JP2007223487A - Transmission by operational mode changing type compound planetary gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission suitable for both the low-speed travel and the high-speed travel of a vehicle by effectively using the large influence of the distance in the coordinate axes between the engine speed and the number of rotations of an output shaft on the alignment chart when performing the speed change between an engine and a wheel driving shaft by a compound planetary gear device. <P>SOLUTION: A rotation output member Out is coupled in a changing manner by a clutch CL between two rotation units of a compound planetary gear device having four rotation units by combining two planetary gear devices P1, P2. The transmission has two operational modes in which the magnitude of the speed change range of the vehicle speed to the engine speed is different. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a transmission, and more particularly to a transmission using a compound planetary gear device.

Two planetary gear mechanisms, and each of the two rotating elements of the first planetary gear mechanism is directly and individually connected to each of the two rotating elements of the second planetary gear mechanism. Patent Document 1 below describes that the four rotating parts are directly connected to any one of the first motor, the second motor, and the engine separately, and the remaining one rotating element is used as a drive output part. ing. Further, in Patent Document 2 below, there are four rotating members as rotating members arranged on the nomograph, and when the rotating state of two members among these rotating members is determined, the rotating state of the other members In a hybrid transmission comprising a differential device having two degrees of freedom, wherein each of the rotating members has an input from a main power source, an output to a drive system, and two motors / generators, One of the generators and a rotating member to which the one motor / generator is to be connected are connected via a planetary gear set including a sun gear, a ring gear, and a carrier, and the planetary gear set is brought into a directly connected state by connecting two elements. And a control means for transmitting torque from the one motor / generator to the corresponding rotating member under increase by fixing one element. Hybrid transmission according to claim kick is described.
JP 2002-271607 A JP2002-239278

  In vehicles such as automobiles, the number of rotations of the wheel varies greatly from 0 to a high value depending on the operation status of the vehicle, but the number of rotations of the engine that drives this is too large in terms of its operating efficiency. It is desirable that it cannot be changed. In order to drive a vehicle with an engine, a transmission with a variable gear ratio is required. In recent years, in particular, in a hybrid type vehicle drive in which a vehicle is driven by a combination of an engine and an electric motor, Each of the two rotating elements is connected to each other, and a compound planetary gear unit having four rotating parts that rotate while maintaining mutual relations is used. The engine is connected to one of these rotating parts, and the other two By connecting a motor generator (motor / generator) to the two and changing the rotation speed of these two motor generators, the rotation speed of the remaining one rotating part that drives the wheel as the output shaft and the rotation speed of the engine To achieve the required speed change.

  The rotation speed of each of the four rotating portions of the compound planetary gear device configured to have four rotating portions by connecting the two rotating elements of the two planetary gear devices to each other is four in parallel. By arbitrarily drawing a straight line across the four coordinate axes of the collinear chart composed of the rotational speed coordinate axes, the coordinate values of the coordinate axes intersecting with the straight line are related. Therefore, when one of the coordinate axes corresponds to the engine and the other one of the coordinate axes corresponds to the output member, the rotational speed of the engine depends on the angle formed by the one straight line with respect to the four parallel coordinate axes. And the rotational speed of the output member change, which indicates the gear ratio between the engine and the wheel drive shaft. In this case, the difference between the engine rotational speed and the wheel drive shaft rotational speed is approximately proportional to the change as the angle formed by the single line with respect to the coordinate axis changes from 90 degrees (more precisely, the change of the change). However, it is the distance between the coordinate axis representing the engine speed and the coordinate axis representing the output shaft speed that dominates the value of the difference. When this distance is small, the engine speed and the output shaft speed do not differ so much even if the one straight line is greatly inclined. Conversely, if this distance is large, the one straight line is slightly inclined. There is a large difference between the engine speed and the output shaft speed.

  In the present invention, if a shift between the engine and the wheel drive shaft is to be performed by the compound planetary gear device as described above, the gear ratio is on a collinear chart corresponding to each of the engine speed and the output shaft speed. Focusing on the fact that it is greatly affected by the distance between the coordinate axes, it is an object of the present invention to provide a transmission that is well adapted to both low-speed and high-speed driving of a vehicle by making effective use of this.

  In order to solve the above-mentioned problems, the present invention is directed to the following. In the present invention, each of the two rotating elements in one of the first and second planetary gear devices each having three rotating elements, which are a sun gear, a ring gear, and a carrier, is the other. 4 types of rotating parts, in which the relative rotational speeds are related by a collinear chart composed of four parallel rotational speed coordinate axes by being combined in the manner of being individually connected to each of the two rotational elements in FIG. A first planetary gear device, a rotation output member, and a clutch, wherein the rotation output member is connected to a rotation portion corresponding to one of the rotation speed coordinate axes by the clutch and the rotation. The output member is configured to be switched between a second operation mode connected to a rotation unit corresponding to the other one of the rotation speed coordinate axes by the clutch. It proposes a transmission to.

  In one embodiment of the transmission as described above, the carrier and the ring gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively. The rotation output member is connected to a carrier of the first planetary gear device and a sun gear of the second planetary gear device, and the rotation output member is connected to the first planetary gear device in the second operation mode. It may be connected to the sun gear of one planetary gear device.

  As another embodiment, the transmission as described above is configured such that the carrier and the ring gear of the first planetary gear device are respectively connected to the sun gear and the carrier of the second planetary gear device, and the first operation mode is as described above. In the second operation mode, the rotation output member is connected to a coupling body of a ring gear of the first planetary gear device and a carrier of the second planetary gear device, and the rotation output member is connected in the second operation mode. The second planetary gear unit may be connected to a ring gear.

  According to still another embodiment of the transmission as described above, the carrier and the sun gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively, and the first operation is performed. In the mode, the rotation output member is connected to a carrier of the first planetary gear device and the sun gear of the second planetary gear device, and in the second operation mode, the rotation output member. May be connected to the ring gear of the first planetary gear set.

  According to still another embodiment of the transmission as described above, the carrier and the ring gear of the first planetary gear device are respectively connected to the ring gear and the carrier of the second planetary gear device, and the first operation is performed. In the mode, the rotation output member is connected to the carrier of the first planetary gear unit and the ring gear of the second planetary gear unit, and in the second operation mode, the rotation output member. May be connected to the sun gear of the first planetary gear set.

  Further, in the transmission as described above, the rotational speeds of all the three rotating elements of the first and second planetary gear devices are made equal to each other between the first operating mode and the second operating mode. Control means for switching may be provided.

  The control means is in the first operation mode until the rotation speed of the rotation output member reaches a predetermined upper limit value, and when the rotation speed of the rotation output member exceeds the upper limit value, the second operation mode is set. The operation mode may be controlled to do so.

  The control means is configured to return the operation mode to the first operation mode when the number of rotations of the rotation output member decreases below a predetermined lower limit value lower than the upper limit value in the second operation mode. You may come to control.

  The transmission as described above further includes a rotation input member and another clutch, and the rotation output member corresponds to one of the rotation speed coordinate axes and a rotation unit corresponding to the other one. The rotation input member is switched and connected between the two rotating parts by the other one clutch, contrary to the connection switching of the rotation output member. It's okay.

  Further, in the transmission as described above, the four rotation speed coordinate axes in the collinear chart are set as the first coordinate axis, the second coordinate axis, the third coordinate axis, and the fourth coordinate axis from one end to the other end. When the rotation unit corresponding to the first coordinate axis is connected to at least a first electric device that operates as a generator, the rotation unit corresponding to the second coordinate axis is connected to an engine, and the rotation input member is at least an electric motor. The vehicle may be driven by the rotation output member connected to a second electric device that operates.

  As described above, each of the two rotating elements in one of the first and second planetary gear units having three rotating elements, each of which is a sun gear, a ring gear, and a carrier, is each of the two rotating elements in the other. A combined planetary gear device having four types of rotating parts associated with each other by a collinear chart composed of four parallel rotation speed coordinate axes, and a rotation output. A first operation mode in which the rotation output member is connected to a rotation portion corresponding to one of the rotation speed coordinate axes by the clutch, and the rotation output member is rotated by the clutch. According to the transmission that is switched between the second operating mode connected to the rotating part corresponding to the other one of the coordinate axes, By switching the rotation output member between the two rotation speed coordinate axes to correspond to each other, the distance at which the rotation speed coordinate axis of the rotation output member is separated from any one of the other rotation speed coordinate axes can be changed in two ways. Therefore, for example, if the other one rotation speed coordinate axis is made to correspond to the engine rotation speed, the distance that the rotation speed coordinate axis of the rotation output member is separated from the engine rotation speed coordinate axis is switched in two ways. A speed change operation mode suitable for low-speed traveling, which is small and has a small range in which the rotational speed of the rotation output member changes with respect to the engine rotational speed, thereby enabling a more delicate and stable speed change when the vehicle is traveling at low speed, The distance that the rotational speed coordinate axis of the rotational output member is separated from the engine rotational speed coordinate axis is large, and the range in which the rotational speed of the rotational output member changes with respect to the engine rotational speed is wide. Even if the gin rotation speed is not increased so much, the rotation speed of the rotation output member can be greatly increased and the operation mode of the transmission can be switched between the operation modes suitable for high-speed driving of the vehicle. A transmission that can better cope with high-speed traveling can be obtained.

  There can be several embodiments of the combination of the two planetary gear units, the rotation output member, and the clutch based on the above technical idea, each of which shows the relative separation distance between the coordinate axes when viewed in the collinear diagram. Depending on the features that appear in the array, the first and second modes of operation will have their respective features.

  That is, the carrier and the ring gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively, and the rotation output member is the first planetary gear in the first operation mode. It is connected to the coupling body of the carrier of the gear device and the sun gear of the second planetary gear device, and the rotation output member is connected to the sun gear of the first planetary gear device in the second operation mode. And the carrier and the ring gear of the first planetary gear device are respectively connected to the ring gear and the carrier of the second planetary gear device, and in the first operation mode, the rotation output member is The first planetary gear unit is connected to the carrier of the first planetary gear unit and the ring gear unit of the second planetary gear unit, and in the second operation mode, the rotation is performed. When the output member is connected to the sun gear of the first planetary gear device, the ratio of the number of teeth of the sun gear to the number of teeth of the ring gear in the planetary gear device (in the description of the embodiment) (rho) is a value much smaller than 1 in the range of about 0.4 to 0.6. Therefore, the rotation axis is output in the second operation mode and the coordinate axis to which the rotation output member is connected in the first operation mode. The distance between the coordinate axes to which the members are connected increases, and therefore, when another coordinate axis is the coordinate axis for the engine speed, the engine speed coordinate axis is changed between the first operation mode and the second operation mode. The difference in the distance of the rotation output member rotational speed coordinate axis with respect to can be increased, and a shift characteristic better adapted to a vehicle having a high vehicle speed during high speed traveling can be obtained.

  On the other hand, the carrier and the ring gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively, and the rotation output member is the first planetary gear in the first operation mode. It is connected to a connecting body of a ring gear of the gear device and a carrier of the second planetary gear device, and the rotation output member is connected to the ring gear of the second planetary gear device in the second operation mode. And the carrier and sun gear of the first planetary gear device are respectively connected to the sun gear and carrier of the second planetary gear device, and in the first operation mode, the rotation output member is The first planetary gear device is connected to the carrier of the second planetary gear device and the sun gear of the second planetary gear device, and the rotation in the second operation mode. When the force member is connected to the ring gear of the first planetary gear device, the coordinate axis to which the rotation output member is connected in the first operation mode and the second operation mode. Since the distance between the coordinate axes to which the rotation output member is connected is relatively small, when another coordinate axis is a coordinate axis for the engine speed, the engine is operated in the first operation mode and the second operation mode. The difference in the distance of the rotational output member rotational speed coordinate axis relative to the rotational speed coordinate axis is relatively small, and it is possible to obtain a speed change characteristic that is better adapted to a vehicle whose vehicle speed during high speed traveling is not very high.

  Also, depending on each of the above modes, the distance between the remaining two rotation speed coordinate axes other than the two rotation speed coordinate axes to which the rotation output member is switched and connected is different, and one of them corresponds to the engine rotation speed. When the other one corresponds to the number of rotations of the motor generator mainly for power generation, the restrictions imposed on the capacity and the number of rotations of the engine and motor generator when designing the amount of power generation relative to the engine output Can be compensated by the above selection of the magnitude of the distance.

  In this regard, the carrier and the ring gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively, and the rotation output member is the first planetary gear device in the first operation mode. The planetary gear device is connected to the ring gear of the second planetary gear device and the carrier of the second planetary gear device. In the second operation mode, the rotation output member is connected to the ring gear of the second planetary gear device. And the carrier and the ring gear of the first planetary gear device are respectively coupled to the ring gear and the carrier of the second planetary gear device, and the rotational output in the first operation mode. A member is connected to the connecting body of the carrier of the first planetary gear device and the ring gear of the second planetary gear device, and in the second operation mode. In the case where the rotation output member is connected to the sun gear of the first planetary gear device, the engine rotation speed and the rotation speed of the motor generator mainly for power generation can be made to correspond. The distance between the two rotational speed coordinate axes is relatively large, while the carrier and the ring gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively, and the first operation mode In the second operation mode, the rotation output member is connected to a connecting body of the carrier of the first planetary gear device and the sun gear of the second planetary gear device, and the rotation output member is connected in the second operation mode. When the first planetary gear device is connected to the sun gear, and the carrier of the first planetary gear device and the sun gear are respectively connected to the second planetary gear device. And the rotation output member is connected to the carrier of the first planetary gear device and the sun gear of the second planetary gear device in the first operation mode, In the second operation mode, when the rotation output member is connected to the ring gear of the first planetary gear device, the rotation speed of the motor generator mainly for engine rotation and power generation The distance between the two rotation speed coordinate axes that can correspond to is relatively small.

  The transmission as described above can switch between the first operation mode and the second operation mode by making all the rotation speeds of the three rotation elements of the first and second planetary gear devices equal to each other. Therefore, the operation mode can be smoothly switched without causing any step change in all the rotational speeds of the four rotating parts in the compound planetary gear device.

  The control means is in the first operation mode until the rotation speed of the rotation output member reaches a predetermined upper limit value, and the second operation is performed when the rotation speed of the rotation output member exceeds the upper limit value. If the operation mode is controlled so as to be in the mode, the upper limit value is appropriately set, so that the timing for switching from the operation mode for the low-speed driving to the operation mode for the high-speed driving is set to the vehicle speed. Can be done appropriately.

  Further, the control means operates to return the operation mode to the first operation mode when the rotation speed of the rotation output member decreases below a predetermined lower limit value lower than the upper limit value in the second operation mode. If the mode is controlled, it is possible to switch from the operation mode for high-speed traveling to the operation mode for low-speed traveling by providing an appropriate hysteresis for switching the operation mode according to the vehicle speed.

  The transmission further includes a rotation input member and another clutch, and the rotation output member is disposed between a rotation unit corresponding to one of the rotation speed coordinate axes and a rotation unit corresponding to the other one. When the connection can be switched, the rotation input member is switched and connected between the two rotating parts by the other one clutch, contrary to the connection switching of the rotation output member. A hybrid power source device that can drive a vehicle in response to both low-speed and high-speed running by the engine and the electric motor by connecting a motor generator that operates mainly as an electric motor to the rotation input member. Can be obtained.

  Corresponds to the first coordinate axis when the four rotation speed coordinate axes in the collinear diagram are set as the first coordinate axis, the second coordinate axis, the third coordinate axis, and the fourth coordinate axis from one end to the other end. The rotating unit is connected to at least a first electric device that operates as a generator, the rotating unit corresponding to the second coordinate axis is connected to an engine, and the rotation input member is connected to at least a second electric device that operates as an electric motor. If connected and the vehicle is driven by the rotational output member, the rotational output member rotational speed coordinate axis is switched between the third coordinate axis and the fourth coordinate immediately adjacent to the second coordinate axis with respect to the engine rotational speed. By switching between the first and second operation modes, the degree of change in the distance between the rotation output member rotation speed coordinate axis and the engine rotation speed coordinate axis is emphasized, and the speed change characteristics and high performance suitable for low-speed driving of the vehicle are achieved. It can take adequate response to the difference between the transmission characteristics suitable for traveling.

  FIG. 1 is a schematic view showing an embodiment in which a transmission according to the present invention is applied to a hybrid power source device for a vehicle. In the figure, P1 and P2 are planetary gear units having sun gears S1, S2, ring gears R1, R2, and carriers C1, C2, respectively. The carrier C1 is connected to the sun gear S2 and the ring gear R1 is connected to the carrier C2. As a result, the two planetary gear units are combined to form a compound planetary gear unit having four parts, that is, the sun gear S1, the coupling body of the carrier C1 and the sun gear S2, the coupling body of the ring gear R1 and the carrier C2, and the ring gear R2. Yes.

  In this example, the engine ENG is connected to the connecting body of the ring gear R1 and the carrier C2, the first motor generator MG1 is connected to the ring gear R2, and the connecting body of the carrier C1 and the sun gear S2 and the sun gear S1 are 2 The rotation output member Out for driving the wheel and the second motor generator MG2 are switched to be coupled to each other through a clutch CL including two interlocking switching engaging portions. In the illustrated clutch switching state, the rotation output member Out is connected to the connecting body of the carrier C1 and the sun gear S2, and the second motor generator MG2 is connected to the sun gear S1. The first motor generator MG1 and the second motor generator MG2 are electrically connected to the battery B via the inverter I. The operations of the engine ENG, the clutch CL, and the inverter I are controlled by an electronic control unit ECU having a microcomputer.

  2A and 2B are individual alignment charts for planetary gear devices P1 and P2 in the transmission shown in FIG. 1, respectively. In FIG. 3A, three coordinate axes R1, C1, and S1 that are parallel to each other are coordinate axes that represent the rotational speeds of the ring gear R1, the carrier C1, and the sun gear S1, respectively, and are relative to the number of teeth (or diameter) of the ring gear R1. If the ratio of the number of teeth (or diameter) of the sun gear S1 is ρ1 (<1), the contrast between the distance between the coordinate axis R1 and the coordinate axis C1 and the distance between the coordinate axis C1 and the coordinate axis S1 is ρ1: 1. . If a straight line that crosses these three coordinate axes is drawn, the values on the coordinate axes R1, C1, and S1 at the points where they intersect with the coordinate axes R1, C1, and S1 are the rotational speeds of the ring gear R1. Nr1, the rotation speed Nc1 of the carrier C1, and the rotation speed Ns1 of the sun gear S1 are given.

  Similarly, in FIG. 3B, three coordinate axes R2, C2, and S2 that are parallel to each other are coordinate axes that represent the rotational speeds of the ring gear R2, the carrier C2, and the sun gear S2, respectively, and the number of teeth (or diameter) of the ring gear R2. ) Is the ratio of the number of teeth (or diameter) of the sun gear S2 to ρ2 (<1), the contrast between the distance between the coordinate axis R2 and the coordinate axis C2 and the distance between the coordinate axis C2 and the coordinate axis S2 is ρ2: 1. ing. Similarly, if a straight line that crosses these three coordinate axes is drawn, the values on the coordinate axes R2, C2, and S2 at the points where they intersect with the coordinate axes R2, C2, and S2 are the values of the ring gear R2. The rotational speed Nr2, the rotational speed Nc2 of the carrier C2, and the rotational speed Ns2 of the sun gear S2 are given.

  If the carrier C1 is connected to the sun gear S2 and the ring gear R1 is connected to the carrier C2 as described above, as shown in FIG. 3 (A) and (B), 2A and 2B are combined in the manner of superimposing the coordinate axis C1 and the coordinate axis S2 and superimposing the coordinate axis R1 and the coordinate axis C2, thereby combining the R2 coordinate axis and R1. / C2 coordinate axis, C1 / S2 coordinate axis, and S1 coordinate axis establish four rotating parts whose relative rotational speeds are contrasted, and draw a single straight line across these four coordinate axes. The values on the coordinate axes at the points where R2, R1 / C2, C1 / S2, and S1 intersect are the rotation speed of the ring gear R2 in order from the left, and in the example of FIG. 1, the rotation speed of the first motor generator MG1. Nmg1 The rotational speed of the coupling body of the ring gear R1 and the carrier C2, which is the rotational speed Neng of the engine ENG in the example of FIG. 1, and the rotational speed of the coupling body of the carrier C1 and the sun gear R2, and in the example of FIG. The rotation speed Nout or the rotation speed Nmg2 of the second motor generator MG2 and the rotation speed of the sun gear S2, which are the rotation speed Nmg2 of the second motor generator MG2 or the rotation speed Nout of the rotation output member Out in the example of FIG. To give.

  Therefore, when the rotational speed of the engine ENG corresponds to the coordinate axis for the coupling body of the ring gear R1 and the carrier C2 as in this example, the rotational speed of the rotational output member Out corresponds to the coordinate axis for the coupling body of the carrier C1 and the sun gear S2. When the rotation output member Out is in the state of FIG. 3A and when the rotation speed of the rotation output member Out is in the state of FIG. 3B corresponding to the coordinate axis for the sun gear S1, the rotation output member for the engine rotation speed Neng. The degree of change in the rotation speed Nout of the latter can be made larger than that of the former in the latter. This is because when the vehicle is driven by the apparatus shown in FIG. 1, when the vehicle is traveling at a low speed, it is operated in the operation mode shown in FIG. It shows that it is appropriate to operate in the operation mode shown in FIG.

  In particular, in the example shown in FIG. 1, if the distance between the coordinate axis for the coupling body of the ring gear R1 and the carrier C2 and the coordinate axis for the coupling body of the carrier C1 and the sun gear S2 is 1, the coordinate axis for the coupling body of the carrier C1 and the sun gear S2. And the coordinate axis for the sun gear S1 is 1 / ρ1. The value of ρ1 is the ratio of the number of teeth (or diameter) of the sun gear to the number of teeth (or diameter) of the ring gear in the planetary gear device, and is a value around 0.5, so 1 / ρ1 is a value around 2 is there. Therefore, in this example, in the operation mode of FIG. 3A and the operation mode of FIG. 3B, the degree of change in the rotational speed of the rotational output member with respect to the engine rotational speed Neng is compared with the former in the latter. Thus, it can be made particularly large as 1: 1 + 1 / ρ1 (about 1: 3). This indicates that the apparatus shown in FIG. 1 is particularly suitable for a vehicle having a high maximum speed.

  FIG. 4 is a collinear diagram illustrating a state where the hybrid vehicle including the power source device described above with reference to FIGS. 1 to 3 is in a stopped state and the engine is also stopped. When the vehicle is started from such a stopped state, for example, as shown in FIG. 5, first, the second motor generator MG2 is operated as an electric motor while the engine is stopped, and at this time, the engine is stopped. The low-speed operation of the vehicle may be started by electric drive by simultaneously operating the first motor generator MG1 as a motor.

  As a result, the running speed of the vehicle increases, and when the engine speed reaches an appropriate value for starting the engine as shown in the nomogram of FIG. 6, if the engine is cranked, the engine is started here. Can do.

  Further, if the traveling speed of the vehicle increases and the alignment chart is in a state as shown in FIG. 7, the vehicle may be appropriately operated using either or both of engine driving and electric driving. When the running speed of the vehicle increases beyond a predetermined upper limit value Ncu as seen from the rotational speed Nout of the rotational output member, the rotational speeds of the engine, the first motor generator, and the second motor generator are set appropriately. To create a state in which these rotational speeds are once the same as shown in the collinear diagram of FIG. 8, and in this state, the clutch is switched, and the operation mode of FIG. It is only necessary to switch to the operation mode B), whereby the operation mode can be switched smoothly. Further, when operating in the operation mode of FIG. 3B, when the vehicle speed decreases, the vehicle speed decreases below a predetermined lower limit value Ncd that is lower than the upper limit value Ncu by an appropriate value as shown in FIG. It is only necessary to switch from the operation mode of FIG. 3B to the operation mode of FIG. Also at this time, if the control for creating the state shown in the collinear diagram of FIG. 9 is performed prior to switching, the operation mode can be switched smoothly.

  When the switching from the operation mode of FIG. 3A to the operation mode of FIG. 3B is completed, the operation can be arbitrarily performed within the operation mode as illustrated in the alignment chart of FIG. May be performed appropriately. In the operation mode of FIG. 3B, the vehicle speed can be greatly increased without increasing the engine speed as shown in FIG.

  FIG. 12 is an alignment chart showing an example when the vehicle is driven backward by electric drive. As a matter of course, the operation mode of FIG. 3A is suitable for the reverse drive of the vehicle by such electric drive.

  FIG. 13 is a schematic view showing another embodiment when the transmission according to the present invention is applied to a hybrid power source device for a vehicle. FIGS. 14 (A) and 14 (B) are the same as FIG. 15A and 15B are collinear diagrams for each of the planetary gear devices P1 and P2 constituting the transmission of FIG. 15, and FIGS. 15A and 15B are collinear diagrams for the compound planetary gear device in the transmission of FIG. It shows about two operation modes switched by a clutch. 13 to FIG. 15 correspond to FIG. 1 to FIG. 3 showing the first embodiment in the manner shown in the figure, and P1, P2,. . . 1 to 3 are the same as those in FIGS. 1 to 3, and therefore, the embodiment of FIGS. 13 to 15 is duplicated with respect to matters that can be easily inferred from the description of FIGS. 1 to 3. The explanation is omitted to avoid redundancy of the specification.

  In this embodiment, the carrier C1 is connected to the sun gear S2, and the ring gear R1 is connected to the carrier C2, so that the two planetary gear devices are combined, and the sun gear S1, the connecting body of the carrier C1 and the sun gear S2, A compound planetary gear device is configured in which the connecting body of the ring gear R1 and the carrier C2 and the ring gear R2 are four rotating parts. Therefore, the structure of the compound planetary gear device itself is the same as that in FIG. However, in this embodiment, the engine ENG is connected to the connecting body of the carrier C1 and the sun gear S2, the first motor generator MG1 is connected to the sun gear S1, and the connecting body of the ring gear R1 and the carrier C2 and the ring gear. R2 is connected to the rotation output member Out for driving the wheel and the second motor generator MG2 through the two clutches CL1 and CL2 while being switched reciprocally. In the illustrated clutch switching state, the rotation output member Out is connected to the connecting body of the ring gear R1 and the carrier C2, and the second motor generator MG2 is connected to the ring gear R2, which is suitable for low-speed driving of the vehicle shown in FIG. The operation mode shown in FIG.

  Also in this embodiment, the distance that the coordinate axis with respect to the rotation speed of the rotation output member Out is separated from the coordinate axis with respect to the engine rotation speed in the operation mode shown in FIG. Since the operation mode is increased by switching to the operation mode shown in B), the operation modes shown in FIGS. 15A and 15B are suitable for low-speed driving and high-speed driving of the vehicle, respectively. However, in this embodiment, the distance that the coordinate axis for the rotational speed of the rotation output member is separated from the coordinate axis for the engine rotational speed by the mode switching from the operational mode of FIG. 15 (A) to the operational mode of FIG. 15 (B). 1 to 3 is smaller than that in the embodiment shown in FIGS. 1 to 3, the range in which the rotation speed of the rotation output member is changed with respect to the engine rotation speed is the same as that in the embodiment shown in FIGS. Therefore, if this embodiment is compared with the embodiment shown in FIGS. 1 to 3, the embodiment shown in FIGS. 1 to 3 is suitable for a vehicle having a high maximum vehicle speed. The embodiment shown in FIGS. 13 to 15 is suitable for a vehicle whose maximum vehicle speed is not so high.

  However, on the other hand, regarding the distance between the coordinate axis with respect to the rotational speed of the first motor generator MG1 mainly operating as a power generator and the coordinate axis with respect to the engine rotational speed, the embodiment shown in FIGS. 1 to 3 and FIGS. In the embodiment shown in FIG. 15, the distance in the former is short and the distance in the latter is long. Accordingly, in the embodiment shown in FIGS. 13 to 15, the adjustment is made between the engine speed obtained by switching the operation mode between the two operation modes and the rotation speed of the first motor generator. The allowable width is larger in the embodiment shown in FIGS. 13 to 15 than in the embodiment shown in FIGS.

  FIG. 16 is a schematic view showing still another embodiment in which the transmission according to the present invention is applied to a hybrid power source device for a vehicle, and FIGS. 17 (A) and 17 (B) are diagrams. 18 is a collinear diagram for each of the planetary gear devices P1 and P2 constituting the sixteen transmissions, and FIGS. 18A and 18B are collinear diagrams for the compound planetary gear device in the transmission of FIG. Are shown for two operation modes that can be switched by a clutch. FIGS. 16 to 18 also correspond to FIGS. 1 to 3 showing the first embodiment in the manner shown in the drawings, and P1, P2,. . . 1 to 3 are the same as those in FIGS. 1 to 3, and the embodiments of FIGS. 16 to 18 are duplicated with respect to matters that can be easily inferred from the description of FIGS. 1 to 3. The description is omitted to avoid redundancy of the specification.

  In this embodiment, the carrier C1 is connected to the sun gear S2, and the sun gear S1 is connected to the carrier C2, whereby the two planetary gear units are combined, and the ring gear R2, the connected body of the sun gear S1 and the carrier C2, A compound planetary gear device is configured in which the connecting body of the carrier C1 and the sun gear S2 and the ring gear R1 are four rotating parts. The engine ENG is connected to the connecting body of the sun gear S1 and the carrier C2, the first motor generator MG1 is connected to the ring gear R2, and the connecting body of the carrier C1 and the sun gear S2 and the ring gear R1 have two switching portions. The rotation output member Out for driving the wheel and the second motor generator MG2 are switched and coupled to each other via the interlocking clutch CL. In the illustrated clutch switching state, the rotation output member Out is connected to the connecting body of the carrier C1 and the sun gear S2, and the second motor generator MG2 is connected to the ring gear R1, which is suitable for low-speed driving of the vehicle in FIG. The operation mode shown in FIG.

  Also in this embodiment, the distance that the coordinate axis with respect to the rotation speed of the rotation output member Out is separated from the coordinate axis with respect to the engine rotation speed in the operation mode shown in FIG. Since the operation mode is increased by switching to the operation mode shown in B), the operation modes shown in FIGS. 18A and 18B are suitable for low-speed driving and high-speed driving of the vehicle, respectively. Also in this embodiment, the distance that the coordinate axis for the rotational speed of the rotation output member is separated from the coordinate axis for the engine rotational speed by the mode switching from the operational mode of FIG. 18 (A) to the operational mode of FIG. 18 (B). 1 to 3 is smaller than that in the embodiment shown in FIGS. 1 to 3, the range in which the rotation speed of the rotation output member is changed with respect to the engine rotation speed is the same as that in the embodiment shown in FIGS. Therefore, if this embodiment is compared with the embodiment shown in FIGS. 1 to 3, the embodiment shown in FIGS. 1 to 3 is suitable for a vehicle having a high maximum vehicle speed. The embodiment shown in FIGS. 16 to 18 is suitable for a vehicle whose maximum vehicle speed is not so high.

  FIG. 19 is a schematic diagram showing still another embodiment in which the transmission according to the present invention is applied to a hybrid power source device for a vehicle, and FIGS. 20 (A) and 20 (B) are diagrams. FIG. 22 is a collinear diagram for each of the planetary gear devices P1 and P2 constituting the nineteen transmission device, and FIGS. 21A and 21B are collinear diagrams for the compound planetary gear device in the transmission device of FIG. Are shown for two operation modes that can be switched by a clutch. FIGS. 19 to 21 also correspond to FIGS. 1 to 3 showing the first embodiment in the manner shown in the drawing, and P1, P2,. . . 1 to 3 are the same as those in FIGS. 1 to 3, and the embodiments of FIGS. 19 to 21 are duplicated with respect to matters that can be easily inferred from the description of FIGS. 1 to 3. The description is omitted to avoid redundancy of the specification.

  In this embodiment, the ring gear R1 is connected to the carrier C2, and the carrier C1 is connected to the ring gear R2, whereby the two planetary gear units are combined, and the sun gear S2, the connecting body of the ring gear R1 and the carrier C2, A compound planetary gear device is configured in which the connecting body of the carrier C1 and the ring gear R2 and the sun gear S1 are four rotating parts. The engine ENG is connected to the connecting body of the ring gear R1 and the carrier C2, the first motor generator MG1 is connected to the sun gear S2, and the connecting body of the carrier C1 and the ring gear R2 and the sun gear S1 include two switching portions. The rotation output member Out for driving the wheel and the second motor generator MG2 are switched in a reciprocal manner and connected to each other via the interlocking clutch CL. In the illustrated clutch switching state, the rotation output member Out is connected to the connecting body of the carrier C1 and the ring gear R2, and the second motor generator MG2 is connected to the sun gear S1, which is suitable for low-speed driving of the vehicle in FIG. The operation mode shown in FIG.

  Also in this embodiment, the distance that the coordinate axis with respect to the rotation speed of the rotation output member Out is separated from the coordinate axis with respect to the engine rotation speed in the operation mode shown in FIG. Since the operation mode is increased by switching to the operation mode shown in B), the operation modes shown in FIGS. 21A and 21B are suitable for low-speed driving and high-speed driving of the vehicle, respectively. Further, in this embodiment, the distance that the coordinate axis for the rotation speed of the rotation output member is separated from the coordinate axis for the engine rotation speed by the mode switching from the operation mode of FIG. 21 (A) to the operation mode of FIG. 21 (B). 1 to 3 is large as in the embodiment shown in FIGS. 1 to 3, the range in which the rotational speed of the rotation output member is changed with respect to the engine rotational speed is the embodiment shown in FIGS. 1 to 3. Therefore, this embodiment is suitable for a vehicle having a high maximum vehicle speed as in the embodiment shown in FIGS.

  In this embodiment, the distance between the coordinate axis with respect to the rotational speed of the first motor generator MG1 that mainly operates as a power generator and the coordinate axis with respect to the engine rotational speed is as shown in FIGS. As big as in form. Therefore, in this embodiment, the width allowed for adjustment between the engine speed obtained by switching the operation mode between the two operation modes and the rotation speed of the first motor generator is also as follows: The embodiment shown in FIGS. 1 to 3 and the embodiment shown in FIGS. 16 to 18 are larger than those in the embodiment.

  While the present invention has been described in detail with respect to several embodiments thereof, it will be apparent to those skilled in the art that various modifications can be made to these embodiments within the scope of the present invention. .

BRIEF DESCRIPTION OF THE DRAWINGS Schematic which shows one embodiment at the time of applying the transmission device by this invention to the hybrid type power source device for vehicles. (A) And (B) is an individual alignment chart about two planetary gear apparatuses contained in the transmission shown in FIG. 1, respectively. (A) And (B) is a collinear diagram which shows two operation modes of the hybrid type power source device shown in FIG. 1, respectively. The collinear diagram which shows a state when the hybrid vehicle provided with the power source device shown in FIGS. 1-3 is a stop state and the engine is also stopped. The collinear diagram which shows a state when the hybrid vehicle provided with the power source device shown in FIGS. 1 to 3 is operated at a low speed by electric drive while the engine is stopped. The collinear diagram which shows a state when an engine is cranked during driving | running | working of the hybrid vehicle provided with the power source device shown in FIGS. 1-3 is a collinear diagram showing the upper limit value and the lower limit value of the operation mode switching depending on the running state of the hybrid vehicle having the power source device shown in FIGS. . FIG. 4 is a collinear diagram showing an operation state adjusted when switching from the operation mode of FIG. 3A to the operation mode of FIG. FIG. 9 is a collinear diagram illustrating an operation state immediately after switching from the operation mode of FIG. 3A to the operation mode of FIG. FIG. 4 is a collinear diagram illustrating an example of an operation state in the operation mode of FIG. FIG. 4 is a collinear diagram illustrating an ultra-high speed operation state according to the operation mode of FIG. The collinear diagram which shows an example at the time of moving backward of a vehicle by electric drive. Schematic which shows another one Embodiment at the time of applying the transmission by this invention to the hybrid type power source device for vehicles. (A) And (B) is an individual alignment chart about two planetary gear apparatuses contained in the transmission shown in FIG. 13, respectively. (A) And (B) is a collinear diagram which shows two operation modes of the hybrid type power source device shown in FIG. 13, respectively. Schematic which shows another one Embodiment at the time of applying the transmission by this invention to the hybrid type power source device for vehicles. (A) And (B) is an individual alignment chart about two planetary gear apparatuses contained in the transmission shown in FIG. 16, respectively. (A) And (B) is a collinear diagram which shows two operation modes of the hybrid type power source device shown in FIG. 16, respectively. Schematic which shows another one Embodiment at the time of applying the transmission by this invention to the hybrid type power source device for vehicles. (A) And (B) is an individual alignment chart about two planetary gear apparatuses contained in the transmission shown in FIG. 19, respectively. (A) And (B) is a collinear diagram which shows two operation modes of the hybrid type power source device shown in FIG. 19, respectively.

Explanation of symbols

  P1, P2 ... planetary gear unit, S1, S2 ... sun gear, R1, R2 ... ring gear, C1, C2 ... carrier, CL, CL1, CL2 ... clutch, ENG ... engine, machine MG1, MG2 ... motor generator, Out ... rotation Output member, I ... Inverter, B ... Battery, ECU ... Electronic control unit

Claims (10)

  Each of the two rotating elements in one of the first and second planetary gear units each having three rotating elements, each of which is a sun gear, ring gear and carrier, is individually connected to each of the two rotating elements in the other. A combined planetary gear device having four types of rotating parts, which are associated with each other by a collinear diagram composed of four parallel rotation speed coordinate axes, a rotation output member, and a clutch A first operation mode in which the rotation output member is connected to a rotation portion corresponding to one of the rotation speed coordinate axes by the clutch, and the rotation output member is connected to another rotation speed coordinate axis by the clutch. A transmission device characterized in that it can be switched between a second operation mode connected to a rotating part corresponding to one.   The carrier and the ring gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively, and the rotation output member is the first planetary gear device in the first operation mode. Of the second planetary gear device, and the rotation output member is connected to the sun gear of the first planetary gear device in the second operation mode. The transmission according to claim 1.   The carrier and the ring gear of the first planetary gear device are connected to the sun gear and the carrier of the second planetary gear device, respectively, and the rotation output member is the first planetary gear device in the first operation mode. And the rotation output member is connected to the ring gear of the second planetary gear device in the second operation mode. The transmission according to claim 1.   The carrier and the sun gear of the first planetary gear device are respectively connected to the sun gear and the carrier of the second planetary gear device, and in the first operation mode, the rotation output member is the first planetary gear device. Of the second planetary gear device and the sun gear of the second planetary gear device, and in the second operation mode, the rotation output member is connected to the ring gear of the first planetary gear device. The transmission according to claim 1.   The carrier and the ring gear of the first planetary gear device are respectively coupled to the ring gear and the carrier of the second planetary gear device, and the rotation output member is the first planetary gear device in the first operation mode. Of the second planetary gear unit and the ring gear of the second planetary gear unit. In the second operation mode, the rotation output member is coupled to the sun gear of the first planetary gear unit. The transmission according to claim 1.   And control means for switching between the first operation mode and the second operation mode by making all the rotation speeds of the three rotation elements of the first and second planetary gear devices equal to each other. The transmission according to any one of claims 1 to 5.   The control means is in the first operation mode until the rotation speed of the rotation output member reaches a predetermined upper limit value, and when the rotation speed of the rotation output member exceeds the upper limit value, the second operation mode is set. The transmission according to any one of claims 1 to 6, wherein the operation mode is controlled so as to perform the operation.   The control means sets an operation mode to return the operation mode to the first operation mode when the number of rotations of the rotation output member decreases below a predetermined lower limit value lower than the upper limit value in the second operation mode. The transmission according to claim 7, wherein the transmission is controlled.   Furthermore, it has a rotation input member and another one clutch, and the said rotation output member can switch a connection between the rotation part corresponding to one of the said rotation speed coordinate axes, and the rotation part corresponding to another one. The rotation input member is switched and connected between the two rotation parts by the other one clutch, contrary to the connection switching of the rotation output member. The transmission according to any one of 1 to 8. Corresponds to the first coordinate axis when the four rotation speed coordinate axes in the collinear diagram are set as the first coordinate axis, the second coordinate axis, the third coordinate axis, and the fourth coordinate axis from one end to the other end. The rotating unit is connected to at least a first electric device that operates as a generator, the rotating unit corresponding to the second coordinate axis is connected to an engine, and the rotation input member is connected to at least a second electric device that operates as an electric motor. The transmission according to claim 9, wherein the transmission is connected and the vehicle is driven by the rotation output member.

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