JPS588852A - Transmitting mechanism for variable ratio - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates primarily to variable ratio transmission mechanisms for use in automobiles.

Continuously varying speed ratio transmissions can be used in motor vehicles when used with effective control systems. This is because such transmissions automatically and steplessly change the transmission ratio depending on engine and vehicle operating parameters.
This is because the engine speed can be designed to always be kept at an appropriate value for the operating conditions at that time. Operating conditions include, for example, cruising conditions where the engine is operated at close to economical speeds to meet all power demands, and high torque demand conditions where the wheels are able to produce their maximum horsepower at the time. In actual application,
``Transmission performance and transmission efficiency are related design factors.

The present invention relates to a mechanical continuously variable ratio drive which essentially includes a mechanical variator. For example, interconnected planets (
In particular, it includes a pair of variable pitch V-groove pulleys that are interlocked with a rotating internal type gear set.

In the variable ratio transmission mechanism according to the invention, the rotary drive member is coupled to drive the input member of a mechanical variator, and the variator is operated to provide a continuously variable ratio drive at its output member. , the output member of the variator is the first. Second. The first... a second member, the first member of the first planetary gear set being coupled to the output member of the variator, and the second member of the first planetary gear set being coupled to the first member of the third planetary gear set. the carrier member of the first planetary gear set is connected to the first member of the second planetary gear set, the second member of the second planetary gear set is held stationary, and the second. The carrier members of the third planetary gear set are connected to each other, and the carrier members of the third planetary gear set are connected to each other.
A second member of the planetary gear set is connected to the output member of the transmission mechanism, one of said carrier members having a drive connection leading to the input member of the variator, for retransmitting torque from said carrier member to the input member of the variator. It is designed to circulate.

The first gear of each planetary gear set. The second members are preferably a sun gear and a ring gear, respectively.

By appropriately choosing the ratio of the planetary gear set, the ratio range provided by the variator itself (e.g. 6:1)
A considerably larger ratio range can be obtained at the output member of the transmission. Although a ratio range approximately twice that of a variator can be obtained, and even higher ratio ranges are possible in principle, in practice the effective ratio range is limited by losses during recirculation.

In operation, the carrier member of the first planetary gear set rotates at a speed proportional to the variator input speed, and a torque recirculation connection back to the variator input member can be made with this carrier member. However, the second. The carrier members of the third planetary gear set are also rotating at a speed proportional to the variator input speed, and a torque recirculation connection may be provided with these interconnected carrier members. However, since the loss during recirculation is somewhat large, the efficiency at the highest ratio is slightly lower.

In any case, in a transmission, it must be taken into account that the speed changes usually occur at the carrier member and at the variator input in a torque recirculation connection.

The input member of the variator is usually forward drive, backward drive,
The engine is driven through a forward and reverse drive that is selectively activated to establish a neutral state with no transmission of drive power. Therefore, it is activated selectively. A differential gear system having a forward ratio, reverse ratio friction drive establishing device (friction clutch, brake) is provided, or an epicyclic gear system is used.

A fluid coupling may be provided between the engine and the variator input, for example between the engine and the forward and reverse drive.

It may also have a lock-up device that selectively engages to prevent loss of fluid pressure during cruise operation. In this case, a torsional vibration damper can be provided adjacent to the joint.

By using a bypass clutch that can be selectively operated to directly mechanically connect the output member of the transmission mechanism and the rotary drive member that constitutes the drive input section of the variator, the full efficiency of the transmission mechanism can be utilized. can be increased to

In bypass mode, this clutch disengages the input shaft, variator, and recirculation member from each other.

To reduce rotational losses in bypass mode, locking clutches may be provided to selectively hold the reaction members of the interconnected planetary gear set stationary. The fixed clutch may take the form of a multi-disc brake between the fixed housing part and the ring gear forming the second member of the intermediate planetary gear set. When such a reaction brake is released, the variator output speed is reduced to approximately the output shaft speed. For example, it decreases to 89%.

The transmission mechanism can have various arrangements depending on the application. A bevel gear set may be provided between the input and the variator, with the output taken at right angles to the input, and a grooved pulley chain system or a second bevel gear set in the torque recirculation connection to the input. may also be used. Alternatively, the variator input may be concentric with the engine axis, with a toothed drive chain or belt providing a torque recirculation path leading to the variator input in order to extract power parallel to the input. good. In either arrangement, an output differential is provided, the rotating housing of which is connected to the output member of the transmission mechanism, the output member of the differential being parallel to the input axes of the engine and the variator and in opposite directions. It consists of an extending shaft portion, and one shaft portion may be either a sun gear or a burr of a planetary gear set. For example, a pulley chain (or belt) system, a friction overdrive using a sphere, etc. (Kopp)
There is a Per-bury type, which performs frictional drive using a rotational disc. Variable Pitch - Between Grooves and Pulleys Pulley-chain types, which utilize a drive chain with variable pitch, are often used in vehicles, offering the advantages of high power transmission (including good torque performance).
-ru. For heavy-duty applications requiring greater play capacity, a mechanical barrier 1-
It can be combined with one or more other units of similar type connected parallel to it. In order to reduce wear due to the small ratio difference between the respective variators, it is possible to connect a differential gear to each variator.
2 In the variable ratio transmission mechanism according to the invention, the variable planetary gear set steplessly widens the ratio range 2 of the mechanical variator, for example at least twice as limited by the power. With a proper control system for the variator, the overall function becomes that of a properly proportioned transmission.

The invention will now be described by way of the upstream side with reference to the accompanying drawings.

FIG. 1 shows a variable ratio mechanism according to a first embodiment of the present invention, which includes a mechanical variator 10 and a first variator 10. Second. Third
Interconnected star (especially epicyclic internal type) gear set 12
4.16, and drive torque is transmitted from the input shaft 18 to the output shaft 20 at a continuously variable speed ratio.

The mechanical variator 10 has a known structure and has a variable pitch V
It includes an input member in the form of a grooved pulley 22, a corresponding output member in the form of a variable pitch groove pulley 4, and a drive chain 6 interconnecting these two pitchable pulleys. To change the transmission ratio, a ratio controller (both left and right) that responds to a differential parameter (reduces unintended distortion and increases the pitch of the other pulley, causing the drive chain to operate at a larger radius of one pulley) The transmission ratio of the variator is changed steplessly by being constrained to operate at a small radius.The possible ratio range of this variator is about 6:1.

The output pulley 24 of the variator is connected to the first planetary gear set 12
It is connected to drive the sun gear 28 (which becomes the input gear set).

The ring gear 30 of this first planetary gear set is the sun gear 3 of the third planetary gear set 16 (which becomes the output gear set).
It is connected to drive 2. Input gear set 12
The sun gear 28 and ring gear 30 of the planetary pinion 3
4, and these pinions are rotatably mounted on the planet carrier 36.

This planetary carrier is connected to the sun gear 38 of the second planetary gear set 14 (which becomes the intermediate gear set).

The ring gear 40 of the output gear set 16 is coupled to drive the output shaft 20. The sun gear 32 and ring gear 40 of this output gear set mesh with planet pinions 42 which are rotatably mounted on a planet carrier 44. The ring gear 46 of the intermediate gear set 14 is connected to a fixed housing part of the transmission mechanism via a fixed clutch 47. Sun gear 38 and ring gear 46 of intermediate gear set 14 mesh with planet pinions 48 which are rotatably mounted on planet carrier 50 . This planet carrier 50 is connected to the planet carrier 44 of the output gear set 16.

The planet carrier 36 of the input gear set 12, together with the sun gear 38 of the second planet gear set 14, has a drive connection 52 leading to a first grooved pulley 54;
is connected via a drive chain 56 to a second grooved pulley 58 that concentrically surrounds a portion of the input shaft 18 .

This second grooved pulley 58 can be selectively connected to the input coupler 22 of the variator via a drive connection 60, a clutch 62 and a pulley shaft 61. When they are engaged with each other, both pulleys are connected to the input shaft 18. These parts 52 to 62 are part of the planetary carrier 3
6 and the input pulley 22 of the variator.

As an optional but preferred feature, a selectively actuatable bypass connection is provided, which establishes a direct drive connection between input shaft 18 and output shaft 20. To this end, the second multi-disc clutch 64 can be selectively actuated to couple the input shaft 18 to the grooved manual pulley 66 . This grooved manual pulley 66 is connected to the grooved output boolean 0 via a drive chain 68. This grooved output boolean 0 is concentric with the output shaft 20 and has a drive connection 72 leading thereto. When the bypass clutch 64 is engaged, the variable mode clutch 62- is disengaged.

FIG. 2 shows a variable ratio transmission mechanism according to a second embodiment of the invention, which is similar in most respects to the embodiment of FIG. It's a dike. However, in this embodiment of FIG. 2, instead of providing the drive connection 52 leading from the planet carrier 36 to the first grooved pulley 54 in the embodiment of FIG. A drive connection 74 leading from the sixteen interconnected planet carriers 50.44 to the first grooved pulley 54' constitutes a torque recirculation connection.

Selectively actuated bypass connections (64-72) are also an optional, but preferred feature of the embodiment of FIG. 1 and 2, the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear of input, intermediate, and output gear sets 12, 14, 16, respectively, is, for example, 4
:1, 1.65:1, 2:1.

The operation of the embodiment shown in FIG. 1 will be described below, but the operation of the embodiment shown in FIG. 2 is almost the same. First multi-plate clutch 62
When engaged, the input torque from the input shaft 18 is sent to the input pulley 22 of the variator 10 and from there via the drive chain 26 to the output pulley 24 determined by the current pitch of these two variable pitch pulleys. is transmitted to the sun gear 22 of the input gear set 12.

In the case of the ratio extended above, the carrier 36 of the input gear set
, thus the sun gear 38 of the intermediate gear set 14 also rotates in the same direction as the sun gear 28, at a speed proportional to the speed of the input shaft 18, with the torque increasing in proportion to the input gear set 12. This is expressed by the following formula. That is, Tc = Ts (-L+ 4 ) Here, Tc is the torque of the carrier 36, Ts is the torque of the sun gear 28, and R and S are the numbers of teeth of the ring gear 30 and the sun gear 28, respectively. The ring gear 30 of the input gear set 12 therefore also has a torque reaction in the opposite direction to the torque of the sun gear 28 of the input gear set, so that the sun gear 32 of the output gear set 16 also has a torque reaction in the opposite direction to the torque of the sun gear 28 of the input gear set; The direction is the same as the direction of the sun gear 28 from a low speed range of about 95%. The ring gear 30 is at rest at 95 percent value and reverses at the top 5 percent of the variator range. The percentages will vary for different planetary gear and variator transmission ratios.

If the torque on the sun gear 38 of the intermediate gear set 14 is of the value already mentioned and the fixed clutch 47 is engaged to hold the ring gear 46 of the intermediate gear set 14 stationary and provide a reaction force. In this case, the planet pinion 48 of the intermediate gear set is connected to the planet pinion 34 of the input gear set 12.
will apply a torque to the carrier 50.44 along the torque path from .

Since the sun gear 32 of the output gear set 16 is subjected to a reaction torque in the opposite direction to the torque of the input sun gear 28, as described above, the planet pinion 42 of the output gear set
A reaction is applied to the output ring gear 40 to generate torque, thereby driving the output shaft 20.

However, the torque extracted at the output ring gear 40 is limited by the torque reaction produced at the sun gear 32, and in reality, the theoretical excess torque at the carrier 44 is extracted at the sun gear 38 and the torque is restored. It is recirculated to the mechanical variator 100 input member 22 via circulation connections 52-62. In reality, a force-balancing reaction occurs instantaneously, so that the greater the torque ratio produced in the variator, the greater the amount of recirculated energy that is passed back through the variator and acts to increase the output torque (1<+). The amount of equilibrium torque increases.

When the variator 10 reaches the minimum ratio condition, the first multi-disc clutch 62 is disengaged and the optional second multi-disc clutch 6 is disengaged.
4 can be engaged □ to establish a bypass state in which the input shaft 18 and the output shaft 20 are mechanically directly connected.

This effectively unloads the variator and variable mode elements and can eliminate losses associated with torque recirculation.

Even in this case, the variator and variable mode element will experience rotational losses that are considered excessive. This is because the relevant parts rotate at a speed consistent with the generation of a normal range of transmitted output speeds from the variable mode element.

In order to reduce such losses and also to reduce wear on the variator, the fixed clutch 47 can be released in the bypass mode, thereby freeing the variator and the variable mode element to rotate together, thereby reducing the variator's wear. The actual speed is - in the example shown, approximately 11 of the previous value.
decrease to %.

Although the locking clutch 47 shown in FIG. 1 is a plate clutch, a high performance dog clutch with conventional synchronizing elements to facilitate engagement may also be used.

The operation of the embodiment of FIG. 2 is substantially the same as that of the first embodiment, but the surplus torque is transferred from the two carriers 50.44 rather than from the sun gear 38 as in the embodiment of FIG. Take it out directly. The speed of both carriers 50.44 is proportional to the input speed, but different from the speed of the sun gear 38.

The embodiment of FIG. 1 is preferred because recirculated torque is extracted further up the torque path, thereby reducing losses in the intermediate gear set 14. Also, while the embodiment of FIG. 2 requires a ratio of, for example, 4:1, a more practical gear ratio of, for example, 2:1 may be used in the torque recirculation connection.

FIG. 3 shows a first practical embodiment of a variable ratio transmission according to the invention, which corresponds functionally to the embodiment of FIG. 2 described above.

As shown in FIG. 3, an engine 80 is coupled to provide torque to a fluid coupling and an adjacent torsional vibration damper (both shown at 82), which includes a selectively actuatable lock-up clutch. (not shown). For special applications in special environments, fluid torque converters may be used in place of fluid couplings.

The hydraulic pump 84 is driven at engine speed by being directly coupled to the rotating casing of the fluid coupling. The output torque from the fluid coupling is provided to an input gear 86 of a forward/reverse differential unit 88 . The input gear 86 and a pinion gear meshing with the differential output gear 90 are rotatably mounted on a cross bin 92 carried by a rotating differential case 94. A friction brake 96 having alternating friction plates coupled to the rotating differential case 94 and the stationary transmission housing 98 is selectively engaged by supplying fluid to an annular hydraulic cylinder associated therewith to selectively engage the differential case 94.
is held stationary, and the output gear 90 and the drive shaft 118 connected thereto are driven in the opposite direction and at the same speed as the input. This is the backward drive state.

In much the same manner, the second annular hydraulic cylinder is selectively engaged by supplying fluid to the differential case 94.
is coupled to the clutch drum 104 fixed to the drive shaft 118 to establish a forward drive state, in which the drive shaft is driven in the same direction and at the same speed as the input section. When neither brake 96 nor clutch 102 is in a stopped state, a neutral state is established and no torque is transmitted from the engine to drive shaft 118.

A solenoid 10 is installed adjacent to the fluid pressure pump 84 to selectively pressurize the fluid pressure cylinder in response to signals from the exerciser.
6 and a valve block 108 are provided. A locking pawl 109 is selectively engageable with clutch drum 104 to lock the transmission when required.

The drive shaft 118 is connected to the mechanical variator 110 and the first . Second.
It is connected to the third planetary gear set 112, 114, 116 in a shape including bevel gears.

The mechanical variator 110 includes a variable pitch V-groove pulley 12
2-shaped input member and the corresponding variable pitch V
It includes an output member in the form of a grooved pulley 124 and a drive chain 126 interconnecting the two variable pitch pulleys. To change the transmission ratio, a ratio controller (not shown) responsive to operating parameters decreases the pitch of one pulley and correspondingly increases the pitch of the other pulley, thereby causing the drive chain to increase the pitch of one pulley. It operates at a larger radius and is constrained to act at a smaller radius on the other pulley, changing the transmission ratio of the variator steplessly. With this variator a ratio range of about 6:1 can be obtained.

The output pulley 124 of the variator is the first planetary gear set 1.
connected to drive twelve sun gears 128;
This first planetary gear set becomes the input gear set. 1st
The ring gear 130 of the planetary gear set is coupled to drive the sun gear 132 of the third planetary gear set 116 (which serves as the output gear set).

Sun gear 128 and ring gear 130 of input gear set 112 mesh with planetary pinions 134 that are rotatably mounted on planetary carrier 136 . This planet carrier 136 is drivingly connected to the sun gear 138 of the second planet gear set 114 (which constitutes an intermediate gear set).

The ring gear 140 of the output gear set 116 is the pulley 17
It is connected to drive an output containing 0. Sun gear 132 and ring gear 140 of the output gear set
are in mesh with planetary pinions 142, which are rotatably mounted on a planetary carrier 144.

The ring gear 146 of the intermediate gear set 114 is connected to a fixed housing portion of the transmission mechanism via a fixed clutch (not shown, but corresponding to the fixed clutch 47 of FIG. 2). Sun gear 138 and ring gear 146 of intermediate gear set 114 mesh with planet pinions 148 that are rotatably mounted on planetary carrier 150 .

The planetary carriers 144, 150 of each of the output and intermediate gear sets 116, 114 are interconnected and include a flange-like extension forming a first grooved pulley 154. This first grooved pulley 154 is connected via a drive chain 156 to a second grooved pulley 158 that concentrically surrounds a portion of the input shaft 11B. This second grooved pulley 15B is connected to the first multi-disc clutch 162.
It has a drive connection 160 that leads to. This first multi-plate clutch 162 can be selectively engaged to provide a drive connection to the input pulley 122 and input shaft 118 of the variator 110 via the shaft 161. These parts 154 to 162 are connected to both planetary carriers 144°1
50 and the input pulley 122 of the mechanical variator 110.

As discussed in connection with FIG. 2, the embodiment of FIG. 3 also includes a selectively actuatable bypass connection between input shaft 118 and pulley 170 forming part of the output section. A direct drive connection is established. For this purpose,
A second plate clutch 164 can be selectively actuated to couple input shaft 118 to grooved manual pulley 166 . This manual pulley 166 is connected to a grooved output pulley 170 by a drive chain 16B.

The grooved output pulley 170 is connected to an output differential unit 180, which has a rotating housing 182 and a conventional differential gearing of cross pins and interlocking pinion gears. This differential unit 180 still has an output shaft extending parallel to the input shaft 118 and extending in parallel and opposite directions. One of these output shafts is shaft 184;
On the other hand, the shaft 1 runs concentrically through the gear set 116, 114, 112 and the output 124 of the mechanical variator 110.
It is 86.

Similar to the embodiment of FIG. 2, the ratio of the number of teeth on the sun gear of the input, intermediate, and output gear sets 112, 114, and 116, respectively, is, for example, 4:1, 1.
65:1, 2:1.

The operation of the embodiment of FIG. 3 is substantially the same as that described for the embodiment of FIG. Thus, when the first clutch 162 is engaged, input torque from the input shaft 118 is transmitted to the input pulley 122 of the mechanical parryer 110 and from there to the output pulley 124 by the drive chain 126.
are transmitted in a ratio determined by the current pitch of these two variable pitch pulleys, and input gear set 11
2 sun gear 128. For the previously mentioned ratios, the input gear set carrier 136, and therefore also the sun gear 138 of the intermediate gear 114, will rotate in the same direction as the sun gear 128 at a speed proportional to the input shaft 118 speed. The torque at this time increases according to the ratio of the input gear set 112, as shown by the following equation.

Tc = Ts (i+1) Here, Tc is the torque of the carrier 136, TS is the torque of the sun gear 12B, and R and S are the torque of the ring gear 1, respectively.
30. This is the number of teeth of the sun gear 128. Input gear set 1
12 ring gear 130 is therefore also sun gear 132 of the output gear set 116 as well as sun gear 1 of the input gear set 116.
28, the direction of rotation is the same as the direction of rotation of the sun gear 128 for approximately 95 percent of the time from the low speed range of the variator range, and the ring gear 130 At a value of 95 percent, it is stationary and the top of the variator range is 5.
Rotate in the opposite direction at the percent point. This percentage will vary for different planetary gear ratios and variator ratios.

If the torque of the sun gear 13B of the intermediate gear set 114 is the value described above, and when the fixed clutch is engaged and the ring gear 146 of the intermediate gear set 114 is kept stationary to provide a reaction force, the intermediate gear The planetary pinion 148 of the set is the planetary pinion 13 of the input gear set 112.
Torque will be supplied to the carriers 150, 144 along the torque path from 4. As previously mentioned, sun gear 132 of output gear set 116 is connected to input sun gear 128.
Since the planetary pinion 142 of the output gear set is subjected to a reaction torque in the opposite direction to the torque of Become. □However, the torque available at the output ring gear 140 is limited by the torque reaction occurring at the sun gear 132, and the theoretical excess torque is actually extracted at both carrier pulleys 154 and connected to the torque recirculation connection. 1
54 to 162 to the input member 122 of the mechanical variator 110.

Since there is an instantaneous reaction that balances the forces, the greater the torque ratio developed in the variator, the greater the amount of recirculated balancing torque that is fed back through the variator and acts to increase the output torque.

When the mechanical variator 110 reaches the minimum ratio condition, the first
By disengaging the second clutch 162 and engaging the second clutch 164, a bypass state can be established, and the input shaft 118 and the output section can be directly connected mechanically. This will effectively unload the mechanical variator and variable mode elements and eliminate losses associated with torque recirculation.

Furthermore, similar to the embodiment of FIG. 2, in order to prevent rotational losses in the mechanical variator and the variable mode element, the fixed clutch is released in the bypass mode and the mechanical variator and the variable mode element are free to rotate together. let me,
This reduces rotational losses and also reduces wear on the mechanical variator.

FIG. 4 is a fragmentary view showing a slightly modified embodiment of the embodiment shown in FIG. Portions of FIG. 4 that are similar to those of FIG. 3 are designated by the same reference numerals of FIG. 3 with a prime.

In the embodiment of FIG. 4, the forward and backward unit 88
' and valve block 108' are connected to mechanical variator 11
0' input member 122' (and adjacent grooved pulleys 15.8', clutches 162', 164', and grooved pulleys 166') and connects the fluid coupling (FIG. 4) via the deflection shaft 89'. (not shown).

The arrangement of FIGS. 3 and 4 is suitable for a four-wheel drive vehicle, with output shafts 184, 186 used as front and rear propeller shafts. In this case, instead of a working gear, a planetary gear can be used to distribute the torque depending on the axle load.

FIG. 5 shows a more practical embodiment of the variable ratio transmission mechanism according to the invention, which corresponds functionally to the embodiment of FIG. It extends perpendicularly to the rotational axis of the drive member and parallel to the rotational axis of the output member of the transmission mechanism.

The variable ratio transmission shown in FIG. 5 includes an engine 187 adapted to provide torque to a hydraulic coupling and an adjacent torsional vibration damper, similar to the embodiment of FIG. The fluid coupling includes a selectively actuated lock-up clutch (not shown). The transmission further includes a hydraulic pump driven at engine speed and directly connected to the rotating casing of the fluid coupling. Also, similar to the embodiment of FIG. 3, the output torque from the fluid coupling is sent to the input gear of the forward/reverse differential unit 188. The differential output gear device 190 of this forward/reverse differential unit 188 is connected to the drive shaft 20.
It is connected to 0.

The drive shaft 200 is connected to drive the control unit 202, and is directly or indirectly connected to a rotary drive member constituted by a hollow input shaft 218. This input shaft 218 is connected by a bevel gear set 219 to an input drive shaft and a variable pitch manual pulley 2 of a mechanical variator 210.
22. The variable pitch output pulley 224 of the mechanical variator 210 is connected to the input pulley by a drive chain 226 and provides drive torque to the input sun gear 228 of the first planetary gear set 212 via an output drive shaft.

The first planetary gear set 212 constitutes an input planetary gear set, which is in turn connected to the second and third planetary gear sets 214, which constitute intermediate and output planetary gear sets, respectively.
, 216.

1st. Second. Third planetary gear set 212°214.2
16, which is described in connection with the embodiment of FIG. Second
．． It has a part that corresponds to and operates in the same way as that of the third planetary gear set 12, 14, 16 to supply the drive torque to the output shaft 220.

Thus, in the embodiment of FIG. 5, the output member 224 of the mechanical variator 210 is connected to the input planetary gear set 212.
The ring gear 246 of the intermediate planetary gear set 214 may be selectively held stationary by a fixed brake 247 . In order to recirculate the torque from the carriers 244, 250 of each intermediate and output planetary gear cellar + 214, 216, these carriers 244, 250 are provided with an annular flange extension 254, similar to the crown gears. Slanted teeth are formed. These inclined teeth cooperate with another set of bevel gears 258 to clutch 263 . Mechanical variator 21 via shaft 217 and bevel gear set 219
0 input member 222 is provided with a return torque path for recirculating torque.

Bypass clutch 263 selectively operates to
8 through the shaft 217 and the bevel gear set 254, 2
58 and the external teeth 27 of the output ring gear 244 of the input bevel gear set 219 or the output planetary gear set 216
0 and is connected to a bypass bevel gear 266 that meshes with the bypass bevel gear 266.

A control unit 202 mounted on drive shaft 200 is responsive to road speed, engine speed, engine load and driver signals to actuate variable pitch pulleys 222, 224 and bypass latch 263.

The operation of the embodiment of FIG. 5 is basically the same as the embodiment of FIG.

Alternatively, a direct drive can be achieved by interconnecting the output ring gear 240 of the output planetary gear set 216 and the sun gear 232 of the output planetary gear set and simultaneously disengaging the mechanical variator 210 from the shaft driving it. can. However, such an arrangement is less desirable. This is because they tend to increase losses in the variable mode or limit the minimum ratio.

6 and 7 respectively show the speed relationships and transmitted torque and power in various elements of the embodiment of FIG. 5, and the respective values are given by five variator ratios in FIGS. 6 and 7. The values in the bypass state are given in FIG. The ratio range of the variator is 6:1, and the number of teeth on the ring gear is intermediate.

The ratio of the number of sun teeth of each output gear set 212, 214, 216 is 4:1, 1.65:1, and 2:1, respectively. The bevel gear set 219 has a 1:1 ratio,
The value it gives ignores losses in the system.

In FIG. 6, the element speeds for a range of variator ratios are shown as r, p, m, and 100 r, p,
A straight line 278 represents the speed of the input shaft 218, a slow line 280 represents the speed of the input carrier 236, and a lower speed line 282 represents the speed of the keys 171J, 244, 250.

Curve 2 rises rapidly as the variator ratio increases
84 represents the speed of input sun gear 228. Curve 286 that slowly rises as the variator ratio increases
represents the speed of output ring gear 240 and output shaft 220. Descending straight line 28B represents the speed of input ring gear 230. Descending dashed curve R
represents the total transmission ratio. , 4P1. P2 shows the linear velocity at zero pitch in the input and output gear sets 212 and 216, respectively.

In FIG. 7, the reference numerals of the various parts correspond to the reference numerals used in FIG.

FIG. 8 shows a multi-variator arrangement with a plurality of mechanical variators associated with a variable ratio transmission according to the invention. Roughly speaking, it is possible to combine dissimilar variators, or to combine two variators with one another, to provide a simple differential action between similar variators and planetary gearing, and thus The resulting dissimilar loads can be balanced by a planetary gear differential.

In particular, in the arrangement shown in FIG. 8, the input shaft 300 is an input member 301a of a conical variator.

301b and 301c, and the output member 302a
, 302b, 302c are belts or chains 303a
, 303b and 303c are connected to the respective input members.

Variators a, b are connected to side gears 304 of a differential 305 and the combined power is transmitted to differential pinions 306 . It is taken out via cross pin 307 and shaft 308.

To connect with the third variator C, the torque on shaft 308 is sent to ring gear 309 of planetary gear differential 310 and balanced by sun gear 311 connected to output member 302C. In this way, all torque is extracted via planet carrier 312 and output shaft 313.

This arrangement can be used in place of a combination of several similar variators.

Figures 9 to 14 show various known forms of variator, in connection with the variable ratio transmission mechanism according to the invention, the output or input part (13) parallel to the input part (9 to 12).
．． Figure 14) shows a configuration that provides a perpendicular output section.

These forms use the same basic principles. In other words, the three planetary gear sets are now operated by the variator, and (b) the output from the variator is directly connected to the sun gear of the first gear set, and Torque is recirculated to the variator input member by suitably geared connections from any of the carriers, and the prime mover input is routed to any of the carriers or variator inputs of the three gear sets.

In this method, various variators and configurations are used in three basic configurations: parallel;

It can be used to obtain perpendicular and concentric arrangements. Angular drive arrangements can also be easily obtained if required for more specific applications.

Figures 15 and 16 show the two states of the speedometer and tachometer combination described above.

FIG. 17 shows one possible form of a steerable transmission for a tracked vehicle utilizing a variable ratio transmission according to the invention.

As shown in FIG. 17, the prime mover 480 connects to the fluid coupling 482
The fluid coupling transmits torque to the shaft 5oo and the hydraulic pump 484. A system of toothed pulleys and chains 510 transmits the drive power to a second shaft 519 that divides the power between each half of the transmission.

If we consider only one side (since the other side works as well),
The second shaft 519 is fixed to the side gear of the differential gear set, and from this point all downstream components operate in the same manner as in the embodiment of FIG. However, the bypass feature is not required.

Drive power is extracted via output shaft 520 to track drive cogs (not shown) on each side of the vehicle.

The symmetrically arranged halves can operate independently,
The entire unit can be operated to provide the required drive and provide the advantages associated with the invention and the following features: That is, a) By eliminating or locking the balanced differential unit, it is possible to steer the vehicle by changing the speed for each track.

Mouth) By selectively operating the retreat unit, it is possible to reverse the rotation on each orbit and perform a turn.

→ You can get the same performance by moving forward or backward.

2) A single control rod can move forward, reverse, accelerate, and steer.

The variable ratio transmission mechanism according to the invention so far described offers a number of potential advantages. That is, (2) the transmission device is fully automatic, and by using a fluid coupling together, the extraction of the driving force becomes smooth, and a "hold" state can be easily obtained. To reduce engagement losses, the joint can be designed to lock up under certain conditions.

2) In variable mode, the transmission ratio can be changed continuously (that is, it can be changed steplessly).

Power can be applied throughout the ratio range by shifting to and from bypass mode. This shift is imperceptible, especially by using a bypass ratio that is approximately the same as the minimum variable ratio.

3) A wide range can be used. The variator ratio is normally limited to about 6:1, but if the present invention is applied,
A ratio range twice this ratio can be used, allowing the engine to operate at maximum efficiency while the vehicle is running, and providing maximum power for maximum acceleration at any time in response to driver signals. I can do it.

4) The overall operating efficiency is potentially better than that of a conventional hydraulic unit and its associated final drive gear;
! 7 is also excellent. , 5) Bypass efficiency is superior to that of ordinary hypoid axles due to the more moderate load that does not have to be used in place of maximum output torque. Bevel gears with relatively high efficiency can be used effectively.

6) Can be applied to a variety of vehicles including transverse engine front wheel drive, conventional front engine rear wheel drive, and four wheel drive vehicles.

The floor height of a pan-type rear-wheel drive vehicle can be made as low as that of a front-wheel drive pan by providing a drive unit for each wheel, and the unit is driven by a universal joint type shaft from a differential mounted on the body. can be driven, and these axles can be connected to the unit approximately below the wheel center height. A pulley-type variator is housed within the wheel enclosure with the output section eccentric to the wheel center.
This output can drive gears concentric with the wheels. In this case, the brake drum may be installed adjacent to each wheel or inside the respective drive unit.

7) Reduced engine torque reaction effects in rear wheel drive vehicles. This is because only engine torque is transmitted through the drive line. Especially when the output torque is high, there is less tendency for the right-hand rear wheel to lift and rotate at high torque, and there is little chance of sudden tilting of the cab or orbi-ting of the drive line in commercial vehicles. Also, if the output torque extracted from the unit is high and the unit is compact, it is possible to replace it with a less efficient hub-reduced rear axle to obtain climbing ability and ground clearance.

8) Maximum engine braking can be obtained when going downhill.

9) Despite the increased efficiency, the oil cooler used in conventional hydraulic drive units is no longer required.

10) Therefore, considerable advantages can be obtained in the following points. Namely: a) Economy. By using suitable gearing, fuel savings of up to 20% are theoretically possible. The ratio range can be further increased by improving aerodynamics and deceleration at cruise speed.

b) Acceleration. You can always do something that gives you maximum power.

C) Convenience. No gear shift required.

d) Sophistication. Lower engine speeds at cruise, improved drivability and no transmission snatch.

e) Safety. There is no shifting out of gear, maximum acceleration is available, there is no sudden tilting of the cab, there is less tendency for wheelspin, and the full potential of engine braking is utilized.

f) Placement. The gearbox, floor-mounted gear shift lever and clutch pedal can be eliminated.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing a first embodiment of a variable ratio transmission mechanism according to the present invention, FIG. 2 is a schematic diagram showing a second embodiment of a variable ratio transmission mechanism according to the present invention, and FIGS. 6 is a fragmentary schematic diagram illustrating a possible automotive application of the variable ratio transmission mechanism according to the invention; FIG. 6 illustrates the relative speeds of the elements of the three interconnected planetary gear sets of the embodiment of FIG. 5; FIG. 7 is a graphical representation of the element speeds plotted against the variator ratios for the purpose of the invention; FIG. , FIG. 8 is a diagram showing a multi-variator type embodiment, FIGS. 9 to 12 are diagrams showing various forms of variators providing an output section parallel to the input section, and FIGS. 13 and 14 are diagrams showing an input section. Figure 15.16 shows the preferred speedometer-tachometer combination for a variable ratio transmission; Figure 17 shows the preferred speedometer/tachometer combination for a variable ratio transmission. FIG. 2 is a diagram showing a variable ratio transmission mechanism applied as a steering type transmission device for a traveling vehicle. 10... Mechanical variator, 12.14°16...
Planetary gear set, 1B...Input shaft, 20...Output shaft, 22...Variable pitch V-groove pulley, 26...Drive chain, 28...Sun gear, 30...Ring gear,
32... Sun gear, 34... Planetary pinion, 36...
... Planet carrier, 38 ... Sun gear, 40 ... Ring gear, 44 ... Planet carrier, 47 ... Fixed clutch, 54.58 ... Grooved pulley, 56 ... Drive chain, 62...Clutch, 66...Clutch, 68...Drive chain ρExample Fudeyasu Iyuki -Deaf゛5女lβkuno5vβamf.

Claims (1)

Claims: (1) A rotary drive member (e.g. 18) is coupled to drive an input member (e.g. 22) of a mechanical variator (e.g. 10), and the variator is connected to an output register of the variator. For example, step 24) provides stepless variable ratio drive,
The output member of this variator is interconnected with the first. Second,
A third planetary gear set (e.g. 12, 14° 16) is coupled to drive an output member (e.g. 20) of the transmission mechanism, each of the planetary gear sets having at least one The first one meshes with one planetary member. a second member, the first member (e.g. 28) of the first planetary gear set being connected to the output member of the variator;
Speaking of members, 30) is the first member (30) of the third planetary gear set
For example, the carrier member (for example, 36) of the first planetary gear set is connected to the first planetary gear set of the second planetary gear set.
member (e.g. 38) of the second planetary gear set, the second member (e.g. 46) of the second planetary gear set remains stationary and the second member (e.g. 46) of the second planetary gear set remains stationary. Carrier member of the third planetary gear set (fl
50, 44) are connected to each other, a second member (e.g. 40) of the third planetary gear set is connected to an output member of the transmission mechanism, and one of said carrier members (e.g. 3
Variable ratio transmission mechanism, characterized in that 6) has a drive connection (for example 52 to 62) leading to the input member of the variator, for recirculating torque from said carrier member to the input member of the variator. (2. In the variable ratio transmission mechanism according to claim 1, the first, second, and third planetary gear sets (for example, 12
, 14.16) includes a sun gear (e.g. 28.3B. 32); Second. Each second member of the third planetary gear set includes a ring gear (eg, 30, 46, .
40) A variable ratio transmission mechanism comprising: (3) In the variable ratio transmission mechanism according to claim 1 or 2, the ratio range taken out at the output member (for example 20) of the transmission mechanism during operation is the ratio range given by the variator (for example 10). A variable ratio transmission mechanism characterized in that the ratio of a planetary gear set (for example, 12, 14, 16) is determined so that it is considerably larger than . (4) In the variable ratio transmission mechanism according to any one of claims 1 to 3, the carrier member (for example, 36) of the first planetary gear set (for example, 12) is the input of the variator (for example, 10). A variable ratio transmission mechanism characterized in that it has a drive connection as described above leading to a member (eg 22). (5) In the variable ratio transmission mechanism according to any one of claims 1 to 3, the carrier member (for example, 50
．． Variable ratio transmission mechanism, characterized in that 44) has a drive connection as described above leading to an input member (for example 22) of a variator (for example 10). (6) In the variable ratio transmission mechanism according to any one of claims 1 to 5, a rotary drive member (for example, one
18) is coupled to be driven by the engine (e.g. 80) via a forward/reverse drive device (e.g. 88), and the forward/reverse drive device is connected to the rotary drive member in a forward drive state, a reverse drive state, or a neutral state. A variable ratio transmission mechanism characterized in that it is selectively actuatable to establish a condition. (7) In the variable ratio transmission mechanism according to any one of claims 1 to 6, the bypass clutch (e.g. 64) connects the rotational drive member (e.g. 18) and the protruding member (e.g. 20) of the transmission mechanism. A variable ratio transmission mechanism characterized in that it is selectively operable to establish a direct mechanical connection between the variable ratio transmission mechanism and the engine. A fixed clutch (e.g. 47) holds the reaction members (e.g. 4) of an interconnected planetary gear set (e.g. 12, 14, 16) stationary in a variable mode and operates in a variable mode with free rotation allowed in a bypass mode. (9) The variable ratio transmission mechanism according to any one of claims 1 to 8. In the variator (e.g. 21
The axis of rotation of the input member QI1 (for example 222) extends perpendicularly to the axis of rotation of the rotary drive member (for example 218) and parallel to the axis of rotation of the output member (for example 222) of the transmission mechanism, The rotational drive member is the first. The input member of the variator and said one carrier member (e.g. 2
44) A variable ratio transmission mechanism characterized in that the variable ratio transmission mechanism is connected to each of (10) In the variable ratio transmission mechanism according to any one of claims 1 to 8, the rotation axes of the variator (for example, 110) and the input member (for example, 122) are aligned with the rotational drive member (for example, 118). and extending concentrically to the rotational axis of the transmission mechanism and parallel to the rotational axis of the transmission mechanism output member (e.g. 170) between said one carrier member (e.g. 150, 144) and the variator input member. The drive connection is a drive chain or a drive belt, e.g.
6) A variable ratio transmission mechanism comprising: (11) In the variable ratio transmission mechanism according to claim 10, the output member of the transmission mechanism, for example 170, is an output shaft (fJ, for example 184...186) extending in opposite directions.
) with a differential mechanism (JFII example 180) connected to drive a rotary housing (for example 182), one of these output shafts is connected to a planetary gear set (for example 11'
2. '114.11 sun gear (e.g. 128.13
8,132) and a variable ratio transmission mechanism characterized by extending through a central hole provided in an output member (for example, 12) of a variator (for example, 110). A variable ratio transmission according to any of clauses 11, wherein the input and output registers (e.g. 22, 24) of the variator (e.g. 10) include variable pitch pulleys interconnected by a drive belt or drive chain (e.g. 26). (13) In the variable ratio transmission mechanism according to any one of claims 1 to 12, the variable ratio transmission mechanism is configured to transmit driving force from a vehicle engine to a pair of drive wheels. It is connected to
Variable ratio transmission mechanism, characterized in that it is provided with a speed ratio control device for the variator depending on the operating parameters of the engine and the vehicle and the controls that can be actuated by the driver. (14) In the variable ratio transmission mechanism according to claim 13, a fluid coupling (for example, 82) is provided between the engine (for example, 80) and the rotational drive member (for example, 118) of the transmission mechanism.
) is provided. (15) The variable ratio transmission mechanism according to claim 13 or 14, which includes a speedometer/tachometer combination having a scale dial having a vehicle speed scale and an engine speed scale; The first one is connected to display the speed of each. A variable ratio transmission mechanism comprising a second concentrically mounted indicator member, the relationship between the two scales indicating a differential mode of the transmission mechanism.