular shape having the second axis X2 as the central axis. Is fitted and supported rotatably via the fifth bearing 15 on the second axis X2. As a result, the second transmission member 8 rotates around the second axis X2 with respect to the eccentric shaft portion 6e of the first output shaft 6 while rotating around the first axis X1 of the first output shaft 6 while rotating the main shaft The part 6j can revolve around the first axis X1.

  The second output shaft 7 is rotatably supported via a fourth bearing 14 on the first axis X1, and a main shaft portion 7j to which the left drive axle S2 is spline-coupled, and an inner end portion of the main shaft portion 7j And a disk portion 7c that is coaxially connected to each other, and constitutes a third transmission member of the present invention.

  The inner surface of the first case half C1 and the first output shaft 6 (eccentric shaft portion 6e), and the inner surface of the second case half C2 and the second output shaft 7 (disc portion 7c) A first thrust washer 29 and a second thrust washer 30 are interposed between the first thrust washer 29 and the second thrust washer 30, respectively.

  Incidentally, in the present embodiment, the second transmission member 8 is divided into a pair of transmission member halves 8a and 8b that are adjacent to each other in the axial direction and are integrally coupled, and the two transmission member halves 8a and 8b are divided. The two are integrally connected with each other by appropriate fixing means (for example, welding, bolting, etc.). And one side (namely, one transmission member half body 8a) of this 2nd transmission member 8 adjoins and opposes the inner surface of the 1st case half body C1 as a 1st transmission member, and the 2nd transmission member The other side of 8 (that is, the other transmission member half 8b) is adjacent to and faces the inner surface of the disk portion 7d of the second output shaft 7 as the third transmission member.

  As shown in FIGS. 1, 2, and 5, the inner surface of the first case half C <b> 1 as the first transmission member that faces one side surface of the second transmission member 8 (that is, one transmission member half body 8 a). Is formed with a wave-shaped annular first transmission groove 21 centered on the first axis X1, and in the illustrated example, the first transmission groove 21 is a hypo circle based on a virtual circle centered on the first axis X1. It extends in the circumferential direction along the trochoid curve. On the other hand, a corrugated annular second transmission groove 22 centering on the second axis X2 is formed on one side surface of the second transmission member 8 facing the first case half C1. 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 overlaps the first transmission groove 21 at a plurality of locations. A plurality of first transmission balls 23 as first rolling elements are interposed in the overlapping portion of the first transmission groove 21 and the second transmission groove 22, and each of the first transmission balls 23 includes the first and second transmission balls 23. 2 The inner surfaces of the transmission grooves 21 and 22 can roll freely. The plurality of first transmission balls 23 are held at substantially equal intervals on the same circumference by an annular first race plate 27.

  As shown in FIGS. 1 to 4, the other side surface of the second transmission member 8 (that is, the other transmission member half body 8 b) has a wavy annular third transmission groove 24 centered on the second axis X <b> 2. The third transmission groove 24 is formed and extends in the circumferential direction along a hypotrochoidal curve having a virtual circle centered on the second axis X2 as a base circle in the illustrated example. On the other hand, on the surface facing the second transmission member 8 of the second output shaft 7 as the third transmission member, that is, on the inner surface of the disc portion 7c, a wavy annular fourth transmission groove centered on the first axis X1. 25 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 overlaps with the third transmission groove 24 at a plurality of locations. A plurality of second transmission balls 26 as second rolling elements are interposed in the overlapping portion of the third transmission groove 24 and the fourth transmission groove 25, and each of the second transmission balls 26 includes the third and the third transmission balls 26. 4 The inner surfaces of the transmission grooves 24 and 25 can roll freely. The plurality of second transmission balls 26 are held at substantially equal intervals on the same circumference by the annular second race plate 28.

In the above, when 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 following equation is established. Thus, the first to fourth transmission grooves 21, 22, 24, 25 are formed.
(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 overlap at seven locations, and seven first transmission balls 23 are interposed in the seven overlapping portions, Further, the six-wave third transmission groove 24 and the four-wave fourth transmission groove 25 overlap at five locations, and five second transmission balls 26 are interposed at the five overlapping portions.

  Thus, the first transmission groove 21, the second transmission groove 22, and the first transmission ball 23 cooperate with each other to shift between the first case half C1 (first transmission member) and the second transmission member 8. The first transmission mechanism T1 capable of transmitting torque while constituting the third transmission groove 24, the fourth transmission groove 25, and the second transmission ball 26 cooperate with each other to form the second transmission member 8 and the second output shaft 7. A second transmission mechanism T2 capable of transmitting torque while shifting between the (third transmission members) is configured.

  By the way, in this embodiment, the position of the gravity center Ge of the eccentric rotation system including the eccentric shaft portion 6e of the first output shaft 6 as the eccentric rotation member and the second transmission member 8 is the direction from the first axis X1 to the second axis X2. Are unevenly distributed at positions separated from each other. Therefore, as the first output shaft 6 rotates about the first axis X1, the second transmission member 8 rotates about the second axis X2 relative to the eccentric shaft 6e and rotates about the first axis X1 relative to the main axis 6j. Since the centrifugal force of the eccentric rotation system is biased in a specific direction (that is, the second axis X2 side) with respect to the first axis X1, the rotation of the eccentric rotation system becomes unbalanced. This is a cause of vibration of the differential device D.

  Therefore, in the differential device D of the first embodiment, a balance weight W for eliminating or reducing the rotation unbalanced state of the eccentric rotation system is specially disposed on the radially outer side of the second transmission member 8. Further, a synchronous rotation mechanism I is provided that rotates the balance weight W in synchronization with the eccentric rotation member 6 while maintaining the balance weight W at a position opposite to the eccentric shaft portion 6e with respect to the first axis X1.

  In particular, the synchronous rotation mechanism I of the first embodiment includes a large-diameter cylindrical first support portion 31 that is supported on the outer periphery of the second transmission member 8 via the sixth bearing 16 so as to be rotatable about the second axis X2. The second output shaft 7 as the third transmission member is supported by the second output shaft 7 via the seventh bearing 17 so as to be rotatable about the first axis X, and the second support portion 32 having a small diameter cylindrical shape, and the first and second supports. It has the cyclic | annular connection cylinder part 33 as a connection part which connects between the parts 31 and 32 integrally. And the balance weight W is hold | maintained in the outer-phase part of the 1st support part 31 in the position of an antiphase with respect to the eccentric shaft part 6e regarding the 1st axis line X1.

  In the present embodiment, the balance weight W connects an arc-shaped outer peripheral edge Wo centered on the first axis X1 as viewed from the projection plane orthogonal to the first axis X1 and both ends of the outer peripheral edge Wo. It has a string-like inner peripheral edge Wi and is formed in an arcuate shape. The inner peripheral edge portion Wi is fixed to the outer periphery of the first support portion 31 via a connecting plate portion 34 extending in the circumferential direction. The connecting plate part 34 is coupled to the central part of the inner peripheral edge Wi of the balance weight W in the direction along the first axis X1. For this reason, the connecting plate portion 34 can support the balance weight W in a well-balanced manner without falling in the axial direction (left and right direction in FIG. 1), the load on the connecting plate portion 34 is reduced, and the support rigidity to the balance weight W is increased. Enhanced. Since the outer peripheral edge Wo has an arc shape along the inner peripheral surface of the differential case C (second case half C2), it does not interfere even if it is close to the inner peripheral surface.

  In the illustrated example, the sixth and seventh bearings 16 and 17 are connected to the first and second support portions 31 and 32 and their mating members (the second transmission member 8 and the second output shaft 7) on both the outer and inner circumferences. Although it is press-fitted and fixed, the fixing method is not limited to the illustrated example, and can be appropriately selected. For example, only the inner peripheral sides of the sixth and seventh bearings 16 and 17 are press-fitted into the second transmission member 8 and the second output shaft 7 respectively, and the outer peripheral sides of the sixth and seventh bearings 16 and 17 are first and second. The support portions 31 and 32 may be fitted (light press fit), respectively, and may be prevented from being detached from the first and second support portions 31 and 32 by separate stopper means.

  Next, the operation of the first embodiment will be described.

  Now, for example, by fixing the right drive axle S1, the driven gear 3 is driven by the power from the engine in the state where the first output shaft 6 (and hence the eccentric shaft portion 6e) is fixed, and the differential case C and accordingly the first When the case half C1 is rotated around the first axis X1, the first transmission groove 21 of the first case half C1 moves the second transmission groove 22 of the six waves of the second transmission member 8 to the first transmission ball. 23, the first case half C1 drives the second transmission member 8 serving as the eccentric rotation member with a speed increasing ratio of 8/6. Then, 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 7 c of the second output shaft 7. Since the second transmission ball 26 is driven via the second transmission ball 26, the second transmission member 8 drives the second output shaft 7 with a speed increasing ratio of 6/4.

After all, the first case half C1 is
(Z1 / Z2) × (Z3 / Z4) = (8/6) × (6/4) = 2
The second output shaft 7 is driven with the speed increasing ratio.

  Further, by fixing the left driving axle S2, when the first case half C1 is rotated in a state where the second output shaft 7 (and hence the disc portion 7c) is fixed, the rotation of the first case half C1 is performed. Due to the driving force and the driving reaction force of the second transmission member 8 against the stationary second output shaft 7, the second transmission member 8 rotates about the eccentric shaft portion 6 e of the first output shaft 6 while rotating around the first axis. Revolving around X1, the eccentric shaft portion 6e is driven around the first axis X1. As a result, the first case half C1 drives the first output shaft 6 with a double speed increasing ratio.

  Thus, when the loads of the first and second output shafts 6 and 7 are balanced or changed with each other, the amount of rotation and the amount of revolution of the second transmission member 8 change steplessly. , 7 is equal to the rotation speed of the first case half C1. Thus, the rotation of the first case half C1 is distributed to the first and second output shafts 7, so that the rotational force transmitted from the driven gear 3 to the differential case C can be distributed to the left and right drive axles S1, S2. .

  At that time, by setting Z1 = 8, Z2 = 6, Z3 = 6, Z4 = 4, or by setting Z1 = 6, Z2 = 4, Z3 = 8, Z4 = 6, the necessary minimum wave number is obtained. It is possible to simplify the eaves structure while ensuring the differential function.

  By the way, in this differential device D, the rotational torque of the first case half C1 is applied to the second transmission member 8 via the first transmission groove 21, the plurality of first transmission balls 23, and the second transmission groove 22, and Since the rotational torque of the second transmission member 8 is transmitted to the second output shaft 7 through the third transmission groove 24, the plurality of second transmission balls 26, and the fourth transmission groove 25, respectively, the first case half C1. Torque transmission between the second transmission member 8 and the second transmission member 8 and the second output shaft 7 is distributed to a plurality of locations where the first and second transmission balls 23 and 26 exist. The strength of the first case half C1 (first transmission member), the second transmission member 8, the second output shaft 7 (third transmission member), and the transmission members such as the first and second transmission balls 23 and 26; Weight reduction can be achieved.

  By the way, in the present embodiment, the position of the center of gravity Ge of the eccentric rotation system including the eccentric shaft portion 6e of the first output shaft 6 as the eccentric rotation member and the second transmission member 8 is changed from the first axis X1 to the second axis X2. It is unevenly distributed at positions separated in the direction. Therefore, as described above, when the second transmission member 8 revolves around the first axis X1 while rotating around the second axis X2, the centrifugal force of the eccentric rotation system is in a specific direction (second direction with respect to the first axis X1). Since the rotation of the eccentric rotation system is in an unbalanced state, the balance weight W for eliminating or reducing the unbalanced state of the rotation is the second transmission member. 8, a synchronous rotation mechanism I is provided that rotates in synchronization with the eccentric rotation member 6 while holding the weight W at a position opposite to the eccentric shaft portion 6e with respect to the first axis X1. . As a result, the centrifugal force of the eccentric rotation system and the centrifugal force of the balancer rotation system including the balance weight W and the rotation synchronization mechanism I can be balanced as much as possible. The unbalanced state can be eliminated or reduced, and the occurrence of vibration of the differential device D due to the rotation unbalanced state can be effectively suppressed.

  In this case, in particular, the balance weight W is disposed radially outward of the second transmission member 8, so that there is no possibility that the differential device D is lengthened in the axial direction for the installation of the balance weight. This is advantageous in reducing the axial size of D. Further, since the rotation radius of the center of gravity Gw of the balancer rotation system including the balance weight W and the rotation synchronization mechanism I can be set sufficiently larger than the rotation radius of the center of gravity Ge of the eccentric rotation system, the weight of the balance weight W can be reduced. As a result, weight reduction of the differential device D is achieved. Moreover, since the axial shift amount of both the center of gravity Gw and Ge can be set to zero or slightly, the generation of the couple due to the reverse centrifugal force acting on both the center of gravity Gw and Ge is effectively suppressed. In addition, the vibration of the differential device D due to the generation of the couple can be effectively prevented. In addition, since the dead space generated around the second transmission member 8 to allow the eccentric rotation of the second transmission member 8 in the differential case C can be effectively used as the installation space for the balance weight W, the differential device D is accordingly increased. Can be reduced in size.

  In particular, the synchronous rotation mechanism I of the first embodiment has a large-diameter cylindrical first support portion 31 that is supported on the outer periphery of the second transmission member 8 via the sixth bearing 16 so as to be rotatable about the second axis X2. A second support portion 32 having a small diameter cylindrical shape that is supported by the second output shaft 7 as the third transmission member via the seventh bearing 17 so as to be rotatable about the first axis X, and the first and second Since it has the cyclic | annular connection cylinder part 33 as a connection part which connects between the support parts 31 and 32 integrally, the outer periphery of the 2nd transmission member 8, and the 2nd output shaft 7 (disk part 7c). The first output shaft 6 is held by a simple synchronous rotation mechanism I straddling the outer periphery while maintaining the balance weight W at a position opposite in phase to the eccentric shaft portion 6e of the first output shaft 6 with respect to the first axis X1. (Eccentric rotating member) can be reliably rotated synchronously.

  Next, a second embodiment of the present invention shown in FIGS.

  The synchronous rotation mechanism I of the second embodiment includes a cylindrical first support portion 31 supported on the outer periphery of the second transmission member 8 via a sixth bearing 16 so as to be rotatable about the second axis X2, and a differential case. A cylindrical second support portion 32 rotatably supported around the first axis X via a seventh bearing 17 on the inner periphery of C (particularly the second case half C2), and the first and second supports; It has the cyclic | annular connection board part 33 as a connection part which connects between the parts 31 and 32 integrally.

  And the balance weight W is hold | maintained in the position of an antiphase with respect to the eccentric shaft part 6e regarding the 1st axis line X1 at the outer peripheral part of the connection board part 33. FIG. As in the first embodiment, the balance weight W is formed between an arcuate outer peripheral edge Wo centered on the first axis X1 as viewed from the projection plane orthogonal to the first axis X1 and both ends of the outer peripheral edge Wo. And has a string-like inner peripheral edge Wi. The inner peripheral edge Wi is fixed to the outer peripheral part of the connecting plate part 33, and the outer peripheral edge Wo is fixed to the inner peripheral part of the second support part 32.

  Since the other configuration is the same as that of the first embodiment, the portions corresponding to those of the first embodiment are denoted by the same reference numerals in FIGS.

  According to the second embodiment, the second support portion 32 of the synchronous rotation mechanism I is supported on the inner periphery of the differential case C (particularly, the second case half C2) as a casing so as to be rotatable about the first axis X1. Except for this point, the same operational effects as the above-described operational effects of the first embodiment are achieved.

  Next, a third embodiment of the present invention shown in FIG. 8 will be described.

  In the third embodiment, the outer peripheral ends of the first and second case halves C1 and C2 of the differential case C are spaced apart in the axial direction, and the outer peripheral ends of the two case halves C1 and C2 are spaced from each other. The driven gear 3 is integrally connected so that the driven gear 3 substantially constitutes a part of the differential case C. The synchronous rotation mechanism I includes a cylindrical first support portion 31 that is supported on the outer periphery of the second transmission member 8 via the sixth bearing 16 so as to be rotatable about the second axis X2, and the inner periphery of the driven gear 3. A cylindrical second support portion 32 that is rotatably supported around the first axis X via the seventh bearing 17 and a connecting portion that integrally connects the first and second support portions 31 and 32. And an annular connecting plate portion 33.

  On the outer peripheral portion of the connecting plate portion 33, a balance weight W is held at a position opposite in phase to the eccentric shaft portion 6e with respect to the first axis X1. Similar to the embodiment, the balance weight W is formed between an arcuate outer peripheral edge Wo centered on the first axis X1 as viewed from the projection plane orthogonal to the first axis X1 and between both ends of the outer peripheral edge Wo. The inner peripheral edge Wi is formed in an arc shape with a string-like inner peripheral edge Wi, and the outer peripheral edge Wo is the inner periphery of the second support part 32. It is fixed to each part.

  Since other configurations are the same as those of the first and second embodiments, portions corresponding to those of the first and second embodiments are denoted by the same reference numerals in FIG. .

  According to the third embodiment, the second support portion 32 of the synchronous rotation mechanism I is rotatable around the first axis X1 on the inner periphery of the driven gear 3 (substantially a differential case C as a casing) as a driven member. Except for the point which is supported, the effect similar to the effect mentioned above of 1st, 2nd embodiment is achieved.

  As mentioned above, although embodiment of this invention was described, this invention can perform a various design change in the range which does not deviate from the summary.

  For example, in the embodiment, the differential device D is exemplified as the transmission device, and the second transmission member 8 and the first and second transmission mechanisms from the differential case D (casing) of the differential device D that receives power from the power source. Although the first output shaft 6 (eccentric rotating member) and the second output shaft 7 (third transmission member) are distributed via T1 and T2 while allowing differential rotation, the present invention shows that The present invention can be applied to various transmission devices other than the differential device.

  For example, a casing corresponding to the differential case C of the above embodiment is a fixed transmission case, and either the first output shaft 6 (eccentric rotating member) or the second output shaft 7 (third transmission member) is an input shaft, By using either one of the output shafts as an output shaft, the differential device D according to the embodiment can change (decelerate or increase) the rotational torque input to the input shaft and transmit it to the output shaft (deceleration). The transmission (speed reducer or speed increaser) is the transmission device of the present invention.

  In the embodiment, the differential device D as a transmission device is accommodated in the transmission case M of the automobile. However, the differential device D is not limited to the differential apparatus for the automobile, 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 with respect 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.

  In the embodiment, the first transmission groove 21 and the second transmission are used as the first transmission mechanism T1 capable of transmitting torque while shifting between the first transmission member (first case half C1) and the second transmission member 8. A rolling ball type speed change mechanism comprising a groove 22 and a first transmission ball 23 interposed between the transmission grooves 21 and 22 is used, and between the second transmission member 8 and the third transmission member (second output shaft 7). As a second speed change mechanism T2 capable of transmitting torque while shifting, a rolling ball type comprising a third transmission groove 24, a fourth transmission groove 25, and a second transmission ball 26 interposed between the two transmission grooves 24, 25. Although a transmission mechanism is used, at least one of the first and second transmission mechanisms of the present invention is not limited to the structure of the above embodiment. That is, various transmission mechanisms including a transmission member (that is, a second transmission member) capable of rotating around the second axis and revolving around the first axis in conjunction with the rotation of the eccentric rotating member, such as an inscribed planetary gear mechanism. Alternatively, a cycloid reduction gear (speed increaser) or a trochoid reduction gear (speed increase) having various structures may be applied to at least one of the first and second transmission mechanisms of the present invention.

  Moreover, in the said embodiment, in order to make individual processing of the 2nd and 3rd transmission grooves 22 and 24 easy, the 2nd transmission member 8 is divided and comprised from a pair of transmission member half bodies 8a and 8b, and both the transmission members Although the one formed by integrally coupling the half bodies 8a and 8b is used, in the present invention, an integral second transmission member may be used.

  Moreover, in the said embodiment, although the cross-sectional shape of the balance weight W was shown as the arch shape that the outer peripheral edge Wo followed the inner peripheral surface of the differential case C, the balance weight of the present invention is shown. The form is not limited to the embodiment, that is, any form can be appropriately set as long as the desired balancer function can be exhibited without interfering with the inner peripheral surface of the differential case C. For example, a ball shape, a rectangular parallelepiped shape, a capsule shape It may be a shape.

  Moreover, in the said embodiment, although each transmission groove 21,22; 24,25 of 1st, 2nd transmission mechanism T1, T2 is made into the waveform annular wave groove along a trochoid curve, these transmission grooves are in embodiment. It is not limited, For example, it is good also as a wave-shaped annular wave groove along a cycloid curve.

  In the above-described embodiment, the first and second ball-shaped first and second transmission grooves 21 and 22 and the third and fourth transmission grooves 24 and 25 of the first and second transmission mechanisms T1 and T2 are provided. Although two rolling elements 23 and 26 are interposed, the rolling elements may be in the form of a roller or a pin. In this case, the first and second transmission grooves 21 and 22, and the third and fourth The transmission grooves 24 and 25 are formed in an inner surface shape so that a roller-like or pin-like rolling element can roll.

  In the embodiment, the first and second output shafts 6 and 7 are directly supported by the differential case C. However, the first and second output shafts 6 and 7 are connected to the drive axles S1 and S2 supported by the differential case C. They can be connected and supported by the differential case via these drive axles.

C ... Differential case D as casing D ... Differential device I as transmission device ... Synchronous rotation mechanism S1 ... Right drive axle S2 as first drive shaft・ ・ ・ Left drive axle T1 as the second drive shaft ... First transmission mechanism T2 ... Second transmission mechanism W ... Balance weight X1 ... First axis X2 ... ... the second axis 6 ... the first output shaft 6j as the eccentric rotating member ... the main shaft portion 6e of the first output shaft as the eccentric rotating member ... the first output shaft as the eccentric rotating member Eccentric shaft portion 7 of the output shaft ... The second output shaft 8 as the third transmission member ... The second transmission members 21, 22, ..., the first and second transmission grooves 23, ... First transmission balls 24, 25 as a single rolling element, third and fourth transmission grooves 26,... Second transmission bolt as a second rolling element Le 31 ... connecting tube portion of the first support portion 32 ... second support portions 33 ... connecting portion, the connecting plate portion

Claims (4)

A casing (C) integrally including a first transmission member (C1) having a first axis (X1) as a central axis;
A main shaft portion (6j) rotatably supported around the first axis (X1) by the casing (C), and an eccentric shaft positioned on the second axis (X2) eccentric from the first axis (X1). An eccentric rotating member (6) formed by integrally connecting the parts (6e) to each other;
A second transmission member (8) disposed adjacent to the first transmission member (C1) and rotatably supported by the eccentric shaft portion (6e);
A third transmission member (7) disposed adjacent to the second transmission member (8) and supported rotatably around the first axis (X1) by the casing (C);
A first transmission mechanism (T1) capable of transmitting torque while shifting between the first and second transmission members (C1, 8);
A second transmission mechanism (T2) capable of transmitting torque while shifting between the second and third transmission members (8, 7);
A balance weight (W) disposed radially outward of the second transmission member (8);
Synchronous rotation mechanism (I) that rotates the balance weight (W) synchronously with the eccentric rotation member (6) while holding the balance weight (W) at a position opposite in phase to the eccentric shaft portion (6e) with respect to the first axis (X1). A transmission device comprising:   The synchronous rotation mechanism (I) includes a first support portion (31) rotatably supported around the second axis (X2) on the outer periphery of the second transmission member (8), and the casing (C) or A second support part (32) supported rotatably around the first axis (X) by the third transmission member (7) and the first and second support parts (31, 32) are integrated. The balance weight (W) is held at the position of the opposite phase by the first support part (31) or the connection part (33). The transmission device according to claim 1. In the transmission device according to claim 1 or 2,
The first transmission mechanism (T1) has a first annular transmission groove formed on the surface of the first transmission member (C1) facing the second transmission member (8) with the first axis (X1) as the center. (21) and the second transmission member (8) facing the first transmission member (C1) on the surface facing the second axis (X2), the corrugated ring having a wave number of the first transmission groove (21) Different from the second transmission groove (22) and a plurality of overlapping portions of the first and second transmission grooves (21, 22), and rolls on the first and second transmission grooves (21, 22). However, the second transmission mechanism (T2) includes a plurality of first rolling elements (23) that perform transmission transmission between the first and second transmission members (C1, 8). ) Of the third annular transmission groove (24) formed around the second axis (X2) on the surface facing the third transmission member (7), and the third transmission A fourth transmission groove having a wave shape and a wave number different from that of the third transmission groove (25) formed around the first axis (X1) on the surface of the material (7) facing the second transmission member (8); The second and third transmission members (8, 8) are interposed in a plurality of overlapping portions of the third and fourth transmission grooves (23, 24) and roll on the third and fourth transmission grooves (23, 24). 7) A transmission device comprising a plurality of second rolling elements (26) for performing transmission transmission between 7). A differential device using the transmission device according to claim 3,
The casing (C) is a differential case that has a first transmission member (C1) integrally and receives power.
The differential case (C) rotatably supports a first drive shaft (S1) connected to the main shaft portion (6j) and a second drive shaft (S2) connected to the third transmission member (7). And
When 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 following formula (Z1 / Z2) × (Z3 / Z4) = 2
A differential device characterized by that.

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