CN111336222A - Four-gear transmission with power output - Google Patents

Four-gear transmission with power output Download PDF

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Publication number
CN111336222A
CN111336222A CN201911340690.4A CN201911340690A CN111336222A CN 111336222 A CN111336222 A CN 111336222A CN 201911340690 A CN201911340690 A CN 201911340690A CN 111336222 A CN111336222 A CN 111336222A
Authority
CN
China
Prior art keywords
clutch
gear
shaft
gear pair
double
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201911340690.4A
Other languages
Chinese (zh)
Inventor
雷作钊
薛天宝
李以聪
罗南昌
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujian Zhongwei Power Technology Co Ltd
Original Assignee
Fujian Zhongwei Power Technology Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fujian Zhongwei Power Technology Co Ltd filed Critical Fujian Zhongwei Power Technology Co Ltd
Priority to CN201911340690.4A priority Critical patent/CN111336222A/en
Publication of CN111336222A publication Critical patent/CN111336222A/en
Pending legal-status Critical Current

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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
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • 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
    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F16H2003/008—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths comprising means for selectively driving countershafts
    • 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
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • 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
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a four-gear transmission with power output, which comprises an input shaft, an output shaft, a middle shaft, a first clutch, a second clutch, a third clutch, a fourth clutch, a shell and a power motor, wherein the input shaft is connected with the output shaft; the central line of the input shaft and the central line of the output shaft are arranged in a collinear manner, 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 the intermediate shaft through the first clutch or the second clutch, then the intermediate shaft transmits the power to the output shaft through the third clutch or the fourth clutch, and one end of the intermediate shaft is in transmission connection with the rotating end of the power motor. The structure of the hybrid vehicle is more compact, and the occupied space is small.

Description

Four-gear transmission with power output
Technical Field
The invention relates to the field of transmissions, in particular to a four-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, a four-speed transmission with power output is needed to solve the problem that the size of the transmission in the hybrid vehicle is large.
In order to achieve the above object, the inventor provides a four-gear transmission with power output, which includes an input shaft, an output shaft, an intermediate shaft, a first clutch, a second clutch, a third clutch, a fourth clutch, a housing and a power motor;
the central line of the input shaft and the central line of the output shaft are arranged in a collinear way, 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 the intermediate shaft through the first clutch or the second clutch, and then the intermediate shaft transmits the power to the output shaft through the third clutch or the fourth clutch; the center line of the intermediate shaft is parallel to the center line of the input shaft and is arranged in the shell;
one end of the intermediate shaft is in transmission connection with the 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 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, and the first switching type double clutch and the second 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 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 intermediate shaft, a second gear pair is arranged between the input shaft and the 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 intermediate shaft, a third gear pair is arranged between the output shaft and the intermediate shaft, one gear of the third gear pair is movably sleeved on the output shaft, the other gear of the third gear pair is arranged on the intermediate shaft, a fourth gear pair is arranged between the output shaft and the intermediate shaft, one gear of the fourth gear pair is movably sleeved on the output shaft, and the other gear of the fourth gear pair is arranged on the 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 output 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 output 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.
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, and the output end of the power motor is fixedly connected into the key groove.
Furthermore, the intermediate shafts are arranged in an annular array around the central lines of the input shaft and the output shaft, the structures of the intermediate shafts are the same, and each intermediate shaft is connected with a power motor.
Further, the power motor is a direct current power motor.
Different from the prior art, the technical scheme is that the power motor is additionally arranged on the intermediate shaft, and the power motor and the power positioned on the input shaft drive the 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 a four speed transmission according to an embodiment;
FIG. 2 is a schematic structural diagram of a four speed transmission according to an embodiment;
FIG. 3 is another schematic structural view of the four speed transmission according to the embodiment;
fig. 4 is a schematic structural diagram of the switching double clutch according to the embodiment.
Description of reference numerals:
1. a four-speed transmission;
11. an input shaft;
12. an output shaft;
13. an intermediate shaft;
14. a housing;
15. a first gear pair;
16. a second gear pair;
161. a common gear pair;
17. a third gear pair;
18. a fourth 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;
k1, first clutch;
k2, second clutch;
k3, third clutch;
k4 and a fourth 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 present embodiment provides a four-gear transmission with power output, the four-gear transmission includes an input shaft 11, an output shaft 12, an intermediate shaft 13, a first clutch K1, a second clutch K2, a third clutch K3, a fourth clutch K4, a housing 14 and a power motor 2; the center line of the input shaft 11 and the center line of the output shaft 12 are arranged in a collinear manner, the input end of the input shaft 11 and the output end of the output shaft 12 are respectively arranged on the housing 14 through two opposite side walls of the housing 14, the input shaft 11 transmits power to the intermediate shaft 13 through the first clutch K1 or the second clutch K2, and then the intermediate shaft 13 transmits power to the output shaft 12 through the third clutch K3 or the fourth clutch K3; the center line of the intermediate shaft 13 is disposed in the housing 14 parallel to the center line of the input shaft 11. The housing 14 can protect various components of the four-speed transmission, such as the input shaft 11, the output shaft 12, the intermediate shaft 13, the first clutch k1, the second clutch k2, the third clutch k3, and the fourth clutch k 4. One end of the intermediate shaft 13 is in transmission connection with a rotating end of the power motor 2, the power motor 2 is arranged outside the shell 14, the power motor 2 is used for transmitting power to the intermediate shaft 13, and the power motor 2 can be a direct-current power motor, an alternating-current power motor, a permanent magnet synchronous motor and the like.
In some embodiments, in order to provide a power source for the four-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 intermediate shaft is a direct connection. Specifically, a key groove is formed in the shaft surface of the 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, such as the connection between the output end of the power motor and one end of the intermediate shaft is realized through a coupler.
In some embodiments, the connection of the power motor and the intermediate shaft may be a geared connection. Specifically, a gear may be sleeved on an output shaft of the power motor, a gear may be sleeved on the intermediate shaft, and the power motor drives the output shaft to rotate by meshing the gear on the power motor and the gear on the 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 and the fourth clutch k4 are conventional clutch structures, such as a friction clutch and a hydraulic clutch, and the clutches are only used for transmitting power. In the case of friction clutches, one friction clutch is disposed next to 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.
The existing clutches are adopted, the two clutches are simultaneously in a closed state to cause the condition of gear jamming, in order to optimize the structure of the transmission, the problem that the gear jamming occurs when the clutches of the traditional transmission are switched is solved, the overall structure is simpler, then in the embodiment, the first clutch and the second clutch are combined into the first switching type double clutch 36, the third clutch and the fourth clutch are combined into the second switching type double clutch 37, and the first switching type double clutch and the second switching type double clutch are the same switching type double 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 some embodiments, a first gear pair is disposed between the input shaft and the intermediate shaft, a gear of the first gear pair 15 is movably sleeved on the input shaft, another gear of the first gear pair 15 is disposed on the intermediate shaft, a second gear pair 16 is disposed between the input shaft and the intermediate shaft, a gear of the second gear pair 16 is movably sleeved on the input shaft, another gear of the second gear pair 16 is disposed on the intermediate shaft, a third gear pair 17 is disposed between the output shaft and the intermediate shaft, a gear of the third gear pair 17 is movably sleeved on the output shaft, another gear of the third gear pair 17 is disposed on the intermediate shaft, a fourth gear pair 18 is disposed between the output shaft and the intermediate shaft, a gear of the fourth gear pair 18 is movably sleeved on the output shaft, and another gear of the fourth gear pair 18 is disposed on the intermediate shaft. The input shaft and the intermediate shaft are in transmission connection through the first gear pair and the second gear pair, and the output shaft and the intermediate shaft are in transmission connection through the third gear pair and the fourth gear pair. 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 first 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 first clutch K3) of the second switching type double clutch is used for clutching the output shaft and a gear of the third gear pair, the second clutch piece (realizing the function of the first clutch K4) of the second switching type double clutch is used for clutching the output 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. 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 jackshaft transmits the output shaft simultaneously can be realized, and through the difference of the gear ratio of the gear pair that sets up on the output shaft, can realize that jackshaft power transmits the output shaft with different moments of torsion. The gear change of the four-gear transmission 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 16 and the third gear pair 17 are formed into the same gear pair, that is, a common gear pair, and the gear pair formed by the second gear pair 16 and the third gear pair 17 is named as a common gear pair 161. One gear of the common gear pair 161 may be movably provided on the input shaft or the output shaft, and the other gear is provided on the intermediate shaft. Taking the example in which the common gear pair is movably disposed on the output shaft, the second clutch piece of the first switching double clutch 36 is used for the clutch of the input shaft with a gear of the common gear pair 161, and the first clutch piece of the second switching double clutch 37 is used for the clutch of the output shaft with a gear of the common gear pair 161. The remaining first gear pair 15 and third gear pair 18 remain unchanged, and the function of each clutch plate of the remaining double clutch is: the first clutch piece of the first switching double clutch 36 is used for engaging and disengaging the input shaft with a gear of the first gear pair 15, and the second clutch piece of the second switching double clutch 37 is used for engaging and disengaging the output shaft with a gear of the fourth gear pair.
In order to realize a clutch structure in the clutch, a clutch mode of friction plates can be adopted, the first clutch block comprises a first friction plate group, the second clutch block comprises a second friction plate group, the first friction plate group is positioned on one side of the other end of the double-end piston body, the second friction plate group is positioned on the other side of the other end of the double-end piston body, and the double-end piston body is used for driving one group of the first friction plate group or the second friction plate group to be combined and the other group to be separated. Namely, the double-end piston body pushes the friction plate of the first clutch block or the friction plate of the second clutch block, so that the first clutch block or the second clutch block can be clutched.
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 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 and the first gear pair of the first switching type double clutch are in a closed state, and the second clutch block and a gear of the common gear pair of the first switching type double clutch are in a separated state. In a similar way, 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 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.
In this embodiment, the number of the intermediate shafts is two, the intermediate shafts are arranged in an annular array around a center line of the input shaft or the output shaft, 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 intermediate shafts is multiple, and may be two, three, or four or even more. A plurality of the intermediate shafts are arranged in a circumferential array on a central axis of the input shaft or the output shaft. The intermediate shafts, such as two, may be disposed at upper and lower positions of the input shaft and the output shaft, respectively. The structure of a plurality of intermediate shafts is the same, for example, gears with the same number of teeth and the same tooth width are arranged. Therefore, the loads of the input shaft and the output shaft can be distributed through the plurality of intermediate shafts, so that the bending strength on the input shaft, the intermediate 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 utility model provides a take power take off's four-gear speed changer which characterized in that: the four-gear speed changer comprises an input shaft, an output shaft, an intermediate shaft, a first clutch, a second clutch, a third clutch, a fourth clutch, a shell and a power motor;
the central line of the input shaft and the central line of the output shaft are arranged in a collinear way, 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 the intermediate shaft through the first clutch or the second clutch, and then the intermediate shaft transmits the power to the output shaft through the third clutch or the fourth clutch; the center line of the intermediate shaft is parallel to the center line of the input shaft and is arranged in the shell;
one end of the intermediate shaft is in transmission connection with the 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 intermediate shaft.
2. A four-speed transmission with power take-off according to claim 1, wherein the first clutch and the second clutch are combined into a first switching double clutch, the third clutch and the fourth clutch are combined into a second switching double clutch, and the first switching double clutch and the second switching double clutch are the same switching 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 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 intermediate shaft, a second gear pair is arranged between the input shaft and the 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 intermediate shaft, a third gear pair is arranged between the output shaft and the intermediate shaft, one gear of the third gear pair is movably sleeved on the output shaft, the other gear of the third gear pair is arranged on the intermediate shaft, a fourth gear pair is arranged between the output shaft and the intermediate shaft, one gear of the fourth gear pair is movably sleeved on the output shaft, and the other gear of the fourth gear pair is arranged on the 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 output 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 output 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.
3. A four-speed transmission with power take-off according to claim 2, wherein 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.
4. The four-speed transmission with power output according to claim 3, wherein the first clutch block comprises a first friction plate set, the second clutch block comprises a second friction plate set, the first friction plate set is located on one side of the other end of the double-head piston body, the second friction plate set 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 plate set or the second friction plate set to be combined and the other to be separated.
5. A four-speed transmission with power take-off according to claim 2, 3 or 4, characterised in that the second gear wheel set and the third gear wheel set constitute a common gear wheel set.
6. A four-speed transmission with power take-off according to claim 1, wherein the intermediate shaft is provided with a key groove on the axial surface thereof, and the output end of the power motor is fixedly connected in the key groove.
7. A four-speed transmission with power take-off as claimed in claim 1, wherein there are multiple intermediate shafts, and the intermediate shafts are arranged in an annular array around the central lines of the input shaft and the output shaft, and the multiple intermediate shafts have the same structure, and each intermediate shaft is connected with a power motor.
8. A four-speed transmission with power take-off according to claim 1, wherein the power motor is a dc power motor.
CN201911340690.4A 2019-12-23 2019-12-23 Four-gear transmission with power output Pending CN111336222A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201911340690.4A CN111336222A (en) 2019-12-23 2019-12-23 Four-gear transmission with power output

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201911340690.4A CN111336222A (en) 2019-12-23 2019-12-23 Four-gear transmission with power output

Publications (1)

Publication Number Publication Date
CN111336222A true CN111336222A (en) 2020-06-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN201911340690.4A Pending CN111336222A (en) 2019-12-23 2019-12-23 Four-gear transmission with power output

Country Status (1)

Country Link
CN (1) CN111336222A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11988268B2 (en) * 2020-12-16 2024-05-21 Shenzhen Xianyu Power Technology Co., Ltd. Integrated power distribution apparatus for cooking robot

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11988268B2 (en) * 2020-12-16 2024-05-21 Shenzhen Xianyu Power Technology Co., Ltd. Integrated power distribution apparatus for cooking robot

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