JP2003034153A - Drive unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive unit suitable for a hybrid vehicle provided with an engine and a motor capable of obtaining a large drive force in a low vehicle speed range. SOLUTION: This drive unit comprises a differential device of 2-freedom having four or more input and output elements, an input In from the engine, an output Out to a drive system, and two motor/generators MGi and MGo are independently assigned to the elements, and a brake B is provided on the elements other than the element to which the output is assigned. The elements other than the output are braked by the brake, whereby a large deceleration ratio can be set between the input In and the output Out. Accordingly, the startability can be improved without increasing the capacity of the motor/ generator.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive device suitable for a hybrid vehicle equipped with a plurality of power sources such as an engine or a motor, and more specifically, to a continuously variable transmission operation by a differential device such as a planetary gear mechanism. Drive device capable of

[0002]

2. Description of the Related Art As a drive device using this type of differential device, for example, a sun gear, a planet carrier, and a ring gear which constitute a planetary gear mechanism are provided, and a generator, an engine, and a drive system. A drive device for a hybrid vehicle having a structure in which motors are connected to each other is known (see Japanese Patent Application Laid-Open No. 2000-142146). According to this drive device, part of the engine output is distributed to the drive of the generator by utilizing the differential function of the gears, and the generated power is supplied to the motor to continuously change the speed and increase or decrease the output torque. It can be carried out.

However, in such a conventional drive device, it is difficult to increase the mechanical energy passing through the planetary gears due to mechanical restrictions, and therefore it is necessary to make the generator and the motor larger. In particular, the ratio of the power passing through the generator and the motor to the power passing through the differential device approaches 1 on the low speed side and cannot be increased more than that. Requires a generator and a motor that have the same high output as that of the engine, which increases the size and weight of the drive unit and lowers the efficiency.

The present invention has been made in view of such conventional problems, and in a two-degree-of-freedom differential device having three or more elements, a brake is provided for a specific element to rotate the element. By suppressing the above, it is possible to provide a driving device that can obtain a large driving force from a stopped state.

[0005]

According to a first aspect of the present invention, a two-degree-of-freedom differential device having four or more input / output elements is provided, in which the elements are input from an engine, output to a drive system, and two. Motors / generators are individually assigned, and brakes are provided on elements other than the elements to which the outputs are assigned.

A second invention is the same as the first invention,
A motor / generator, an input, an output, and a motor / generator were assigned in the order of rotational speed of the elements. In addition,
The order of rotation speed is the order of arrangement of elements in the alignment chart (described later).

A third invention is the same as the first invention,
A brake was provided on the element adjacent to the element to which the output was assigned.

According to a fourth aspect of the present invention, in the first to third aspects, the four elements of the four-element differential device are arranged in order of rotational speed,
Assigned motor / generator, input, output, motor / generator and brake.

In a fifth aspect based on the first to third aspects, the five elements of the five-element differential device are arranged in order of rotational speed,
Assigned motor / generator, input, output, brake, motor / generator.

In a sixth aspect of the present invention, in the first to third aspects, the five elements of the five-element differential device are arranged in the order of rotational speed,
Assigned motor / generator, input, brake, output, motor / generator.

In a seventh aspect based on the first to third aspects, a clutch is provided between the engine and the input element.

An eighth aspect of the present invention is a 2 having three or more elements.
Equipped with a degree of freedom differential, input from engine, output to drive system, two motors / generators are allocated so that inputs and outputs are not coupled to two motors / generators in the same element In addition, a brake is provided on the element to which the input is assigned.

In a ninth aspect based on the eighth aspect,
A motor / generator, an input and a brake, and an output and a motor / generator were assigned to the three elements of the three-element differential device in the order of rotational speed.

A tenth aspect of the present invention is the same as the eighth aspect, wherein three elements of the three-element differential device are arranged in order of rotational speed.
Assigned motor / generator and input / brake, output, motor / generator.

In an eleventh aspect of the invention, in the first to third and eighth aspects of the invention, four elements of the four-element differential device are arranged in the order of rotation speeds: motor / generator, input and brake, output, motor / generator. Assigned a generator.

In a twelfth aspect of the invention, an input from an engine and an output to a drive system are assigned to different elements of a two-degree-of-freedom differential having three or more elements, and a motor is assigned to both the input and the output. / A generator is assigned, and brakes are provided on elements other than the elements to which inputs and outputs are assigned.

A thirteenth invention is the twelfth invention, wherein three elements of the three-element differential device are arranged in order of rotational speed,
Assigned input and motor / generator, output and motor / generator, and brake.

A fourteenth invention is the twelfth invention, wherein the three elements of the three-element differential device are arranged in order of rotational speed,
Assigned brake, input and motor / generator, output and motor / generator.

A fifteenth invention is the twelfth invention, wherein four elements of the four-element differential device are arranged in order of rotational speed,
Assigned brake, input and motor / generator, output and motor / generator, and brake.

A sixteenth invention is the twelfth invention, wherein four elements of the four-element differential device are arranged in order of rotational speed,
Assigned input and motor / generator, brake, output and motor / generator, brake.

The seventeenth invention is characterized in that an input and a motor / generator, an output, a motor / generator and a brake are assigned to three elements of a differential device having three or more elements in the order of rotational speed. To do.

The eighteenth aspect of the present invention is the first, eighth, 12, 1
In the seventh invention, the brake is engaged when the required driving force is large.

The nineteenth invention is the above-mentioned first, eighth, twelfth and first inventions.
In the invention of claim 7, the drive force generated by the motor / generator is reduced in accordance with the increase in vehicle speed during brake operation so that the transmission force at the brake becomes close to zero under the operation condition of brake off, and the drive at the time of brake off is performed. I tried to reduce the force difference.

A twentieth aspect of the present invention is the first, eighth, twelve, first aspect of the invention.
In the seventh aspect of the invention, the differential device is composed of a planetary gear mechanism.

A twenty-first aspect of the present invention provides the planetary gear mechanism of the twentieth aspect of the present invention including a first planetary gear train of a single pinion type and a second planetary gear train of a double pinion type, each sun gear, a carrier, Any two elements of the ring gear are shared to form a two-degree-of-freedom differential device.

[0026]

According to the first aspect of the invention, in the two-degree-of-freedom differential device having four or more elements, if the speed of any two elements is determined, the speed of the other elements is determined. In such a differential device, by providing a brake on an element other than the element to which the output to the drive system is assigned and braking the element, a large reduction ratio can be set between the power source and the drive system. This makes it possible to improve the starting performance without increasing the capacity of the motor / generator. Such a two-degree-of-freedom differential device can be configured by a planetary gear mechanism, for example, as shown in the twentieth or twenty-first invention.

According to the second aspect of the invention, there is a portion where the power passing through the motor / generator can be made zero when the gear ratio is relatively low and high, and the gear passes through the transmission between these two gear ratios. The power passing through the motor / generator can be reduced to about 1/2 to 1/3 as compared with the power. Since the driving force on the low vehicle speed side can be secured by using a brake, a motor having a capacity of about the maximum value of the passing power of the motor / generator in a gear ratio range between two points where the power passing through the motor / generator can be zero. By using the / generator, the driving force required for the vehicle can be secured from low vehicle speed to high vehicle speed.

According to the third aspect of the present invention, the motor / generator and the gear ratio from the input to the output can be set to a low speed when the brake is operated, so that the driving force on the low vehicle speed side can be more easily obtained.

According to the fourth invention, the number of elements of the differential device can be four, and the differential device can be made compact.

According to the fifth aspect of the invention, the gear ratio during braking can be set to a low speed gear, so that a large driving force can be easily obtained.

According to the sixth aspect of the present invention, since the gear ratio at the time of reverse rotation of the output at the time of brake operation can be set to the low speed gear, a large driving force can be obtained when the vehicle moves backward.

According to the seventh aspect of the invention, the engine can be disengaged by the clutch, so that the vehicle can be driven only by the motor / generator without dragging the engine, and the efficiency during electric traveling can be improved. Also, a large driving force can be generated by operating the brake even during electric traveling, but if the vehicle is moved forward or backward with the same brake operated, the differential element of the input will rotate in the opposite direction. It will be. At this time, the reverse rotation of the engine can be prevented by disconnecting the engine.

According to the eighth aspect of the present invention, a large driving force can be generated in the electric traveling state by operating the same brake both forward and backward. Since the input is stopped in both forward and reverse directions, a mechanism for preventing reverse rotation of the engine is not required, and the size can be reduced.

According to the ninth aspect of the invention, in addition to the effect of the eighth aspect of the invention, a single planetary gear unit can be used as the differential gear, which is suitable for further miniaturization.

According to the tenth aspect of the invention, in addition to the effect of the eighth aspect of the invention, a single planetary gear device can be used as the differential gear, which is suitable for further miniaturization.

According to the eleventh invention, the effects of the first to third and eighth inventions can be obtained with a smaller device.

According to the twelfth aspect of the invention, the series hybrid transmission can be operated in the brake-off state, and can be mechanically operated in the brake-on state at a constant gear ratio without power transmission by the motor / generator. Enables efficient operation.

According to the thirteenth invention, in addition to the effect of the twelfth invention, the constant gear ratio can be set to a lower speed.
A large driving force can be generated.

According to the fourteenth invention, in addition to the effect of the twelfth invention, the constant gear ratio can be set to the overdrive side, so that the effect of improving fuel consumption can be expected.

According to the fifteenth invention, the twelfth, thirteenth, first
The same effect as that of the fourth aspect of the invention can be obtained.

According to the sixteenth invention, in addition to the effects of the twelfth and thirteenth inventions, it becomes possible to generate a large driving force at a constant gear ratio even in reverse.

According to the seventeenth invention, since there are three differential elements, the speed change mechanism can be constituted by one planetary gear mechanism,
The machine part can be downsized.

According to the eighteenth aspect of the invention, when a large driving force is required at a low vehicle speed, the engine, 2
Since a driving force can be generated with at least one torque of each motor / generator, a large driving force can be obtained.

According to the nineteenth aspect of the invention, there is little change in the driving force when the brake is off, and a smooth driving force characteristic can be obtained.

[0045]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a power transmission device (transaxle) for a front-wheel drive vehicle will be described with reference to the drawings. Each of the drawings in FIG. 1 and subsequent drawings shows a combination of a schematic configuration and an alignment chart for different embodiments. Since the structure shown in FIG. 1 also serves as a component related to another embodiment, the configuration of this embodiment will be described in detail first, and only different parts of the other embodiment will be described. . Further, members common to the respective embodiments are denoted by the same reference numerals.

[FIG. 1: Embodiment 1 (5 elements-1 brake)] In the figure, Hm is a motor housing, Ct is a transmission casing, Hc is a clutch housing, and Ha is an axle housing. The clutch housing Hc is provided with a clutch CL that connects or disconnects the engine output shaft Je and the transmission input shaft Jr1. The structure of the transmission is such that a single-pinion planetary gear train P1 and a double-pinion planetary gear train P2 are connected in a manner sharing a ring gear R and a carrier C and housed in a casing Ct. The input shaft Jr1 to which the clutch CL is connected is the ring gear shaft of P1. The input shaft Jr1 is provided with a one-way clutch CLo for preventing reverse rotation of the engine. In the reference numerals indicating the components of the planetary gear train, the subscript 1 is the first planetary gear train P1.
2 shows the second planetary gear train P2. Further, for the double pinion type planetary gear train, for convenience, the structure is represented by a diagram developed in a cross section passing through two pinion shafts (the same applies to each of the following configuration diagrams).

The inner rotor R is attached to the motor housing Hm.
mi and a ring-shaped outer rotor Rmo are supported coaxially, and two motor / generator MGs are supported thereby.
A small electric machine that functions as i and MGo is configured. An annular coil Cm is provided between the inner and outer rotors Rmi and Rmo, and each of the rotors Rmi and Rmo can be individually operated as a generator or a motor by the coil Cm. The inner rotor shaft Jmi penetrates the hollow outer rotor shaft Jmo and is connected to the sun gear S1 of P1.
The outer rotor shaft Jmo is connected to the sun gear S2 of P2. Ssi and Sso in the figure are rotation sensors for measuring the rotation speeds of the inner rotor shaft Jmi and the outer rotor shaft Jmo, respectively. In the reference numerals indicating the constituent elements of the motor / generator, the subscript i indicates the first motor / generator MGi and the subscript o indicates the second motor / generator MGo.

The axle housing Ha is provided on the side surface of the transmission casing Ct, and the reduction gear Fin and the drive axle Drv are supported inside the axle housing Ha in parallel with the planetary gear mechanism. The final reduction gear Fi
The rotation of the carrier C is transmitted to n through the speed reducer Rg. That is, in this case, the carrier shaft Jc is an output shaft connected to the final reduction gear Fin which is a drive system.

Sun gear S2 of P2 and outer pinion p
A ring gear R3 coaxially supported by the ring gear R of P1 is meshed with a large-diameter inner pinion pi that meshes with o, and a brake B that brakes the rotation of the ring gear R3 is provided in the casing Ct.

In the above structure, by braking the ring gear R3 with the brake B, a large reduction ratio can be set as shown in the alignment chart in FIG. 1 and FIGS. The driving force and starting performance of the vehicle can be improved. The symbol EV on the nomographic chart is the characteristic when running only with the motor / generator, START
Represents the characteristics when the brake B is actuated at the time of starting, MAX represents the characteristics at the maximum vehicle speed, and REV represents the characteristics when the vehicle retreats. Further, the symbol Out represents an output to the drive system, and In represents an input from the engine.

Explaining the collinear chart here, the collinear chart shows that the number of teeth is distributed on the horizontal axis, and the rotational speed of each element is expressed in the vertical direction on the points distributed by the ratio of the number of teeth. It was done,
The rotation speed of each element is always represented by a linear relationship proportional to the gear ratio. When two sets of planetary gear trains are combined in such a manner that the ring gear and the carrier of the first planetary gear train P1 are shared by the ring gear and the carrier of the second planetary gear train P2 as in this embodiment, the input and output sides are combined. First as connectable element
A sun gear S1 of the planetary gear train P1, a sun gear S2 of the second planetary gear train P2, a carrier C shared by the planetary gear trains,
There are four elements of the ring gear R (five elements if the ring gear R3 is added). Such a compound planetary gear mechanism is a so-called Ravigneawx planetary gear system.
set). This compound planetary gear mechanism has two degrees of freedom, that is, when the rotational speed of any two elements is determined, the rotational speeds of other elements are determined.

When the input from the engine and the output to the drive system are assigned to any two of the four elements other than the ring gear R3 and the motor / generator is connected to each of the remaining two elements, the input and the output are separated. There are a wide range of speed combinations of the two motors / generators that provide some speed ratio. Therefore, it is possible to select a combination from among the combinations in which the energy to be borne on the motor / generator side is minimized. Particularly, in the present embodiment, the input In from the engine and the output Out to the drive system are assigned to the inner two elements of the alignment graph, and the motor / generators MGo and MGi are connected to the respective outer two elements sandwiching them. Therefore, the torque that the motor / generator side bears with respect to the engine output can be further reduced.
Since the energy passing through the generator can be made smaller, the transmission efficiency of the drive device can be effectively improved.

On the other hand, the fifth element, the ring gear R3
Is braked by brake B, STA of the alignment chart
As can be seen in the RT characteristic line, it functions as a speed reducer that transmits the rotations of the three drive sources that have been reduced at individual reduction ratios to the carrier C that is connected to the drive system, and thus is a power source with a relatively small output. It is possible to secure good starting performance.

More specifically, when the vehicle is moving forward, in the brake-on state in which the ring gear R3 is braked, the second motor / generator MGo is rotated forward, the engine (input In) is rotated forward, and the first motor is rotated. / Generator MG
When i is generated in the reverse rotation side, a positive torque is generated in the output portion Out. At this time, the torque output from the two motors / generators MGi and MGo and the input In is amplified by the respective ratios and output Out.
And a large driving force is obtained.

When it is attempted to increase the output rotation by turning on the brake, two motor / generators MGi and MGo are used.
And the engine becomes high rotation, and the rotation of the output Out cannot be sufficiently increased due to the respective rotation limits. Therefore, in this case, the brake is turned off so that the ring gear R3 can rotate, and the first motor / generator MGi
The output rotation can be increased without increasing the rotation on the input In side by changing the rotation of the above from reverse rotation to stop and normal rotation.

The maximum drive force that can be generated is larger when the brake is on than when it is off, but it is smooth by controlling the output torque of the motor / generator so as to reduce the change in the drive force when the brake is turned off. Driving force characteristics can be obtained.

When the brake is turned on, the torque can be transmitted to the output Out by generating the torque in any one of the drive sources, and both motors / generators can be turned from the out state.

When the brake is off, one motor / generator generates electric power, and the electric power drives the other motor / generator. At this time, by controlling the rotational speeds and torques of the two motors / generators, it is possible to obtain an arbitrary gear ratio (ratio between the rotational speed of the input In and the rotational speed of the output Out) while keeping the balance of the electric power. Yes (see MAX in collinear chart). It is also possible to output more than the engine power by increasing the output on the drive side.

Further, when the brake is off, there are two gear ratios at which the rotation of the first or second motor / generator becomes zero, and at these two points, operation can be performed without electrically transmitting power. In addition, in the gear ratio between these two points, the ratio of electrically transmitted power, which is less efficient than mechanical transmission, to the power transmitted as the transmission can be reduced, so that the transmission efficiency can be improved. it can. Besides this,
It is also possible to use two motors / generators MGi and MGo for driving to output an output, so that electric running is possible.
At this time, by releasing the engagement of the input clutch CL,
You can drive with low friction without dragging the engine.

When the vehicle is moving backward, when the brake is turned on, the second motor / generator MGo is generated in the reverse rotation side and the first motor / generator MGi is generated in the normal rotation side. Can be generated. As a result, when the output is reversed, the engine rotation also reverses, so the clutch is turned off at this time. In this case, the one-way clutch CLo for preventing reverse rotation is not provided.

With both the brake and clutch off,
By driving both motors / generators MGi and MGo in the reverse rotation direction, electric running can be performed. When the clutch is on and the brake is off, the first motor / generator MGi is driven in the reverse rotation direction and the second motor / generator MGo generates electric power, whereby the electric power can be operated in a balanced state. .

FIG. 2 shows the maximum driving force in various states when the above configuration is applied to a hybrid vehicle, and FIG. 3 shows the ratio of the motor / generator passing power to the transmission power (output sharing ratio) in a state where the power balance is balanced. ) Is represented.
In FIG. 2, a1 and a2 are maximum driving force characteristics when the battery power is used when the brake B is not used and when it is not used. On the other hand, b1 and b
2 is the maximum driving force characteristic when the battery power when the brake B is used is used and when it is not used. As shown in the figure, by using the brake, a large driving force can be obtained in a low speed range including starting. Note that c is the maximum driving force characteristic during electric traveling using only the power of the motor / generator,
Reference character d denotes a driving force characteristic when the driving force is controlled so as to change smoothly.

On the other hand, "present invention (1)" and "present invention" in FIG.
(2) ”is different only in the setting of the final deceleration stage of the vehicle, and both can be operated in a state where the output sharing ratio of the motor / generator is 30% or less in most of the vehicle speed range. As can be seen from these drawings, according to the present invention, a motor / generator having a lower output can be applied and transmission efficiency can be improved as compared with the related art. Note that "SHV" in FIG. 3 is a series hybrid vehicle, and since the entire engine output is used to drive the generator, the output sharing ratio is always 1.

[FIGS. 4 to 7: Embodiments 2 to 5] FIGS. 4 to 7
2 shows another embodiment of a drive device having a configuration in which one element is provided with a brake in a differential device having five elements as in FIG. In the following, only parts different from FIG. 1 will be mainly described.

In the second embodiment shown in FIG. 4, the P1 sun gear S1 is connected to the outer rotor shaft Jmo, and the P2 sun gear S2 is connected to the inner rotor shaft Jmi. Note that Fw in the figure is a flywheel of the engine.

The third embodiment shown in FIG. 5 is provided with two independent motor / generators MGi and MGo.

In the fourth embodiment shown in FIG. 6, the first planetary gear train P1 in which the sun gear S1 is connected to the inner rotor shaft Jmi is a double pinion type, and the second planetary gear train P2 is in the sun gear S2 is connected to the outer rotor shaft Jmo. The planetary gear train P2 is of single pinion type.

In the fifth embodiment shown in FIG. 7, the carrier shaft Jc is connected as an input shaft to the engine output shaft Je via a clutch CL, and the ring gear shaft Jr is used as an output shaft for final deceleration via a reduction gear Rg. It is connected to the device Fin.

[FIG. 8: Embodiment 6 (4 elements-1 brake)] FIG. 8 shows four elements of a differential device having two degrees of freedom and four elements, in order of rotation speed, motor / generator MGo and input In. , Output Out, and a sixth embodiment in which the motor / generator MGi and the brake B are connected. A common ring gear R and a carrier C are provided, the common carrier C is connected to an engine output shaft Je via a clutch CL, and a rotor shaft Jmi of a motor / generator MGi is braked by a brake B. This embodiment is
The same as the above-described embodiment except that the motor / generator MGi cannot rotate when the brake is turned on. Figure 9
The driving force characteristics according to this embodiment are shown in FIG. The symbols in the figure have the same meanings as in FIG. Further, the ratio of the motor / generator passing power to the transmitted power in the state where the power balance is balanced is the same as in FIG.

[FIGS. 10 to 13: Embodiments 7 to 10] FIG.
0 to 13 show the seventh to tenth aspects related to the embodiment of FIG. 8.
2 shows an embodiment of the present invention. The embodiment of FIGS. 10 and 11 corresponds to FIG.
The two planetary gear trains P1 and P2 are both of the single pinion type, and the ring gear R
1, R2, a common sun gear S, P
2 ring gear R2 to the second motor / generator MG
The difference is that a brake B that is connected to o and brakes the rotation axis Jr2 is provided. FIG. 10 is different in that it further includes two independent motor / generators MGo and MGi.

In the embodiment of FIG. 12, the first planetary gear train P1 is used.
And the second planetary gear train P2 are used in common to brake the carrier C by the brake B. In the embodiment of FIG. 13, the first planetary gear train P1 and the second planetary gear train P2 are commonly used. The ring gear R is braked by the brake B.

[FIG. 14: Embodiment 11 (3 elements-1 brake)] In FIG. 14, three elements of a differential device having two degrees of freedom and three elements are arranged in order of rotational speed in order of input In and motor / generator MGi. , Output Out, Motor / Generator MGo
It is an eleventh embodiment in which a brake B and a brake B are connected. The sun gear S and the carrier C of the single double-pinion type planetary gear train P are respectively motor / generators MGo and MG.
i, the carrier shaft Jc is connected to the engine output shaft Je via the clutch CL, and the ring gear shaft Jr.
Is connected to the final reduction gear Fin through a reduction gear Rg. The brake B brakes the sun gear shaft Js. In this embodiment, when the brake is turned on, the motor / generator M
It is the same as the above-described embodiment except that Go cannot rotate, and that there is only one operating point at which the passing power of the motor / generator becomes zero. FIG. 15 shows the output sharing ratio when the power balance is balanced.

[FIGS. 16-18: Embodiments 12-14] FIGS. 16-18 show the twelfth-first embodiment related to the embodiment of FIG.
4 shows four embodiments. In the embodiment of FIG. 16, the sun gear S and the ring gear R of the single planetary gear train P of the single pinion type are provided to the motor / generators MGo and MGi, respectively.
, The ring gear shaft Jr is connected to the engine output shaft Je, and the carrier shaft Jc is connected to the final reduction gear Fin via the reduction gear Rg. The brake B brakes the sun gear shaft Js. In the embodiment of FIG. 17, the planetary gear train P
Of the sun gear S and the ring gear R are connected to the motor / generators MGi and MGo, respectively, the carrier shaft Jc is connected to the engine output shaft Je, and the ring gear shaft Jr is connected to the final reduction gear Fin through the reduction gear Rg. .
The brake B brakes the carrier shaft Jc. In the embodiment of FIG. 18, the sun gear S and the ring gear R of the planetary gear train P are connected to motors / generators MGi and MGo, respectively.
The sun gear shaft Js is connected to the engine output shaft Je, and the carrier shaft Jc is connected to the final reduction gear F via the reduction gear Rg.
connected to in. The brake B brakes the sun gear shaft Js.

[FIGS. 19 and 20: Embodiments 15 and 16 (4
Element-2 Brake)] FIG. 19 shows a four-element differential device having two degrees of freedom, in which the brake B1, the input In and the motor / generator MGi, the output Out and the motor / generator MGo, and the brake B2 are connected in order of rotational speed. It is an embodiment. The ring gear R is composed of the first planetary gear train P1 of the single pinion type and the second planetary gear train P2 of the double pinion type.
And the carrier C, the carrier shaft Jc is connected to the motor / generator MGi and the engine output shaft Je, the ring gear shaft Jr is connected to the motor / generator MGo, and the final reduction gear Fin is connected via the reduction gear Rg. is doing. Further, the first sun gear shaft Js1 is the first brake B1 and the second sun gear shaft Js2 is the second brake B2.
Then, brake each. In this embodiment, when the two brakes B1 and B2 are off, the input In and the output Ou are output.
Since t does not affect rotation or torque, they function as a series hybrid. When the brake B1 adjacent to the input In is engaged, it can be driven with a fixed gear ratio of overdrive, and when the brake B2 adjacent to the output Out is engaged, it can be driven with a fixed gear ratio of low. If the engine rotation transmission to the carrier shaft Jc is disengaged by the clutch, the backward movement can be driven by fixing the low gear using two motors / generators. By eliminating the brake B1 of this configuration and the sun gear S1 fixed to B1, a three-element differential device with two degrees of freedom is provided in order of rotational speed.
It is a drive device that connects the input and the motor / generator, the output and the motor / generator, and the brake. The operation in this case is the same except that there is no fixed gear ratio for the above-mentioned overdrive.

FIG. 20 shows an embodiment related to the embodiment shown in FIG. In this embodiment, in order of rotation speed,
Input In, Motor / Generator MGi, Brake B
1. The output Out is connected to the motor / generator MGo and the brake B2. The ring gear R and the carrier C are shared by the first planetary gear train P1 and the second planetary gear train P2, the motor / generator MGo is coupled to the carrier shaft Jc, and the final reduction gear Fin is coupled via the reduction gear Rg. The second sun gear shaft Js2 is connected to the engine output shaft Je via the clutch CL and is also connected to the motor / generator MGi. Brake B1 is ring gear shaft J
r, and the second brake B2 brakes the first sun gear shaft Js1.

In this embodiment, a low fixed gear ratio can be obtained regardless of which brake is engaged, and in particular, when B1 is engaged, retraction can be performed at a fixed low gear ratio.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram of a first embodiment of the present invention.

FIG. 2 is a characteristic diagram showing maximum driving force characteristics in various states according to the embodiment.

FIG. 3 is a characteristic diagram showing an output sharing characteristic of an electromechanical system with respect to an engine output according to the embodiment in relation to a vehicle speed.

FIG. 4 is a schematic configuration diagram of a second embodiment of the present invention.

FIG. 5 is a schematic configuration diagram of a third embodiment of the present invention.

FIG. 6 is a schematic configuration diagram of a fourth embodiment of the present invention.

FIG. 7 is a schematic configuration diagram of a fifth embodiment of the present invention.

FIG. 8 is a schematic configuration diagram of a sixth embodiment of the present invention.

FIG. 9 is a characteristic diagram showing maximum driving force characteristics in various states according to the sixth embodiment.

FIG. 10 is a schematic configuration diagram of a seventh embodiment of the present invention.

FIG. 11 is a schematic configuration diagram of an eighth embodiment of the present invention.

FIG. 12 is a schematic configuration diagram of a ninth embodiment of the present invention.

FIG. 13 is a schematic configuration diagram of a tenth embodiment of the present invention.

FIG. 14 is a schematic configuration diagram of an eleventh embodiment of the present invention.

FIG. 15 is a characteristic diagram showing an output sharing characteristic of an electromechanical system with respect to an engine output according to the eleventh embodiment in relation to a speed ratio (reciprocal of a gear ratio).

FIG. 16 is a schematic configuration diagram of a twelfth embodiment of the present invention.

FIG. 17 is a schematic configuration diagram of a thirteenth embodiment of the present invention.

FIG. 18 is a schematic configuration diagram of a fourteenth embodiment of the present invention.

FIG. 19 is a schematic configuration diagram of a fifteenth embodiment of the present invention.

FIG. 20 is a schematic configuration diagram of a sixteenth embodiment of the present invention.

[Explanation of symbols]

P1 1st planetary gear train P2 Second planetary gear train S, S1, S2 sun gear R, R1, R2 ring gear C, C1, C2 carriers (planet carriers) p, pi, po pinion CL clutch B, B1, B2 brake CLo one-way clutch Fw flywheel MGo 1st (outer) motor generator MGi second (inner) motor generator Cm, Cmi, Cmo coil Hc clutch housing Hm motor housing Ct transmission casing Ha axle housing Ssi, Sso rotation sensor Rg reducer Fin final reduction gear Drv drive axle

Front page continued (51) Int.Cl. ⁷ Identification code FI theme code (reference) // B60K 6/02 F16H 59:06 F16H 59:06 59:14 59:14 B60K 9/00 E (72) Inventor Shinobu Sinichi 2 Takara-cho, Kanagawa-ku, Yokohama, Kanagawa Nissan Motor Co., Ltd. (72) Inventor Masaki Nakano 2 Takara-cho, Kanagawa-ku, Yokohama, Kanagawa Nissan Motor Co., Ltd. (72) Cayban Calgar France 78230 Rupek Ru De Prédignon Wilson 36 (72) Inventor Joel Pupane France 75013 Paris Luluel 22 F Term (reference) 3D039 AA02 AA04 AB26 AC03 AC24 AC39 AC74 AD02 AD23 3J028 EA25 EA27 EB04 EB10 EB31 EB37 FB62 EB63 EB66 FCFB24 FC13 FC04 FC13 FC13 FC04 FC64 GA02 GA40 HA12 HC08 3J552 MA02 MA11 MA30 NA01 NB01 NB05 NB08 PA32 PA59 PA67 RB17 SA03 UA07 UA08 VA02W VA32W VA39W VA39Y VB01W VC02W 5H115 PA01 PA11 PG04 PU24 SE04 SE08 SE09 TB00

Claims (21)

[Claims] 1. A two-degree-of-freedom differential device having four or more input / output elements, wherein each element is individually assigned an input from an engine, an output to a drive system, and two motors / generators. A drive device characterized in that a brake is provided on an element other than an element to which an output is assigned. 2. The drive device according to claim 1, wherein a motor / generator, an input, an output, and a motor / generator are assigned in the order of rotation speeds of the elements. 3. The drive device according to claim 1, wherein a brake is provided in an element adjacent to the element to which the output is assigned. 4. The differential device according to claim 1, wherein the differential device comprises four elements, and the four elements are assigned to a motor / generator, an input, an output, a motor / generator and a brake in order of rotational speed. The drive device according to any one of 3 above. 5. The differential device comprises five elements, and the five elements are assigned to a motor / generator, an input, an output, a brake, and a motor / generator in order of rotational speed. The drive device according to any one of 3 above. 6. The differential device according to claim 1, wherein the differential device includes five elements, and the five elements are assigned a motor / generator, an input, a brake, an output, and a motor / generator in order of rotational speed. The drive device according to any one of 3 above. 7. The drive device according to claim 1, further comprising a clutch provided between the engine and the input element. 8. A two-degree-of-freedom differential having three or more elements, which is input from an engine, output to a drive system, and 2.
2 motors / generators with input and output
A drive device characterized in that the motors / generators are assigned so that they are not coupled to the same element, and a brake is provided on the element to which the input is assigned. 9. The differential according to claim 8, wherein the differential device includes three elements, and the three elements are assigned to a motor / generator, an input and a brake, and an output and a motor / generator in the order of rotational speed. Drive. 10. The differential device comprises three elements, the three elements
The drive device according to claim 8, wherein a motor / generator, an input and a brake, an output, and a motor / generator are assigned to the respective elements in the order of rotation speed. 11. The differential device comprises four elements, the four elements comprising:
9. The drive device according to claim 1, wherein a motor / generator, an input and a brake, an output, and a motor / generator are assigned to these elements in the order of rotational speed. 12. An input from an engine and an output to a drive system are assigned to different elements of a two-degree-of-freedom differential having three or more elements, and a motor / generator is assigned to both the input and the output. , A drive device characterized in that a brake is provided on an element other than an element to which inputs and outputs are assigned. 13. The differential device comprises three elements, the three elements
The drive device according to claim 12, wherein an input and a motor / generator, an output and a motor / generator, and a brake are assigned to these elements in the order of rotational speed. 14. The differential device comprises three elements, the three elements
Brake, input and motor /
The drive device according to claim 12, wherein a generator, an output and a motor / generator are assigned. 15. The differential device comprises four elements, the four elements comprising:
Brake, input and motor /
The drive device according to claim 12, wherein a generator, an output, a motor / generator, and a brake are assigned. 16. The differential device comprises four elements, the four elements comprising:
The drive device according to claim 12, wherein an input and a motor / generator, a brake, and an output and a motor / generator and a brake are assigned to these elements in the order of rotation speed. 17. A drive system characterized in that an input and a motor / generator, an output, and a motor / generator and a brake are assigned to three elements of a differential device having three or more elements in order of rotational speed. 18. The drive device according to claim 1, wherein the brake is engaged when a required driving force is large. 19. When the brake is applied, the driving force generated by the motor / generator is reduced in accordance with the increase in vehicle speed so that the transmission force of the brake becomes close to zero under the operation condition of the brake off. The drive device according to any one of claims 1, 8, 12, and 17, wherein the driving force difference is reduced. 20. The drive device according to claim 1, wherein the differential device comprises a planetary gear mechanism. 21. The planetary gear mechanism includes a first planetary gear train of a single pinion type and a second planetary gear train of a double pinion type, wherein any two elements of a sun gear, a carrier and a ring gear are provided. The drive device according to claim 20, wherein the drive device is shared to form a differential device having two degrees of freedom.