CN105673836A - Gear shifting control system for automatic speed changer - Google Patents
Gear shifting control system for automatic speed changer Download PDFInfo
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- CN105673836A CN105673836A CN201410657662.6A CN201410657662A CN105673836A CN 105673836 A CN105673836 A CN 105673836A CN 201410657662 A CN201410657662 A CN 201410657662A CN 105673836 A CN105673836 A CN 105673836A
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Abstract
The invention provides a gear shifting control system for an automatic speed changer. The gear shifting control system comprises a main pump, four gear shifting oil cylinders, a gear shifting control valve, a first gear shifting valve, a second gear shifting valve, a first gear switching valve and a second gear switching valve. The gear shifting control valve is provided with a pressure input opening and two pressure output openings. The first gear shifting valve is provided with two pressure input openings and four pressure output openings. The second gear shifting valve is provided with two pressure input openings and four pressure output openings. The first gear switching valve is connected to the position between the first gear shifting valve and the gear shifting control valve to enable the gear shifting control valve and the first gear shifting valve to be disconnected or communicate. The second gear switching valve is connected to the position between the second gear shifting valve and the gear shifting control valve to enable the gear shifting control valve and the second gear shifting valve to be disconnected or communicate. The four pressure output openings of the first gear shifting valve and the four pressure output openings of the second gear shifting valve are connected with the four gear shifting oil cylinders.
Description
Technical field
The present invention relates to the technical field of the automatic transmission of automobile, especially relate to the shifting control system of a kind of automatic transmission.
Background technology
Along with the progress of science and technology, the mode that automobile realizes speed change is developed towards automatic transmission by manual speed change gradually, and automatic transmission is realized by automatic transmission. Wherein, double-clutch automatic gearbox receives the welcome in market owing to having the advantages such as transmission efficiency height, double-clutch automatic gearbox have employed two clutch couplinges, one of them clutch coupling is for controlling odd number gear, and another clutch coupling is for controlling even number gear, by between two clutch couplinges automatically switching thus complete gearshift program, therefore can realize the power gearshift of shift process, namely interrupt power at shift process, improve the comfortable property of vehicle operating.
Automatic transmission is when realizing self shifter, it is necessary to this system parts of gear shifting actuating mechanism, and its effect realizes automatic gear change function, current more employing hydraulic pressure formula gear shifting actuating mechanism. Gearshift is generally by being keyed to relevant axle and the synchronizer thereupon rotated completes, single side or two side of synchronizer are provided with the gear that can provide different drive ratios, under the effect of gear shifting actuating mechanism, synchronizer be struck move in the axial direction and with contiguous gear engagement, by on gear couplings to axle thus to realize gear synchronous with axle, thus outputting power.
The more employing of current automatic transmission eight gears (comprise and reversing gear), utilize shifting control system to be controlled by gear shifting actuating mechanism, to complete the gear shift operation of these eight gears. In prior art, in order to realize gearshift control and the safety control function of automatic transmission, this shifting control system generally have employed guiding valve and the magnetic valve of a greater number, makes system become comparatively complicated, and the efficiency of transmission control is lower.
Summary of the invention
It is an object of the invention to provide the shifting control system of a kind of automatic transmission, to realize when the quantity of spool control valve and magnetic valve is the least possible, it is achieved the gearshift control of automatic transmission and safety control function.
The embodiment of the present invention provides the shifting control system of a kind of automatic transmission, comprises main pump and four shift cylinders, and this shifting control system also comprises:
Gearshift control valve, this gearshift control valve has pressure introduction port and two pressure outputs, this gearshift control valve can switch between the first working position and the 2nd working position, when this gearshift control valve is in the first working position, one of them in this pressure introduction port and this two pressure outputs is connected, when this gearshift control valve is in the 2nd working position, in this pressure introduction port and this two pressure outputs wherein another is connected;
First gear switching valve, this the first gear switching valve has two pressure introduction port and four pressure outputs, this the first gear switching valve can switch between the first working position and the 2nd working position, when this first gear switching valve is in the first working position, two pressure introduction port of this first gear switching valve are connected with wherein two pressure outputs in four pressure outputs of this first gear switching valve respectively, when this first gear switching valve is in the 2nd working position, two pressure introduction port of this first gear switching valve are connected with two other pressure output in four pressure outputs of this first gear switching valve respectively,
Second gear position switching valve, this second gear position switching valve has two pressure introduction port and four pressure outputs, this second gear position switching valve can switch between the first working position and the 2nd working position, when this second gear position switching valve is in the first working position, two pressure introduction port of this second gear position switching valve are connected with wherein two pressure outputs in four pressure outputs of this second gear position switching valve respectively, when this second gear position switching valve is in the 2nd working position, two pressure introduction port of this second gear position switching valve are connected with two other pressure output in four pressure outputs of this second gear position switching valve respectively,
First gear bit switch valve, this first gear bit switch valve is connected between this first gear switching valve and this gearshift control valve, this first gear bit switch valve can switch between a closed position and a open position, when this first gear bit switch valve is in the closed position, two pressure outputs of this gearshift control valve respectively two pressure introduction port with this first gear switching valve disconnect, when this first gear bit switch valve is in an open position, two pressure outputs of this gearshift control valve are connected with two pressure introduction port of this first gear switching valve respectively; And
Second gear bit switch valve, this second gear bit switch valve is connected between this second gear position switching valve and this gearshift control valve, this second gear bit switch valve can switch between a closed position and a open position, when this second gear bit switch valve is in the closed position, two pressure outputs of this gearshift control valve respectively two pressure introduction port with this second gear position switching valve disconnect, when this second gear bit switch valve is in an open position, two pressure outputs of this gearshift control valve are connected with two pressure introduction port of this second gear position switching valve respectively;
Wherein, wherein two shift cylinders in four pressure outputs and this four shift cylinders of this first gear switching valve are connected, and two other shift cylinder in four pressure outputs and this four shift cylinders of this second gear position switching valve is connected.
In the embodiment of the present invention, by the gearshift control valve in shifting control system, the first gear switching valve, second gear position switching valve, first gear bit switch valve and second gear bit switch valve are controlled, the automatic gear change function to the automatic transmission with eight speed (seven forward gears and reverse gear) can be realized, greatly simplify the quantity of element in system, make when the quantity of spool control valve and magnetic valve is the least possible, realize gearshift control and the safety control function of automatic transmission, making system become simpler, the efficiency of transmission control is higher.
Above-mentioned explanation is only the general introduction of technical solution of the present invention, in order to the technique means of the present invention can be better understood, and can be implemented according to the content of specification sheets, and in order to the above and other object of the present invention, feature and advantage can be become apparent, below especially exemplified by better embodiment, and coordinate accompanying drawing, it is described in detail as follows.
Accompanying drawing explanation
Fig. 1 is the principle sketch of the shifting control system of automatic transmission in the embodiment of the present invention.
Embodiment
Reaching, for further setting forth the present invention, technique means and effect that predetermined goal of the invention is taked, below in conjunction with accompanying drawing and better embodiment, it is as follows that the present invention is described in detail.
Fig. 1 is the principle sketch of the shifting control system of automatic transmission in the embodiment of the present invention, please refer to the drawing 1, this shifting control system is used in automatic gearbox, especially double-clutch automatic gearbox, and this shifting control system comprises main pump 11, gearshift control valve 12, first gear switching valve 13, second gear position switching valve 14, first gear bit switch valve 15, second gear bit switch valve 16, odd even selector valve 17, first clutch solenoid valve 18, the 2nd clutch solenoid valve 19.
Main pump 11 is via oil absorption filter 21 oil suction from fuel tank 22, thus provides the pressure oil needed for work in this shifting control system. In the present embodiment, main pump 11 is by the internal combustion engine drive of automobile, this shifting control system is also provided with auxiliary pump 23, auxiliary pump 23 is driven by motor, main pump 11 can be assisted when the oil transportation amount deficiency of main pump 11 in auxiliary pump 23 1 aspect, can stop at oil engine on the other hand and therefore main pump 11 stopping guaranteeing pressure oil supplying in system. Auxiliary pump 23 is same via oil absorption filter 21 oil suction from fuel tank 22. Multiple positions of Fig. 1 employ fuel tank symbol, and these fuel tank symbols are interpreted as by relevant pipeline connection to fuel tank 22.
In order to stop fluid reversed flow, the delivery port of main pump 11 is connected with main pump check valve 24, in the present embodiment, main pump check valve 24 is the check valve of hydraulic control, the pressure oil retroactive effect that main pump 11 exports is at the control end of main pump check valve 24, to resist the spring being arranged on spring terminal, only when the output pressure of main pump 11 is enough to overcome spring power, main pump check valve 24 just switches to open position from the off-position shown in Fig. 1, that is, as long as when enough pressure also do not set up by main pump 11, the rest part of main pump 11 with this shifting control system is just disconnected by main pump check valve 24. for stoping, fluid flows towards the direction of main pump 11 in main pump check valve 24 1 aspect, on the other hand for ensureing the starting characteristic of necessity of main pump 11. understandably, main pump check valve 24 can also be common check valve.
In order to the peak pressure in Controlling System, the delivery port of main pump check valve 24 is also connected with security of system valve 25, security of system valve 25 can be safety overflow valve or common check valve, in the present embodiment, security of system valve 25 is common check valve, it is connected between the delivery port of main pump check valve 24 and fuel tank 22, the oil-in of check valve is connected with the delivery port of main pump check valve 24, the oil outlet of check valve is connected with fuel tank 22, by the peak pressure allowed in check valve initialization system, when the pressure in system exceedes this peak pressure, one-way valve opens carries out letting out oil.
Gearshift control valve 12 has pressure introduction port 121 and two pressure outputs 122,123 (hereinafter referred to as the first pressure output 122 and the 2nd pressure output 123), and the pressure introduction port 121 of gearshift control valve 12 is connected with main pump 11 via main pump check valve 24. Gearshift control valve 12 can switch between the first working position and the 2nd working position, when gearshift control valve 12 is in the first working position, pressure introduction port 121 is connected with one of them in two pressure outputs 122,123, gearshift control valve 12 is when being in the 2nd working position, pressure introduction port 121 with in two pressure outputs 122,123 wherein another is connected.In the present embodiment, when control valve 12 of shifting gears is in the first working position (left position as shown in Figure 1), pressure introduction port 121 is connected with the first pressure output 122, and the 2nd pressure output 123 is connected with fuel tank 22; When shift gears control valve 12 switch to be in the 2nd working position (right position as shown in Figure 1) time, pressure introduction port 121 is connected with the 2nd pressure output 123, and the first pressure output 122 is connected with fuel tank 22. That is, by changing the working position of gearshift control valve 12, it is possible to optionally the pressure oil from main pump 11 is directed on one of these two pressure outputs 122,123.
Gearshift control valve 12 can be solenoid operated directional valve or the liquid controlled reversing valve of side valve type. when control valve 12 of shifting gears be solenoid operated directional valve, by simple the electric switch operation that can realize gearshift control valve 12 with dead electricity. when different gear carries out gear shift operation, required gearshift pressure usually can be different, in order to realize two pressure outputs 122, the 123 gearshift pressure exported can meet the gearshift demand under different gear, in the present embodiment, gearshift control valve 12 adopts the hydraulic control proportional reversing valve of side valve type, this shifting control system also comprises gearshift pressure solenoid valve 26, the pressure output of gearshift pressure solenoid valve 26 is connected with the control end of gearshift control valve 12, when pressure solenoid valve 26 of shifting gears is opened, the control pressure that gearshift pressure solenoid valve 26 exports acts on the control end of gearshift control valve 12, to promote gearshift control valve 12 to carry out switch operation, in addition, pressure feedback is also acted on the two ends of gearshift control valve 12 by two pressure outputs 122,123 of gearshift control valve 12 respectively, exports different gearshift pressure with two pressure outputs 122,123 by gearshift pressure solenoid valve 26 realization gearshift control valve 12 under difference gearshift demand.
First gear switching valve 13 has two pressure introduction port 131,132 (hereinafter referred to as the first pressure introduction port 131 and the 2nd pressure introduction port 132) and four pressure outputs 133,134,135,136 (hereinafter referred to as the first pressure output 133, the 2nd pressure output 134, the 3rd pressure output 135 and the 4th pressure output 136). First gear switching valve 13 can switch between the first working position and the 2nd working position, when first gear switching valve 13 is in the first working position, two pressure introduction port 131,132 are connected with wherein two pressure outputs in four pressure outputs 133,134,135,136 respectively, when first gear switching valve 13 is in the 2nd working position, two pressure introduction port 131,132 are connected with two other pressure output in four pressure outputs 133,134,135,136 respectively. In the present embodiment, when the first gear switching valve 13 is in the first working position (left position as shown in Figure 1), two pressure introduction port 131,132 are connected with the 3rd pressure output 135 with the first pressure output 133 respectively, and the 2nd pressure output 134 and the 4th pressure output 136 are communicated to fuel tank 22; When the first gear switching valve 13 is in the 2nd working position (right position as shown in Figure 1), two pressure introduction port 131,132 are connected with the 4th pressure output 136 with the 2nd pressure output 134 respectively, and the first pressure output 133 and the 3rd pressure output 135 are communicated to fuel tank 22. That is, by changing the working position of the first gear switching valve 13, optionally the first pressure introduction port 131 can be connected with the first pressure output 133 or the 2nd pressure output 134, and optionally the 2nd pressure introduction port 132 is connected with the 3rd pressure output 135 or the 4th pressure output 136.
Second gear position switching valve 14 has two pressure introduction port 141,142 (hereinafter referred to as the first pressure introduction port 141 and the 2nd pressure introduction port 142) and four pressure outputs 143,144,145,146 (hereinafter referred to as the first pressure output 143, the 2nd pressure output 144, the 3rd pressure output 145 and the 4th pressure output 146). Second gear position switching valve 14 can switch between the first working position and the 2nd working position, when second gear position switching valve 14 is in the first working position, two pressure introduction port 141,142 are connected with wherein two pressure outputs in four pressure outputs 143,144,145,146 respectively, when second gear position switching valve 14 is in the 2nd working position, two pressure introduction port 141,142 are connected with two other pressure output in four pressure outputs 143,144,145,146 respectively. In the present embodiment, when second gear position switching valve 14 is in the first working position (right position as shown in Figure 1), two pressure introduction port 141,142 are connected with the 3rd pressure output 145 with the first pressure output 143 respectively, and the 2nd pressure output 144 and the 4th pressure output 146 are communicated to fuel tank 22; When second gear position switching valve 14 is in the 2nd working position (left position as shown in Figure 1), two pressure introduction port 141,142 are connected with the 4th pressure output 146 with the 2nd pressure output 144 respectively, and the first pressure output 143 and the 3rd pressure output 145 are communicated to fuel tank 22. That is, by changing the working position of second gear position switching valve 14, optionally the first pressure introduction port 141 can be connected with the first pressure output 143 or the 2nd pressure output 144, and optionally the 2nd pressure introduction port 142 is connected with the 3rd pressure output 145 or the 4th pressure output 146.
First gear bit switch valve 15 is connected between the first gear switching valve 13 and gearshift control valve 12, first gear bit switch valve 15 can switch between a closed position and a open position, when first gear bit switch valve 15 is in the closed position, two pressure outputs 122,123 of gearshift control valve 12 respectively two pressure introduction port 131,132 with the first gear switching valve 13 disconnect; When first gear bit switch valve 15 is in an open position, two pressure outputs 122,123 of gearshift control valve 12 are connected with two pressure introduction port 131,132 of the first gear switching valve 13 respectively. In the present embodiment, when first gear bit switch valve 15 (left position as shown in Figure 1) in the closed position, two pressure outputs 122,123 of gearshift control valve 12 are cut off at first gear bit switch valve 15, two pressure introduction port 131,132 of the first gear switching valve 13 are communicated to fuel tank 22 via first gear bit switch valve 15, thus two pressure introduction port 131,132 of two pressure outputs 122,123 and first gear switching valve 13 of control valve 12 of shifting gears are off state; When first gear bit switch valve 15 (right position as shown in Figure 1) in an open position, two pressure outputs 122,123 of gearshift control valve 12 respectively two pressure introduction port 131,132 with the first gear switching valve 13 be connected together.
Second gear bit switch valve 16 is connected between second gear position switching valve 14 and gearshift control valve 12, second gear bit switch valve 16 can switch between a closed position and a open position, when second gear bit switch valve 16 is in the closed position, two pressure outputs 122,123 of gearshift control valve 12 respectively two pressure introduction port 141,142 with second gear position switching valve 14 disconnect;When second gear bit switch valve 16 is in an open position, two pressure outputs 122,123 of gearshift control valve 12 are connected with two pressure introduction port 141,142 of second gear position switching valve 14 respectively. In the present embodiment, when second gear bit switch valve 16 (right position as shown in Figure 1) in the closed position, two pressure outputs 122,123 of gearshift control valve 12 are cut off at second gear bit switch valve 16, two pressure introduction port 141,142 of second gear position switching valve 14 are communicated to fuel tank 22 via second gear bit switch valve 16, thus two pressure introduction port 141,142 of two pressure outputs 122,123 of control valve 12 of shifting gears and second gear position switching valve 14 are off state; When second gear bit switch valve 16 (left position as shown in Figure 1) in an open position, two pressure outputs 122,123 of gearshift control valve 12 respectively two pressure introduction port 141,142 with second gear position switching valve 14 be connected together.
First gear bit switch valve 15 and second gear bit switch valve 16 can be specifically solenoid operated directional valve or the liquid controlled reversing valve of side valve type. when first gear bit switch valve 15 and second gear bit switch valve 16 adopt solenoid operated directional valve, electric first gear bit switch valve 15 and the switch operation of second gear bit switch valve 16 must can be realized with dead electricity by simple. in the present embodiment, first gear bit switch valve 15 and second gear bit switch valve 16 all adopt the liquid controlled reversing valve of side valve type, this shifting control system also comprises the first gear magnetic valve 27 and second gear position magnetic valve 28, first gear magnetic valve 27 and second gear position magnetic valve 28 are specifically as follows proportion magnetic valve, first gear magnetic valve 27 can export adjustable first gear control pressure, second gear position magnetic valve 28 can export adjustable second gear position control pressure, wherein this first gear control pressure acts on the opening end 151 of first gear bit switch valve 15 and the closedown end 162 of second gear bit switch valve 16, this second gear position control pressure acts on the opening end 161 of second gear bit switch valve 16 and the closedown end 152 of first gear bit switch valve 15, thus, two gear on-off valves 15, 16 can also realize interlocking while realizing commutation by this first gear control pressure and this second gear position control pressure, improve security of system, that is: when the first gear control pressure exported when the first gear magnetic valve 27 makes first gear bit switch valve 15 be in opened condition, by making simultaneously, second gear bit switch valve 16 is in closing condition to this first gear control pressure, when the second gear position control pressure that second gear position magnetic valve 28 exports makes second gear bit switch valve 16 be in opened condition, by making simultaneously, first gear bit switch valve 15 is in closing condition to this second gear position control pressure. in addition, the closedown end 152 of first gear bit switch valve 15 and the closedown end 162 of second gear bit switch valve 16 are also respectively equipped with spring, the reset function of these two gear on-off valves 15,16 after shutting down is provided to utilize spring.
First gear switching valve 13 and second gear position switching valve 14 can be specifically solenoid operated directional valve or the liquid controlled reversing valve of side valve type. When the first gear switching valve 13 and second gear position switching valve 14 adopt solenoid operated directional valve, electric the first gear switching valve 13 and the switch operation of second gear position switching valve 14 must can be realized with dead electricity by simple. In the present embodiment, first gear switching valve 13 and second gear position switching valve 14 all adopt the liquid controlled reversing valve of side valve type, first gear switching valve 13 also has the first control end 137 and the 2nd control end 138, first control end 137 and the 2nd control end 138 lay respectively at the two ends of the first gear switching valve 13, second gear position switching valve 14 also has the two ends that the first control end 147 and the 2nd control end 148, first control end 147 and the 2nd control end 148 lay respectively at second gear position switching valve 14.First control end 137 of the first gear switching valve 13 is connected with the first control end 147 of second gear position switching valve 14 and is connected to an oil circuit control, and the 2nd control end 138 of the first gear switching valve 13 is connected with the 2nd control end 148 of second gear position switching valve 14 and is connected to another oil circuit control.
This shifting control system also comprises four shift cylinders 41,42,43,44 (hereinafter referred to as the first shift cylinder 41, the 2nd shift cylinder 42, the 3rd shift cylinder 43 and the 4th shift cylinder 44). four pressure outputs 133,134,135,136 of the first gear switching valve 13 are connected with wherein two shift cylinders in four shift cylinders 41,42,43,44, and four pressure outputs 143,144,145,146 of second gear position switching valve 14 are connected with two other shift cylinder in four shift cylinders 41,42,43,44. in the present embodiment, four pressure outputs 133,134,135,136 of the first gear switching valve 13 are connected with the 2nd shift cylinder 42 with the first shift cylinder 41, and four pressure outputs 143,144,145,146 of second gear position switching valve 14 are connected with the 4th shift cylinder 44 with the 3rd shift cylinder 43. first pressure output 133 of the first gear switching valve 13 and the 3rd pressure output 135 are connected to the two ends of the first shift cylinder 41 respectively, 2nd pressure output 134 of the first gear switching valve 13 and the 4th pressure output 136 are connected to the two ends of the 2nd shift cylinder 42 respectively, first pressure output 143 of second gear position switching valve 14 and the 3rd pressure output 145 are connected to the two ends of the 3rd shift cylinder 43 respectively, and the 2nd pressure output 144 of second gear position switching valve 14 and the 4th pressure output 146 are connected to the two ends of the 4th shift cylinder 44 respectively. each shift cylinder realizes putting into gear or plucking gear of two gears for driving a corresponding selector fork to move, such as it is used for controlling three gears and seven gears by the first shift cylinder 41, 2nd shift cylinder 42 is used for control reverse gear and six gears, it is used for controlling a gear and five gears by the 3rd shift cylinder 43, and be used for controlling two gears and four gears by the 4th shift cylinder 44, like this, by to the gearshift control valve 12 in this shifting control system, first gear switching valve 13, second gear position switching valve 14, first gear bit switch valve 15 and second gear bit switch valve 16 control, the automatic gear change function to the automatic transmission with eight speed (seven forward gears and reverse gear) can be realized, greatly simplify the quantity of element in system, make when the quantity of spool control valve and magnetic valve is the least possible, realize gearshift control and the safety control function of automatic transmission, system is made to become simpler, control realization is more efficient.
Odd even selector valve 17 has pressure introduction port 171, first pressure output 172 and the 2nd pressure output 173, first pressure output 172 is connected with the first control end 137 of the first gear switching valve 13 and the first control end 147 of second gear position switching valve 14, and the 2nd pressure output 173 is connected with the 2nd control end 138 of the first gear switching valve 13 and the 2nd control end 148 of second gear position switching valve 14. Odd even selector valve 17 can switch between the first working position and the 2nd working position, when odd even selector valve 17 is in the first working position, pressure introduction port 171 is connected with the first pressure output 172, when odd even selector valve 17 is in the 2nd working position, pressure introduction port 171 is connected with the 2nd pressure output 173.In the present embodiment, when odd even selector valve 17 is in the first working position (right position as shown in Figure 1), pressure introduction port 171 is connected with the first pressure output 172, and the 2nd pressure output 173 is connected with fuel tank 22; When odd even selector valve 17 switch to be in the 2nd working position (left position as shown in Figure 1) time, pressure introduction port 171 is connected with the 2nd pressure output 173, and the first pressure output 172 is connected with fuel tank 22.
In the present embodiment, odd even selector valve 17 is the liquid controlled reversing valve of side valve type, the two ends of odd even selector valve 17 have the first control end 175 and the 2nd control end 176 respectively, first control end 175 of pressure output 182 and odd even selector valve 17 that the first clutch solenoid valve 18 has pressure introduction port 181 and pressure output 182, first clutch solenoid valve 18 is connected. When first clutch solenoid valve 18 is opened, pressure introduction port 181 is connected with pressure output 182, the control pressure that first clutch solenoid valve 18 exports acts on the first control end 175 of odd even selector valve 17, promotes odd even selector valve 17 commutation to make it be in the 2nd working position (left position as shown in Figure 1).
2nd control end 176 of pressure output 192 and odd even selector valve 17 that the 2nd clutch solenoid valve 19 has pressure introduction port 191 and pressure output the 192, two clutch solenoid valve 19 is connected. When 2nd clutch solenoid valve 19 is opened, pressure introduction port 191 is connected with pressure output 192, the control pressure that 2nd clutch solenoid valve 19 exports acts on the 2nd control end 176 of odd even selector valve 17, promotes odd even selector valve 17 commutation to make it be in the first working position (right position as shown in Figure 1). Wherein, first clutch solenoid valve 18 is for controlling the joint of the first clutch coupling (not shown), 2nd clutch solenoid valve 19 is for controlling the joint of the 2nd clutch coupling (not shown), and the pressure introduction port 181 of pressure introduction port 171, first clutch solenoid valve 18 of odd even selector valve 17 is all connected with main pump 11 with the pressure introduction port 191 of the 2nd clutch solenoid valve 19.
When the first clutch solenoid valve 18 is opened, odd even selector valve 17 will be made to be in the 2nd working position (left position as shown in Figure 1), now the pressure introduction port 171 of odd even selector valve 17 is connected with the 2nd pressure output 173, 2nd control end 138 of the first gear switching valve 13 and the 2nd control end 148 of second gear position switching valve 14 are applied control pressure by odd even selector valve 17 simultaneously, the first gear switching valve 13 is made to switch to the 2nd working position (right position as shown in Figure 1), first pressure introduction port 131 of the first gear switching valve 13 can only be connected with the 4th pressure output 136 with the 2nd pressure output 134 with the 2nd pressure introduction port 132, and make second gear position switching valve 14 switch to the 2nd working position (left position as shown in Figure 1) simultaneously, first pressure introduction port 141 of second gear position switching valve 14 can only be connected with the 4th pressure output 146 with the 2nd pressure output 144 with the 2nd pressure introduction port 142. and the first clutch solenoid valve 18 is when opening, first clutch coupling of this control odd number gear is in the working order engaged, double-clutch automatic gearbox is just being operated in odd number gear, the gear being then next linked into is even number gear, therefore by the design of suitable gear, such as the 2nd shift cylinder 42 being connected with the 4th pressure output 136 with the 2nd pressure output 134 of the first gear switching valve 13 and the 4th shift cylinder 44 that is connected with the 4th pressure output 146 with the 2nd pressure output 144 of second gear position switching valve 14 are all designed for control even number gear, then can only be linked into even number gear when the first clutch solenoid valve 18 is opened by the first gear switching valve 13 and second gear position switching valve 14, thus realize when the first clutch coupling of odd number gear works, forbid operation odd number gear.
When the 2nd clutch solenoid valve 19 is opened, odd even selector valve 17 will be made to be in the first working position (right position as shown in Figure 1), now the pressure introduction port 171 of odd even selector valve 17 is connected with the first pressure output 172, first control end 137 of the first gear switching valve 13 and the first control end 147 of second gear position switching valve 14 are applied control pressure by odd even selector valve 17 simultaneously, the first gear switching valve 13 is made to switch to the first working position (left position as shown in Figure 1), first pressure introduction port 131 of the first gear switching valve 13 can only be connected with the 3rd pressure output 135 with the first pressure output 133 with the 2nd pressure introduction port 132, and make second gear position switching valve 14 switch to the first working position (right position as shown in Figure 1) simultaneously, first pressure introduction port 141 of second gear position switching valve 14 can only be connected with the 3rd pressure output 145 with the first pressure output 143 with the 2nd pressure introduction port 142. and the 2nd clutch solenoid valve 19 is when opening, 2nd clutch coupling of this control even number gear is in the working order engaged, double-clutch automatic gearbox is just being operated in even number gear, the gear being then next linked into is odd number gear, therefore by the design of suitable gear, such as the first shift cylinder 41 being connected with the 3rd pressure output 135 with the first pressure output 133 of the first gear switching valve 13 and the 3rd shift cylinder 43 that is connected with the 3rd pressure output 145 with the first pressure output 143 of second gear position switching valve 14 are all designed for control odd number gear, then can only be linked into odd number gear when the 2nd clutch solenoid valve 19 is opened by the first gear switching valve 13 and second gear position switching valve 14, thus realize when the 2nd clutch coupling of even number gear works, forbid operation even number gear. that is, by the first gear switching valve 13 in this shifting control system, second gear position switching valve 14, odd even selector valve 17, first clutch solenoid valve 18 and the 2nd clutch solenoid valve 19 are controlled, can realize when the clutch coupling of odd number gear (or even number gear) works, forbid operation odd number gear (or even number gear), thus avoid mishandle occurs and damage automatic transmission, it is to increase security of system and robustness.
Reverse gear to hang up when the first clutch solenoid valve 18 and the 2nd clutch solenoid valve 19 are not all opened, odd even selector valve 17 also has the 3rd control end 177, 3rd control end 177 and the first control end 175 are positioned at same one end of odd even selector valve 17, 3rd control end 177 is connected with the first switch electromagnetic valve 29, when the first switch electromagnetic valve 29 is opened, first switch electromagnetic valve 29 pressure output control is also applied to the 3rd control end 177 of odd even selector valve 17, odd even selector valve 17 commutation is promoted to make it be in the 2nd working position (left position as shown in Figure 1), it is beneficial to can select to reverse gear.
In the present embodiment, the pressure output 182 at the first clutch solenoid valve 18 is also connected with odd number gear pressure transmitter 31, to detect operating pressure when driving the first clutch coupling to engage, same, the pressure output 192 at the 2nd clutch solenoid valve 19 is also connected with even number gear pressure transmitter 32, to detect operating pressure when driving the 2nd clutch coupling to engage. in order to pipeline being cut off when the pipeline that engages at clutch coupling occurring, pressure is abnormal, the pressure output 182 of the first clutch solenoid valve 18 and the pressure output 192 of the 2nd clutch solenoid valve 19 are also connected with clutch coupling safety cut-off valve 33, the pressure output of the first gear magnetic valve 27 and the pressure output of second gear position magnetic valve 28 are also connected to the same control end of clutch coupling safety cut-off valve 33 simultaneously, when the first gear magnetic valve 27 and second gear position magnetic valve 28 are all opened, first gear magnetic valve 27 export control pressure and second gear position magnetic valve 28 export control pressure force action under, off-position (left position as shown in Figure 1) is switched to from open position (right position as shown in Figure 1) by promoting clutch coupling safety cut-off valve 33, the oil circuit control engaged with cutting-off controlling clutch coupling.
In order to make to be applied to gearshift control valve 12, first gear switching valve 13, second gear position switching valve 14, control pressure on each control end of first gear bit switch valve 15 and second gear bit switch valve 16 tends to be steady, to improve the steady degree of each valve body when switch operation, delivery port at main pump 11 is also connected with electromagnetic pressure variable valve 34, electromagnetic pressure variable valve 34 is the ratio reducing valve of side valve type, electromagnetic pressure variable valve 34 has pressure introduction port 341 and pressure output 342, pressure introduction port 341 is connected with main pump 11, pressure output 342 and each magnetic valve 26, 27, 28, 29 and odd even selector valve 17 pressure introduction port be connected, pressure feedback is also acted on one end of electromagnetic pressure variable valve 34 by the pressure output 342 of electromagnetic pressure variable valve 34, to react on the spring being arranged on electromagnetic pressure variable valve 34 the other end. like this, even if there is fluctuation in the output pressure of main pump 11, after the adjustment through electromagnetic pressure variable valve 34, the pressure that pressure output 342 is exported remains relatively steady, so that also tended to be steady by each magnetic valve 26,27,28,29 and the after-applied control pressure on each control end of odd even selector valve 17.
This shifting control system further comprises working connection pressure solenoid valve 35 and working connection Pressure relief valve 36, the pressure introduction port of working connection pressure solenoid valve 35 is connected with the pressure output 342 of electromagnetic pressure variable valve 34, the pressure output of working connection pressure solenoid valve 35 is connected with the closedown end (this closedown end is also provided with spring) of working connection Pressure relief valve 36, working connection Pressure relief valve 36 has pressure introduction port, first pressure output and the 2nd pressure output, the opening end of working connection Pressure relief valve 36 (namely contrary with closing end one end) and pressure introduction port all delivery port with main pump 11 be connected, first pressure output of working connection Pressure relief valve 36 is connected with the oil mouth that enters of main pump 11, 2nd pressure output of working connection Pressure relief valve 36 then leads to lubricating and cooling system 50. the control pressure on the closedown end being applied to working connection Pressure relief valve 36 can be changed by working connection pressure solenoid valve 35, working connection Pressure relief valve 36 is changed from off-position to open position, thus make a part of fluid in working connection system can transfer to lubricating and cooling system 50 via working connection Pressure relief valve 36, to meet the needs being cooled by fluid and being lubricated by related elements.
Lubricating and cooling system 50 comprises cooling flow pressure limiting valve 51, oil cooler 52, pressure filter 53, check valve 54, little flow control valve 55, large flux control valve 56 and the 2nd switch electromagnetic valve 57. Cooling flow pressure limiting valve 51 is connected with the 2nd pressure output of working connection Pressure relief valve 36, the effect of the oil pressure that cooling flow pressure limiting valve 51 limits in lubricating and cooling system 50 for playing. Oil cooler 52 is connected with cooling flow pressure limiting valve 51 with pressure filter 53, for being cooled by fluid and fine filtering. Check valve 54 is connected in parallel on oil cooler 52 and pressure filter 53, it is bigger that the opening pressure of check valve 54 sets, therefore under normal circumstances oil stream through oil cooler 52 and pressure filter 53, only when oil cooler 52 and pressure filter 53 exist such as block, fluid just flows through from check valve 54 bypass. Fluid, after overcooling with filtration, can be distributed to via little flow control valve 55 and need the element of lubrication to carry out lubrication use, and unnecessary fluid can be back to fuel tank 22 by large flux control valve 56.When the fluid needed for lubricating is large discharge, large flux control valve 56 can be opened by the 2nd switch electromagnetic valve 57,2nd switch electromagnetic valve 57 has pressure introduction port and pressure output, the pressure introduction port of the 2nd switch electromagnetic valve 57 is connected with the pressure output of electromagnetic pressure variable valve 34, the pressure output of the 2nd switch electromagnetic valve 57 is connected with the control end of large flux control valve 56, therefore large flux control valve 56 can be promoted to commutate by the 2nd switch electromagnetic valve 57, to open large flux control valve 56.
The above, it it is only the better embodiment of the present invention, not the present invention is done any restriction in form, although the present invention discloses as above with better embodiment, but and be not used to limit the present invention, any those skilled in the art, do not departing within the scope of technical solution of the present invention, make a little change when the technology contents of above-mentioned announcement can be utilized or it is modified to the equivalent embodiment of equivalent variations, in every case it is do not depart from technical solution of the present invention content, the any simple modification above embodiment done according to the technical spirit of the present invention, equivalent variations and modification, all still belong in the scope of technical solution of the present invention.
Claims (10)
1. a shifting control system for automatic transmission, comprises main pump (11) and four shift cylinders (41,42,43,44), it is characterised in that, this shifting control system also comprises:
Gearshift control valve (12), this gearshift control valve (12) has pressure introduction port (121) and two pressure outputs (122, 123), this gearshift control valve (12) can switch between the first working position and the 2nd working position, when this gearshift control valve (12) is in the first working position, this pressure introduction port (121) and these two pressure outputs (122, 123) one of them in is connected, when this gearshift control valve (12) is in the 2nd working position, this pressure introduction port (121) and these two pressure outputs (122, 123) wherein another connection in,
First gear switching valve (13), this first gear switching valve (13) has two pressure introduction port (131, 132) and four pressure outputs (133, 134, 135, 136), this first gear switching valve (13) can switch between the first working position and the 2nd working position, when this first gear switching valve (13) is in the first working position, two pressure introduction port (131 of this first gear switching valve (13), 132) respectively with four pressure outputs (133 of this first gear switching valve (13), 134, 135, 136) wherein two pressure outputs in are connected, when this first gear switching valve (13) is in the 2nd working position, two pressure introduction port (131 of this first gear switching valve (13), 132) respectively with four pressure outputs (133 of this first gear switching valve (13), 134, 135, 136) two other pressure output in is connected,
Second gear position switching valve (14), this second gear position switching valve (14) has two pressure introduction port (141, 142) and four pressure outputs (143, 144, 145, 146), this second gear position switching valve (14) can switch between the first working position and the 2nd working position, when this second gear position switching valve (14) is in the first working position, two pressure introduction port (141 of this second gear position switching valve (14), 142) respectively with four pressure outputs (143 of this second gear position switching valve (14), 144, 145, 146) wherein two pressure outputs in are connected, when this second gear position switching valve (14) is in the 2nd working position, two pressure introduction port (141 of this second gear position switching valve (14), 142) respectively with four pressure outputs (143 of this second gear position switching valve (14), 144, 145, 146) two other pressure output in is connected,
First gear bit switch valve (15), this first gear bit switch valve (15) is connected between this first gear switching valve (13) and this gearshift control valve (12), this first gear bit switch valve (15) can switch between a closed position and a open position, when this first gear bit switch valve (15) is in the closed position, two pressure outputs (122 of this gearshift control valve (12), 123) respectively with two pressure introduction port (131 of this first gear switching valve (13), 132) disconnect, when this first gear bit switch valve (15) is in an open position, two pressure outputs (122 of this gearshift control valve (12), 123) respectively with two pressure introduction port (131 of this first gear switching valve (13), 132) it is connected, and
Second gear bit switch valve (16), this second gear bit switch valve (16) is connected between this second gear position switching valve (14) and this gearshift control valve (12), this second gear bit switch valve (16) can switch between a closed position and a open position, when this second gear bit switch valve (16) is in the closed position, two pressure outputs (122 of this gearshift control valve (12), 123) respectively with two pressure introduction port (141 of this second gear position switching valve (14), 142) disconnect, when this second gear bit switch valve (16) is in an open position, two pressure outputs (122 of this gearshift control valve (12), 123) respectively with two pressure introduction port (141 of this second gear position switching valve (14), 142) it is connected,
Wherein, wherein two shift cylinders in four pressure outputs (133,134,135,136) and this four shift cylinders (41,42,43,44) of this first gear switching valve (13) are connected, and two other shift cylinder in four pressure outputs (143,144,145,146) and this four shift cylinders (41,42,43,44) of this second gear position switching valve (14) is connected.
2. the shifting control system of automatic transmission as claimed in claim 1, it is characterised in that: the solenoid operated directional valve that this gearshift control valve (12), this first gear switching valve (13), this second gear position switching valve (14), this first gear bit switch valve (15) and this second gear bit switch valve (16) they are side valve type.
3. the shifting control system of automatic transmission as claimed in claim 1, it is characterized in that: the hydraulic control proportional reversing valve that this gearshift control valve (12) is side valve type, this shifting control system also comprises gearshift pressure solenoid valve (26), the pressure output of this gearshift pressure solenoid valve (26) is connected with the control end of this gearshift control valve (12), and pressure feedback is also acted on the two ends of this gearshift control valve (12) by two pressure outputs (122,123) of this gearshift control valve (12) respectively.
4. the shifting control system of automatic transmission as claimed in claim 3, it is characterized in that: this shifting control system also comprises electromagnetic pressure variable valve (34), the ratio reducing valve that this electromagnetic pressure variable valve (34) is side valve type, this electromagnetic pressure variable valve (34) has pressure introduction port (341) and pressure output (342), the pressure introduction port (341) of this electromagnetic pressure variable valve (34) is connected with the delivery port of this main pump (11), the pressure output (342) of this electromagnetic pressure variable valve (34) is connected with the pressure introduction port of this gearshift pressure solenoid valve (26).
5. the shifting control system of automatic transmission as claimed in claim 1, it is characterized in that: the liquid controlled reversing valve that this first gear switching valve (13) and this second gear position switching valve (14) are side valve type, the two ends of this first gear switching valve (13) have the first control end (137) and the 2nd control end (138) respectively, the two ends of this second gear position switching valve (14) have the first control end (147) and the 2nd control end (148) respectively, first control end (137) of this first gear switching valve (13) is connected with first control end (147) of this second gear position switching valve (14) and is connected to an oil circuit control, 2nd control end (138) of this first gear switching valve (13) is connected with the 2nd control end (148) of this second gear position switching valve (14) and is connected to another oil circuit control.
6. the shifting control system of automatic transmission as claimed in claim 5, it is characterized in that: this shifting control system also comprises odd even selector valve (17), this odd even selector valve (17) has pressure introduction port (171), first pressure output (172) and the 2nd pressure output (173), first pressure output (172) of this odd even selector valve (17) is connected with first control end (147) of first control end (137) of this first gear switching valve (13) and this second gear position switching valve (14), 2nd pressure output (173) of this odd even selector valve (17) is connected with the 2nd control end (148) of the 2nd control end (138) of this first gear switching valve (13) and this second gear position switching valve (14), this odd even selector valve (17) can switch between the first working position and the 2nd working position, when this odd even selector valve (17) is in the first working position, the pressure introduction port (171) of this odd even selector valve (17) is connected with first pressure output (172) of this odd even selector valve (17), when this odd even selector valve (17) is in the 2nd working position, the pressure introduction port (171) of this odd even selector valve (17) is connected with the 2nd pressure output (173) of this odd even selector valve (17).
7. the shifting control system of automatic transmission as claimed in claim 6, it is characterized in that: the liquid controlled reversing valve that this odd even selector valve (17) is side valve type, the two ends of this odd even selector valve (17) have the first control end (175) and the 2nd control end (176) respectively, this shifting control system also comprises the first clutch solenoid valve (18) and the 2nd clutch solenoid valve (19), this first clutch solenoid valve (18) is for controlling the joint of the first clutch coupling, 2nd clutch solenoid valve (19) is for controlling the joint of the 2nd clutch coupling, this first clutch solenoid valve (18) has pressure introduction port (181) and pressure output (182), the pressure output (182) of this first clutch solenoid valve (18) is connected with first control end (175) of this odd even selector valve (17), 2nd clutch solenoid valve (19) has pressure introduction port (191) and pressure output (192), the pressure output (192) of the 2nd clutch solenoid valve (19) is connected with the 2nd control end (176) of this odd even selector valve (17).
8. the shifting control system of automatic transmission as claimed in claim 1, it is characterized in that: the liquid controlled reversing valve that this first gear bit switch valve (15) and this second gear bit switch valve (16) are side valve type, this first gear bit switch valve (15) comprises opening end (151) and closes end (152), this second gear bit switch valve (16) also comprises opening end (161) and closes end (162), this shifting control system also comprises the first gear magnetic valve (27) and second gear position magnetic valve (28), the control pressure that this first gear magnetic valve (27) exports acts on the opening end (151) of this first gear bit switch valve (15) and the closedown end (162) of this second gear bit switch valve (16), the control pressure that this second gear position magnetic valve (28) exports acts on the closedown end (152) of this first gear bit switch valve (15) and the opening end (161) of this second gear bit switch valve (16).
9. the shifting control system of automatic transmission as claimed in claim 1, it is characterized in that: four pressure outputs (133 of this first gear switching valve (13), 134, 135, 136) the first pressure output (133) is comprised, 2nd pressure output (134), 3rd pressure output (135) and the 4th pressure output (136), when this first gear switching valve (13) is in the first working position, two pressure introduction port (131 of this first gear switching valve (13), 132) it is connected with the 3rd pressure output (135) with first pressure output (133) of this first gear switching valve (13) respectively, when this first gear switching valve (13) is in the 2nd working position, two pressure introduction port (131 of this first gear switching valve (13), 132) it is connected with the 4th pressure output (136) with the 2nd pressure output (134) of this first gear switching valve (13) respectively,Four pressure outputs (143 of this second gear position switching valve (14), 144, 145, 146) the first pressure output (143) is comprised, 2nd pressure output (144), 3rd pressure output (145) and the 4th pressure output (146), when this second gear position switching valve (14) is in the first working position, two pressure introduction port (141 of this second gear position switching valve (14), 142) it is connected with the 3rd pressure output (145) with first pressure output (143) of this second gear position switching valve (14) respectively, when this second gear position switching valve (14) is in the 2nd working position, two pressure introduction port (141 of this second gear position switching valve (14), 142) it is connected with the 4th pressure output (146) with the 2nd pressure output (144) of this second gear position switching valve (14) respectively.
10. the shifting control system of automatic transmission as claimed in claim 9, it is characterized in that: these four shift cylinders (41,42,43,44) the first shift cylinder (41) is comprised, 2nd shift cylinder (42), 3rd shift cylinder (43) and the 4th shift cylinder (44), first pressure output (133) of this first gear switching valve (13) and the 3rd pressure output (135) are connected to the two ends of this first shift cylinder (41) respectively, 2nd pressure output (134) of this first gear switching valve (13) and the 4th pressure output (136) are connected to the two ends of the 2nd shift cylinder (42) respectively, first pressure output (143) of this second gear position switching valve (14) and the 3rd pressure output (145) are connected to the two ends of the 3rd shift cylinder (43) respectively, 2nd pressure output (144) of this second gear position switching valve (14) and the 4th pressure output (146) are connected to the two ends of the 4th shift cylinder (44) respectively.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410657662.6A CN105673836B (en) | 2014-11-18 | 2014-11-18 | The shifting control system of automatic transmission |
| EP15861626.8A EP3222889B1 (en) | 2014-11-18 | 2015-11-04 | Gear-shifting control system of automatic transmission |
| PCT/CN2015/093782 WO2016078512A1 (en) | 2014-11-18 | 2015-11-04 | Gear-shifting control system of automatic transmission |
| US15/527,708 US10571017B2 (en) | 2014-11-18 | 2015-11-04 | Gear-shifting control system of automatic transmission |
| EP18214667.0A EP3486532B1 (en) | 2014-11-18 | 2015-11-04 | Gear-shifting control system of automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410657662.6A CN105673836B (en) | 2014-11-18 | 2014-11-18 | The shifting control system of automatic transmission |
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| CN105673836A true CN105673836A (en) | 2016-06-15 |
| CN105673836B CN105673836B (en) | 2017-11-24 |
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| CN201410657662.6A Active CN105673836B (en) | 2014-11-18 | 2014-11-18 | The shifting control system of automatic transmission |
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| CN113417997A (en) * | 2021-07-02 | 2021-09-21 | 贵州凯星液力传动机械有限公司 | Clutch and oil cylinder integrated control hydraulic system |
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