Method for controlling operating modes of a hybrid powertrain mechanism

Abstract

A method for controlling operating modes of a hybrid powertrain mechanism including a first epicyclic train having first and second sun gears and a planetary gear couplable to these sun gears; a second epicyclic train having third and fourth sun gears and a planetary gear couplable to these sun gears; a first electric machine having one end coupled to the second sun gear; a second electric machine having one end coupled to the fourth sun gear; a first clutch having one end coupled to another end of the first electric machine; a first brake having one end coupled to another end of the first clutch and another end coupled to the third sun gear; and an engine coupled to the first sun gear. Various driving modes are provided by changing the states of the first clutch and the first brake and the operating modes of the first and second electric machines.

Claims

1. A method for controlling operating modes of a hybrid powertrain mechanism including a first epicyclic train, a second epicyclic train, a first electric machine, a second electric machine, a first clutch, a first brake, and an engine, the method comprising: releasing the first clutch; and engaging the first brake to generate an operating mode that is selected from: a second electric mode, wherein when the engine is stopped, the first electric machine is started as a power source to output power through the first epicyclic train and cause the engine to idle, and the second electric machine is started to drive the second epicyclic train to output power; a third hybrid mode, wherein the engine is started as a power source to output power through the first epicyclic train, the first electric machine is started to output power through the first epicyclic train, and the second electric machine is started as a power source to drive the second epicyclic train to output power; or a fourth engine mode, wherein the engine is started as a power source to output power through the first epicyclic train, but neither the first electric machine nor the second electric machine is started to serve as a power source, instead, the first electric machine or the second electric machine serves as a generator.

2. A method for controlling operating modes of a hybrid powertrain mechanism including a first epicyclic train, a second epicyclic train, a first electric machine, a second electric machine, a first clutch, a first brake and an engine, the method comprising: engaging the first clutch; and releasing the first brake to generate an operating mode that is an optimum engine mode, wherein the first electric machine or the second electric machine serves as a generator or a motor so as to cause the engine to operate under an optimum rotating speed according to the rotating speed of the first electric machine or the second electric machine.

3. A method for controlling operating modes of a hybrid powertrain mechanism including a first epicyclic train, a second epicyclic train, a first electric machine, a second electric machine, a first clutch, a first brake, a third clutch and an engine, the method comprising: releasing the first clutch; engaging the first brake; and engaging the third clutch to generate an operating mode that is selected from: a second electric mode, wherein when the engine is stopped, the first electric machine is started as a power source to output power through the first epicyclic train and cause the engine to idle, and the second electric machine is started to drive the second epicyclic train to output power; a third hybrid mode, wherein the engine is started as a power source to output power through the first epicyclic train, the first electric machine is started to output power through the first epicyclic train, and the second electric machine is started as a power source to drive the second epicyclic train to output power; or a fourth engine mode, wherein the engine is started as a power source to output power through the first epicyclic train, but neither the first electric machine nor the second electric machine is started to serve as a power source, instead, the first electric machine or the second electric machine serves as a generator.

4. A method for controlling operating modes of a hybrid powertrain mechanism including a first epicyclic train, a second epicyclic train, a first electric machine, a second electric machine, a first clutch, a first brake, a third clutch and an engine, the method comprising: engaging the first clutch; releasing the first brake; and engaging the third clutch to generate an operating mode that is selected from: a second electric mode, wherein the engine is not started, the first electric machine is started as a power source to output power through the first epicyclic train and cause the engine to idle, and the second electric machine is started as a power source to drive the second epicyclic train to output power; a third hybrid mode, wherein the engine is started to output power through the first epicyclic train, the second electric machine is started to drive the second epicyclic train to output power; or a fourth engine mode, wherein the engine is started, but neither the first electric machine nor the second electric machine is started to serve as a power source, instead, the first electric machine and the second electric machine serve as generators.

5. A method for controlling operating modes of a hybrid powertrain mechanism including a first epicyclic train, a second epicyclic train, a first electric machine, a second electric machine, a first clutch, a first brake, a third clutch, and an engine, the method comprising: releasing the first clutch; engaging the first brake; and releasing the third clutch to generate an operating mode that is a second electric mode, wherein when the engine is stopped, the first electric machine is started as a power source to output power through the first epicyclic train and the second electric machine is started to drive the second epicyclic train to output power.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1A is a schematic diagram of a hybrid powertrain mechanism according to a first embodiment of the present disclosure;

(2) FIG. 1B is a schematic diagram of a hybrid powertrain mechanism according to a second embodiment of the present disclosure;

(3) FIG. 2 is a schematic diagram of a hybrid powertrain mechanism according to a third embodiment of the present disclosure;

(4) FIG. 3 is a schematic diagram of a hybrid powertrain mechanism according to a fourth embodiment of the present disclosure; and

(5) FIGS. 4A to 4D are schematic diagrams showing various driving modes of the hybrid powertrain mechanism of the present disclosure.

DETAILED DESCRIPTION

(6) The following illustrative embodiments are provided to illustrate the present disclosure, these and other advantages and effects can be apparent to those in the art after reading this specification. It should be noted that all the drawings are not intended to limit the present disclosure. Various modifications and variations can be made without departing from the spirit of the present disclosure.

(7) FIGS. 1A and 1B are schematic diagrams of a hybrid powertrain mechanism 1000 according to a first embodiment and a second embodiment of the present disclosure. Referring to FIG. 1A, the hybrid powertrain mechanism 1000 of the first embodiment has a first epicyclic train 1, a second epicyclic train 2, a first electric machine 30, a second electric machine 31, a first clutch 40, a first brake 41, a first transmission shaft 50, a second transmission shaft 51, a differential 6 and an engine 7. The second embodiment differs from the first embodiment in that the hybrid powertrain mechanism 1000 further has a third clutch 42.

(8) Referring to FIG. 1A, the first epicyclic train 1 has a first sun gear 10, a second sun gear 11, and a first planetary gear 12 coupled to the first sun gear 10 and the second sun gear 11. The first planetary gear 12 has a first planetary gear 120, a second planetary gear 121, a first planetary shaft 122 coupled to the first planetary gear 120 and the second planetary gear 121, and a first planetary carrier 123 coupled to the first planetary shaft 122. The first planetary gear 120 is coupled to an outer periphery of the first sun gear 10, and the second planetary gear 121 is coupled to an outer periphery of the second sun gear 11.

(9) The second epicyclic train 2 has a third sun gear 20, a fourth sun gear 21, and a second planetary gear 22 coupled to the third sun gear 20 and the fourth sun gear 21. The second planetary gear 22 has a third planetary gear 220, a fourth planetary gear 221, a second planetary shaft 222 coupled to the third planetary gear 220 and the fourth planetary gear 221, and a second planetary carrier 223 coupled to the second planetary shaft 222. The third planetary gear 220 is coupled to an outer periphery of the third sun gear 20, and the fourth planetary gear 221 is coupled to an outer periphery of the fourth sun gear 21.

(10) One end of the first electric machine 30 is coupled to the second sun gear 11 so as to be connected to the first epicyclic train 1, and another end of the first electric machine 30 coupled to one end of the first clutch 40. Another end of the first clutch 40 is coupled to one end of the first brake 41. Another end of the first brake 41 is coupled to the third sun gear 20. One end of the second electric machine 31 is coupled to the fourth sun gear 21. The first brake is fixingly disposed. The first electric machine 30 and the first clutch 40 are disposed between the first epicyclic train 1 and the second epicyclic train 2.

(11) The differential 6 is coupled to the first planetary carrier 123 and the second planetary carrier 223 through the first transmission shaft 50 so as to be coupled to the first epicyclic train 1 and the second epicyclic train 2. Further, a transmission mechanism such as a gear train can be disposed between the differential 6 and the first epicyclic train 1 and between the differential 6 and the second epicyclic train 2 for coupling the differential 6 to the first epicyclic train 1 and the second epicyclic train 2. That is, the connection relationship between the differential 6 and the first epicyclic train 1 and between the differential 6 and the second epicyclic train 2 can be varied according to the practical need and detailed description thereof is omitted herein.

(12) The engine 7 is coupled to the first sun gear 10 through the second transmission shaft 51.

(13) Therefore, the first epicyclic train 1, the second epicyclic train 2, the first clutch 40 and the first brake 41 constitute a hybrid powertrain mechanism. The first electric machine 30 and the second electric machine 31 can deliver power through the first epicyclic train 1 and the second epicyclic train 2. Further, by changing the states (engaged or released) of the first clutch 40 and the first brake 41, the operating modes of the first electric machine 30, the second electric machine 31, the engine 7 and the differential 6 can be adjusted, which will be detailed later.

(14) Referring to FIG. 1B, the second embodiment differs from the first embodiment in that the third clutch 42 is provided between the first epicyclic train 1 and the engine 7. One end of the third clutch 42 is coupled to the engine 7 and another end of the third clutch 42 is coupled to the first sun gear 10 so as to be connected to the first epicyclic train 1. As such, when the third clutch 42 is released, the engine 7 that is not started will not be brought to idle by the first electric machine 30 or the second electric machine 31, thereby saving energy.

(15) FIGS. 2 and 3 are schematic diagrams showing the hybrid powertrain mechanism 1000 according to a third embodiment and a fourth embodiment of the present disclosure. It should be noted that the third and fourth embodiments are based on the first embodiment. In the third and fourth embodiments, the connection relationship between the differential 6 and other components is changed.

(16) Referring to FIG. 2, in the third embodiment, the first epicyclic train 1 further has a first connection gear 13 coupled to the first planetary gear 12, and the differential 6 further has a second connection gear 60 engaging with the first connection gear 13. As such, the differential 6 is connected to the first epicyclic train 1 and the operating state of the differential 6 can be changed through the first epicyclic train 1.

(17) Referring to FIG. 3, in the fourth embodiment, the second epicyclic train 2 further has a third connection gear 23 coupled to the second planetary gear 22, and the differential 6 further has a second connection gear 60 engaging with the third connection gear 23. As such, the differential 6 is connected to the second epicyclic train 2 and the operating state of the differential 6 can be changed through the second epicyclic train 2.

(18) In the first to fourth embodiments, the first epicyclic train 1, the second epicyclic train 2, the first electric machine 30, the second electric machine 31, the first clutch 40, the first brake 41, the third clutch 42, the differential 6 and the engine 7 are coaxially disposed so as to simplify the transmission space of the hybrid powertrain mechanism 1000.

(19) Further, the hybrid powertrain mechanism 1000 of the present disclosure dispenses with the internal gears. In the first to fourth embodiments, the first sun gear 10, the second sun gear 11, the third sun gear 20, the fourth sun gear 21, the first planetary gear 120, the second planetary gear 121, the third planetary gear 220, the fourth planetary gear 220, the first connection gear 13, the second connection gear 60 and the third connection gear 23 are external gears. Compared with the internal gears, the external gears are easy to fabricate, thereby reducing the fabrication time. Also, the heat treatment deformation of the external gears is easy to control.

(20) Therefore, the coaxial disposing of the components simplifies the transmission space of the hybrid powertrain mechanism 1000. Further, by dispensing with the internal gears, the present disclosure simplifies the fabrication process and reduces the fabrication cost.

(21) Further, according to the first to fourth embodiments, the differential 6 can be coupled to at least one of the first planetary carrier and the second planetary carrier, thus allowing the hybrid powertrain mechanism 1000 to be designed according to the practical available space. Therefore, the design of the hybrid powertrain mechanism 1000 is very flexible and diversified.

(22) Transmission methods of the hybrid powertrain mechanism 1000 of the present disclosure allow the hybrid powertrain mechanism 1000 to operate at different modes according to various operating states of an object, for example, a vehicle.

(23) Referring to FIG. 4A, a first transmission method of the hybrid powertrain mechanism 1000 includes releasing the first clutch 40 and engaging the first brake 41 (indicated by a black block). Further, the engine 7, the first electric machine 30 and the second electric machine 31 are started, respectively, so as to generate different modes. In a first electric mode, neither the engine 7 nor the first electric machine 30 is started. But only the second electric machine 31 is started as a power source to drive the second epicyclic train 2 to output power to the differential 6. In a second electric mode, the engine 7 is not started. The first electric machine 30 is started as a power source. Through the first epicyclic train 1, the first electric machine 30 provides a torque to output power to the differential 6 and cause the engine to idle. Also, the second electric machine 31 is started to drive the second epicyclic train 2 to output power to the differential 6. In a third hybrid mode, the engine 7 is started as a power source. Through the first epicyclic train 1, the engine 7 provides a torque to output power to the differential 6. Also, the first electric machine 30 is started. Through the first epicyclic train 1, the first electric machine 30 provides a torque to output power to the differential 6. Further, the second electric machine 31 is started as a power source to drive the second epicyclic train 2 to output power to the differential 6. In a fourth engine mode, the engine 7 is started to output power through the first epicyclic train 1. But neither the first electric machine 30 nor the second electric machine 31 is started to serve as a power source. Instead, the first electric machine 30 and the second electric machine 31 can serve as generators. Therefore, the rotating speed of the engine can be adjusted according to different road conditions.

(24) Referring to FIG. 4B, a second transmission method of the hybrid powertrain mechanism 1000 includes releasing the first clutch 40 and engaging and the first brake 41 and the third clutch 42. Since the third clutch 42 between the engine 7 and the electric machine 30 is engaged, the modes generated by the second transmission method are similar to FIG. 4A. Otherwise, if the third clutch 42 is released, different modes will be generated, which are detailed in FIG. 4D.

(25) Referring to FIG. 4C, a third transmission method of the hybrid powertrain mechanism 1000 includes engaging the first clutch 40, releasing the first brake 41, and engaging the third clutch 42. In a first electric mode, neither the engine 7 nor the first electric machine 30 is started. But only the second electric machine 31 is started to drive the second epicyclic train 2 to output power to the differential 6. In a second electric mode, the engine 7 is not started. The first electric machine 30 is started as a power source. Through the first epicyclic train 1, the first electric machine 30 provides a torque to output power to the differential 6 and cause the engine to idle. The second electric machine 30 is started as a power source to drive the second epicyclic train 2 to output power to the differential 6. In a third hybrid mode, the engine 7 is started. Through the first epicyclic train 1, the engine 7 provides a torque to output power to the differential 6. Also, the second electric machine 31 is started to drive the second epicyclic train 2 to output power to the differential 6. In a fourth engine mode, the engine 7 is started. But neither the first electric machine 30 nor the second electric machine 31 is started to serve as a power source. Instead, the first electric machine 30 and the second electric machine 31 can serve as generators. Therefore, the rotating speed of the engine can be adjusted according to different road conditions.

(26) Referring to FIG. 4D, a fourth transmission method of the hybrid powertrain mechanism 1000 includes releasing the first clutch 40, engaging the first brake 41 and releasing the third clutch 42. Different from FIG. 4B, the third clutch 42 is released in FIG. 4D. Different from FIG. 4A, the third clutch 42 at a released state is provided between the engine 7 and the first electric machine 30 in FIG. 4D. As such, when the engine 7 is not started and the first electric machine 30 is started as a power source to provide a torque through the first epicyclic train 1, the engine 7 will not be brought to idle, thereby saving energy. The other operating modes of FIG. 4D are the same as FIG. 4A. Therefore, according to the transmission methods of the hybrid powertrain mechanism 1000, by changing the states (engaged or released) of the first clutch 40, the first brake 41 and the third clutch 42 and respectively starting the engine 7, the first electric machine 30 and the second electric machine 31 as a power source, the hybrid powertrain mechanism 1000 can operate at different modes corresponding to different driving states of the vehicle having the hybrid powertrain mechanism 1000 of the present disclosure.

(27) In the following detailed description, for purposes of explanation, numerous specific details are set forth in order to provide a through understanding of the disclosed embodiments. It will be apparent, however, that one or more embodiments may be practiced without these specific details. In other instances, well-known structures and devices are schematically shown in order to simplify the drawing.