CN111322366A - Eight-gear transmission with power output - Google Patents
Eight-gear transmission with power output Download PDFInfo
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- CN111322366A CN111322366A CN201911354301.3A CN201911354301A CN111322366A CN 111322366 A CN111322366 A CN 111322366A CN 201911354301 A CN201911354301 A CN 201911354301A CN 111322366 A CN111322366 A CN 111322366A
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- clutch
- shaft
- gear
- intermediate shaft
- gear pair
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses an eight-gear transmission with power output, which comprises an input shaft, an output shaft, a first intermediate shaft, a second intermediate shaft, a transmission shaft, a first clutch, a second clutch, a third clutch, a fourth clutch, a fifth clutch, a sixth clutch, a shell and a power motor, wherein the input shaft is connected with the output shaft; the central lines of the input shaft, the transmission shaft and the output shaft are arranged in a collinear way and are sequentially arranged on the shell; a first clutch and a second clutch are arranged between the first intermediate shaft and the input shaft, a third clutch and a fourth clutch are arranged between the first intermediate shaft and the transmission shaft, a fifth clutch is arranged between the second intermediate shaft and the transmission shaft, and a sixth clutch is arranged between the second intermediate shaft and the output shaft; the first intermediate shaft or the second intermediate shaft is in transmission connection with the rotating end of the power motor, and the power motor is used for transmitting power to the intermediate shafts. The structure of the hybrid vehicle is more compact, and the occupied space is small.
Description
Technical Field
The invention relates to the field of transmissions, in particular to an eight-gear transmission with power output.
Background
The transmission can change different torques input in front and back through different gear changes and different power drives. Through the switching to the different clutches of derailleur, can realize the switching to the different fender position of derailleur, hybrid vehicle system can realize the hybrid drive to the derailleur through installing driving motor additional to the engine simultaneously. The hybrid vehicle has the characteristics of energy saving and low emission. The existing hybrid power system is generally used on a small-sized automobile, the existing hybrid power system of a large-sized vehicle is relatively overstaffed, and if a power motor is added, the two ends of the power motor are respectively connected with a speed changer, so that the speed changer is large in size and large in occupied space.
Disclosure of Invention
Therefore, an eight-gear transmission with power output needs to be provided, and the problem that the size of the transmission of the hybrid vehicle is large is solved.
In order to achieve the above object, the inventor provides an eight-gear transmission with power output, which includes an input shaft, an output shaft, a first intermediate shaft, a second intermediate shaft, a transmission shaft, a first clutch, a second clutch, a third clutch, a fourth clutch, a fifth clutch, a sixth clutch, a housing and a power motor;
the input shaft, the transmission shaft and the output shaft are sequentially arranged, the center lines of the input shaft, the transmission shaft and the output shaft are arranged in a collinear manner, and the input end of the input shaft and the output end of the output shaft respectively penetrate through two opposite side walls of the shell and are arranged on the shell;
the input shaft transmits power to a first intermediate shaft through the first clutch or the second clutch, the first intermediate shaft transmits power to the transmission shaft through the third clutch or the fourth clutch, and then the transmission shaft is transmitted to the output shaft through the fifth clutch, or the transmission shaft is transmitted to the output shaft through the sixth clutch through the second intermediate shaft, and the center lines of the first intermediate shaft and the second intermediate shaft are arranged in a shell in parallel with the center line of the input shaft;
one end of the first intermediate shaft or the second intermediate shaft is in transmission connection with a rotating end of the power motor, the power motor is arranged outside the shell, and the power motor is used for transmitting power to the first intermediate shaft or the second intermediate shaft.
Further, the first clutch and the second clutch form a first switching type double clutch, the third clutch and the fourth clutch form a second switching type double clutch, the fifth clutch and the sixth clutch form a third switching type double clutch, and the first switching type double clutch, the second switching type double clutch and the third switching type double clutch are the same switching type double clutch;
the switching double clutch comprises a first clutch block, a second clutch block and a piston unit; the first clutch block is positioned on one side of the piston unit, the second clutch block is positioned on the other side of the piston unit, and the piston unit is used for enabling the first clutch block and the second clutch block to be in clutch;
a first gear pair is arranged between the input shaft and the first intermediate shaft, one gear of the first gear pair is movably sleeved on the input shaft, the other gear of the first gear pair is arranged on the first intermediate shaft, a second gear pair is arranged between the input shaft and the first intermediate shaft, one gear of the second gear pair is movably sleeved on the input shaft, the other gear of the second gear pair is arranged on the first intermediate shaft, a third gear pair is arranged between the transmission shaft and the first intermediate shaft, one gear of the third gear pair is movably sleeved on the transmission shaft, the other gear of the third gear pair is arranged on the first intermediate shaft, a fourth gear pair is arranged between the transmission shaft and the first intermediate shaft, one gear of the fourth gear pair is movably sleeved on the transmission shaft, the other gear of the fourth gear pair is arranged on the first intermediate shaft, and a fifth gear pair is arranged between the transmission shaft and the second intermediate shaft, one gear of the fifth gear pair is arranged on the transmission shaft, the other gear of the fifth gear pair is arranged on the second intermediate shaft, a sixth gear pair is arranged between the output shaft and the second intermediate shaft, one gear of the sixth gear pair is movably sleeved on the output shaft, and the other gear of the sixth gear pair is arranged on the second intermediate shaft;
the first clutch piece of the first switching type double clutch is used for the clutch of the input shaft and a gear of the first gear pair, the second clutch piece of the first switching type double clutch is used for the clutch of the input shaft and a gear of the second gear pair, and the first clutch piece of the first switching type double clutch and the second clutch piece of the first switching type double clutch are mutually exclusive clutches;
the first clutch piece of the second switching type double clutch is used for clutching the transmission shaft and a gear of the third gear pair, the second clutch piece of the second switching type double clutch is used for clutching the transmission shaft and a gear of the fourth gear pair, and the first clutch piece of the second switching type double clutch and the second clutch piece of the second switching type double clutch are mutually exclusive clutches;
the first clutch piece of the third switching type double clutch is used for engaging and disengaging a transmission shaft and a gear of the fifth gear pair, the second clutch piece of the third switching type double clutch is used for engaging and disengaging an output shaft and a gear of the sixth gear pair, and the first clutch piece of the third switching type double clutch and the second clutch piece of the third switching type double clutch are mutually exclusive.
Further, the piston unit comprises a double-ended piston body and a cavity;
the cross section of the double-end piston body is I-shaped, one end of the double-end piston body is arranged in the cavity, the other end of the double-end piston body is located outside the cavity, and two ends of the cavity are respectively connected with one hydraulic unit.
Further, the first clutch piece comprises a first friction piece group, the second clutch piece comprises a second friction piece group, the first friction piece group is located on one side of the other end of the double-head piston body, the second friction piece group is located on the other side of the other end of the double-head piston body, and the double-head piston body is used for driving one of the first friction piece group or the second friction piece group to be combined and the other friction piece group to be separated.
Further, the second gear pair and the third gear pair form the same gear pair.
Furthermore, a key groove is formed in the shaft surface of the intermediate shaft of the power motor, and the output end of the power motor is fixedly connected into the key groove.
Furthermore, the first intermediate shafts or the second intermediate shafts are arranged in an annular array around the central line of the input shaft or the output shaft, the first intermediate shafts or the second intermediate shafts are identical in structure, and the first intermediate shafts or the second intermediate shafts are respectively connected with a power motor.
Further, the power motor is a direct current power motor.
Different from the prior art, the technical scheme is additionally arranged on a power motor on an intermediate shaft, and the power motor and the power at the input end of the input shaft drive a transmission together. When the power is needed, the power motor can also independently provide power for the transmission to drive the transmission to work. During the joint operation, the power motor shares the load of the output shaft, and the output of the hybrid power is realized together with the power of the input shaft. Because the power motor is arranged on the middle shaft at the side of the speed changer and is not arranged on the output shaft, the structure is more compact, and the occupied space is reduced.
Drawings
FIG. 1 is a simplified schematic structural diagram of an eight speed transmission according to the present embodiment;
FIG. 2 is a schematic structural diagram of an eight speed transmission according to other embodiments;
FIG. 3 is another schematic construction diagram of the eight speed transmission of the present embodiment;
fig. 4 is a schematic structural diagram of the switching double clutch according to the embodiment.
Description of reference numerals:
1. an eight speed transmission;
11. an input shaft;
12. an output shaft;
13. a first intermediate shaft;
14. a second intermediate shaft;
15. a drive shaft;
16. a housing;
17. a first gear pair;
18. a second gear pair;
181. a common gear pair;
19. a third gear pair;
20. a fourth gear pair;
21. a fifth gear pair;
22. a sixth gear pair;
2. a power motor;
3. a switching clutch;
31. a first clutch block;
311. a first friction plate set;
32. a second clutch block;
321. a second friction plate set;
33. a double-ended piston body;
34. a cavity;
35. a hydraulic unit;
36. a first switching clutch;
37. a second switching clutch;
38. a third switching clutch;
k1, a first clutch;
k2, a second clutch;
k3, third clutch;
k4, a fourth clutch;
k5, fifth clutch;
k6, sixth clutch.
Detailed Description
To explain technical contents, structural features, and objects and effects of the technical solutions in detail, the following detailed description is given with reference to the accompanying drawings in conjunction with the embodiments.
Referring to fig. 1 to 4, the embodiment provides an eight-gear transmission with power output, and the eight-gear transmission includes an input shaft 11, an output shaft 12, a first intermediate shaft 13, a second intermediate shaft 14, a transmission shaft 15, a first clutch k1, a second clutch k2, a third clutch k3, a fourth clutch k4, a fifth clutch k5, a sixth clutch k6, a housing 16 and a power motor 2; the input shaft 11, the transmission shaft 15 and the output shaft 11 are arranged in a collinear manner and are sequentially arranged, and the input end of the input shaft 11 and the output end of the output shaft 12 respectively penetrate through two opposite side walls of the shell 16 and are arranged on the shell 16; the input shaft 11 transmits power to the first intermediate shaft 13 through the first clutch k1 or the second clutch k2, the first intermediate shaft 13 transmits power to the transmission shaft 15 through the third clutch k3 or the fourth clutch k4, and then the transmission shaft 15 is transmitted to the output shaft through the fifth clutch k5, or the transmission shaft 15 is transmitted to the output shaft through the sixth clutch through the second intermediate shaft, and the center lines of the first intermediate shaft 13 and the second intermediate shaft 14 are disposed in the housing 16 in parallel with the center line of the input shaft 11. It is to be noted here that the countershafts herein include a first countershaft 13 and a second countershaft 14; one end of the first intermediate shaft 13 or the second intermediate shaft 14 is in transmission connection with a rotating end of the power motor 2, the power motor 2 is arranged outside the shell 16, and the power motor 2 is used for transmitting power to the intermediate shaft connected with the power motor. The power motor 2 can be a direct current power motor, an alternating current power motor, a permanent magnet synchronous motor and the like.
The power motor and the power mechanism connected with the input end are combined into a driving force which can be used as a power vehicle system of a hybrid vehicle, and the power motor and the power mechanism connected with the input shaft can jointly provide power for the output shaft; the power motor can also transmit power to the output shaft through the intermediate shaft (the first intermediate shaft or the second intermediate shaft) independently; by means of the power motor as another power source to provide additional power required for acceleration or climbing, the overall efficiency can be improved to a great extent without sacrificing performance. The power motor and the power mechanism can be complemented, the power motor can be used for driving to run at low speed, the power motor can share the load of the output shaft, and the power of the output shaft and the power of the input shaft realize hybrid power output. Meanwhile, the whole structure of the vehicle is compact, the emission is reduced, the energy is saved, and the overall efficiency of the vehicle is improved.
In some embodiments, in order to provide a power source for the eight speed transmission 1, a power mechanism may be connected to the input end of the input shaft 11, and the power mechanism is used for driving the input shaft 11 to rotate.
In this embodiment, the connection between the power motor and the first intermediate shaft or the second intermediate shaft is a direct connection. Specifically, a key groove is formed in a shaft surface between the first intermediate shaft and the second intermediate shaft, and the output end of the power motor can be inserted and fixed into the key groove in an interference fit manner. Or the direct connection can be other embodiments, for example, the output end of the power motor and one end of the first intermediate shaft or the second intermediate shaft are connected through a coupling.
In some embodiments, the connection between the power motor and the first or second countershaft may be a geared connection. Specifically, a gear may be sleeved on an output shaft of the power motor, a gear may be also sleeved on the first intermediate shaft or the second intermediate shaft, and the power motor drives the output shaft to rotate through mutual engagement between the gear on the power motor and the gear on the first intermediate shaft or the second intermediate shaft.
Generally, to implement the operation of the clutch, the clutch is disposed on the power input end, and one end of the clutch is connected to the power input end and the other end is connected to the power output end. In this embodiment, the power input end may be an input shaft, and the power output end is a gear rotatably sleeved on the input shaft; or the power output end is an output shaft, and the power input end is a gear which is rotatably sleeved on the output shaft.
In some embodiments, the first clutch k1, the second clutch k2, the third clutch k3, the fourth clutch k4, the fifth clutch k5 and the sixth clutch k6 are conventional clutch structures, such as a friction clutch and a hydraulic clutch, and when the clutches are friction clutches, one friction clutch is disposed beside each gear of each gear pair. One end of the friction clutch is fixed on the input shaft (or the output shaft), the other end of the friction clutch is connected with the gear of the gear pair, when the friction clutch is in an on state, the input shaft (or the output shaft) is in transmission with the gear, and when the friction clutch is in an off state, the input shaft (or the output shaft) is not in transmission with the gear.
Referring to fig. 4, in order to optimize the structure of the transmission, the problem of the conventional transmission that the two clutches are simultaneously engaged and cause gear jamming is solved, and the overall structure is simpler. In this embodiment, the first clutch k1 and the second clutch k2 form a first switching dual clutch 36, the third clutch k3 and the fourth clutch k4 form a second switching dual clutch 37, the fifth clutch k5 and the sixth clutch k6 form a third switching dual clutch 38, and the first switching dual clutch 36, the second switching dual clutch 37 and the third switching dual clutch 38 are the same switching dual clutch 3. The dual switching clutch 3 comprises a first clutch plate 31, a second clutch plate 32 and a piston unit. The first clutch piece 31 is located on one side of the piston unit, the second clutch piece 32 is located on the other side of the piston unit, and the piston unit is used for enabling the first clutch piece 31 and the second clutch piece 32 to be in clutch. The piston unit of the dual clutch 3 can only push the first clutch piece 31 or the second clutch piece 32 to be in the engaged state, so that the situation of being in the engaged state at the same time is avoided.
Referring to fig. 2, in other embodiments, a first gear pair 17 is disposed between the input shaft and the first intermediate shaft, one gear of the first gear pair 17 is movably sleeved on the input shaft, and the other gear of the first gear pair 17 is disposed on the first intermediate shaft; a second gear pair 18 is arranged between the input shaft and the first intermediate shaft, one gear of the second gear pair is movably sleeved on the input shaft, and the other gear of the second gear pair is arranged on the first intermediate shaft; a third gear pair is arranged between the transmission shaft and the first intermediate shaft, one gear of the third gear pair is movably sleeved on the transmission shaft, and the other gear of the third gear pair is arranged on the first intermediate shaft; a fourth gear pair is arranged between the transmission shaft and the first intermediate shaft, one gear of the fourth gear pair is movably sleeved on the transmission shaft, and the other gear of the fourth gear pair is arranged on the first intermediate shaft; a fifth gear pair is arranged between the transmission shaft and the second intermediate shaft, one gear of the fifth gear pair is movably sleeved on the transmission shaft, and the other gear of the fifth gear pair is arranged on the second intermediate shaft; a sixth gear pair is arranged between the output shaft and the second intermediate shaft, one gear of the sixth gear pair is movably sleeved on the output shaft, and the other gear of the sixth gear pair is arranged on the second intermediate shaft; the input shaft and the first intermediate shaft are in transmission connection through the first gear pair and the second gear pair, the transmission shaft and the first intermediate shaft are in transmission connection through the third gear pair and the fourth gear pair, the transmission shaft and the second intermediate shaft are in transmission connection through the fifth gear pair, and the output shaft and the second intermediate shaft are in transmission connection through the sixth gear pair. Namely, the relationship between the gear pairs of the switching type double clutch is as follows: the first clutch piece (realizing the function of the first clutch K1) of the first switching double clutch is used for the clutch of the input shaft and a gear of the first gear pair, the second clutch piece (realizing the function of the second clutch K2) of the first switching double clutch is used for the clutch of the input shaft and a gear of the second gear pair, and the first clutch piece of the first switching double clutch and the second clutch piece of the first switching double clutch are mutually exclusive clutches; the first clutch piece (realizing the function of the third clutch K3) of the second switching type double clutch is used for clutching the transmission shaft and a gear of the third gear pair, the second clutch piece (realizing the function of the fourth clutch K4) of the second switching type double clutch is used for clutching the transmission shaft and a gear of the fourth gear pair, and the first clutch piece of the second switching type double clutch and the second clutch piece of the second switching type double clutch are mutually exclusive clutches; the first clutch piece (realizing the function of the fifth clutch K5) of the third switching type double clutch is used for engaging and disengaging a transmission shaft with a gear of a fifth gear pair, the second clutch piece (realizing the function of the sixth clutch K6) of the third switching type double clutch is used for engaging and disengaging an output shaft with a gear of a sixth gear pair, and the first clutch piece of the third switching type double clutch and the second clutch piece of the third switching type double clutch are mutually exclusive clutches. Through foretell gear pair and switching formula double clutch, can realize whether the power of input shaft transmits the jackshaft, and through the difference of the gear ratio of the gear pair that sets up on the input shaft, can realize that input shaft power transmits the jackshaft with different moments of torsion. Whether the power of the intermediate shaft is transmitted to the transmission shaft and the output shaft or not can be achieved, and the power of the transmission shaft can be transmitted to the output shaft with different torques through the difference of the gear ratios of the gear pairs arranged on the transmission shaft and the output shaft. The gear change of the eight-gear gearbox is realized by controlling the change of the torque in the power transmission process.
The piston unit can be pushed left and right respectively to clutch the clutch blocks on two sides. In this embodiment, one piston unit includes a double-headed piston body 33 and a cavity 34, the double-headed piston body 33 has an i-shaped cross section, one end of the double-headed piston body 33 is disposed in the cavity 34, and the other end of the double-headed piston body 33 is located outside the cavity 34. The double-end piston body 33 can only push one clutch block and gear pair to form a closed state, so that one switching type double clutch 3 can only be in a closed state with one gear pair, and is in a separated state with the other gear pair, the condition that the clutch blocks on two sides are closed simultaneously can not occur, and the transmission is more accurate and flexible in gear shifting. Meanwhile, the other end of the double-end piston body is arranged outside the cavity 34 and used for pushing the clutch blocks on the two sides to be engaged and disengaged, so that the transverse width of the double-end piston body 33 is reduced, and the structure is compact.
Referring to fig. 3, in order to reduce the excessive gear setting and optimize the structure, in this embodiment, the second gear pair 18 and the third gear pair 19 are formed into the same gear pair, that is, a common gear pair, here, the gear pair formed by the second gear pair 18 and the third gear pair 19 is named as a common gear pair 181, one gear of the common gear pair 181 may be slidably disposed on the input shaft 11 or may be slidably disposed on the transmission shaft 15, and the other gear is disposed on the first intermediate shaft. Taking the common gear pair disposed on the transmission shaft as an example, the gear pair of the switching dual clutch has a relationship that the second clutch piece of the first switching dual clutch is used for engaging and disengaging the transmission shaft with a gear of the common gear pair, and the first clutch piece of the second switching dual clutch is used for engaging and disengaging the transmission shaft with a gear of the common gear pair. The rest of the first gear pair, the rest of the fourth gear pair, the rest of the fifth gear pair and the rest of the sixth gear pair are kept unchanged, and the functions of each clutch piece of the rest of the switching type double clutches are as follows: the first clutch piece of the first switching type double clutch is used for engaging and disengaging the input shaft with a gear of the first gear pair, the second clutch piece of the second switching type double clutch is used for engaging and disengaging the transmission shaft with a gear of the fourth gear pair, the first clutch piece of the third switching type double clutch is used for engaging and disengaging the transmission shaft with a gear of the fifth gear pair, and the second clutch piece of the third switching type double clutch is used for engaging and disengaging the output shaft with a gear of the sixth gear pair.
In order to realize the clutch structure inside the clutch, a friction plate clutch mode can be adopted, the first clutch piece 31 comprises a first friction plate set 311, the second clutch piece 32 comprises a second friction plate set 321, the first friction plate set 311 is positioned on one side of the other end of the double-end piston body 33, the second friction plate set 311 is positioned on the other side of the other end of the double-end piston body 33, and the double-end piston body 33 is used for driving one set of the first friction plate set 311 or the second friction plate set 321 to be combined and the other set to be separated. That is, the first clutch plate 31 or the second clutch plate 32 can be clutched by pushing the friction plate of the first clutch plate 31 or the friction plate of the second clutch plate 32 by the double-headed piston body 33.
In this embodiment, the double-ended piston body is used for pushing the first friction plate group and the second friction plate group, and in order to provide power to the double-ended piston body, two ends of the cavity of the switching type double clutch are respectively connected with a hydraulic unit 35 for driving the double-ended piston body to move. The hydraulic unit 35 comprises a hydraulic pump and hydraulic pipelines, one end of each hydraulic pipeline is connected with the hydraulic pump, the other end of each hydraulic pipeline is communicated with the cavity, each hydraulic pipeline comprises a first hydraulic pipeline and a second hydraulic pipeline, the first hydraulic pipeline is communicated with the cavity on the left side of the double-head piston body, and the second hydraulic pipeline is communicated with the cavity on the right side of the double-head piston body. Hydraulic oil is injected into the hydraulic pipeline, the hydraulic pipeline works in a state of being full of hydraulic oil, and the hydraulic pipeline can respectively convey the hydraulic oil to the cavity. Consequently only need to make behind the hydraulic oil pressurization in the hydraulic pressure pipeline of one side the oil pressure in the cavity is unbalanced, and then the drive the double-end piston body is in the cavity removes, reaches control the double-end piston body is in the purpose that removes is carried out to the oil pressure through hydraulic oil in the cavity.
In the present embodiment, the first gear pair, the common gear pair, and the first switching double clutch are taken as an example. The double-head piston body is pushed to move towards one side of the first hydraulic pipeline by applying pressure to the hydraulic oil in the second hydraulic pipeline, so that the first clutch block of the first switching type double clutch and one gear of the first gear pair are in a closed state, and the second clutch block of the first switching type double clutch and one gear of the common gear pair are in a separated state. Similarly, the pressure of the hydraulic oil in the first hydraulic pipeline is greater than that of the second hydraulic pipeline, and the double-end piston body is pushed to move towards one side of the second hydraulic pipeline, so that the second clutch block of the first switching type double clutch and one gear of the common gear pair are in a closed state, and the first clutch block of the first switching type double clutch and the first gear pair are in a separated state. Furthermore, the pressures in the hydraulic pipelines on the two sides are equal, so that the double-end piston body is located in the middle position in the cavity, the second clutch block and the common gear pair of the first switching type double clutch are in a separated state, the first clutch block and the first gear pair of the first switching type double clutch are in a separated state, and the neutral gear state is achieved.
Taking the embodiment of fig. 3 as an example, it is to be explained here that the eight-gear clutch realizes the circuit of the power motor alone in the hybrid power as follows: the power mechanism connected with the input shaft does not work and does not conduct power to the input shaft, and the power motor alone provides power to the first intermediate shaft or the second intermediate shaft. When the power motor is connected with the first intermediate shaft, the first intermediate shaft transmits power to the transmission shaft through the common gear pair or the fourth gear pair, and the transmission shaft transmits the power to the output shaft. When the power motor is connected with the second intermediate shaft, the power is directly transmitted to the output shaft by the second intermediate shaft. Therefore, the hybrid power realizes the independent operation of the power motor.
In this embodiment, the number of the first intermediate shaft and the number of the second intermediate shaft are two, the first intermediate shaft and the second intermediate shaft are arranged around a center line of the input shaft or the output shaft in an annular array, and the power motor may be disposed at any one end of the intermediate shafts. According to actual needs, the power motor can be arranged on the same side as the input shaft or the same side as the output shaft. In some embodiments, the number of the first intermediate shaft and the second intermediate shaft is multiple, and may be two, three or four or even more. A plurality of first intermediate shafts and second intermediate shafts are arranged in a circumferential array on a central axis of the input shaft or the output shaft. The first intermediate shaft and the second intermediate shaft, such as two, may be disposed at upper and lower positions of the input shaft and the output shaft, respectively. The first intermediate shaft and the second intermediate shaft of the multiple groups have the same structure, such as gears with the same tooth number and the same tooth width. Therefore, the loads of the input shaft and the output shaft can be distributed through the first middle shafts and the second middle shafts, so that the bending strength on the input shaft, the middle shafts and the output shaft is enhanced, the bearing capacity of the input shaft and the output shaft is improved, and the purpose of improving the loads is achieved. Meanwhile, through the plurality of power motors, under the condition of the same output power, the lengths of the single bodies of the plurality of power motors can be greatly reduced relative to one power motor, so that the length of the hybrid power system can be greatly reduced, and the structure is compact. Particularly in the field of mine cars and the like needing high-power motors, the power motors of the existing passenger cars can be adopted by adopting a plurality of small power motors, so that the cost can be greatly reduced. The power motor and the power mechanism together or independently drive the transmission to operate. When the power motor and the power system are driven together, the power motor is used as auxiliary power to be matched with the power system for driving; at some time, the power motor can also drive the transmission to work independently.
It should be noted that, although the above embodiments have been described herein, the invention is not limited thereto. Therefore, based on the innovative concepts of the present invention, the technical solutions of the present invention can be directly or indirectly applied to other related technical fields by making changes and modifications to the embodiments described herein, or by using equivalent structures or equivalent processes performed in the content of the present specification and the attached drawings, which are included in the scope of the present invention.
Claims (8)
1. The eight-gear transmission with power output is characterized by comprising an input shaft, an output shaft, a first intermediate shaft, a second intermediate shaft, a transmission shaft, a first clutch, a second clutch, a third clutch, a fourth clutch, a fifth clutch, a sixth clutch, a shell and a power motor;
the input shaft, the transmission shaft and the output shaft are sequentially arranged, the center lines of the input shaft, the transmission shaft and the output shaft are arranged in a collinear manner, and the input end of the input shaft and the output end of the output shaft respectively penetrate through two opposite side walls of the shell and are arranged on the shell;
the input shaft transmits power to a first intermediate shaft through the first clutch or the second clutch, the first intermediate shaft transmits power to the transmission shaft through the third clutch or the fourth clutch, and then the transmission shaft is transmitted to the output shaft through the fifth clutch, or the transmission shaft is transmitted to the output shaft through the sixth clutch through the second intermediate shaft, and the center lines of the first intermediate shaft and the second intermediate shaft are arranged in a shell in parallel with the center line of the input shaft;
one end of the first intermediate shaft or the second intermediate shaft is in transmission connection with a rotating end of the power motor, the power motor is arranged outside the shell, and the power motor is used for transmitting power to the first intermediate shaft or the second intermediate shaft.
2. A power take-off eight speed transmission as defined in claim 1 wherein said first clutch and said second clutch are combined into a first shift type dual clutch, said third clutch and said fourth clutch are combined into a second shift type dual clutch, said fifth clutch and said sixth clutch are combined into a third shift type dual clutch, and said first shift type dual clutch, said second shift type dual clutch and said third shift type dual clutch are identical shift type dual clutches;
the switching double clutch comprises a first clutch block, a second clutch block and a piston unit; the first clutch block is positioned on one side of the piston unit, the second clutch block is positioned on the other side of the piston unit, and the piston unit is used for enabling the first clutch block and the second clutch block to be in clutch;
a first gear pair is arranged between the input shaft and the first intermediate shaft, one gear of the first gear pair is movably sleeved on the input shaft, the other gear of the first gear pair is arranged on the first intermediate shaft, a second gear pair is arranged between the input shaft and the first intermediate shaft, one gear of the second gear pair is movably sleeved on the input shaft, the other gear of the second gear pair is arranged on the first intermediate shaft, a third gear pair is arranged between the transmission shaft and the first intermediate shaft, one gear of the third gear pair is movably sleeved on the transmission shaft, the other gear of the third gear pair is arranged on the first intermediate shaft, a fourth gear pair is arranged between the transmission shaft and the first intermediate shaft, one gear of the fourth gear pair is movably sleeved on the transmission shaft, the other gear of the fourth gear pair is arranged on the first intermediate shaft, and a fifth gear pair is arranged between the transmission shaft and the second intermediate shaft, one gear of the fifth gear pair is arranged on the transmission shaft, the other gear of the fifth gear pair is arranged on the second intermediate shaft, a sixth gear pair is arranged between the output shaft and the second intermediate shaft, one gear of the sixth gear pair is movably sleeved on the output shaft, and the other gear of the sixth gear pair is arranged on the second intermediate shaft;
the first clutch piece of the first switching type double clutch is used for the clutch of the input shaft and a gear of the first gear pair, the second clutch piece of the first switching type double clutch is used for the clutch of the input shaft and a gear of the second gear pair, and the first clutch piece of the first switching type double clutch and the second clutch piece of the first switching type double clutch are mutually exclusive clutches;
the first clutch piece of the second switching type double clutch is used for clutching the transmission shaft and a gear of the third gear pair, the second clutch piece of the second switching type double clutch is used for clutching the transmission shaft and a gear of the fourth gear pair, and the first clutch piece of the second switching type double clutch and the second clutch piece of the second switching type double clutch are mutually exclusive clutches;
the first clutch piece of the third switching type double clutch is used for engaging and disengaging a transmission shaft and a gear of the fifth gear pair, the second clutch piece of the third switching type double clutch is used for engaging and disengaging an output shaft and a gear of the sixth gear pair, and the first clutch piece of the third switching type double clutch and the second clutch piece of the third switching type double clutch are mutually exclusive.
3. A power take-off eight speed transmission as claimed in claim 2, wherein said piston unit comprises a double ended piston body and a cavity;
the cross section of the double-end piston body is I-shaped, one end of the double-end piston body is arranged in the cavity, the other end of the double-end piston body is located outside the cavity, and two ends of the cavity are respectively connected with one hydraulic unit.
4. The eight speed transmission with power take off of claim 3, wherein the first clutch comprises a first set of friction plates and the second clutch comprises a second set of friction plates, the first set of friction plates is located on one side of the other end of the double-ended piston body, the second set of friction plates is located on the other side of the other end of the double-ended piston body, and the double-ended piston body is used for driving one set of the first set of friction plates or the second set of friction plates to be combined and the other set to be separated.
5. A power take-off eight speed transmission as claimed in claim 2, 3 or 4, wherein the second gear set and the third gear set comprise the same gear set.
6. The eight speed transmission with power output according to claim 1, wherein a key groove is provided on a shaft surface of an intermediate shaft of the power motor, and an output end of the power motor is fixedly connected in the key groove.
7. The eight-speed transmission with power output according to claim 1, wherein the first intermediate shaft or the second intermediate shaft is multiple, the multiple first intermediate shaft or the multiple second intermediate shaft are arranged around a central line of the input shaft or the output shaft in an annular array, the multiple first intermediate shaft or the multiple second intermediate shaft are identical in structure, and a power motor is connected to each of the multiple first intermediate shaft or the multiple second intermediate shaft.
8. An eight speed transmission with power take off according to claim 1, wherein the power motor is a dc power motor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911354301.3A CN111322366A (en) | 2019-12-25 | 2019-12-25 | Eight-gear transmission with power output |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911354301.3A CN111322366A (en) | 2019-12-25 | 2019-12-25 | Eight-gear transmission with power output |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111322366A true CN111322366A (en) | 2020-06-23 |
Family
ID=71172505
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911354301.3A Pending CN111322366A (en) | 2019-12-25 | 2019-12-25 | Eight-gear transmission with power output |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111322366A (en) |
-
2019
- 2019-12-25 CN CN201911354301.3A patent/CN111322366A/en active Pending
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