CN112879553B - Power shift transmission and control method thereof - Google Patents

Power shift transmission and control method thereof Download PDF

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Publication number
CN112879553B
CN112879553B CN202110076357.8A CN202110076357A CN112879553B CN 112879553 B CN112879553 B CN 112879553B CN 202110076357 A CN202110076357 A CN 202110076357A CN 112879553 B CN112879553 B CN 112879553B
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gear
transmission
clutch
valve
control
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CN112879553A (en
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胡建飞
史源
陈程
胡建华
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Hangzhou Advance Gearbox Group Co Ltd
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Hangzhou Advance Gearbox Group Co Ltd
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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
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • F16H59/0278—Constructional features of the selector lever, e.g. grip parts, mounting or manufacturing
    • 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
    • F16H61/02—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 characterised by the signals used
    • F16H61/0202—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 characterised by the signals used the signals being electric
    • F16H61/0204—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 characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
    • 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
    • F16H61/04—Smoothing ratio shift
    • 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
    • F16H61/4008—Control of circuit pressure
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms

Abstract

The invention discloses a power shift transmission and a control method thereof, wherein the method comprises the following steps: responding to starting and shifting requirements, applying pressure to the corresponding gear clutch, and setting a speed gear; applying a first control oil pressure P1 to the control valve of the clutch in the corresponding direction to enable the main disc and the driven disc to quickly eliminate the gap, and preparing for sliding grinding; the control oil pressure of the control valve is rapidly reduced to be close to the effective sliding pressure, so that the main driving disc and the auxiliary driving disc of the directional clutch start sliding; gradually and gently increasing the control oil pressure of the control valve, so that the driving direction of the control valve is gradually increased to transfer torque to the clutch driving and driven discs, and the rotating speed of gears connected with the driving and driven discs is gradually approaching; when the control oil pressure of the control valve is increased to the full pressure P, the main driven plate and the auxiliary driven plate of the directional clutch are completely combined, so that gears connected with the directional clutch synchronously rotate. The method can realize the automation of the starting and shifting process, and the starting and shifting process is more stable by dynamically controlling the starting and shifting of the transmission.

Description

Power shift transmission and control method thereof
Technical Field
The invention relates to a control device of a transmission, in particular to a power shift transmission and a control method thereof.
Background
Heavy engineering vehicles, such as road rollers and the like, have large dead weight, high requirements on climbing slopes and large range of running driving torque variation in combination with application environments, and are difficult to meet the requirements even though a hydraulic driving system with a large speed variation range is adopted.
The traditional road roller power transmission device is composed of a main clutch plus a power box or a power box with a torque converter or directly a power box with a torque converter, and the required performance requirement is ensured, but the main clutch is required to be manually operated to work, so that the labor intensity of a driver is high, the driver can have good performance only by skilled technology, and the service life of the main clutch is short; the power box with torque converter has the functions of buffering and improving torque, but has lower efficiency and higher cost.
Disclosure of Invention
Based on the technical problems, the invention aims to provide a control method of a power shift transmission, which can realize the automation of a starting and shifting process, and the starting and shifting process is more stable by dynamically controlling the starting and shifting of the transmission.
A second object of the present invention is to provide a transmission that performs start shifting using the control method described above.
In order to achieve the above object, the present invention provides a control method of a power shift transmission, the method comprising the steps of:
applying a first control oil pressure P1 to the control valve of the clutch in the corresponding direction to enable the main disc and the driven disc to quickly eliminate the gap, and preparing for sliding grinding;
the control oil pressure of the control valve is rapidly reduced to be close to the effective sliding pressure, so that the main driving disc and the auxiliary driving disc of the directional clutch start sliding;
gradually and gently increasing the control oil pressure of the control valve, so that the driving direction of the control valve is gradually increased to transfer torque to the clutch driving and driven discs, and the rotating speed of gears connected with the driving and driven discs is gradually approaching;
when the control oil pressure of the control valve is increased to the full pressure P, the main driven plate and the auxiliary driven plate of the directional clutch are completely combined, so that gears connected with the directional clutch synchronously rotate.
Preferably, the applying pressure to the corresponding gear clutch realizes gear setting, specifically: the control valve drives the gear clutch to combine with the driving and driven discs, so that gears connected with the driving and driven discs can synchronously rotate.
Preferably, the first oil pressure P1E [1/4P,2/5P ]. When the total pressure is 20bar, P1 is preferably 6bar.
Preferably, when the start gear shift requirement is flat ground start or flat ground gear shift, the time t1 required for increasing the control oil pressure of the control valve to the full pressure is 2-3s, and the process is a gentle boosting process, so that the start process is smoother.
Preferably, when the starting gear-shifting requirement is hill starting, the step-up control method comprises a step-up stage for eliminating a gap and a step-up stage for fast combining, wherein the time consumption t2 of the step-up stage for eliminating the gap is 40-100ms, and the time consumption t3 of the step-up stage for fast combining is 60-100 ms.
Preferably, the control oil pressure P2E [1/5P,1/4P ] corresponding to the effective sliding pressure.
Preferably, the method further comprises controlling the current direction clutch to be disconnected in response to the power reversing demand, and controlling the corresponding reverse direction clutch to be smoothly combined to complete the starting action when the output speed of the power shifting transmission 1 is lower than the set safety speed.
Preferably, the directional clutch is controlled to be disconnected in response to a brake signal until the brake signal is canceled, and if the brake signal is currently in 1 gear or 2 gear, the same gear is started; if the current gear is 3, starting from 2 nd gear and then increasing to 3 rd gear.
The invention further provides a power shift transmission for starting and shifting control by the control method, which comprises a transmission input shaft, a first transmission shaft, a second transmission shaft, a third transmission shaft and a transmission output shaft which are arranged in parallel, wherein a first input gear is arranged on the transmission input shaft; the first transmission shaft is provided with a second input gear, a first direction clutch, a first transmission gear, a first gear clutch and a first output gear in sequence from left to right, and the second input gear, the first transmission gear and the first output gear are all connected with the first transmission shaft through bearings; a third input gear, a second directional clutch, a second transmission gear, a second gear clutch, a second output gear and a third output gear are sequentially arranged on the second transmission shaft from left to right, and the third input gear, the second transmission gear, the second output gear and the third output gear are all connected with the second transmission shaft through bearings; a third transmission gear, a third gear clutch, a fourth output gear and a fifth output gear are sequentially arranged on the third transmission shaft from left to right, and the third transmission gear, the fourth output gear and the fifth output gear are all connected with the third transmission shaft through bearings; a sixth output gear is arranged on the transmission output shaft;
The first input gear is meshed with the second input gear, so that the rotating speed of the transmission input shaft is transmitted into the transmission through the second input gear; simultaneously, the first input gear is meshed with the third input gear, so that the rotating speed of the transmission input shaft can be reversely transmitted into the transmission through the third input gear;
one side of the second transmission gear is meshed with the first transmission gear, the other side of the second transmission gear is meshed with the third transmission gear, so that linkage of the first transmission gear, the second transmission gear and the third transmission gear is realized, the first output gear is meshed with the second output gear, the second output gear is linked with the third output gear, the third output gear is meshed with the fourth output gear, and the fourth output gear is linked with the fifth output gear; in this way, the output speed ratio of the transmission in different gears is adjusted by setting the root circle diameters of the gears corresponding to the different gears to different specifications and combining the control of the clutch.
Compared with the prior art, the invention has the beneficial effects that:
the invention can be applied to a power shift transmission, and the starting and shifting processes of the transmission are dynamically controlled by adjusting the control oil pressure of different valves in the control valve group, so that the starting and shifting processes are more stable.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiments of the application and together with the description serve to explain the application and do not limit the application.
FIG. 1 is a schematic diagram of a transmission architecture of a powershift transmission in accordance with an embodiment of the present invention;
FIG. 2 is a connection block diagram of a hydraulic control device in a powershift transmission in accordance with an embodiment of the present invention;
FIG. 3 is a schematic diagram of a connection configuration of a control system of a powershift transmission in accordance with an embodiment of the present invention;
FIG. 4 is a flow chart of a method of controlling a powershift transmission in an embodiment of the present invention;
FIG. 5 is a pressure control curve during a flat start or shift of a powershift transmission in an embodiment of the present invention;
FIG. 6 is a pressure control curve during hill start of a powershift transmission according to an embodiment of the present invention;
FIG. 7 is a drive train frame diagram of a single steel wheel roller;
FIG. 8 is a flow chart of a method of start shift control for a single steel wheel road roller;
FIG. 9 is a graph showing the speed change of the engine N1 and the powershift transmission N2 during a start shift of a single steel wheel road roller in accordance with an embodiment of the present invention;
1, a power shift transmission; 2. a hydraulic control device; 3. a controller; 4. an operation handle; 5. a sampling unit; 6. a gear display unit;
101. A transmission input shaft; 102. a first drive shaft; 103. a second drive shaft; 104. a third drive shaft; 105. a transmission output shaft; 106. a first input gear; 107. a second input gear; 108. a first directional clutch; 109. a first transmission gear; 110. a first gear clutch; 111. a first output gear; 112. a third input gear; 113. a second directional clutch; 114. a second transmission gear; 115. a second gear clutch; 116. a second output gear; 117. a third output gear; 118. a third transmission gear; 119. a third gear clutch; 120. a fourth output gear; 121. a fifth output gear; 122. a sixth output gear;
201. a first oil-dividing passage; 202. a second oil-dividing path; 203. a third oil-dividing passage; 204. a fourth oil-dividing passage; 205. an oil source; 206. a first electromagnetic directional valve; 207. a second electromagnetic directional valve; 208. a third electromagnetic directional valve; 209. a fourth electromagnetic directional valve; 210. a first hydraulic reversing valve; 211. a second hydraulic reversing valve; 212. a third hydraulic reversing valve; 213. a fourth hydraulic reversing valve; 214. a first proportional valve; 215. a second proportional valve; 216. a pressure control valve; 217. a pressure measuring device; 218. a first one-way valve; 219. a second one-way valve; 220. a first throttle valve; 221. a second throttle valve; 222. a third throttle valve; 223. a cooler; 224. a safety valve; 225. an oil pump; 226. a fine filter; 227. a main pressure valve.
Detailed Description
The invention will be further described with reference to the drawings and examples.
It should be noted that the following detailed description is illustrative and is intended to provide further explanation of the present application. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
The power shift transmission comprises a hydraulic control device 2 and a transmission device, wherein the transmission device comprises a transmission input shaft 101, a first transmission shaft 102, a second transmission shaft 103, a third transmission shaft 104 and a transmission output shaft 105 which are arranged side by side, and as shown in fig. 1, a first input gear 106 is arranged on the transmission input shaft 101; a second input gear 107, a first direction clutch 108, a first transmission gear 109, a first gear clutch 110 and a first output gear 111 are sequentially installed on the first transmission shaft 102 from left to right, and the second input gear 107, the first transmission gear 109 and the first output gear 111 are all connected with the first transmission shaft 102 through bearings; a third input gear 112, a second directional clutch 113, a second transmission gear 114, a second gear clutch 115, a second output gear 116 and a third output gear 117 are sequentially arranged on the second transmission shaft 103 from left to right, and the third input gear 112, the second transmission gear 114, the second output gear 116 and the third output gear 117 are all connected with the second transmission shaft 103 through bearings; a third transmission gear 118, a third gear clutch 119, a fourth output gear 120 and a fifth output gear 121 are sequentially arranged on the third transmission shaft 104 from left to right, and the third transmission gear 118, the fourth output gear 120 and the fifth output gear 121 are all connected with the third transmission shaft 104 through bearings; a sixth output gear 122 is mounted on the transmission output shaft 105;
The first input gear 106 meshes with the second input gear 107, so that the rotational speed of the transmission input shaft 101 is transmitted into the transmission via the second input gear 107; at the same time, the first input gear 106 meshes with the third input gear 112, so that the rotational speed of the transmission input shaft 101 can be reversely transmitted into the transmission through the third input gear 112;
one side of the second transmission gear 114 is meshed with the first transmission gear 109, and the other side is meshed with the third transmission gear 118, so that the linkage of the first transmission gear 109, the second transmission gear 114 and the third transmission gear 118 is realized, the first output gear 111 is meshed with the second output gear 116, the second output gear 116 is linked with the third output gear 117, the third output gear 117 is meshed with the fourth output gear 120, and the fourth output gear 120 is linked with the fifth output gear 121; in this way, the output speed ratio of the transmission in different gears is adjusted by setting the root circle diameters of the gears corresponding to the different gears to different specifications and combining the control of the clutch. The transmission structure removes the traditional structure of a main clutch and a torque converter, adopts a transmission structure of two-direction clutches and three-gear clutches, applies a hydraulic valve group to control, and adjusts the output speed ratios of different gears of the transmission by setting the diameters of root circles of gears corresponding to different gears to different specifications and combining electromagnetic and hydraulic combination control of the clutches; not only is the automation of the starting and gear shifting process facilitated, but also dynamic starting and gear shifting control can be performed, so that the starting and gear shifting process is smoother.
Preferably, the root diameters of the first output gear 111 and the third output gear 117 are smaller than the root diameter of the second output gear 116 meshed with the first output gear 111 and the third output gear 117, the root diameter of the third output gear 117 is smaller than the root diameter of the fourth output gear 120, and the root diameter of the fifth output gear 121 is smaller than the root diameter of the fourth output gear 120; when the transmission is set to a first gear output, four stages of continuous downshifts are formed among the first output gear 111, the second output gear 116, the third output gear 117, the fourth output gear 120 and the fifth output gear 121 to obtain a first gear speed;
when the transmission is set to be in a second gear output state, two stages of continuous speed reduction are formed among the third output gear 117, the fourth output gear 120 and the fifth output gear 121 to obtain a second gear speed;
when the transmission is set to a three-speed output, the output speed of the transmission is close to or the same as the input speed of the transmission.
Preferably, the range of the transmission ratio of the first gear is Q1, the transmission ratio of the second gear is Q2, and the transmission ratio of the third gear is Q3 is as follows: q1 epsilon [5.521,8.936], Q2 epsilon [2.807,4.543], Q3 epsilon [1.719,1.900].
Specifically, the gear ratios are preferably set forth in 4 parameters, as shown in Table 1:
table 1 Transmission ratio
Figure BDA0002907618220000061
As a preferred embodiment, the transmission further comprises a box, and the first transmission shaft 102, the second transmission shaft 103, the third transmission shaft 104, and gears and clutches on the transmission shafts are all arranged in the box.
As a preferred embodiment, the hydraulic control device 2 is disposed in the housing and is connected to the first directional clutch 108, the second directional clutch 113, the first gear clutch 110, the second gear clutch 115 and the third gear clutch 119, respectively, for driving the same to be engaged or disengaged so as to determine the rotation speed and the steering direction of the transmission output shaft 105. Specifically: the hydraulic control device 2 realizes the switching among gears by controlling the on-off combination of the clutches of each gear; the dynamic control of the clutch combining process in the corresponding direction realizes that the transmission starts gear shifting smoothly, and further realizes speed and direction change.
The present embodiment further provides a hydraulic control device 2 of a transmission, where the hydraulic control device 2 may be applied to the power shift transmission 1 described above, and includes a hydraulic control oil path connected to the oil source 205 and a control valve group, where the hydraulic control oil path includes a main oil path and at least three sub oil paths communicating with the main oil path, the main oil path is provided with an oil pump 225, and the control valve group is disposed on the sub oil paths and is used for controlling on-off of each sub oil path; preferably: the control valve group is respectively connected with the first direction clutch, the second direction clutch, the first gear clutch, the second gear clutch and the third gear clutch, and the switching among gears is realized by controlling the on-off of the gear clutches; by dynamically controlling the combination process of the clutches in the corresponding directions, the transmission can start and shift gears smoothly.
As shown in fig. 2, the control valve set includes a first electromagnetic directional valve 206, a second electromagnetic directional valve 207, a third electromagnetic directional valve 208, a fourth electromagnetic directional valve 209, a first hydraulic directional valve 210, a second hydraulic directional valve 211, a third hydraulic directional valve 212, a fourth hydraulic directional valve 213, a first proportional valve 214, and a second proportional valve 215, where the first electromagnetic directional valve 206, the second electromagnetic directional valve 207, the third electromagnetic directional valve 208, and the fourth electromagnetic directional valve 209 are respectively connected downstream of the first oil distribution path 201 (it is to be noted that the direction of the oil path approaching the oil source 205 is assumed to be upstream, and the direction of the oil path away from the oil source 205 is assumed to be downstream); the first hydraulic directional valve 210 is connected downstream of the second oil distribution path 202, and the third hydraulic directional valve 212 is communicated with the first hydraulic directional valve 210; the first proportional valve 214 and the second proportional valve 215 are respectively communicated with the third hydraulic reversing valve 212; the fourth hydraulic directional valve 213 is connected to the downstream of the third oil dividing path 203, the second hydraulic directional valve 211 is communicated with the fourth directional valve, wherein the first proportional valve 214 is connected to the first directional clutch 108 and is used for controlling the connection or disconnection of the first directional clutch 108 and the transmission shaft where the first directional clutch 108 is located, and the second proportional valve 215 is connected to the second directional clutch 113 and is used for controlling the connection or disconnection of the second directional clutch 113 and the transmission shaft where the second directional clutch 113 is located; the first electromagnetic directional valve 206, the second electromagnetic directional valve 207, the third electromagnetic directional valve 208 and the fourth electromagnetic directional valve 209 are mutually communicated and perform combined control on the first shift clutch, the second shift clutch and the third shift, so that the combined control of the control valve groups realizes the combined adjustment of the rotation direction and the output speed of the transmission.
As a preferred embodiment, a pressure control valve 216 is further disposed upstream of the second oil diversion passage 202, and downstream of the second oil diversion passage 202 is also communicated with a fourth hydraulic directional valve 213 and a second hydraulic directional valve 211, and the pressure control valve 216 is used for fine-tuning the oil pressure of the oil passages communicating with the first hydraulic directional valve 210, the second hydraulic directional valve 211, the third hydraulic directional valve 212 and the fourth hydraulic directional valve 213.
As a preferred embodiment, the output end of the oil pump 225 is further connected to a fourth oil dividing path 204, a pressure measuring device 217 is disposed at an upstream junction of the four oil dividing paths, and a main pressure valve 227 is disposed on the fourth oil dividing path, and the main pressure valve 227 is used for discharging excess oil pressure when the pressure at the junction is too limited, so that the oil pressures of the first oil dividing path 201, the second oil dividing path 202 and the third oil dividing path 203 are maintained within a limited pressure range.
As a preferred embodiment, the limiting pressure has a value in the range of 1.3-1.7MPa.
As a preferred embodiment, the passages of the second oil-dividing passage 202, which are communicated with the first hydraulic directional valve 210 and the fourth hydraulic directional valve 213, are respectively provided with a first check valve 218 and a second check valve 219.
As a preferred embodiment, the first throttle valve 220 and the second throttle valve 221 are disposed upstream of the second oil-dividing passage 202 and the third oil-dividing passage 203, respectively.
As a preferred embodiment, the output of the oil pump 225 is also provided with a relief valve 224.
As a preferred embodiment, a third throttle valve 222 is disposed downstream of the fourth oil-dividing passage 204.
As a preferred embodiment, a cooler 223 is further disposed between the main pressure valve 227 and the third throttle valve 222 of the fourth oil-dividing passage 204.
The power shift transmission 1 is preferably used on a road roller, and based on this, the embodiment also provides a road roller with the power shift transmission 1.
The present embodiment also provides a control system of the power shift transmission 1, as shown in fig. 3, including: the gear display unit 6 and the hydraulic control device 2, the controller 3 respectively with operating handle 4, sampling unit 5, gear display unit 6 and the hydraulic control device 2 electric connection, wherein:
the operating handle 4 is used for sending out direction, gear shifting, slope starting and vibration starting signals;
the sampling unit 5 is used for collecting the current transmission output rotating speed and the vehicle inclination angle;
The gear display unit 6 is used for displaying the output gear, direction and diagnostic information of the current transmission;
the hydraulic control device 2 comprises a main oil way connected with the oil source 205 and at least three sub oil ways communicated with the main oil way, the control valve group is arranged on the sub oil way, the control valve group is respectively connected with a directional clutch and a gear clutch in the power shift transmission 1, and the output transmission ratio of the transmission is adjusted by controlling the connection or disconnection of each gear clutch and a corresponding transmission shaft; dynamic adjustment of torque transmitted by the directional clutch is realized through dynamic control of the combination process of the main driving plate and the auxiliary driving plate of the directional clutch, so that the starting and gear shifting process is smoother;
the controller 3 responds to starting or gear shifting signals, adjusts the control oil pressure on-off of the gear clutch and continuously adjusts the control oil pressure of the directional clutch.
As a preferred embodiment, as shown in fig. 2, the hydraulic control device 2 includes a main oil path and at least three sub-oil paths communicated with the main oil path, an oil pump 225 is disposed on the main oil path, and the control valve group is disposed on the sub-oil paths and is used for controlling on-off of each sub-oil path;
the control valve group comprises a first electromagnetic directional valve 206, a second electromagnetic directional valve 207, a third electromagnetic directional valve 208, a fourth electromagnetic directional valve 209, a first hydraulic directional valve 210, a second hydraulic directional valve 211, a third hydraulic directional valve 212, a fourth hydraulic directional valve 213, a first proportional valve 214 and a second proportional valve 215, wherein the first electromagnetic directional valve 206, the second electromagnetic directional valve 207, the third electromagnetic directional valve 208 and the fourth electromagnetic directional valve 209 are respectively connected to the downstream of the first oil distribution path 201 (it is to be noted that the direction of the oil path approaching the oil source 205 is assumed to be the upstream, and the direction of the oil path departing from the oil source 205 is assumed to be the downstream); the first hydraulic directional valve 210 is connected downstream of the second oil distribution path 202, and the third hydraulic directional valve 212 is communicated with the first hydraulic directional valve 210; the first proportional valve 214 and the second proportional valve 215 are respectively communicated with the third hydraulic reversing valve 212; the fourth hydraulic directional valve 213 is connected downstream of the third oil dividing path 203, and the second hydraulic directional valve 211 is in communication with the fourth directional valve, where, as shown in fig. 2, the first proportional valve 214 is connected to the first directional clutch 108 and is used to control the connection or disconnection of the first directional clutch 108 and the transmission shaft where the first directional clutch is located, and the second proportional valve 215 is connected to the second directional clutch 113 and is used to control the connection or disconnection of the second directional clutch 113 and the transmission shaft where the second directional clutch is located; the first electromagnetic directional valve 206, the second electromagnetic directional valve 207, the third electromagnetic directional valve 208 and the fourth electromagnetic directional valve 209 are mutually communicated and perform combined control on the first shift clutch, the second shift clutch and the third shift, so that the combined control of the control valve groups realizes the combined adjustment of the rotation direction and the output speed of the transmission.
As a preferred embodiment, a pressure control valve 216 is further disposed upstream of the second oil diversion passage 202, and downstream of the second oil diversion passage 202 is also communicated with a fourth hydraulic directional valve 213 and a second hydraulic directional valve 211, and the pressure control valve 216 is used for fine-tuning the oil pressure of the oil passage communicating with the first hydraulic directional valve 210, the second hydraulic directional valve 211, the third hydraulic directional valve 212 and the fourth hydraulic directional valve 213.
As a preferred embodiment, the output end of the oil pump 225 is further connected to a fourth oil dividing path 204, a pressure measuring device 217 is disposed at an upstream junction of the four oil dividing paths, and a main pressure valve 227 is disposed on the fourth oil dividing path, and the main pressure valve 227 is configured to drain excess oil pressure when the pressure at the junction is too limited, so that the oil pressures of the first oil dividing path 201, the second oil dividing path 202, and the third oil dividing path 203 are maintained within a limited pressure range.
The gear control logic of the control valve block is shown in table 2:
table 2 gear control logic for a control valve block
Figure BDA0002907618220000091
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Figure BDA0002907618220000101
As a preferred embodiment, a plurality of control buttons for inputting operation demands are provided on the operation handle 4.
As a preferred embodiment, the sampling unit 5 is provided with an angular velocity sensor provided on an input shaft and an output shaft of the power shift transmission 1, and a gradient sensor provided on a bottom of the power shift transmission 1.
As a preferred embodiment, the gear display unit 6 is used for displaying the output gear, the traveling direction and the diagnostic information of the current transmission.
The embodiment also provides a control method based on the power shift transmission, as shown in fig. 4, comprising the following steps:
in response to starting or gear shifting requirements, applying pressure to the corresponding gear clutch to set a speed gear;
applying a first control oil pressure P1 to the control valve of the clutch in the corresponding direction to enable the main disc and the driven disc to quickly eliminate the gap, and preparing for sliding grinding;
the control oil pressure of the control valve is rapidly reduced to be close to the effective sliding pressure, so that the main driving disc and the auxiliary driving disc of the directional clutch start sliding;
gradually and gently increasing the control oil pressure of the control valve, so that the driving direction of the control valve is gradually increased to transfer torque to the clutch driving and driven discs, and the rotating speed of gears connected with the driving and driven discs is gradually approaching;
when the control oil pressure of the control valve is increased to the full pressure P, the main driven plate and the auxiliary driven plate of the directional clutch are completely combined, so that gears connected with the directional clutch synchronously rotate.
As a preferred embodiment, the application of pressure to the corresponding gear clutch realizes gear setting, specifically: and applying oil pressure to a reversing valve connected with the gear clutch, so that the control valve pushes the gear clutch to be combined with the driving disc and the driven disc, and gears connected with the driving disc and the driven disc can synchronously rotate.
As a preferred embodiment, the first oil pressure P1E [1/4P,2/5P ]. When the total pressure is 20bar, P1 is preferably 6bar.
As a preferred embodiment, as shown in fig. 5, when the start-shift demand is a flat start or a flat shift, the time t1 required to increase the control oil pressure of the control valve to the full pressure is 2-3s, and the process is a gentle boosting process, so that the start-shift process is smoother.
As a preferred embodiment, as shown in fig. 6, when the starting requirement is hill start, the step-up stage and the quick-combination step-up stage are specifically included to eliminate the gap and boost the time t2 of the gap and boost the time t3 of the quick-combination step-up stage by 40-100ms, and the step-up process is faster than the flat start process, so as to quickly combine the main driving disk and the auxiliary driving disk of the corresponding directional clutch, so as to quickly synchronize the gears connected with the corresponding directional clutch, thereby ensuring quick start of heavy machinery such as road rollers and avoiding sliding slopes.
As a preferred embodiment, the control oil pressure P2E [1/5P,1/4P ] corresponding to the effective skid pressure.
As a preferred embodiment, the method further comprises controlling the current direction clutch to be disconnected in response to the power reversing demand, and controlling the other direction clutch to be smoothly combined to execute reverse smooth starting action when the output speed of the power shifting transmission is lower than the set safe reversing speed. .
As a preferred embodiment, the directional clutch is controlled to be disconnected in response to the brake signal until the brake signal is cancelled, and if the brake signal is currently in 1 st gear or 2 nd gear, the same gear is started; if the current gear is 3, starting from 2 nd gear and then increasing to 3 rd gear.
The embodiment also provides a single steel wheel road roller, which is provided with the starting gear shifting control system.
The embodiment provides a starting and gear shifting control method of a single steel wheel road roller, as shown in fig. 7 and 8, comprising the following steps:
responding to a starting signal or a gear shifting signal, disconnecting the engine from a transmission part of the transmission, enabling the rotating speed of the engine to be reduced to a set starting gear shifting speed by controlling the rotating speed of the accelerator in the time T1, and keeping the rotating speed;
applying pressure to a corresponding gear clutch in the power shift transmission 1 to realize the setting of a speed gear; applying pressure to the directional clutch of the powershift transmission 1 to gradually establish a connection with the engine output shaft over a period of T2, thereby increasing the output speed of the transmission to a first speed attained in gear ratio;
And controlling the rotation speed of the engine to rise to the original throttle control rotation speed in the time T3, and rising the rotation speed of the transmission to the output speed of the set gear along with the rotation speed of the transmission, wherein T1 is more than or equal to 200ms and less than or equal to 500ms, T2 is more than or equal to 2s and less than or equal to 3s, and T3 is more than or equal to 2s and less than or equal to 3s. The engine is controlled to be decelerated to the set starting and shifting speed when starting or shifting starts, so that the loss caused by the combination of the clutch is reduced, and smooth starting and shifting are facilitated; after starting and shifting are completed, the engine is controlled to gradually accelerate to the control speed of the crude throttle, and the power shifting transmission 1 follows the acceleration, so that the starting and shifting process of the vehicle can be stable through the combined control of the engine and the transmission, and the vehicle can be accelerated stably along with the gradual recovery speed of the engine.
As a preferred embodiment, the throttle control rotating speed of the engine is generally 1000-2200r/min, and the set starting gear shifting speed is 800-900 r/min.
In a preferred embodiment, the set start shift speed is preferably 850r/min.
As a preferred embodiment, T1 is preferably 350ms, T2 is preferably 2.5s, and T3 is preferably 2.5s.
A start shift control system for a single steel wheel road roller, as shown in fig. 3, the system comprising: the gear display unit 6 and the hydraulic control device 2, the controller 3 respectively with operating handle 4, sampling unit 5, gear display unit 6 and the hydraulic control device 2 electric connection, wherein:
The operating handle 4 is used for sending out direction, gear shifting, slope starting and vibration starting signals;
the sampling unit 5 is used for collecting the output rotating speed of the current engine and the transmission and the inclination angle of the vehicle;
the gear display unit 6 is used for displaying the output gear of the current speed changer, the transmission direction of the speed changer and diagnostic information;
the hydraulic control device 2 comprises a main oil way connected with the oil source 205 and at least three sub oil ways communicated with the main oil way, the control valve group is arranged on the sub oil way, the control valve group is respectively connected with a directional clutch and a gear clutch in the power shift transmission 1, and the output transmission ratio of the transmission is adjusted by controlling the connection or disconnection of each gear clutch and a corresponding transmission shaft; dynamic adjustment of torque transmitted by the directional clutch is realized through dynamic control of the combination process of the main driving plate and the auxiliary driving plate of the directional clutch, so that the starting and gear shifting process is smoother;
the controller 3 responds to a starting or gear shifting signal, controls the clutch in the corresponding direction in the transmission to be disconnected with the engine, and controls the rotating speed of the engine to be reduced to a starting gear shifting set speed from the accelerator control rotating speed in the time T1;
Applying pressure to a corresponding gear clutch in the power shift transmission 1 to realize the setting of a speed gear; applying pressure to the directional clutch of the powershift transmission 1 to gradually establish a connection with the engine output shaft over a period of T2, thereby increasing the output speed of the transmission to a first speed attained in gear ratio;
the engine speed is controlled to rise to the original throttle control speed in the time T3, and the transmission speed is followed by rising to the output speed of the set gear.
As a preferred embodiment, the hydraulic control device 2 includes a main oil path and at least three sub-oil paths communicated with the main oil path, the main oil path is provided with an oil pump 225, and the control valve group is arranged on the sub-oil paths and is used for controlling the on-off of each sub-oil path;
the control valve group comprises a first electromagnetic directional valve 206, a second electromagnetic directional valve 207, a third electromagnetic directional valve 208, a fourth electromagnetic directional valve 209, a first hydraulic directional valve 210, a second hydraulic directional valve 211, a third hydraulic directional valve 212, a fourth hydraulic directional valve 213, a first proportional valve 214 and a second proportional valve 215, wherein the first electromagnetic directional valve 206, the second electromagnetic directional valve 207, the third electromagnetic directional valve 208 and the fourth electromagnetic directional valve 209 are respectively connected to the downstream of the first oil distribution path 201 (it is to be noted that the direction of the oil path approaching the oil source 205 is assumed to be the upstream, and the direction of the oil path departing from the oil source 205 is assumed to be the downstream); the first hydraulic directional valve 210 is connected downstream of the second oil distribution path 202, and the third hydraulic directional valve 212 is communicated with the first hydraulic directional valve 210; the first proportional valve 214 and the second proportional valve 215 are respectively communicated with the third hydraulic reversing valve 212; the fourth hydraulic directional valve 213 is connected downstream of the third oil dividing path 203, and the second hydraulic directional valve 211 is in communication with the fourth directional valve, where, as shown in fig. 2, the first proportional valve 214 is connected to the first directional clutch 108 and is used to control the connection or disconnection of the first directional clutch 108 and the transmission shaft where the first directional clutch is located, and the second proportional valve 215 is connected to the second directional clutch 113 and is used to control the connection or disconnection of the second directional clutch 113 and the transmission shaft where the second directional clutch is located; the first electromagnetic directional valve 206, the second electromagnetic directional valve 207, the third electromagnetic directional valve 208 and the fourth electromagnetic directional valve 209 are mutually communicated and perform combined control on the first shift clutch, the second shift clutch and the third shift, so that the combined control of the control valve groups realizes the combined adjustment of the rotation direction and the output speed of the transmission.
As a preferred embodiment, a pressure control valve 216 is further disposed upstream of the second oil diversion passage 202, and downstream of the second oil diversion passage 202 is also communicated with a fourth hydraulic directional valve 213 and a second hydraulic directional valve 211, and the pressure control valve 216 is used for fine-tuning the oil pressure of the oil passage communicating with the first hydraulic directional valve 210, the second hydraulic directional valve 211, the third hydraulic directional valve 212 and the fourth hydraulic directional valve 213.
As a preferred embodiment, the output end of the oil pump 225 is further connected to a fourth oil dividing path 204, a pressure measuring device 217 is disposed at an upstream junction of the four oil dividing paths, and a main pressure valve 227 is disposed on the fourth oil dividing path, and the main pressure valve 227 is configured to drain excess oil pressure when the pressure at the junction is too limited, so that the oil pressures of the first oil dividing path 201, the second oil dividing path 202, and the third oil dividing path 203 are maintained within a limited pressure range.
As a preferred embodiment, a plurality of control buttons for inputting operation demands are provided on the operation handle 4.
As a preferred embodiment, the sampling unit 5 is provided with an angular velocity sensor provided on an input shaft and an output shaft of the power shift transmission 1, and a gradient sensor provided on a bottom of the power shift transmission 1.
As a preferred embodiment, the gear display unit 6 is used for displaying the output gear, direction and diagnostic information of the current transmission.
The present embodiment also provides a computer-readable storage medium having a computer program stored therein, which when processed and executed, implements the start shift control method described above.
In addition, it should be noted that:
in the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
Although embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives and variations may be made to the above embodiments by those skilled in the art without departing from the spirit and principles of the invention, and any simple modification, equivalent variation and modification of the above embodiments in light of the technical principles of the invention may be made within the scope of the present invention.

Claims (6)

1. A control method of a power shift transmission, characterized by comprising the steps of:
responding to starting and shifting requirements, applying pressure to the corresponding gear clutch, and setting a speed gear;
applying a first control oil pressure P1 to the control valve of the clutch in the corresponding direction to enable the main disc and the driven disc to quickly eliminate the gap, and preparing for sliding grinding;
the control oil pressure of the control valve is rapidly reduced to be close to the effective sliding pressure, so that the main driving disc and the auxiliary driving disc of the directional clutch start sliding;
gradually and gently increasing the control oil pressure of the control valve, so that the driving direction of the control valve is gradually increased to transfer torque to the clutch driving and driven discs, and the rotating speed of gears connected with the driving and driven discs is gradually approaching;
when the control oil pressure of the control valve is increased to the full pressure P, the main driving plate and the auxiliary driving plate of the directional clutch are completely combined, so that the gears connected with the directional clutch synchronously rotate;
when the starting and gear shifting requirement is flat ground starting or flat ground gear shifting, the time t1 required for increasing the control oil pressure of the control valve to the full pressure is 2-3s, and the process is a gentle boosting process, so that the starting process is smoother;
when the starting gear-shifting requirement is hill starting, the step-up stage and the quick combination step-up stage are specifically included in the step-up control oil pressure to full pressure, wherein the time consumption t2 of the step-up stage is 40-100ms, the time consumption t3 of the quick combination step-up stage is 50-100ms, the process is faster than the flat starting process, and the purpose is to enable the main driving disc and the auxiliary driving disc of the corresponding directional clutch to be quickly combined and quickly synchronized with the gears connected with the main driving disc, so that the road roller is guaranteed to quickly start, and the sliding slope is avoided:
The power shifting transmission comprises a hydraulic control device and a transmission device, wherein the transmission device comprises a transmission input shaft, a first transmission shaft, a second transmission shaft, a third transmission shaft and a transmission output shaft which are arranged side by side, and a first input gear is arranged on the transmission input shaft; the first transmission shaft is provided with a second input gear, a first direction clutch, a first transmission gear, a first gear clutch and a first output gear in sequence from left to right, and the second input gear, the first transmission gear and the first output gear are all connected with the first transmission shaft through bearings; a third input gear, a second directional clutch, a second transmission gear, a second gear clutch, a second output gear and a third output gear are sequentially arranged on the second transmission shaft from left to right, and the third input gear, the second transmission gear, the second output gear and the third output gear are all connected with the second transmission shaft through bearings; a third transmission gear, a third gear clutch, a fourth output gear and a fifth output gear are sequentially arranged on the third transmission shaft from left to right, and the third transmission gear, the fourth output gear and the fifth output gear are all connected with the third transmission shaft through bearings; a sixth output gear is arranged on the transmission output shaft; the first input gear is meshed with the second input gear, so that the rotating speed of the transmission input shaft is transmitted into the transmission through the second input gear; simultaneously, the first input gear is meshed with the third input gear, so that the rotating speed of the transmission input shaft can be reversely transmitted into the transmission through the third input gear; one side of the second transmission gear is meshed with the first transmission gear, the other side of the second transmission gear is meshed with the third transmission gear, so that linkage of the first transmission gear, the second transmission gear and the third transmission gear is realized, the first output gear is meshed with the second output gear, the second output gear is linked with the third output gear, the third output gear is meshed with the fourth output gear, and the fourth output gear is linked with the fifth output gear;
The hydraulic control device comprises a hydraulic control oil way and a control valve group, wherein the hydraulic control oil way is connected with an oil source and comprises a main oil way and at least three branch oil ways communicated with the main oil way, an oil pump is arranged on the main oil way, and the control valve group is arranged on the branch oil ways and is used for controlling the on-off of each branch oil way;
the control valve group comprises a first electromagnetic directional valve, a second electromagnetic directional valve, a third electromagnetic directional valve, a fourth electromagnetic directional valve, a first hydraulic directional valve, a second hydraulic directional valve, a third hydraulic directional valve, a fourth hydraulic directional valve, a first proportional valve and a second proportional valve, wherein the first electromagnetic directional valve, the second electromagnetic directional valve, the third electromagnetic directional valve and the fourth electromagnetic directional valve are respectively connected to the downstream of the first oil dividing way; the first hydraulic reversing valve is connected to the downstream of the second oil dividing way, and the third hydraulic reversing valve is communicated with the first hydraulic reversing valve; the first proportional valve and the second proportional valve are respectively communicated with the third hydraulic reversing valve; the second hydraulic reversing valve is communicated with the fourth hydraulic reversing valve, wherein the first proportional valve is connected with the first directional clutch and used for controlling the connection or disconnection of the first directional clutch and a transmission shaft where the first directional clutch is positioned, and the second proportional valve is connected with the second directional clutch and used for controlling the connection or disconnection of the second directional clutch and the transmission shaft where the second directional clutch is positioned; the first electromagnetic directional valve, the second electromagnetic directional valve, the third electromagnetic directional valve and the fourth electromagnetic directional valve are mutually communicated and are used for carrying out combined control on the first gear clutch, the second gear clutch and the third gear clutch.
2. The control method of a powershift transmission according to claim 1, wherein the application of pressure to the corresponding gear clutch effects a speed gear setting, specifically: and applying oil pressure to a reversing valve connected with the gear clutch, so that the reversing valve pushes the gear clutch to be combined with a driving disc and a driven disc, and a transmission gear connected with the reversing valve synchronously rotates.
3. A control method of a powershift transmission according to claim 1, characterized in that the first control oil pressure p1 e [1/4P,2/5P ].
4. The control method of a powershift transmission according to claim 1, wherein the control oil pressure p2_e [1/5P,1/4P ] corresponding to the effective skid pressure.
5. The method of claim 1, further comprising controlling a smooth reverse direction clutch engagement to execute a smooth reverse launch when the power shift transmission output speed is below a set safe reverse speed after the current direction clutch is disengaged in response to a power shift demand.
6. The method of claim 1, wherein the directional clutch is controlled to be disconnected in response to a brake signal until the brake signal is canceled, and the same gear is started if the brake signal is currently in 1 or 2 gear; if the current gear is 3, starting from 2 nd gear and then increasing to 3 rd gear.
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