JP2006183861A - Hybrid transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hybrid transmission capable of operating an oil pump without using a power source different from a drive source.
SOLUTION: An input In, an output Out, a first motor generator MG1, and a second motor generator MG2 are fastened to separate rotation elements on a collinear diagram representing the rotation relationship of each rotation element of a Ravigneaux planetary gear train PGR. In the hybrid transmission, the low brake LB, the high brake HB, or the high brake HB among the five rotation elements of the first sun gear Sd, the first ring gear Rd, the second sun gear Ss, the second ring gear Rs, and the common carrier C In addition to the rotating element to which the output is connected, a mechanical oil pump O / P is provided.
[Selection] Figure 1

Description

  The present invention relates to a hybrid transmission in which two input, output, and motor generators are fastened to separate rotating elements on a collinear diagram representing the rotational relationship of each rotating element of the differential gear, and in particular, a technology for installing a mechanical oil pump. About.

Conventionally, for hybrid transmissions in which two input / output / motor generators are fastened to separate rotating elements on a collinear diagram representing the rotational relationship of each rotating element of the differential gear, for lubrication of a system having an idle stop function. In general, an oil pump is operated by using a separate motor as a power source. (For example, refer to Patent Document 1).
JP 2003-34154 A

  However, in a vehicle equipped with a conventional hybrid transmission and operating an oil pump using a separate motor as a power source, there is a problem that if the oil pump motor breaks down, it may become impossible to travel and costs increase. .

  That is, in a normal hybrid transmission, when stopping the vehicle, the motor generator must be stopped to stop the vehicle. Therefore, even if an oil pump is installed on any rotating element, the oil pump also stops when the vehicle stops. End up. For this reason, since it is impossible to fasten lubrication, brakes, or the like when starting, it is necessary to provide a power source for the oil pump separately from the driving force source. In addition, the oil pump could not be operated during reverse. This makes the unit configuration (oil path, etc.) complicated because it is necessary to install a power source for the oil pump, unlike conventional automatic transmissions that can rotate the oil pump by idling. Increase the unit size and increase the cost.

  The present invention has been made paying attention to the above problems, and an object of the present invention is to provide a hybrid transmission capable of operating an oil pump without using a power source different from a drive source.

In order to achieve the above object, in the present invention, in a hybrid transmission in which two input, output, and two motor generators are fastened to separate rotating elements on a collinear diagram representing the rotational relationship of each rotating element of the differential device,
Among the rotating elements, a mechanical oil pump is provided in addition to a brake or a rotating element to which an output is connected.

  Therefore, in the hybrid transmission of the present invention, a mechanical oil pump is provided in addition to the rotating element to which the brake or the output is connected among the rotating elements. That is, if a mechanical oil pump is provided in the rotating element to which the brake is connected, the mechanical oil pump is also stopped when the brake is engaged, where the rotating element of the case is fixed. Further, when a mechanical oil pump is provided in the rotating element to which the output is connected, the mechanical oil pump is also stopped when the output rotation is zero. Therefore, by providing a mechanical oil pump in addition to the rotating element to which the brake or output is connected, the oil pump can be operated without using a power source different from the drive source.

  Hereinafter, the best mode for carrying out the hybrid transmission of the present invention will be described based on Examples 1 to 14 shown in the drawings.

First, the configuration will be described.
FIG. 1 is an overall cross-sectional view showing a hybrid transmission according to a first embodiment. An engine (input), a first motor generator MG1, a second motor generator MG2, and an output gear OG (output) (not shown) are connected to the hybrid transmission of the first embodiment.

  The first motor generator MG1 and the second motor generator MG2 are synchronous motor generators in which a permanent magnet is embedded in a rotor and a stator coil is wound around a stator. This synchronous motor generator comprises a first motor generator MG1 composed of an inner rotor IR and a stator S, out of a multi-layer motor CM in which an inner rotor IR, a stator S and an outer rotor OR are overlapped in the radial direction. The OR and stator S constitute a second motor generator MG2. The inner rotor IR and the outer rotor OR are independently applied to the stator S by applying a composite current composed of two three-phase alternating currents generated by an inverter based on a control command from a motor controller (not shown). Controlled.

  The hybrid transmission includes a Ravigneaux planetary gear train PGR (differential device), a low brake LB, and a high brake HB. The Ravigneaux type planetary gear train PGR has five rotating elements: a first sun gear Sd, a first ring gear Rd, a second sun gear Ss, a second ring gear Rs, and a common carrier C.

  The connection relationship of input / output elements with respect to these five rotating elements will be described. An inner rotor IR (first motor generator MG1) is connected to the first sun gear Sd, and a high brake HB that can be fixed to the transmission case TC is connected to the first sun gear Sd. A low brake LB that can be fixed to the transmission case TC is connected to the first ring gear Rd. An outer rotor OR (second motor generator MG2) is connected to the second sun gear Ss. An engine (not shown) is connected to the second ring gear Rs via a mechanical oil pump O / P and an engine clutch EC. An output gear OG is directly connected to the common carrier C.

  A first counter gear CG1 meshes with the output gear OG, and a second counter gear CG2 provided via a countershaft CS meshes with a drive gear DG. A driving force is transmitted to the driving wheels.

  Due to the above connection relationship, the first motor generator MG1 (first sun gear Sd), the engine input In (second ring gear Rs), the gear output Out (common carrier C), and the second motor generator on the alignment chart shown in FIG. It is possible to introduce a rigid lever model that is arranged in the order of MG2 (second sun gear Ss) and can simply express the dynamic operation of the Ravigneaux planetary gear train PGR. Here, the “collinear diagram” is a velocity diagram used in a simple and easy-to-understand method of drawing instead of the method of obtaining by equation when considering the gear ratio of the differential gear, Take the number of rotations (rotation speed) of the rotating elements, take each rotating element on the horizontal axis, and set the interval between each rotating element to the collinear lever ratio (α: 1: β) based on the gear ratio of the sun gear and ring gear (See FIG. 3).

  The engine clutch EC, the low brake LB, and the high brake HB are a multi-plate friction clutch and a multi-plate friction brake that are fastened by hydraulic pressure from a hydraulic control device. The engine clutch EC is arranged at a position that coincides with the rotational speed axis of the second ring gear Rs on the alignment chart of FIG. 2, and the low brake LB is located on the first ring gear Rd of the alignment chart of FIG. The high brake HB is disposed on the rotational speed axis, and the high brake HB is disposed on the rotational speed axis of the first sun gear Sd on the alignment chart of FIG.

Next, the operation will be described.
[Calculation of required torque for each motor generator]
First, the gear ratio of the hybrid transmission of the first embodiment shown in FIG.
1 gear ratio from engine to output gear OG
The gear ratio from the engine to the first motor generator MG1 is α
The gear ratio from the output gear OG to the second motor generator MG2 is β
(See FIG. 3).

  Here, it is a continuously variable transmission ratio mode in which the low brake LB and the high brake HB are released based on a nomographic chart representing the rotational relationship of the rotating elements of the Ravigneaux type planetary gear train PGR of the first embodiment shown in FIG. The calculation of the required torque of each motor generator MG1, MG2 during direct power distribution that minimizes battery consumption will be described.

When the target torque To for tire output is specified, the target gear ratio i (= Ne / No), target motor torque, target motor speed, target engine torque Te, and target engine speed Ne are set so as to achieve these. .
At this time, the target torque To of the tire output, the target engine torque Te, the target engine speed Ne, the target output speed No, and the target speed ratio i (= Ne / No) are determined by a torque map or the like.
No = Ne × (1 / i)… (1)
Each motor speed N1, N2 is
N1 ＝ Ne ＋ α (Ne-No)… (2)
N2 ＝ No−β (Ne-No)… (3)
It is represented by
Also, the balance on the nomograph can be expressed by the following equation, assuming that the torque of each motor is T1 and T2.
The balance in the vertical direction of the torque is
To = T1 + T2 + Te (4)
The balance of motor power is
N1 / T1 + N2 / T2 = Pb (5)
The torque balance in the direction of lever rotation around the engine is
αT1 + To = (1 + β) T2 (6)
It becomes.
Solving these, and assuming battery power Pb = 0 (theoretically, battery power consumption is zero)
T1 ＝ [N2 / {β ・ N1 + (α + 1) ・ N2}] ・ Te… (7)
T2 = [N1 / {β ・ N1 + (α + 1) ・ N2}] ・ Te… (8)
It becomes. The required torque of the motor corresponding to the torque at each engine speed can be calculated from the above equation.

The speed and torque of each motor generator required when the vehicle speed is 0 [km / h], if the minimum required speed of the mechanical oil pump O / P installed on the engine input shaft is x [rpm]
N1 = (α + 1) · x
N2 = −β · x (9)
It becomes. The required torques T1 and T2 of the motor generators MG1 and MG2 at this time release the engine clutch EC, and the required torque of the mechanical oil pump O / P is Top,
(α + 1) T1 = (β) T2 + Top (10)
It is determined to satisfy
The engine G input shaft torque Tin when the engine clutch EC is engaged is
Tin ＝ Te−Top… (11)
It becomes. The required torques T1 and T2 of motor generators MG1 and MG2 at this time are
(α + 1) T1 = (β) T2 + Tin (12)
It is determined to satisfy

[Oil pump action]
In the hybrid transmission of the first embodiment, in the hybrid transmission in which the first motor generator MG1, the engine input In, the gear output Out, and the second motor generator MG2 are arranged on the alignment chart, the low brake LB, the high brake HB, Since the mechanical oil pump O / P is installed in an input element (engine input In) other than the gear output Out, the shift range can be increased even though the input shaft rotation direction is limited to the positive direction.

The operation at start is shown below.
1. All rotation elements have zero rotation speed.
2. Control the speed of each motor generator MG1 and MG2 so that the number of revolutions of the output element at the time of start is controlled to zero and the oil pump speed becomes the required speed.
3. Start with the motor generator output (If the required driving force is large, slip the low brake LB and accelerate).
At this time, if the specification is such that the low brake LB is fastened without hydraulic pressure, a large driving force can be obtained from the start.

Next, the effect will be described.
In the hybrid transmission of the first embodiment, the effects listed below can be obtained.

  (1) Among the five rotating elements of the Ravigneaux planetary gear train PGR, a mechanical oil pump O / P is provided in addition to the low brake LB, the high brake HB, or the rotating element to which the output is connected. In other words, when the vehicle speed is zero or when the brake LB or HB is operated, the mechanical oil pump O / P is installed in an element that does not necessarily need to be at zero speed. The mechanical oil pump O / P can be operated without operating the oil pump by using a power source different from the drive source.

  (2) A mechanical oil pump O / P was installed on the rotating element close to the output among the five rotating elements of the Ravigneaux planetary gear train PGR. In other words, the shift range of the mechanical oil pump O / P can be increased because the rotating element of the mechanical oil pump O / P is close to the output.

  (3) Among the five rotating elements of the Ravigneaux planetary gear train PGR, a mechanical oil pump O / P is provided on the second ring gear Rs to which the engine input shaft is connected. For this reason, since the engine input point is controlled to always keep the forward rotation, even if there is no clutch, it is possible to shift without reverse rotation of the engine and to generate hydraulic pressure.

  (4) Among the five rotating elements of the Ravigneaux planetary gear train PGR, the rotating elements (second ring gear Rs) provided with the mechanical oil pump O / P are rotated so that the rotational speed is always positive. The number (gear ratio) is controlled. For this reason, the mechanical oil pump O / P can always be operated even when the vehicle speed is zero or when the vehicle is moving backward.

  The second embodiment is an example in which a mechanical oil pump is set at the position of the high brake in the first embodiment.

  First, the configuration will be described. The Ravigneaux planetary gear train PGR of the hybrid transmission of the second embodiment, as shown in FIG. 4, is similar to the first embodiment, in which the first sun gear Sd, the first ring gear Rd, It has five rotating elements, that is, a two sun gear Ss, a second ring gear Rs, and a common carrier C.

  The connection relationship of input / output elements with respect to these five rotating elements will be described. An inner rotor IR (first motor generator MG1) is connected to the first sun gear Sd, and a mechanical oil pump O / P is provided between the connection hollow shaft and the transmission case TC. A low brake LB that can be fixed to the transmission case TC is connected to the first ring gear Rd. An outer rotor OR (second motor generator MG2) is connected to the second sun gear Ss. An engine (not shown) is connected to the second ring gear Rs via an engine clutch EC. An output gear OG is directly connected to the common carrier C.

  Due to the above connection relationship, the first motor generator MG1 (first sun gear Sd), the engine input In (second ring gear Rs), the gear output Out (common carrier C), the second motor generator on the alignment chart shown in FIG. It is possible to introduce a rigid lever model that is arranged in the order of MG2 (second sun gear Ss) and can simply express the dynamic operation of the Ravigneaux planetary gear train PGR. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.

  Next, the operation will be described. According to the hybrid transmission of the second embodiment, even when the vehicle speed is zero or when the low brake LB is operated, the mechanical oil pump is not necessarily required to make the speed zero. By installing the O / P, the mechanical oil pump O / P can be operated at all times, and the mechanical oil pump O / P can be operated without operating the oil pump using a power source different from the drive source. Can be operable.

  In addition, since the mechanical oil pump O / P is provided in the rotating element far from the gear output Out on the alignment chart of FIG. 5, the low element provided on the rotating element (first ring gear Rd) close to the gear output Out on the alignment chart. The number of revolutions of the brake LB can be kept low when engaged. As a result, it is possible to reduce the engagement shock and perform a shift with little energy loss.

  Furthermore, since the mechanical oil pump O / P is provided at the position of the first motor generator MG1 far from the gear output Out on the nomogram of FIG. 5, the motor generator output can be reduced to set the required oil pump speed, In addition, there is little loss when the low brake LB is engaged because there are few steps.

  In addition, the vehicle speed is zero because the rotation speed (transmission ratio) of each rotation element is controlled so that the rotation speed of the rotation element (first sun gear Sd) installed with the mechanical oil pump O / P is always positive. It is possible to always operate the mechanical oil pump O / P even during reverse.

Next, the effect will be described.
In the hybrid transmission of the second embodiment, the effects listed below can be obtained in addition to the effects (1) and (4) of the first embodiment.

  (5) Since the mechanical oil pump O / P is provided on the rotating element far from the gear output Out on the nomograph, the low brake provided on the rotating element (first ring gear Rd) close to the gear output Out on the nomograph The rotational speed of the LB can be kept low at the time of engagement, the engagement shock can be reduced, and a shift with less energy loss can be performed.

  (6) Since the mechanical oil pump O / P is provided at the position of the first motor generator MG1 far from the gear output Out on the nomograph, the motor generator output can be reduced to set the required oil pump speed, Even when the low brake LB is engaged, there are few steps, so there is little loss.

  The third embodiment is an example in which a mechanical oil pump is set at the position of the second motor generator in the first embodiment.

  First, the configuration will be described. As shown in FIG. 6, the Ravigneaux type planetary gear train PGR of the hybrid transmission of the third embodiment is similar to the first embodiment in that the first sun gear Sd, the first ring gear Rd, It has five rotating elements, that is, a two sun gear Ss, a second ring gear Rs, and a common carrier C.

  The connection relationship of input / output elements with respect to these five rotating elements will be described. An inner rotor IR (first motor generator MG1) is connected to the first sun gear Sd, and a high brake HB that can be fixed to the transmission case TC is connected to the first sun gear Sd. A low brake LB that can be fixed to the transmission case TC is connected to the first ring gear Rd. An outer rotor OR (second motor generator MG2) is connected to the second sun gear Ss, and the connecting shaft is extended to the end position of the multilayer motor CM, and between the connecting shaft and the transmission case TC. A mechanical oil pump O / P is provided. An engine (not shown) is connected to the second ring gear Rs via an engine clutch EC. An output gear OG is directly connected to the common carrier C.

  Due to the above connection relationship, the first motor generator MG1 (first sun gear Sd), the engine input In (second ring gear Rs), the gear output Out (common carrier C), and the second motor generator on the alignment chart shown in FIG. It is possible to introduce a rigid lever model that is arranged in the order of MG2 (second sun gear Ss) and can simply express the dynamic operation of the Ravigneaux planetary gear train PGR. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.

  Next, the operation will be described. According to the hybrid transmission of the third embodiment, even when the vehicle speed is zero or when the low brake LB is operated, the mechanical oil pump is not necessarily required to make the speed zero. By installing the O / P, the mechanical oil pump O / P can be operated at all times, and the mechanical oil pump O / P can be operated without operating the oil pump using a power source different from the drive source. Can be operable.

  In addition, since the mechanical oil pump O / P is provided on the rotating element far from the gear output Out on the alignment chart of FIG. 7, the low element provided on the rotating element (first ring gear Rd) close to the gear output Out on the alignment chart. The number of revolutions of the brake LB can be kept low when engaged. As a result, it is possible to reduce the engagement shock and perform a shift with little energy loss.

  Furthermore, since the mechanical oil pump O / P is provided at the position of the first motor generator MG1 far from the gear output Out on the alignment chart of FIG. 7, the motor generator output can be reduced to set the required oil pump rotation speed. In addition, there is little loss when the low brake LB is engaged because there are few steps.

  In addition, the vehicle speed is zero because the rotation speed (speed ratio) of each rotation element is controlled so that the rotation speed of the rotation element (second sun gear Ss) where the mechanical oil pump O / P is installed is always positive. It is possible to always operate the mechanical oil pump O / P even during reverse.

  Next, the effects will be described. In the hybrid transmission of the third embodiment, the effects (1) and (4) of the first embodiment and the effects (5) and (6) of the second embodiment are obtained. be able to.

  In the fourth embodiment, instead of the Ravigneaux type planetary gear train used in the first to third embodiments as a differential device, three sets of planetary gear trains using three single pinion type planetary gears capable of setting a plurality of travel modes are provided. It is an example used.

First, the configuration will be described.
FIG. 8 is an overall cross-sectional view showing the hybrid transmission of the fourth embodiment. An engine (input), a first motor generator MG1, a second motor generator MG2, and an output gear OG (output) (not shown) are connected to the hybrid transmission of the fourth embodiment. As in the first embodiment, in the multilayer motor CM in which the inner rotor IR, the stator S, and the outer rotor OR are overlapped in the radial direction, the first motor generator MG1 includes the outer rotor OR and the stator S. The second motor generator MG2 includes an inner rotor IR and a stator S.

  The hybrid transmission includes three planetary gear trains PGS (differential gear) including a first planetary gear PG1, a second planetary gear PG2, and a third planetary gear PG3, a low brake LB, a high clutch HC, and a high-low brake HLB. Have The three planetary gear train PGS includes a first ring gear R1, a first carrier / third ring gear C1 / R3, a third carrier C3, a first sun gear / second sun gear S1 / S2, and a third sun gear. -It has six rotating elements of the second ring gears S3 and R2 and the second carrier C2.

  The connection relationship of input / output elements with respect to these six rotating elements will be described. An outer rotor OR (first motor generator MG1) is connected to the first ring gear R1, and a high / low brake HLB that can be fixed to the transmission case TC is connected to the first ring gear R1. An engine (not shown) is connected to the first carrier / third ring gear C1, R3 via a mechanical oil pump O / P and an engine clutch EC. An output shaft OUT is directly connected to the third carrier C3. An inner rotor IR (second motor generator MG2) is connected to the first sun gear / second sun gear S1, S2. The third sun gear and the second ring gear S3 / R2 are directly connected to each other. A low brake LB that can be fixed to the transmission case TC is connected to the second carrier C2, and a high clutch HC is interposed between the third sun gear S3 and the directly connected member of the second ring gear R2. ing. A driving force is transmitted from the output shaft OUT to the left and right driving wheels via a propeller shaft, a differential gear, and a drive shaft (not shown).

  Due to the above connection relationship, the first motor generator MG1 (first ring gear R1), engine input on the collinear diagram of the continuously variable transmission mode in which the low brake LB and the high / low brake HLB shown in FIG. In (first carrier / third ring gear C1, R3), output Out (third carrier C3), second motor generator MG2 (first sun gear / second sun gear S1, S2), low brake LB (second carrier C2) It is possible to introduce a rigid lever model that can be arranged in the order of and can easily express the dynamic operation of the three planetary gear train PGS. The third sun gear S3 and the second ring gear R2 are connected by a direct connection member.

  The collinear diagram of FIG. 9 is drawn by three levers representing the rotational relationships of the first planetary gear PG1, the second planetary gear PG2, and the third planetary gear PG3 and the direct connection member, and the gear ratio of the first planetary gear PG1. Is α, the gear ratio of the second planetary gear PG2 is δ, and the gear ratio of the third planetary gear PG3 is β, the horizontal axis of the collinear chart is the lever ratio of (α: 1: β: 1: δ) It is arranged to be.

  The engine clutch EC is a clutch that is mechanically engaged and released, and the low brake LB, the high / low brake HLB, and the high clutch HC are a multi-plate friction clutch and a multi-plate friction brake that are engaged by hydraulic pressure from a hydraulic control device. It is.

Next, the operation will be described.
In the hybrid transmission of the fourth embodiment, the mechanical oil pump O / P is provided in addition to the low brake LB, the high / low brake HLB, or the rotary element to which the output is connected among the six rotary elements of the three planetary gear train PGS. . In other words, even when the vehicle speed is zero or when the brake LB or HLB is operated, the mechanical oil pump O / P is installed in an element that does not necessarily require zero speed. The mechanical oil pump O / P can be operated without operating the oil pump by using a power source different from the drive source.

  Further, as shown in FIG. 9, a mechanical oil pump O / P is provided on a rotating element close to the output among the six rotating elements of the three planetary gear train PGS. In other words, the shift range of the mechanical oil pump O / P is close to the output, so that the shift range can be increased.

  Further, among the six rotating elements of the three planetary gear train PGS, the mechanical oil pump O / P is provided on the rotating elements of the first carrier and the third ring gears C1 and R3 to which the engine input shaft is connected. For this reason, since the engine input point is controlled to always keep the forward rotation, even if there is no clutch, it is possible to shift without reverse rotation of the engine and to generate hydraulic pressure.

  In addition, among the six rotating elements of the three planetary gear train PGS, the rotational speed of the rotating elements (first carrier, third ring gear C1, R3) provided with the mechanical oil pump O / P is always positive. In addition, the rotational speed (transmission ratio) of each rotating element is controlled. For this reason, the mechanical oil pump O / P can always be operated even when the vehicle speed is zero or when the vehicle is moving backward.

  Next, the effects will be described. In the hybrid transmission of the fourth embodiment, the effects (1), (2), (3), (4) of the first embodiment can be obtained.

  The fifth embodiment is an example in which a mechanical oil pump is set at the position of the engine input shaft when the differential gear is a three-set planetary gear train capable of setting a plurality of travel modes.

  First, the configuration will be described. As shown in FIG. 10, the Ravigneaux type planetary gear train PGR of the hybrid transmission according to the third embodiment is composed of a first planetary gear train PGS, a first sun gear S1, a third carrier gear train PGS. There are six rotational elements of sun gear C1, S3, third carrier C3, first ring gear / second sun gear R1, S2, second ring gear / third ring gear R2 / R3, and second carrier C2.

  The connection relationship of input / output elements with respect to these six rotating elements will be described. An outer rotor OR (first motor generator MG1) is connected to the first sun gear S1. The first carrier / third sun gear C1, S3 is provided with a mechanical oil pump O / P between an engine input shaft and a transmission case, and an engine (not shown) is connected via a flywheel. An output shaft OUT is directly connected to the third carrier C3. An inner rotor IR (second motor generator MG2) is connected to the first ring gear / second sun gear R1, S2. The second ring gear and the third ring gear R2 and R3 are directly connected to each other. A low brake LB that can be fixed to the transmission case TC is connected to the second carrier C2, and a high clutch HC is interposed between the second ring gear R2 and the direct connection member of the third ring gear R3. ing. A driving force is transmitted from the output shaft OUT to the left and right driving wheels via a propeller shaft, a differential gear, and a drive shaft (not shown).

  In the collinear diagram of the continuously variable transmission mode in which the low brake LB shown in FIG. 11 is engaged and the high clutch HC is released, the first motor generator MG1 (first sun gear S1) and the engine input In (first Carrier, third sun gear C1, S3), output Out (third carrier C3), second motor generator MG2 (first ring gear, second sun gear R1, S2), low brake LB (second carrier C2) It is possible to introduce a rigid lever model that can easily express the dynamic operation of the three sets of planetary gear trains PGS. The third ring gear R3 and the second ring gear R2 are connected by a direct connection member.

  Next, functions and effects will be described. In the hybrid transmission according to the fifth embodiment, the same functions and effects as those of the fourth embodiment can be obtained.

  Example 6 is an example in which a mechanical oil pump is set at the position of the engine input shaft in the case where the differential device is a Ravigneaux type planetary gear train.

  First, the configuration will be described. As shown in FIG. 12, the Ravigneaux planetary gear train PGR of the hybrid transmission according to the sixth embodiment includes a first sun gear Sd, a first ring gear Rd, a second sun gear Ss, and a second sun gear Ss. It has five rotating elements, a ring gear Rs and a common carrier C.

  The connection relationship of input / output elements with respect to these five rotating elements will be described. An inner rotor IR (first motor generator MG1) is connected to the first sun gear Sd. An engine (not shown) is connected to the first ring gear Rd via a mechanical oil pump O / P provided between the engine input shaft and the transmission case TC. An outer rotor OR (second motor generator MG2) is connected to the second sun gear Ss, and a high brake HB is provided between the hollow connecting shaft and the transmission case TC. An output gear OG is directly connected to the second ring gear Rs. The common carrier C is provided with a reverse brake RB between the hollow connecting shaft and the transmission case TC.

  Due to the above connection relationship, on the alignment chart shown in FIG. 13, the first motor generator MG1 (first sun gear Sd), the gear output Out (second ring gear Rs), the reverse brake RB (common carrier C), the engine input In ( It is possible to introduce a rigid lever model which is arranged in the order of the first ring gear Rd) and the second motor generator MG2 (second sun gear Ss) and can simply express the dynamic operation of the Ravigneaux planetary gear train PGR. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.

Next, the operation will be described.
In the hybrid transmission of the sixth embodiment, the mechanical oil pump O / P is provided in addition to the reverse brake RB, the high brake HB, or the rotary element to which the output is connected among the five rotary elements of the Ravigneaux planetary gear train PGR. . In other words, even when the vehicle speed is zero or when the brake RB or HB is operated, the mechanical oil pump O / P is installed in an element that does not necessarily require the speed to be zero. The mechanical oil pump O / P can be operated without operating the oil pump by using a power source different from the drive source.

  Further, as shown in FIG. 13, a mechanical oil pump O / P is provided on a rotating element close to the output among the five rotating elements of the Ravigneaux planetary gear train PGR. In other words, the shift range of the mechanical oil pump O / P can be increased because the rotating element of the mechanical oil pump O / P is close to the output.

  Further, among the five rotating elements of the Ravigneaux planetary gear train PGR, a mechanical oil pump O / P is provided on the rotating element of the first ring gear R1 to which the engine input shaft is connected. For this reason, since the engine input point is controlled to always keep the forward rotation, even if there is no clutch, it is possible to shift without reverse rotation of the engine and to generate hydraulic pressure.

  In addition, among the five rotating elements of the Ravigneaux type planetary gear train PGR, each rotating element rotates so that the rotational speed of the rotating element (first ring gear R1) provided with the mechanical oil pump O / P is always positive. The number (gear ratio) is controlled. For this reason, the mechanical oil pump O / P can always be operated even when the vehicle speed is zero or when the vehicle is moving backward.

  In addition, it is possible to generate a large driving force even when reversing by fastening reverse brake RB, so that a large driving force can be obtained while always operating the mechanical oil pump O / P even when reversing. Is possible.

  Next, the effects will be described. In the hybrid transmission of the sixth embodiment, in addition to the effects (1), (2), (3), (4) of the first embodiment, the following effects can be obtained. Can do.

  (7) By engaging the reverse brake RB, it is possible to generate a large driving force even when reversing, so it is possible to obtain a large driving force while always operating the mechanical oil pump O / P even when reversing. It becomes possible.

  The seventh embodiment is an example in which the second transmission for operating the mechanical oil pump in the first embodiment is set.

  First, the configuration will be described. As shown in FIG. 14, the Ravigneaux planetary gear train PGR of the hybrid transmission of the seventh embodiment is similar to the first embodiment in that the first sun gear Sd, the first ring gear Rd, It has five rotating elements, that is, a two sun gear Ss, a second ring gear Rs, and a common carrier C. Further, the second transmission using the single pinion type planetary gear set additionally has an oil pump ring gear Rd ′, an oil pump carrier Cop, and an oil pump sun gear Sop.

  First, the connection relationship of the input / output elements with respect to the five rotating elements will be described. An inner rotor IR (first motor generator MG1) is connected to the first sun gear Sd, and a high brake HB that can be fixed to the transmission case TC is connected to the first sun gear Sd. A low brake LB that can be fixed to the transmission case TC is connected to the first ring gear Rd. An outer rotor OR (second motor generator MG2) is connected to the second sun gear Ss. An engine (not shown) is connected to the second ring gear Rs via an engine clutch EC. An output gear OG is directly connected to the common carrier C.

  The oil pump ring gear Rd ′ of the second transmission is directly connected to the first ring gear Rd and rotates integrally therewith. The oil pump carrier Cop is interposed between a first one-way clutch OWC1 provided between the common carrier C and a second one-way clutch OWC2 provided between the transmission case TC. Is done. A mechanical oil pump O / P is provided between the oil pump sun gear Sop and the transmission case TC.

  15, the first motor generator MG1 (first sun gear Sd), engine input In (second ring gear Rs), gear output Out (common carrier C), low brake LB ( It is possible to introduce a rigid lever model which is arranged in the order of the first ring gear Rd) and the second motor generator MG2 (second sun gear Ss) and can simply express the dynamic operation of the Ravigneaux planetary gear train PGR. In the alignment chart shown in FIG. 15, the oil pump ring gear Rd 'coincides with the position of the low brake LB, the oil pump carrier Cop coincides with the position of the gear output Out, and the oil pump sun gear Sop indicates the engine. Arranged at a position between input In and gear output Out. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.

  Next, the operation will be described. According to the hybrid transmission of the seventh embodiment, when the second transmission is additionally set and the vehicle speed is zero, or when the low brake LB or the high brake HB is operated, By installing the mechanical oil pump O / P in the oil pump sun gear Sop (element of the second transmission) that does not necessarily require zero speed, the mechanical oil pump O / P can be operated at all times. The mechanical oil pump O / P can be operated without operating the oil pump using a power source different from the drive source.

  Further, according to the hybrid transmission of the seventh embodiment, when starting forward, the engine is stopped and the motor is started in the electric vehicle mode using both motor generators MG1 and MG2. When the required driving force is large, the low brake LB is engaged and the vehicle starts. At the time of starting, since the first one-way clutch OWC1 is engaged and the second one-way clutch OWC2 is released when the rotation speed of the output gear OG is in the positive direction, the oil pump sun gear Sop is in the first element row (first Rotation with the first sun gear Sd and the first ring gear Rd). The highest gear ratio at this time is when the first motor generator MG1 is rotating in the positive direction and the second motor generator MG2 is rotating in the negative direction, and the oil pump sun gear Sop is the minimum required rotation speed of the mechanical oil pump O / P. Because of time, it is possible to have a very wide shift range (the low direction depends on the upper limit of the rotational speed of each element).

  When starting on the reverse side, the vehicle starts so that the rotational speeds of the output gear OG and the first ring gear Rd are in the negative direction. At this time, since the second one-way clutch OWC2 is engaged and the first one-way clutch OWC1 is released, the oil pump sun gear Sop rotates in the forward direction by fixing the rotation speed of the oil pump carrier Cop to zero. To do.

  Further, since the mechanical oil pump O / P is provided in the rotating element (oil pump sun gear Sop) close to the output Out on the alignment chart of FIG. 7, it is possible to increase the shift range.

  In addition, the rotational speed (speed ratio) of each rotating element is controlled so that the rotational speed of the rotating element (oil pump sun gear Sop) where the mechanical oil pump O / P is installed is always positive, so the vehicle speed is zero. It is possible to always operate the mechanical oil pump O / P at the time of or during reverse.

  Next, the effects will be described. In the hybrid transmission of the seventh embodiment, in addition to the effects (1), (2), (4) of the first embodiment, the effects listed below can be obtained. .

  (8) In a hybrid transmission in which two input, output, and motor generators are fastened to separate rotary elements on a collinear chart representing the rotational relationship of each rotary element of the differential device, Since the second transmission for operating the mechanical oil pump is connected to the element, the mechanical oil pump O / P can be easily maintained in the positive direction.

  (9) Since there is a rotating element (second one-way clutch OWC2) between the input and output on the collinear diagram in the second transmission that stops the rotation when the vehicle moves backward, the mechanical oil pump O / Maintaining P in the positive direction can be easily achieved.

  The eighth embodiment is an example in which a reverse brake is additionally set in the second motor generator in the seventh embodiment.

  First, the configuration will be described. As shown in FIG. 16, the Ravigneaux planetary gear train PGR of the hybrid transmission of the eighth embodiment can fix the outer rotor OR constituting the second motor generator MG2 to the transmission case TC. A reverse brake RB is added. FIG. 17 is a collinear diagram showing the rotational speed relationship of the hybrid transmission according to the eighth embodiment. Since other configurations are the same as those of the seventh embodiment, the corresponding components are denoted by the same reference numerals and the settings are omitted.

  As for the action, it is possible to generate a large driving force even when reversing by fastening the reverse brake RB, so that a large driving force can be obtained while always operating the mechanical oil pump O / P even when reversing. Is possible. Since other operations are the same as those of the seventh embodiment, description thereof is omitted.

  Next, the effect will be described. In the hybrid transmission of the eighth embodiment, in addition to the effect of the seventh embodiment, the effect of (7) of the sixth embodiment can be obtained.

  The ninth embodiment is a layout example in which the mechanical oil pump is operated by the higher one of the second motor generator and the engine in the first embodiment.

  First, the configuration will be described. As shown in FIG. 18, the Ravigneaux type planetary gear train PGR of the hybrid transmission of the ninth embodiment is similar to the first embodiment in that the first sun gear Sd, the first ring gear Rd, It has five rotating elements, that is, a two sun gear Ss, a second ring gear Rs, and a common carrier C.

  The connection relationship of input / output elements with respect to these five rotating elements will be described. An inner rotor IR (first motor generator MG1) is connected to the first sun gear Sd, and a high brake HB that can be fixed to the transmission case TC is connected to the first sun gear Sd. A low brake LB that can be fixed to the transmission case TC is connected to the first ring gear Rd. An outer rotor OR (second motor generator MG2) is coupled to the second sun gear Ss, and the hollow coupling shaft is extended to the end position of the multilayer motor CM, so that the hollow coupling shaft and the transmission case TC are connected to each other. A mechanical oil pump O / P is provided between them via a first one-way clutch OW1. An engine (not shown) is connected to the second ring gear Rs via an engine clutch EC, and a connecting shaft that passes through the hollow portion of the hollow connecting shaft is extended to the end position of the multilayer motor CM to be connected. A mechanical oil pump O / P is provided between the shaft and the transmission case TC via a second one-way clutch OW2. An output gear OG is directly connected to the common carrier C.

  Due to the above connection relationship, the first motor generator MG1 (first sun gear Sd), the engine input In (second ring gear Rs), the gear output Out (common carrier C), the second motor generator on the alignment chart shown in FIG. It is possible to introduce a rigid lever model that is arranged in the order of MG2 (second sun gear Ss) and can simply express the dynamic operation of the Ravigneaux planetary gear train PGR. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.

  Next, the operation will be described. According to the hybrid transmission of the ninth embodiment, the oil pump rotation is achieved by fastening the high-speed element and the mechanical oil pump O / P between the engine and the second motor generator MG2. It can be easy to maintain the number in the positive direction.

  Further, when there are elements capable of operating a plurality of mechanical oil pumps O / P, as shown in FIG. 19, by disposing each at a distant position on the collinear chart, the operating elements are frequently switched. It is possible to prevent this, and it is possible to reduce the possibility that all the rotation speeds of these oil pump operable elements are in the negative direction.

  In addition, when there are elements that can operate multiple mechanical oil pumps O / P, be sure to install one element on the engine input element. By rotating in the positive rotation direction, the operation of the mechanical oil pump O / P can be secured, and the possibility that all the rotation speeds of the oil pump operable elements are in the negative direction can be reduced.

  Next, the effects will be described. In the hybrid transmission of the ninth embodiment, the effects of (1), (2), (3), (4) of the first embodiment and (6) of the second embodiment. In addition to the effects of (7) of Example 6 and (8) of Example 7, the effects listed below can be obtained.

  (10) In a hybrid transmission in which two input, output, and motor generators are fastened to separate rotary elements on a collinear diagram representing the rotational relationship of each rotary element of the differential device, the at least two or more rotary elements Among them, since the mechanical oil pump O / P is operated by the rotating element having the higher rotation speed, it is possible to easily maintain the oil pump rotation speed in the positive direction.

  (11) Since the rotating elements that can operate multiple mechanical oil pumps O / P are arranged at distant positions on the nomograph, it is possible to prevent frequent switching of the operating elements, and to operate the oil pumps. It is possible to reduce the possibility that all the rotation speeds of the possible elements are in the negative direction.

  (12) If there is an element that can operate multiple mechanical oil pump O / Ps, one of them must be installed on the engine input element, so all the rotation speeds of the oil pump operable elements can be negative. It becomes possible to lower the sex.

  The tenth embodiment is an example in which the mounting positions of the one-way clutches OW1, OW2 are set to the inner positions of the second sun gear Ss in the ninth embodiment.

  First, the configuration will be described. As shown in FIG. 20, the Ravigneaux type planetary gear train PGR of the hybrid transmission of the tenth embodiment forms a recess space at the inner position of the second sun gear Ss, and the engine input is input to this recess space. With the shaft facing, the first one-way clutch OW1 is interposed between the end of the oil pump shaft and the second sun gear Ss, and the second one-way clutch OW2 is connected between the end of the oil pump shaft and the engine input shaft. The oil pump shaft extends through the hollow portion of the hollow connecting shaft to the end position of the multilayer motor CM, and a mechanical oil pump is provided between the extended end portion of the oil pump shaft and the transmission case TC. O / P is provided. FIG. 21 is a collinear diagram showing the rotational speed relationship of the hybrid transmission of the tenth embodiment. Since other configurations are the same as those in the ninth embodiment, the corresponding components are denoted by the same reference numerals, and the settings are omitted.

  That is, the hybrid transmission of the tenth embodiment is the same as that of the ninth embodiment in the hybrid transmission of the ninth embodiment except that the mounting layouts of the one-way clutches OW1 and OW2 are different. Description is omitted.

  In an eleventh embodiment, a seventh embodiment in which a second transmission for operating the mechanical oil pump is set, and an ninth embodiment in which the mechanical oil pump is operated by a higher rotational speed among at least two or more rotating elements. , 10 and a combination example.

  First, the configuration will be described. As shown in FIG. 22, the Ravigneaux planetary gear train PGR of the hybrid transmission of the eleventh embodiment includes a first sun gear Sd, a first ring gear Rd, a second sun gear Ss, and a second sun gear Ss. It has five rotating elements, a ring gear Rs and a common carrier C. Further, the second transmission using the single pinion type planetary gear set additionally has an oil pump ring gear Rd ′, an oil pump carrier Cop, and an oil pump sun gear Sop.

  First, the connection relationship of the input / output elements with respect to the five rotation elements is the same as that of the seventh embodiment, and the description thereof is omitted. The oil pump ring gear Rd ′ of the second transmission is directly connected to the first ring gear Rd and rotates integrally therewith. The oil pump carrier Cop includes a first one-way clutch OWC1 provided between the common carrier C, a second one-way clutch OWC2 provided between the transmission case TC, and the oil pump sun gear. A third one-way clutch OWC3 provided between the Sop and the Sop. A one-way clutch OWC4 is interposed between the oil pump sun gear Sop and the engine input shaft, and a mechanical oil pump O / P is provided between the oil pump sun gear Sop and the fourth transmission case TC.

  23, the first motor generator MG1 (first sun gear Sd), engine input In (second ring gear Rs), gear output Out (common carrier C), low brake LB ( It is possible to introduce a rigid lever model which is arranged in the order of the first ring gear Rd) and the second motor generator MG2 (second sun gear Ss) and can simply express the dynamic operation of the Ravigneaux planetary gear train PGR. 23, the oil pump ring gear Rd 'coincides with the position of the low brake LB, the oil pump carrier Cop coincides with the position of the gear output Out, and the oil pump sun gear Sop indicates the engine. Matches the position of input In. Since other configurations are the same as those of the first embodiment, the corresponding components are denoted by the same reference numerals and description thereof is omitted.

  Next, the operation will be described. According to the hybrid transmission of the eleventh embodiment, at the time of forward start, the motor is started in the electric vehicle mode using both the motor generators MG1 and MG2. When the required driving force is large, the low brake LB is engaged and the vehicle starts. At this start, the first one-way clutch OWC1 and the third one-way clutch OWC3 are engaged and the second one-way clutch OWC2 and the fourth one-way clutch OWC4 are released when the rotational speed of the output gear OG is in the positive direction, so that the oil pump The sun gear Sop rotates with the output rotation. The highest gear ratio at this time is when the first motor generator MG1 is rotating in the positive direction and the second motor generator MG2 is rotating in the negative direction, and the oil pump sun gear Sop is the minimum required rotation speed of the mechanical oil pump O / P. Therefore, it is possible to have a wider shift range than the seventh and eighth embodiments (the low direction depends on the upper limit of the rotational speed of each element).

  When starting on the reverse side, the vehicle starts so that the rotational speeds of the output gear OG and the first ring gear Rd are in the negative direction. At this time, the second one-way clutch OWC2 and the fourth one-way clutch OWC4 are engaged, and the first one-way clutch OWC1 and the third one-way clutch OWC3 are released, so that the oil pump sun gear Sop controls the rotation speed of the oil pump carrier Cop. It rotates in the positive direction together with the engine input shaft while being fixed at zero. Other functions are the same as those of the seventh embodiment.

  Next, the effects will be described. In the hybrid transmission of the eleventh embodiment, the effects of (1), (2), (3), (4) of the first embodiment, (8), In addition to the effect (9) and the effects (10) and (12) of the ninth embodiment, the following effects can be obtained.

  (13) When there are multiple elements that can operate the mechanical oil pump O / P, one element is installed on the rotating element to which the output is connected. As a result, the operation of the mechanical oil pump O / P can be ensured, and the possibility that all the rotation speeds of the oil pump operable elements are in the negative direction can be reduced.

  The twelfth embodiment is an example in which the low brake LB is abolished in the eleventh embodiment and a reverse brake (also used as a low brake) is additionally set in the second motor generator.

  First, the configuration will be described. As shown in FIG. 24, the Ravigneaux planetary gear train PGR of the hybrid transmission of the twelfth embodiment can fix the outer rotor OR constituting the second motor generator MG2 to the transmission case TC. A reverse brake RB is added. FIG. 25 is a collinear diagram showing the rotational speed relationship of the hybrid transmission of the twelfth embodiment. Since other configurations are the same as those of the eleventh embodiment, the corresponding components are denoted by the same reference numerals and the settings are omitted.

  As for the action, it is possible to generate a large driving force even when reversing by fastening the reverse brake RB, so that a large driving force can be obtained while always operating the mechanical oil pump O / P even when reversing. Is possible. Since other functions are the same as those of the eleventh embodiment, description thereof is omitted.

  Next, the effect will be described. In the hybrid transmission of the twelfth embodiment, in addition to the effect of the eleventh embodiment, the effect (7) of the sixth embodiment can be obtained.

  In the thirteenth embodiment, the low brake LB, which is the starting brake, is released and the vehicle is started in the EV mode (electric vehicle continuously variable transmission mode), and then the low brake LB is engaged and the EV-LB mode ( This is an example of shifting to the electric vehicle fixed shift mode. Note that the configuration is the same as that of the first embodiment shown in FIG.

Next, the operation will be described.
[Start control process]
FIG. 26 is a flowchart showing the flow of the start control process according to the thirteenth embodiment. Each step will be described below. This control process constitutes a start control means.

  In step S1, it is determined whether or not to start from the accelerator opening. If yes, then go to step S2, if no, go to return.

  In step S2, the vehicle is started in an EV mode in which both motor generators MG1, MG2 are driven while the engine is stopped.

  In step S3, it is determined whether the required driving force is large from the accelerator opening, the accelerator operation speed, and the like. If YES, the process proceeds to step S4. If NO, the process proceeds to return.

  In step S4, slip control of the low brake LB is performed, and the process proceeds to step S5.

  In step S5, shift control is performed by both motor generators MG1 and MG2 so that the rotational speed of the low brake LB (first ring gear Rd) becomes zero, and the process proceeds to step S6. At this time, the rotation speed of the second ring gear Rs connected to the mechanical oil pump O / P is higher than the rotation speed of the common carrier C connected to the output gear OG, and the speed change of the common carrier C is minimized. Both motor generators MG1 and MG2 are controlled so as to be limited.

  In step S6, it is determined whether or not the rotation speed of the low brake LB (first ring gear Rd) is zero. If YES, the process proceeds to step S7. If NO, the process proceeds to step S4.

  In step S7, the low brake LB is fully engaged and the mode shifts to the EV-LB mode, and then returns.

[Low brake engagement when starting]
In the thirteenth embodiment, as shown in the collinear diagram of FIG. 27 (a), when starting from a vehicle speed of zero, the motor generators MG1 and MG2 start in the EV mode, so there is no need to generate hydraulic pressure in advance. Thus, the time lag until the torque is generated can be reduced, and there is no response delay to the driver's accelerator operation.

  When the driving force requirement at the start is large, the motor generators MG1 and MG2 control the slippage of the low brake LB after starting the EV mode and the rotation speed of the low brake LB (first ring gear Rd) becomes zero. Since the shift control is performed, it is possible to improve both the engagement speed and reduce the engagement shock of the low brake LB (FIG. 27 (b)).

  Further, in the shift control of the motor generators MG1 and MG2, the rotational speed of the second ring gear Rs connected to the mechanical oil pump O / P is set to be higher than the rotational speed of the common carrier C connected to the gear output Out. Since the hydraulic pressure rises quickly, the low brake LB can be quickly engaged. Furthermore, since the speed change of the common carrier C is minimized, the speed change accompanying the engagement of the low brake LB is suppressed, and a high driving force can be output smoothly.

  Subsequently, when the rotation speed of the low brake LB becomes zero, the low brake LB is completely engaged, and the EV mode is shifted to the EV-LB mode. At this time, since the mechanical oil pump O / P has already been activated by the start of the EV mode and the engagement hydraulic pressure can be supplied to the low brake LB, a high driving force corresponding to the required driving force can be generated (FIG. 27 (c )).

FIG. 28 is a diagram illustrating a maximum driving force waveform with respect to the vehicle speed of the hybrid transmission according to the thirteenth embodiment.
In the prior art, when there is a start request, the rotational speed of the rotating element connected to the mechanical oil pump is increased by the motor while maintaining the vehicle speed to zero, and after generating the hydraulic pressure necessary for fastening the low brake, The vehicle starts with a low brake. Therefore, when a large driving force is requested, it takes a long time to generate the required oil pressure, so there is a time lag from the start request to the actual start, making it difficult to take advantage of the motor with good response. There was a problem.

  On the other hand, in the thirteenth embodiment, the motor generators MG1 and MG2 having good responsiveness start in the EV mode, so that the time required from the start request to the actual start can be minimized. Also, when there is a demand for a large driving force, the low brake LB is slip-engaged, and the low brake LB is fully engaged after the rotation speed of the low brake LB becomes zero, so a larger driving force is output quickly. It becomes possible.

Next, the effect will be described.
In the hybrid transmission of the thirteenth embodiment, in addition to the effects of the first embodiment, the following effects can be obtained.

  (14) On the nomograph, connect one rotating element other than the engine input In, gear output Out or the rotating element to which the motor generators MG1, MG2 are connected to the transmission case via the low brake LB. After the vehicle is started with the brake LB released, the start control means for engaging the low brake LB according to the required driving force is provided, so that a high driving force according to the high required driving force can be generated.

  (15) Since the start control means performs slip control on the low brake LB, it is possible to generate the maximum possible driving force as quickly as possible.

  (16) The start control means is configured so that the rotation speed of the second ring gear Rs connected to the mechanical oil pump O / P is higher than the rotation speed of the common carrier C connected to the gear output Out. Since the rotation speed is controlled, the hydraulic pressure rises quickly and the low brake LB can be quickly engaged.

  (17) Since the starting control means completely engages the low brake LB after setting the rotation speed of the low brake LB to zero, the engagement shock of the low brake LB can be reduced.

  (18) Since the start control means controls the rotation speed of each rotating element so that the speed change of the gear output Out is reduced, the speed change accompanying the engagement of the low brake LB is suppressed, and a high driving force is output smoothly. it can.

In the fourteenth embodiment, when the driving force requirement is large, after the EV starts, the low brake LB hydraulic control circuit is opened and the low brake LB is engaged according to the hydraulic pressure generated by the mechanical oil pump O / P. . Further, in Example 14, the output characteristic of the mechanical oil pump O / P is set to the minimum required lubrication flow rate before the oil lubrication flow rate to each rotating element reaches the rotational speed that causes a problem in the case of no lubrication. Set to reach.
Note that the configuration is the same as that of the second embodiment shown in FIG.

Next, the operation will be described.
[Start control process]
FIG. 29 is a flowchart showing the flow of the start control process according to the fourteenth embodiment. Each step will be described below. In addition, the step which performs the same process as Example 13 shown in FIG. 26 attaches | subjects the same step number, and abbreviate | omits description. This control process constitutes a start control means.

  In step S11, the hydraulic control circuit (not shown) of the low brake LB is opened, the low brake LB is engaged according to the discharge pressure of the mechanical oil pump O / P, and the process proceeds to return.

[Low brake engagement when starting]
In the fourteenth embodiment, when the driving force requirement at the time of start is large, the low brake LB is controlled while performing the shift control by the motor generators MG1 and MG2 so that the rotational speed of the low brake LB (first ring gear Rd) becomes zero. Conclude. That is, according to the thirteenth embodiment, the low brake LB is engaged while waiting for the rotational speed of the low brake LB to become zero by engaging the low brake LB while making the gear ratio equivalent to the low brake LB engagement at the start. On the other hand, the fastening speed can be further increased. In addition, the low brake LB hydraulic control circuit is opened and the low brake LB is engaged according to the discharge pressure of the mechanical oil pump O / P, so the low brake LB engagement control can be simplified and the maximum possible The driving force can be generated more quickly.

  In addition, since the mechanical oil pump O / P is provided at the position of the first motor generator MG1 far from the gear output Out on the alignment chart of FIG. 5, the rotational speed of the mechanical oil pump O / P increases to the required rotational speed. Since the low brake LB can be engaged at a position where the speed of the gear output Out is lower, the large driving force can be output with good response.

  Furthermore, in Example 14, the output characteristic of the mechanical oil pump O / P is set to the minimum required lubrication flow rate before the oil lubrication flow rate to each rotating element reaches the rotational speed that causes a problem when there is no lubrication. Set to reach. In other words, the output characteristics of the mechanical oil pump O / P can be set so that the required performance does not have to be exhibited from low rotation. / P can be downsized.

  FIG. 30 is a diagram showing a maximum driving force waveform with respect to the vehicle speed of the hybrid transmission of the fourteenth embodiment. In the thirteenth embodiment, the maximum generated hydraulic pressure of the mechanical oil pump O / P is set while the rotation speed of the low brake LB is zero. Since the low brake LB is engaged, a larger driving force can be output more quickly.

Next, the effect will be described.
In the hybrid transmission of the fourteenth embodiment, in addition to the effects of the second embodiment and the effects (14), (16), and (18) of the thirteenth embodiment, the following effects can be obtained.

  (19) The start control means opens the low brake LB hydraulic control circuit and engages the low brake LB according to the hydraulic pressure generated by the mechanical oil pump O / P, thus simplifying the low brake LB engagement control. The maximum driving force possible can be generated more quickly.

  (20) Since the start control means engages the low brake LB while changing the rotational speed of the low brake LB to zero, the engagement speed can be further increased.

  (21) The mechanical oil pump O / P has an output characteristic that reaches the minimum required lubrication flow rate before the rotational speed causing problems when the oil lubrication flow rate to each rotating element is unlubricated. The oil pump O / P can be downsized.

(Other examples)
As mentioned above, although the hybrid transmission of this invention has been demonstrated based on Example 1-Example 14, it is not restricted to these Examples about a concrete structure, Each claim of a claim is a claim. Design changes and additions are allowed without departing from the gist of the invention.

  For example, in the thirteenth and fourteenth embodiments, when the EV mode starts, after the low brake LB is slip-controlled, the shift control by both motor generators MG1 and MG2 is performed so that the rotation speed of the low brake LB (first ring gear Rd) becomes zero. Although the example of performing the above is shown, the slip control of the low brake LB may be performed after the shift control. In this case, the engagement shock of the low brake LB can be further reduced.

  In the first to fourteenth embodiments, examples of a hybrid transmission using a Ravigneaux type planetary gear train as a differential device and a hybrid transmission using a three-set planetary gear train as a differential device are shown, but at least each rotation of the differential device Any hybrid transmission other than those shown in Examples 1 to 14 can be used as long as it is a hybrid transmission in which two input, output, and two motor generators are fastened to separate rotating elements on a collinear diagram showing the rotational relationship of the elements. can do.

1 is an overall cross-sectional view illustrating a hybrid transmission according to a first embodiment. FIG. 3 is a collinear diagram showing a rotational relationship of the differential gear of the hybrid transmission according to the first embodiment. FIG. 3 is a collinear diagram showing a continuously variable transmission mode by direct power distribution in the hybrid transmission of the first embodiment. FIG. 5 is an overall cross-sectional view illustrating a hybrid transmission according to a second embodiment. FIG. 6 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to a second embodiment. FIG. 6 is an overall cross-sectional view illustrating a hybrid transmission according to a third embodiment. FIG. 10 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to a third embodiment. FIG. 10 is an overall cross-sectional view showing a hybrid transmission according to a fourth embodiment. FIG. 10 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to a fourth embodiment. FIG. 10 is an overall cross-sectional view illustrating a hybrid transmission according to a fifth embodiment. FIG. 10 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to a fifth embodiment. FIG. 10 is an overall cross-sectional view illustrating a hybrid transmission according to a sixth embodiment. FIG. 10 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to a sixth embodiment. FIG. 10 is an overall cross-sectional view illustrating a hybrid transmission according to a seventh embodiment. FIG. 10 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to a seventh embodiment. FIG. 10 is an overall cross-sectional view illustrating a hybrid transmission according to an eighth embodiment. FIG. 10 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to an eighth embodiment. FIG. 10 is an overall cross-sectional view illustrating a hybrid transmission according to a ninth embodiment. FIG. 20 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to a ninth embodiment. FIG. 10 is an overall cross-sectional view showing a hybrid transmission of Example 10. FIG. 19 is a collinear diagram illustrating a rotational relationship of a differential gear of the hybrid transmission according to the tenth embodiment. FIG. 10 is an overall cross-sectional view showing a hybrid transmission according to an eleventh embodiment. FIG. 20 is a collinear diagram illustrating a rotational relationship of a differential device of a hybrid transmission according to an eleventh embodiment. FIG. 14 is an overall cross-sectional view showing a hybrid transmission of Example 12. FIG. 19 is a collinear diagram illustrating a rotational relationship of a differential gear of the hybrid transmission according to the twelfth embodiment. It is a flowchart which shows the flow of the start control process of Example 13. FIG. 19 is a collinear diagram illustrating a rotational relationship of a differential gear of the hybrid transmission according to the thirteenth embodiment. FIG. 18 is a diagram illustrating a maximum driving force waveform with respect to the vehicle speed of the hybrid transmission according to the thirteenth embodiment. It is a flowchart which shows the flow of the start control process of Example 14. It is a figure which shows the maximum drive force waveform with respect to the vehicle speed of the hybrid transmission of Example 14. FIG.

Explanation of symbols

MG1 1st motor generator
MG2 Second motor generator
OG output gear
CM multilayer motor
IR inner rotor S stator
OR outer rotor
PGR Ravigneaux type planetary gear train (differential device)
Sd 1st sun gear
Rd 1st ring gear
Ss 2nd sun gear
Rs 2nd ring gear C Common carrier
LB Low brake
HB High brake
TC transmission case
O / P mechanical oil pump
EC engine clutch
PGS 3-set planetary gear train (differential gear)

Claims (21)

On a collinear diagram representing the rotational relationship of each rotating element of the differential device, in a hybrid transmission in which two input, output and two motor generators are fastened to separate rotating elements,
Among the rotating elements, a hybrid oil transmission is provided with a mechanical oil pump other than a rotating element to which a brake or an output is connected. On a collinear diagram representing the rotational relationship of each rotating element of the differential device, in a hybrid transmission in which two input, output and two motor generators are fastened to separate rotating elements,
A hybrid transmission characterized in that a second transmission for operating a mechanical oil pump is connected to one element on the alignment chart. The hybrid transmission according to claim 2, wherein
A hybrid transmission characterized by having a brake element that stops rotation when the vehicle moves backward between an input and an output on the nomographic chart in the second transmission. On a collinear diagram representing the rotational relationship of each rotating element of the differential device, in a hybrid transmission in which two input, output and two motor generators are fastened to separate rotating elements,
A hybrid transmission, wherein a mechanical oil pump is operated by a rotating element having a higher rotational speed among at least two rotating elements capable of installing the mechanical oil pump. The hybrid transmission according to any one of claims 1 to 3,
A hybrid transmission characterized in that a mechanical oil pump is provided on a rotating element close to the output on the alignment chart. The hybrid transmission according to any one of claims 1 to 3,
A hybrid transmission characterized in that a mechanical oil pump is provided on a rotating element far from the output on the alignment chart. The hybrid transmission according to any one of claims 1 to 6,
A hybrid transmission characterized in that a mechanical oil pump is provided on an engine input shaft connected to an input on the alignment chart. The hybrid transmission according to any one of claims 1 to 7,
A hybrid transmission characterized in that a mechanical oil pump is provided at a position of a rotating element to which a motor generator is connected from the output on the alignment chart, or at a position farther from the output from the motor generator connecting element position on the alignment chart. Machine. The hybrid transmission according to any one of claims 1 to 8,
A hybrid transmission characterized in that the rotational speed (speed ratio) of each rotary element is controlled so that the rotational speed of the rotary element provided with the mechanical oil pump is always positive. The hybrid transmission according to any one of claims 1 to 9,
A hybrid transmission characterized in that a brake element capable of generating a large driving force at the time of reverse movement is provided in one of the rotating elements. The hybrid transmission according to any one of claims 1 to 10,
A plurality of rotating elements capable of operating the mechanical oil pump are respectively arranged at distant positions on a nomographic chart. The hybrid transmission according to any one of claims 1 to 11,
When there are a plurality of elements capable of operating the mechanical oil pump, one is installed in a rotating element to which an output member is connected. The hybrid transmission according to any one of claims 1 to 12,
When there are a plurality of elements capable of operating the mechanical oil pump, one is always installed on a rotating element to which the engine is connected. The hybrid transmission according to any one of claims 1 to 13,
On the collinear diagram, one rotation element other than the rotation element to which the input, output or two motor generators are connected is connected to the transmission case via a start brake,
A hybrid transmission comprising start control means for starting the vehicle with the start brake released and then engaging the start brake according to the required driving force. The hybrid transmission according to claim 14, wherein
The hybrid transmission according to claim 1, wherein the start control means performs slip control on the start brake. The hybrid transmission according to claim 14 or 15,
The hybrid transmission is characterized in that the start control means opens a hydraulic control circuit of the start brake and fastens the start brake according to the hydraulic pressure generated by the mechanical oil pump. The hybrid transmission according to any one of claims 14 to 16,
The start control means controls the rotation speed of each rotation element so that the rotation speed of the rotation element provided with the mechanical oil pump is higher than the rotation speed of the rotation element connected to the output. transmission. The hybrid transmission according to any one of claims 14 to 17,
The hybrid transmission is characterized in that the start control means fastens the start brake after changing the number of rotations of each rotary element to the number of rotations when the start brake is engaged. The hybrid transmission according to any one of claims 14 to 17,
The hybrid transmission is characterized in that the start control means engages a start brake while changing the number of rotations of each rotary element to the number of rotations at the time of start brake engagement. The hybrid transmission according to any one of claims 14 to 19,
The hybrid transmission is characterized in that the start control means controls the rotational speed of each rotary element so that a change in output speed is reduced. The hybrid transmission according to any one of claims 14 to 20,
The hybrid transmission characterized in that the mechanical oil pump has an output characteristic that reaches a predetermined minimum lubrication flow rate before reaching a rotational speed that causes a problem when the oil lubrication flow rate to each rotating element is not lubricated. .

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