CN102537217B - The unit ratio serial type can independently control the transmission mechanism - Google Patents

Abstract

A unit ratio sequential type independently controllable transmission mechanism comprising: a first planetary gear set including an energy output; a second planetary gear set connected to the first planetary gear set, the second planetary gear set including a control terminal; an energy input end arranged on the second planetary gear set; and a free transmission end arranged on the first planetary gear set, wherein the control end controls the free transmission end to freely switch the free transmission end to be used as one of an energy input end and an energy output end. The invention has the beneficial effects that: the energy transmission efficiency is improved.

Description

The unit ratio serial type can independently control the transmission mechanism

technical field

The invention relates to a transmission mechanism, in particular to an independently controllable transmission mechanism which can improve energy transmission efficiency.

Background technique

Existing transmission mechanisms, such as the gear box structure for vehicles of the Taiwan Patent Announcement No. I242521, disclose that a main shaft is provided with a slide block, and both sides of the slide block are provided with a forward gear and an afterburner gear. A connecting shaft is provided with a reverse slider, and the connecting shaft located on one side of the reverse slider is provided with a reverse bevel gear and a forward bevel gear, and the reverse bevel gear A final shaft is arranged between the forward bevel gear and the forward bevel gear, and the final shaft is driven by the shaft. The final shaft is located between the reverse bevel gear and the forward bevel gear, and the booster gear and the forward The gear is also located between the bevel gear for reverse and the bevel gear for forward, so that the width direction of the gearbox can be reduced, and the bevel gear for reverse and the bevel gear for forward of the interlocking shaft are used to mesh with the bevel gear. A driving bevel gear of the final shaft can make the gearbox miniaturized. However, the gearbox structure is provided with the sliding block, and the sliding block will inevitably produce mutual frictional sliding, thereby relatively reducing its power transmission efficiency.

Another transmission mechanism, such as "Continuously Variable Transmission" of U.S. Patent No. 6,387,004, discloses a continuously variable transmission group. The continuously variable transmission set includes a first planetary gear set and a second planetary gear set, which are used to transmit the power of a first motor and a second motor to a transmission shaft. However, the continuously variable transmission set only transmits the power of the first motor and the second motor to the transmission shaft through the first planetary gear set and the second planetary gear set. In other words, the continuously variable transmission set only sets the first motor and the second motor as two fixed power input ends, and sets the transmission shaft as a single fixed power output end. In short, in terms of power transmission, it is still necessary to further select a transmission mechanism that provides variable control energy input and energy output, so as to meet different power integration transmission requirements.

Contents of the invention

The purpose of the present invention is to improve the deficiencies of the prior art and provide a unit ratio sequence type independently controllable transmission mechanism that can improve energy transmission efficiency.

To achieve the above object, the present invention adopts the following technical solutions:

A unit-ratio sequential type with independent control of the drive mechanism consisting of:

a first planetary gear set including a power output;

a second planetary gear set connected to the first planetary gear set, the second planetary gear set including a control end;

an energy input disposed on the second planetary gear set; and

A free transmission end is arranged on the first planetary gear set, and the control end controls the free transmission end to freely switch the free transmission end as one of the energy input end and the energy output end.

The first planetary gear set and the second planetary gear set are two positive ratio drive planetary gear sets; or the first planetary gear set and the second planetary gear set are two negative ratio drive planetary gear sets; or the The first planetary gear set is a positive ratio drive planetary gear set and the second planetary gear set is a negative ratio drive planetary gear set; or the first planetary gear set is a negative ratio drive planetary gear set, and The second planetary gear set is a proportional driving type planetary gear set.

The first planetary gear set has a first rotation shaft, a second rotation shaft and a third rotation shaft, and the second planetary gear set has a first rotation shaft, a second rotation shaft and a third rotation shaft Shaft; the first rotation axis of the first planetary gear set is the energy output end of the unit ratio sequence type that can independently control the transmission mechanism; the second rotation axis of the first planetary gear set is the unit ratio sequence type that can independently control the transmission The free transmission end of the mechanism; the third rotation shaft of the first planetary gear set is connected to the second planetary gear set; the first rotation shaft of the second planetary gear set is the control of the unit ratio sequence type independently controllable transmission mechanism The second rotation shaft of the second planetary gear set is the energy input end of the unit ratio sequence type independently controllable transmission mechanism; the third rotation shaft of the second planetary gear set is connected to the first planetary gear set.

A unit-ratio sequential type with independent control of the drive mechanism consisting of:

a first planetary gear set including a power output;

a second planetary gear set connected to the first planetary gear set, the second planetary gear set including a control end;

an energy input terminal disposed on the first planetary gear set; and

A free transmission end is arranged on the second planetary gear set, and the control end controls the free transmission end to freely switch the free transmission end as one of the energy input end and the energy output end.

The first planetary gear set and the second planetary gear set are two positive ratio drive planetary gear sets; or the first planetary gear set and the second planetary gear set are two negative ratio drive planetary gear sets; or the The first planetary gear set is a positive ratio drive planetary gear set and the second planetary gear set is a negative ratio drive planetary gear set; or the first planetary gear set is a negative ratio drive planetary gear set, and The second planetary gear set is a proportional driving type planetary gear set.

The first planetary gear set has a first rotation shaft, a second rotation shaft and a third rotation shaft, and the second planetary gear set has a first rotation shaft, a second rotation shaft and a third rotation shaft Shaft; the first rotation axis of the first planetary gear set is the energy output end of the unit ratio sequence type that can independently control the transmission mechanism; the second rotation axis of the first planetary gear set is the unit ratio sequence type that can independently control the transmission The energy input end of the mechanism; the third rotation shaft of the first planetary gear set is connected to the second planetary gear set; the first rotation shaft of the second planetary gear set is the control of the unit ratio sequence type independently controllable transmission mechanism end; the second rotation shaft of the second planetary gear set is the free transmission end of the unit ratio sequence type independently controllable transmission mechanism; the third rotation shaft of the second planetary gear set is connected to the first planetary gear set.

A unit-ratio sequential type with independent control of the drive mechanism consisting of:

two planetary gear sets interconnected;

an energy output end, which is arranged on the planetary gear set;

a control end, which is arranged on the planetary gear set;

an energy input terminal disposed on the planetary gear set; and

A free transmission end is arranged on the planetary gear set, and the control end controls the free transmission end to freely switch the free transmission end as one of the energy input end and the energy output end.

The two planetary gear sets are two positive ratio drive type planetary gear sets; or the two planetary gear sets are two negative ratio drive type planetary gear sets; or one of the two planetary gear sets is a positive ratio drive type planetary gear group, and the other of the two planetary gear sets is a negative ratio drive type planetary gear set.

The two planetary gear sets have a first rotation shaft, a second rotation shaft, a third rotation shaft, a fourth rotation shaft, a fifth rotation shaft and a sixth rotation shaft; the first rotation shaft is the The unit ratio sequence type can independently control the energy output end of the transmission mechanism; the second rotation shaft is the free transmission end of the unit ratio sequence type and can independently control the transmission mechanism; the third rotation shaft is connected between the two planetary gear sets; The fourth rotation axis is the control end of the unit ratio sequence type that can independently control the transmission mechanism; the fifth rotation axis is the energy input end of the unit ratio sequence type that can independently control the transmission mechanism; the sixth rotation axis is connected to the two between planetary gear sets.

The beneficial effects of the invention are: improving energy transmission efficiency.

The present invention will be further described below by accompanying drawing.

Description of drawings

FIG. 1A and FIG. 1B are schematic diagrams of unit ratio sequence type independently controllable transmission mechanisms of the first and second preferred embodiments of the present invention.

2A and 2B are schematic diagrams of the internal structure of the unit ratio sequence type independently controllable transmission mechanism of the first and second preferred embodiments of the present invention.

FIG. 3A and FIG. 3B are schematic diagrams of the internal structure of the unit ratio sequence type independently controllable transmission mechanism using a planetary gear set in a preferred embodiment of the present invention.

4 to 28 are schematic diagrams showing the combination of the unit ratio sequence type independently controllable transmission mechanism consisting of two planetary gear sets in the third to twenty-seventh preferred embodiments of the present invention.

[Description of main component labels]

1 The first planetary gear set 2 The second planetary gear set

OP first rotation axis AD second rotation axis AE third rotation axis

CR first rotation axis BD second rotation axis BE third rotation axis

ps1 sun gear pss1 sun gear rotation shaft

ps2 central gear pss2 central gear rotation shaft

pp1 first planetary gear pp2 second planetary gear

pa planetary arm rotation axis

ns sun gear nss sun gear rotation shaft

nr ring gear nrs ring gear rotation shaft

np planetary gear na planetary arm rotation axis

Detailed ways

In order to fully understand the present invention, preferred embodiments are exemplified below and described in detail with accompanying drawings, which are not intended to limit the scope of protection of the present invention.

The unit ratio sequence type independently controllable transmission mechanism of the preferred embodiment of the present invention can be applied to various technical fields related to mechanical variable speed transmission, such as: marine generators, wind power generators or transmission gearboxes for hybrid vehicles, etc., but it is not It is used to limit the scope of application of the independently controllable transmission mechanism of the present invention.

Figures 1A and 1B disclose schematic diagrams of the unit ratio sequence type of the first and second preferred embodiments of the present invention that can independently control the transmission mechanism; Figures 2A and 2B disclose the unit ratio sequence type of the first and second preferred embodiments of the present invention The internal structure diagram of the transmission mechanism that can be independently controlled. Please refer to Figures 1A, 1B, 2A and 2B, the unit ratio sequence type independently controllable transmission mechanism of the first and second preferred embodiments of the present invention mainly includes a first planetary gear set 1 and a second planetary gear set 2, and the first planetary gear set 1 is mechanically connected to the second planetary gear set 2.

Please refer to Fig. 1A, 1B, 2A and 2B again, the unit ratio sequence type of the first and second preferred embodiments of the present invention can independently control the transmission mechanism with an energy output terminal, a control terminal, an energy input terminal and A free transmission terminal.

1A and 2A, the unit ratio sequence type of the first preferred embodiment of the present invention can independently control the energy output end and the free transmission end of the transmission mechanism corresponding to the first planetary gear set 1, and the control The end and the energy input end correspond to the second planetary gear set 2 .

Please refer to Fig. 1B and 2B again, the unit ratio sequence type of the second preferred embodiment of the present invention can independently control the energy output end and the energy input end of the transmission mechanism corresponding to the first planetary gear set 1, and the control The end and the free transmission end correspond to the second planetary gear set 2 .

Please refer to FIG. 2A , the first planetary gear set 1 has a first rotation shaft OP, a second rotation shaft AD and a third rotation shaft AE. The first rotation axis OP of the first planetary gear set 1 is the energy output end of the independently controllable transmission mechanism; the second rotation axis AD of the first planetary gear set 1 is the free transmission end of the independently controllable transmission mechanism; The third rotation shaft AE of the first planetary gear set 1 is connected to the second planetary gear set 2 . In contrast, the second planetary gear set 2 has a first rotation shaft CR, a second rotation shaft BD and a third rotation shaft BE. The first rotation axis CR of the second planetary gear set 2 is the control end of the independently controllable transmission mechanism; the second rotation axis BD of the second planetary gear set 2 is the energy input end of the independently controllable transmission mechanism; The third rotation shaft BE of the second planetary gear set 2 is connected to the first planetary gear set 1 .

Please refer to FIG. 2B , the first planetary gear set 1 has a first rotation shaft OP, a second rotation shaft AD and a third rotation shaft AE. The first rotation axis OP of the first planetary gear set 1 is the energy output end of the independently controllable transmission mechanism; the second rotation axis AD of the first planetary gear set 1 is the energy input end of the independently controllable transmission mechanism; The third rotation shaft AE of the first planetary gear set 1 is connected to the second planetary gear set 2 . In contrast, the second planetary gear set 2 has a first rotation shaft CR, a second rotation shaft BD and a third rotation shaft BE. The first rotation axis CR of the second planetary gear set 2 is the control end of the independently controllable transmission mechanism; the second rotation axis BD of the second planetary gear set 2 is the free transmission end of the independently controllable transmission mechanism; The third rotation shaft BE of the second planetary gear set 2 is connected to the first planetary gear set 1 .

Please refer to Fig. 1A and 2A again, the unit ratio sequence type of the first preferred embodiment of the present invention can independently control the transmission mechanism using the control end [the first rotating shaft CR] of the second planetary gear set 2 to control the first planetary gear set 2 The free transmission end (the second rotation axis AD) of the planetary gear set 1 can be freely switched as the energy input end or the energy output end. When the free transmission end AD of the first planetary gear set 1 is switched as the energy input end, the free transmission end AD of the first planetary gear set 1 and the energy input end of the second planetary gear set 2 [second rotation Axis BD] common input energy. On the contrary, when the free transmission end AD of the first planetary gear set 1 is switched as the energy output end, the free transmission end AD of the first planetary gear set 1 and the energy output end of the first planetary gear set 1 [ The first rotating shaft OP] jointly outputs energy.

Please refer to Fig. 1B and 2B again, the unit ratio sequence type of the second preferred embodiment of the present invention can independently control the transmission mechanism using the control end [first rotating shaft CR] of the second planetary gear set 2 to control the second planetary gear set 2 The free transmission end (second rotating shaft BD) of the planetary gear set 2 can be freely switched as the energy input end or the energy output end. When the free transmission end BD of the second planetary gear set 2 is switched as the energy input end, the free transmission end BD of the second planetary gear set 2 is connected to the energy input end of the first planetary gear set 1 [second rotation Axis AD] common input energy. Conversely, when the free transmission end BD of the second planetary gear set 2 is switched as the energy output end, the free transmission end BD of the second planetary gear set 2 is connected to the energy output end of the first planetary gear set 1 [ The first rotating shaft OP] jointly outputs energy.

3A to 3B disclose the internal structure of the unit ratio sequential independently controllable transmission mechanism using planetary gear sets in a preferred embodiment of the present invention, which includes the internal structures of two planetary gear sets, but they are not intended to limit the present invention.

Referring to FIG. 3A , the planetary gear set includes a sun gear ps1 , a sun gear rotation shaft pss1 , a central gear ps2 , a central gear rotation shaft pss2 , a planetary arm rotation shaft pa and at least one compound planetary gear. The compound planetary gear includes a first planetary gear pp1 and a second planetary gear pp2. The first planetary gear pp1 and the second planetary gear pp2 mesh with the sun gear ps1 and the central gear ps2. When the rotation axis pa of the planetary arm is fixed, the rotation directions of the sun gear rotation axis pss1 and the central gear rotation axis pss2 are the same direction, and their speed ratio is positive. The planetary gear set is a proportional drive type planetary gear set.

2A, 2B and 3A, the sun gear rotation shaft pss1, the central gear rotation shaft pss2 and the planetary arm rotation shaft pa can be used as the first rotation shaft OP and the second rotation shaft OP of the first planetary gear set 1. Axis AD and a third axis of rotation AE. Alternatively, the sun gear rotation shaft pss1 , the central gear rotation shaft pss2 and the planetary arm rotation shaft pa can be used as the first rotation shaft CR, the second rotation shaft BD and the third rotation shaft BE of the second planetary gear set 2 .

3B, the planetary gear set includes a sun gear ns, a sun gear rotation shaft nss, a ring gear nr, a ring gear rotation shaft nrs, at least one planetary gear np and a planetary arm rotation shaft na. When the rotation axis na of the planetary arm is fixed, the rotation directions of the rotation axis nss of the sun gear and the rotation axis nrs of the ring gear are opposite directions, and the rotation speed ratio thereof is negative. The planetary gear set is a negative ratio drive type planetary gear set.

2A, 2B and 3B, the sun gear rotation axis nss, the ring gear rotation axis nrs and the planetary arm rotation axis na can be used as the first rotation axis OP and the second rotation axis of the first planetary gear set 1. shaft AD and the third rotation shaft AE; or, the sun gear rotation shaft nss, the ring gear rotation shaft nrs and the planetary arm rotation shaft na can be used as the first rotation shaft CR and the second rotation shaft of the second planetary gear set 2 BD and the third axis of rotation BE.

Please refer to Figures 2A and 2B again, the unit ratio sequence type of the present invention can independently control the transmission mechanism and the rotational speed of the first rotating shaft OP (energy input end) of the first planetary gear set 1 and the second planetary gear set 2 The speed ratio of the first rotating shaft CR (control end) is set as a unit ratio,

Its relationship is: $\frac{{\mathrm{no}}_{\mathrm{OP}}}{{\mathrm{no}}_{\mathrm{CR}}}=1$

Where n _OP and n _CR are the rotation speed of the first rotation shaft OP of the first planetary gear set 1 and the rotation speed of the first rotation shaft CR of the second planetary gear set 2 respectively.

At the same time, the unit ratio sequence type of the present invention can independently control the transmission mechanism to set the rotation speed of the second rotation shaft AD of the first planetary gear set 1 and the rotation speed of the third rotation shaft BE of the second planetary gear set 2 as a unit Ratio, its relationship is:

Where n _AD and n _BE are the rotation speed of the second rotation shaft AD of the first planetary gear set 1 and the rotation speed of the third rotation shaft BE of the second planetary gear set 2 respectively.

At the same time, the unit ratio sequence type of the present invention can independently control the transmission mechanism to set the rotation speed of the second rotation shaft BD of the second planetary gear set 2 and the rotation speed of the third rotation shaft AE of the first planetary gear set 1 as a unit Ratio, its relationship is:

Where n _BD and n _AE are the rotation speed of the second rotation shaft BD of the second planetary gear set 2 and the rotation speed of the third rotation shaft AE of the first planetary gear set 1 respectively.

Figures 4 to 28 disclose the combination schematic diagrams of the unit ratio sequence type independently controllable transmission mechanism consisting of two planetary gear sets in the third preferred embodiment to the twenty-seventh preferred embodiment of the present invention, which includes twenty-five kinds of transmission combinations A preferred embodiment, but it is not intended to limit the present invention. Please refer to Figures 4 to 28, the independently controllable transmission mechanisms of the third preferred embodiment to the twenty-seventh preferred embodiment of the present invention include two planetary gear sets [circular dotted line frame, as shown in Figures 3A and 3B ], its detailed internal structure has been disclosed in FIGS. 3A and 3B , and will not be repeated here.

Please refer to Figures 2A, 2B and 4 again. In the third preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by two proportional values. planetary gear set. The two sun gear rotation shafts pss1A and pss1B of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of the two planetary arms of the two planetary gear sets is pa, the common rotation axis of the two central gears ps2A and ps2B is pss2, and the two common rotation axes pa and pss2 can form the first planetary gear set arbitrarily The second rotation axis AD of 1 (the free transmission end of FIG. 2A or the energy input end of FIG. 2B ] and the second rotation axis BD of the second planetary gear set 2 (the energy input end of FIG. 2A or the free transmission end of FIG. 2B ] .

Please refer to Figures 2A, 2B and 5 again. In the fourth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are a proportional driving type planetary gear sets and a negative ratio driven planetary gear set. The two sun gear rotation shafts pss1 and nss of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of the two planetary arms of the two planetary gear sets is pa, the common rotation axis of a central gear ps2 and a ring gear nr is nrs, and the two common rotation axes pa and nrs can arbitrarily form the first The second rotation axis AD of the planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. transmission end].

Please refer to Figures 2A, 2B and 6 again. In the fifth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are a proportional driving type planetary gear sets and a negative ratio driven planetary gear set. A sun gear rotation shaft pss and a ring gear rotation shaft nrs of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of the two planetary arms of the two planetary gear sets is pa, the common rotation axis of a central gear ps2 and a sun gear ns is nss, and the two common rotation axes pa and nss can be The second rotation axis AD [the free transmission end of FIG. 2A or the energy input end of FIG. 2B ] of the first planetary gear set 1 and the second rotation axis BD [the energy input end of FIG. 2A ] of the second planetary gear set 2 are arbitrarily formed. Or the free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 7 again. In the sixth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by two negative ratios. planetary gear set. The two sun gear rotation shafts nssA and nssB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of the two planetary arms of the two planetary gear sets is na, the common rotation axis of the second ring gear nrA and nrB is nrs, and the two common rotation axes na and nrs can form the first planetary gear set arbitrarily The second rotation axis AD of 1 (the free transmission end of FIG. 2A or the energy input end of FIG. 2B ] and the second rotation axis BD of the second planetary gear set 2 (the energy input end of FIG. 2A or the free transmission end of FIG. 2B ] .

Please refer to Figures 2A, 2B and 8 again. In the seventh preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by two negative ratios. planetary gear set. The second ring gear rotation shafts nrsA and nrsB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of the two planetary arms of the two planetary gear sets is na, the common rotation axis of the two sun gears nsA and nsB is nss, and the two common rotation axes na and nss can form the first planetary gear set arbitrarily The second rotation axis AD of 1 (the free transmission end of FIG. 2A or the energy input end of FIG. 2B ] and the second rotation axis BD of the second planetary gear set 2 (the energy input end of FIG. 2A or the free transmission end of FIG. 2B ] .

Please refer to Figures 2A, 2B and 9 again. In the eighth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by two negative ratios. planetary gear set. A sun gear rotation shaft nssA and a ring gear rotation shaft nrs of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of the two planetary arms of the two planetary gear sets is na, the common rotation axis of a ring gear nrA and a sun gear nsB is nssB, and the two common rotation axes na and ns sB are parallel The second rotation axis AD of the first planetary gear set 1 (the free transmission end in FIG. 2A or the energy input end in FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (the energy input end in FIG. 2A end or the free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 10 again. In the ninth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by two proportional values. planetary gear set. A sun gear rotating shaft pss1 and a planetary arm rotating shaft paB of the two planetary gear sets can arbitrarily form the energy output end [first rotating shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of a planetary arm and a sun gear ps1B of the two planetary gear sets is paA, the common rotation axis of the two central gears ps2A and ps2B is pss2, and the two common rotation axes paA and pss2 And the second rotation axis AD of the first planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. Input end or free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 11 again. In the tenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by two proportional values. planetary gear set. A sun gear rotation shaft pss1A and a central gear rotation shaft pss2B of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation shaft CR]; the common rotation shaft of a central gear ps2A and a planetary arm of the two planetary gear sets is pss2A, a common rotation shaft of a planetary arm and a sun gear ps1B is pss1B, and the two common rotation shafts pss2A Together with pss1B, the second rotation axis AD of the first planetary gear set 1 (the free transmission end of FIG. 2A or the energy input end of FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (Fig. 2A The energy input end or the free transfer end of Figure 2B].

Please refer to Figures 2A, 2B and 12 again. In the eleventh preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by a proportional value. type planetary gear set and a negative ratio drive type planetary gear set. A sun gear rotating shaft pss1 and a planetary arm rotating shaft na of the two planetary gear sets can arbitrarily form the energy output end [first rotating shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [first rotation axis CR]; the common rotation axis of a central gear ps2 and a ring gear nr of the two planetary gear sets is pss2, the common rotation axis of the planetary arm and sun gear ns is nss, and the two common rotation axes pss2 and nss can arbitrarily form the second rotation axis AD of the first planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end or the free transfer end of Fig. 2B].

Please refer to Figures 2A, 2B and 13 again. In the twelfth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by a proportional value. type planetary gear set and a negative ratio drive type planetary gear set. A sun gear rotating shaft pss1 and a planetary arm rotating shaft na of the two planetary gear sets can arbitrarily form the energy output end [first rotating shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of a planetary arm and a ring gear nr of the two planetary gear sets is pa, the common rotation axis of a central gear ps2 and a sun gear ns is nss, and the two common rotation axes pa and nss can arbitrarily form the second rotation axis AD of the first planetary gear set 1 (the free transmission end in FIG. 2A or the energy input end in FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (in FIG. 2A’s energy input end or Figure 2B’s free transfer end].

Please refer to Figures 2A, 2B and 14 again. In the thirteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by a proportional value. type planetary gear set and a negative ratio drive type planetary gear set. A planetary arm rotation axis pa and a sun gear rotation axis nss of the two planetary gear sets can arbitrarily form the energy output end [first rotation axis OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of a sun gear ps1 and a planetary arm of the two planetary gear sets is pss1, a common rotation axis of a central gear ps2 and a ring gear nr is nrs, and the two common rotation axes pss1 and nrs can arbitrarily form the second rotation axis AD of the first planetary gear set 1 (the free transmission end in FIG. 2A or the energy input end in FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (in FIG. 2A’s energy input end or Figure 2B’s free transfer end].

Please refer to Figures 2A, 2B and 15 again. In the fourteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by a proportional value. type planetary gear set and a negative ratio drive type planetary gear set. A planetary arm rotation axis pa and a ring gear rotation axis nrs of the two planetary gear sets can arbitrarily form the energy output end [first rotation axis OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [first rotation axis CR]; the common rotation axis of a sun gear ps1 and a planetary arm of the two planetary gear sets is pss1, a common rotation axis of a central gear ps2 and a sun gear ns is nss, and the two common rotation axes pss1 and nss can arbitrarily form the second rotation axis AD of the first planetary gear set 1 (the free transmission end in FIG. 2A or the energy input end in FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (in FIG. 2A’s energy input end or Figure 2B’s free transfer end].

Please refer to Figures 2A, 2B and 16 again. In the fifteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by a proportional value. type planetary gear set and a negative ratio drive type planetary gear set. The two sun gear rotation shafts pss1 and nss of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of a planetary arm and a ring gear nr of the two planetary gear sets is pa, the common rotation axis of a central gear ps2 and a planetary arm is na, and the two common rotation axes pa and na can be arbitrarily Form the second rotation axis AD of the first planetary gear set 1 (the free transmission end of FIG. 2A or the energy input end of FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (the energy input end of FIG. 2A or The free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 17 again. In the sixteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by a proportional value. type planetary gear set and a negative ratio drive type planetary gear set. A sun gear rotation shaft pss and a ring gear rotation shaft nrs of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of a planetary arm and a sun gear ns of the two planetary gear sets is pa, the common rotation axis of a central gear ps2 and a planetary arm is na, and the two common rotation axes pa and na can arbitrarily form the second rotation axis AD of the first planetary gear set 1 (the free transmission end of FIG. 2A or the energy input end of FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 ( FIG. 2A The energy input end or the free transfer end of Figure 2B].

Please refer to Figures 2A, 2B and 18 again. In the seventeenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative ratios Driven planetary gear set. A sun gear rotating shaft nss and a planetary arm rotating shaft naB of the two planetary gear sets can arbitrarily form the energy output end [first rotating shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of a planetary arm and a sun gear nsB of the two planetary gear sets is naA, the common rotation axis of the second ring gear nrA and nrB is nrs, and the two common rotation axes naA and nrs And the second rotation axis AD of the first planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. Input end or free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 19 again, in the eighteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative ratios Driven planetary gear set. A sun gear rotation shaft nssA and a planetary arm rotation shaft naB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [first rotation axis CR]; the common rotation axis of a planetary arm and a ring gear nrB of the two planetary gear sets is naA, the common rotation axis of a ring gear nrA and a sun gear nsB is nssB, and the two common rotation axes naA and nssB can arbitrarily form the second rotation axis AD of the first planetary gear set 1 (the free transmission end in FIG. 2A or the energy input end in FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (in FIG. 2A’s energy input end or Figure 2B’s free transfer end].

Please refer to Figures 2A, 2B and 20 again. In the nineteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative ratios Driven planetary gear set. The two sun gear rotation shafts nssA and nssB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of a planetary arm and a ring gear nrB of the two planetary gear sets is naA, the common rotation axis of a ring gear nrA and a planetary arm is naB, and the two common rotation axes naA and naB can be arbitrarily Form the second rotation axis AD of the first planetary gear set 1 (the free transmission end of FIG. 2A or the energy input end of FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (the energy input end of FIG. 2A or The free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 21 again. In the twentieth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative ratios Driven planetary gear set. The second ring gear rotation shafts nrsA and nrsB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of a planetary arm and a sun gear nsB of the two planetary gear sets is naA, the common rotation axis of a sun gear nsA and a planetary arm is naB, and the two common rotation axes naA and naB can be arbitrarily Form the second rotation axis AD of the first planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. 2B's free transmission end].

Please refer to Figures 2A, 2B and 22 again. In the twenty-first preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative Ratio driven planetary gear set. A sun gear rotation shaft nss and a ring gear rotation shaft nrs of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of a planetary arm and a sun gear nsB of the two planetary gear sets is naA, the common rotation axis of a ring gear nrA and a planetary arm is naB, and the two common rotation axes naA and naB can arbitrarily form the second rotation axis AD of the first planetary gear set 1 [the free transmission end of Fig. 2A or the energy input end of Fig. 2B] and the second rotation axis BD of the second planetary gear set 2 [ The energy input end of Fig. 2A or the free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 23 again. In the twenty-second preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two positive Ratio driven planetary gear set. The two planetary arm rotation shafts paA and paB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of the two sun gears ps1A and ps1B of the two planetary gear sets is pss1, the common rotation axis of the two central gears ps2A and ps2B is pss2, and the two common rotation axes pss1 and pss2 can form the first The second rotation axis AD of the planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. transmission end].

Please refer to Figures 2A, 2B and 24 again. In the twenty-third preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are a proportional value drive planetary gear sets and one negative ratio drive planetary gear set. The two planetary arm rotation shafts pa and na of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of the two sun gears ps1 and ns of the two planetary gear sets is pss1, the common rotation axis of a central gear ps2 and a ring gear nr is nrs, and the two common rotation axes pss1 and nrs can be formed arbitrarily The second rotation axis AD of the first planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. 2B's free transmission end].

Please refer to Figures 2A, 2B and 25 again. In the twenty-fourth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative Ratio driven planetary gear set. The two planetary arm rotation shafts naA and naB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of the two sun gears nsA and nsB of the two planetary gear sets is nss, the common rotation axis of the second ring gear nrA and nrB is nrs, and the two common rotation axes nss and nrs can form the first The second rotation axis AD of the planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. transmission end].

Please refer to Figures 2A, 2B and 26 again. In the twenty-fifth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative Ratio driven planetary gear set. The two planetary arm rotation shafts naA and naB of the two planetary gear sets can arbitrarily form the energy output end [first rotation shaft OP] of the first planetary gear set 1 and the control end [first rotation shaft OP] of the second planetary gear set 2 CR]; the common rotation axis of a sun gear nsA and a ring gear nrB of the two planetary gear sets is nssA, the common rotation axis of a ring gear nrA and a sun gear nsB is nssB, and the two common rotation axes nssA and nssB are parallel The second rotation axis AD of the first planetary gear set 1 (the free transmission end in FIG. 2A or the energy input end in FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 (the energy input end in FIG. 2A end or the free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 27 again. In the twenty-sixth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative Ratio driven planetary gear set. A ring gear rotation axis nrs and a planetary arm rotation axis na of the two planetary gear sets can arbitrarily form the energy output end [first rotation axis OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [first rotation axis CR]; the common rotation axis of a sun gear nsA and a ring gear nrB of the two planetary gear sets is nssA, a common rotation axis of a planetary arm and a sun gear nsB is nssB, and the two common rotation axes nssA and nssB can arbitrarily form the second rotation axis AD of the first planetary gear set 1 (the free transmission end in FIG. 2A or the energy input end in FIG. 2B ) and the second rotation axis BD of the second planetary gear set 2 [ The energy input end of Fig. 2A or the free transmission end of Fig. 2B].

Please refer to Figures 2A, 2B and 28 again. In the twenty-seventh preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two negative Ratio driven planetary gear set. A ring gear rotation axis nrsA and a planetary arm rotation axis na of the two planetary gear sets can arbitrarily form the energy output end [first rotation axis OP] of the first planetary gear set 1 and the control end of the second planetary gear set 2 [First rotation axis CR]; the common rotation axis of the two sun gears nsA and nsB of the two planetary gear sets is nss, the common rotation axis of a planetary arm and a ring gear nrB is nrsB, and the two common rotation axes nss and nrsB And the second rotation axis AD of the first planetary gear set 1 [the free transmission end of FIG. 2A or the energy input end of FIG. 2B] and the second rotation axis BD of the second planetary gear set 2 [the energy input end of FIG. input end or the free transmission end of Fig. 2B].

The aforementioned preferred embodiments only illustrate the present invention and its technical characteristics, and the technology of this embodiment can still be properly implemented in various substantive equivalent modifications and/or replacements; therefore, the protection scope of the claims of the present invention is as follows: Requirements shall prevail.

Claims (9)

1. unit sequence of ratio values type independently can control a driving mechanism, it is characterized in that, it comprises:

One first planet gear train, it comprises an Energy transmission end;

One second planetary gear set, its sequence is connected to this first planet gear train, and described first planet gear train and described second planetary gear set are combined to form the straight sequence type of a unit ratio, and this second planetary gear set comprises a control end;

One energy input end, it is arranged at this second planetary gear set; And

One free transmission ends, it is arranged at this first planet gear train, and this control end controls this free transmission ends, freely to switch this free transmission ends as one of energy input end and Energy transmission end.

2. unit as claimed in claim 1 sequence of ratio values type independently can control driving mechanism, and it is characterized in that, described first planet gear train and the second planetary gear set are two positive ratio drive-type planetary gear set; Or this first planet gear train and the second planetary gear set are two negative ratio drive-type planetary gear set; Or this first planet gear train is a positive ratio drive-type planetary gear set, and this second planetary gear set is a negative ratio drive-type planetary gear set; Or this first planet gear train is a negative ratio drive-type planetary gear set, and this second planetary gear set is a positive ratio drive-type planetary gear set.

3. unit as claimed in claim 1 sequence of ratio values type independently can control driving mechanism, it is characterized in that, described first planet gear train has one first running shaft, one second running shaft and one the 3rd running shaft, and this second planetary gear set has one first running shaft, one second running shaft and one the 3rd running shaft; First running shaft of this first planet gear train is the Energy transmission end that this unit sequence of ratio values type independently can control driving mechanism; Second running shaft of this first planet gear train is the free transmission ends that this unit sequence of ratio values type independently can control driving mechanism; 3rd running shaft of this first planet gear train is connected to this second planetary gear set; First running shaft of this second planetary gear set is the control end that this unit sequence of ratio values type independently can control driving mechanism; Second running shaft of this second planetary gear set is the energy input end that this unit sequence of ratio values type independently can control driving mechanism; 3rd running shaft of this second planetary gear set is connected to this first planet gear train.

4. unit sequence of ratio values type independently can control a driving mechanism, it is characterized in that, it comprises:

One first planet gear train, it comprises an Energy transmission end;

One second planetary gear set, its sequence is connected to this first planet gear train, and described first planet gear train and described second planetary gear set are combined to form the straight sequence type of a unit ratio, and this second planetary gear set comprises a control end;

One energy input end, it is arranged at this first planet gear train; And

One free transmission ends, it is arranged at this second planetary gear set, and this control end controls this free transmission ends, freely to switch this free transmission ends as one of energy input end and Energy transmission end.

5. unit as claimed in claim 4 sequence of ratio values type independently can control driving mechanism, and it is characterized in that, described first planet gear train and the second planetary gear set are two positive ratio drive-type planetary gear set; Or this first planet gear train and the second planetary gear set are two negative ratio drive-type planetary gear set; Or this first planet gear train is a positive ratio drive-type planetary gear set, and this second planetary gear set is a negative ratio drive-type planetary gear set; Or this first planet gear train is a negative ratio drive-type planetary gear set, and this second planetary gear set is a positive ratio drive-type planetary gear set.

6. unit as claimed in claim 4 sequence of ratio values type independently can control driving mechanism, it is characterized in that, described first planet gear train has one first running shaft, one second running shaft and one the 3rd running shaft, and this second planetary gear set has one first running shaft, one second running shaft and one the 3rd running shaft; First running shaft of this first planet gear train is the Energy transmission end that this unit sequence of ratio values type independently can control driving mechanism; Second running shaft of this first planet gear train is the energy input end that this unit sequence of ratio values type independently can control driving mechanism; 3rd running shaft of this first planet gear train is connected to this second planetary gear set; First running shaft of this second planetary gear set is the control end that this unit sequence of ratio values type independently can control driving mechanism; Second running shaft of this second planetary gear set is the free transmission ends that this unit sequence of ratio values type independently can control driving mechanism; 3rd running shaft of this second planetary gear set is connected to this first planet gear train.

7. unit sequence of ratio values type independently can control a driving mechanism, it is characterized in that, it comprises:

Two planetary gear set, its mutual sequence connects, and described two planetary gear set are combined to form the straight sequence type of a unit ratio;

One Energy transmission end, it is arranged at a first planet gear train of this two planetary gear set;

One control end, it is arranged at one second planetary gear set of this two planetary gear set;

One energy input end, it is arranged at described second planetary gear set of this two planetary gear set or described first planet gear train; And

One free transmission ends, it is arranged at the described first planet gear train of this two planetary gear set or described second planetary gear set, and this control end controls this free transmission ends, freely to switch this free transmission ends as one of energy input end and Energy transmission end.

8. unit as claimed in claim 7 sequence of ratio values type independently can control driving mechanism, and it is characterized in that, described two planetary gear set are two positive ratio drive-type planetary gear set; Or this two planetary gear set is two negative ratio drive-type planetary gear set; Or one of this two planetary gear set is a positive ratio drive-type planetary gear set, and another of this two planetary gear set is a negative ratio drive-type planetary gear set.

9. unit as claimed in claim 7 sequence of ratio values type independently can control driving mechanism, it is characterized in that, described two planetary gear set have one first running shaft, one second running shaft, one the 3rd running shaft, one the 4th running shaft, one the 5th running shaft and one the 6th running shaft; This first running shaft is the Energy transmission end that this unit sequence of ratio values type independently can control driving mechanism; This second running shaft is the free transmission ends that this unit sequence of ratio values type independently can control driving mechanism; 3rd running shaft is connected between this two planetary gear set; 4th running shaft is the control end that this unit sequence of ratio values type independently can control driving mechanism; 5th running shaft is the energy input end that this unit sequence of ratio values type independently can control driving mechanism; 6th running shaft is connected between this two planetary gear set.