CN206145111U - Automatic cooling and lubrication system and hydraulic pressure shift system of derailleur - Google Patents

Abstract

The utility model discloses an automatic cooling and lubrication system and hydraulic pressure shift system of derailleur, cooling and lubrication system include main pump, auxiliary pump, little flow control valve and big flow control valve, and little flow control valve's entry links to each other with the main pump, and two entrys of big flow control valve link to each other with main pump and auxiliary pump respectively, when little flow control valve is in first work position, there is not the flow to pass through little flow control valve, when little flow control valve is in second work position, the lubricated component of the flow directed forced oil cooling of main pump, when big flow control valve is in first work position, there is not the flow to pass through big flow control valve, when big flow control valve is in second work position, the lubricated component of the flow directed forced oil cooling of main pump, when big flow control valve is in third work position, the flow of main pump and auxiliary pump directed forced oil cooling lubrication simultaneously component. The double stage control can be carried out to the cooling and lubrication flow to this embodiment, and the flow is supplied with more accurately, reduces the energy consumption of derailleur.

Description

The cooling and lubricating system and hydraulic gear-shifting system of automatic transmission

Technical field

The utility model is related to the technical field of automatic transmission, more particularly, to a kind of cooling and lubricating of automatic transmission System and hydraulic gear-shifting system.

Background technology

Automatic transmission needs hydraulic gear-shifting system this system unit when self shifter is realized, its effect is to realize Automatic gear change function.Gearshift is completed generally by the synchronized for being keyed to reference axis and rotating with, the list of synchronized Side or bilateral are provided with the gear that can provide different drive ratios, and in the presence of hydraulic gear-shifting system, synchronized is struck along axle To mobile and engage with neighbouring gear, gear is connected on axle it is synchronous with axle so as to realize gear, so as to export power.

With the progress of science and technology, double-clutch automatic gearbox with advantages such as transmission efficiency height due to receiving market Welcome, two clutches are employed in double-clutch automatic gearbox, one of clutch is used to control odd number gear, and another Individual clutch is used to control even number gear, and by automatically switching between two clutches gearshift program is completed, therefore can The power shifting of shift process is realized, i.e., interrupts power in shift process, improve the comfortableness of vehicle operation.Current Double-clutch automatic gearbox is more to adopt eight gears (including reversing gear), is controlled using hydraulic gear-shifting system, completes eight The gear shift operation of individual gear.

The related elements (such as bearing, gear, clutch) of automatic transmission operationally need to carry out cooling and lubricating, mesh In front cooling and lubricating scheme, for cooling and lubricating flow is not typically controlled, or one-level control is only carried out, cause speed change The energy consumption of device is higher, the space that there is optimization.

Utility model content

The purpose of this utility model is to provide a kind of cooling and lubricating system of automatic transmission, can be to automatic transmission Cooling and lubricating flow carry out two-step evolution so that the supply of flow is more accurate, reduce speed changer energy consumption.

The utility model provides a kind of cooling and lubricating system of automatic transmission, including main pump, auxiliary pump, control valve for small flows And large flux control valve, the entrance of the control valve for small flows is connected with the main pump, one of entrance of the large flux control valve It is connected with the main pump, another entrance is connected with the auxiliary pump；The control valve for small flows has the first working position and the second working position, When the control valve for small flows is in the first working position, without flow by the control valve for small flows Directed cooling lubricating element, When the control valve for small flows is in the second working position, flow Directed cooling lubrication unit of the control valve for small flows the main pump Part；The large flux control valve has the first working position, the second working position and the 3rd working position, when the large flux control valve is in the During one working position, without flow by the large flux control valve Directed cooling lubricating element, when the large flux control valve is in the During two working positions, the large flux control valve the flow Directed cooling lubricating element of the main pump, when the large flux control valve is in During three working positions, the large flux control valve is the flow of the main pump and auxiliary pump Directed cooling lubricating element simultaneously.

Further, the control valve for small flows has control end, and the large flux control valve has control end, and the low discharge is adjusted The control end of section valve and the control end of the large flux control valve are connected with the outlet of same electromagnetic pressure control valve simultaneously, by this Electromagnetic pressure control valve changes the work being applied in the control end of the control end of the control valve for small flows and the large flux control valve Firmly, promote the control valve for small flows to commutate between its first working position and the second working position, and promote the big flow to adjust Section valve commutates in its first working position, between the second working position and the 3rd working position.

Further, the active force needed for promoting the control valve for small flows to be commutated is less than the promotion large flux control valve Active force needed for being commutated, when the electromagnet of the electromagnetic pressure control valve is passed through smaller current, is applied to the low discharge and adjusts Active force in the control end of section valve and the control end of the large flux control valve only promotes the control valve for small flows to be commutated, should When the electromagnet of electromagnetic pressure control valve is passed through larger current, the control end and the big flow for being applied to the control valve for small flows is adjusted Active force in the control end of section valve promotes the control valve for small flows and the large flux control valve to be commutated simultaneously.

Further, by driven by engine, the auxiliary pump is driven the main pump by motor, and the output flow of the auxiliary pump continuously may be used Adjust.

The utility model also provides a kind of hydraulic gear-shifting system of automatic transmission, including above-mentioned cooling and lubricating system.

Further, the hydraulic gear-shifting system also include first pressure control magnetic valve, second pressure control magnetic valve, the One flow control electromagnetic valve, second flow control magnetic valve, first switch magnetic valve, second switch magnetic valve, the first gear are opened Close valve, the second driving switch valve, third gear switch valve, fourth speed bit switch valve, the first shift cylinder, the second shift cylinder, 3rd shift cylinder and the 4th shift cylinder, the wherein outlet of the first pressure control magnetic valve and the first flow control electricity The entrance connection of magnet valve, the outlet of the second pressure control magnetic valve is connected with the entrance of the second flow control magnetic valve, should The outlet of first flow control magnetic valve is connected with the entrance of the first driving switch valve and the entrance of the third gear switch valve, The outlet of the second flow control magnetic valve connects with the entrance of the second driving switch valve and the entrance of the fourth speed bit switch valve Connect, the outlet of the first driving switch valve is connected with the oil pocket of first shift cylinder, the outlet of the second driving switch valve with The oil pocket connection of second shift cylinder, the outlet of the third gear switch valve is connected with the oil pocket of the 3rd shift cylinder, should The outlet of fourth speed bit switch valve is connected with the oil pocket of the 4th shift cylinder, the outlet of the first switch magnetic valve with this first The control end connection of the control end of driving switch valve and the second driving switch valve, the first driving switch valve and second gear Switch valve is commutated by the first switch solenoid valve control, the outlet of the second switch magnetic valve and the third gear switch valve Control end and the fourth speed bit switch valve control end connection, the third gear switch valve and the fourth speed bit switch valve are by this Second switch solenoid valve control is commutated, and the entrance of the first pressure control magnetic valve, the second pressure control magnetic valve The entrance of entrance, the entrance of the first switch magnetic valve and the second switch magnetic valve is connected with working connection.

Further, the first pressure control magnetic valve has entrance and exit, and the second pressure control magnetic valve has Entrance and exit, first flow control magnetic valve has entrance and two outlets, second flow control magnetic valve have into Mouthful and two outlets, the entrance and the second pressure of first pressure control magnetic valve control the entrance of magnetic valve with the main oil Road is connected, and the outlet of the first pressure control magnetic valve is connected with the entrance of the first flow control magnetic valve, the second pressure The outlet of control magnetic valve is connected with the entrance of the second flow control magnetic valve, and two of the first flow control magnetic valve go out Mouth is connected with the first driving switch valve and the third gear switch valve, and two of second flow control magnetic valve export and are somebody's turn to do Second driving switch valve and the fourth speed bit switch valve are connected.

Further, first flow control magnetic valve can switch between the first working position and the second working position, and this When one flow control electromagnetic valve is in the first working position, the entrance of the first flow control magnetic valve is electric with the first flow control Connection one of in two of magnet valve outlets, when first flow control magnetic valve is in the second working position, this is first-class Amount controls the entrance of magnetic valve and connects with another in two outlets of first flow control magnetic valve；The second flow control Magnetic valve can switch between the first working position and the second working position, and the second flow control magnetic valve is in the first working position When, one of in the entrance of second flow control magnetic valve and two outlets of second flow control magnetic valve even It is logical, when the second flow control magnetic valve is in the second working position, the entrance and the second of the second flow control magnetic valve Another connection in two outlets of amount control magnetic valve.

Further, the first switch magnetic valve has entrance and exit, and the second switch magnetic valve has entrance and goes out Mouthful, the first driving switch valve has two entrances, two outlets and a control end, and the second driving switch valve has two Entrance, two outlets and a control end, the third gear switch valve has two entrances, two outlets and a control end, The fourth speed bit switch valve have two entrances, two outlet and a control end, the entrance of the first switch magnetic valve and should The entrance of second switch magnetic valve is connected with the working connection, and the outlet of the first switch magnetic valve is opened with first gear simultaneously The control end for closing valve is connected with the control end of the second driving switch valve, and the outlet of the second switch magnetic valve is while with the 3rd The control end of driving switch valve is connected with the control end of the fourth speed bit switch valve, the two entrances point of the first driving switch valve Be not connected with two outlets of first flow control magnetic valve, the two entrances of the second driving switch valve respectively with this second Two outlets of flow control electromagnetic valve are connected, and the two entrances of the third gear switch valve are electric with the first flow control respectively Two outlets of magnet valve are connected, and the two entrances of the fourth speed bit switch valve control respectively two of magnetic valve with the second flow Outlet is connected, and two outlets of the first driving switch valve are connected respectively with two oil pockets of first shift cylinder, and this second Two outlets of driving switch valve are connected respectively with two oil pockets of second shift cylinder, two of the third gear switch valve Outlet is connected respectively with two oil pockets of the 3rd shift cylinder, and two of the fourth speed bit switch valve export respectively with the 4th Two oil pockets of shift cylinder are connected.

Further, the first switch magnetic valve and the second switch magnetic valve are integrated into the switch electricity of a 3-position 4-way Magnet valve, the entrance of the first switch magnetic valve is integrated into the switch electromagnetism of the 3-position 4-way with the entrance of the second switch magnetic valve One entrance of valve and it is connected with the working connection, the outlet of the first switch magnetic valve and the outlet point of the second switch magnetic valve Not Wei the 3-position 4-way two of switch electromagnetic valve outlets.

The cooling and lubricating system that the utility model is provided, is applied to the cooling and lubricating control of automatic transmission, it is possible to achieve Two-step evolution is carried out to the cooling and lubricating flow of automatic transmission so that the supply of flow is more accurate, reduce the energy of speed changer Consumption, the performance for making system more optimizes.

Described above is only the general introduction of technical solutions of the utility model, in order to better understand skill of the present utility model Art means, and being practiced according to the content of specification, and in order to allow above and other purpose of the present utility model, feature Can become apparent with advantage, below especially exemplified by preferred embodiment, and coordinate accompanying drawing, describe in detail as follows.

Description of the drawings

Fig. 1 is the schematic diagram of the hydraulic gear-shifting system of automatic transmission in the utility model first embodiment.

Fig. 2 is the schematic diagram of the hydraulic gear-shifting system of automatic transmission in the utility model second embodiment.

Specific embodiment

Further to illustrate that the utility model is to reach technological means and effect that predetermined utility model purpose is taken, Below in conjunction with accompanying drawing and preferred embodiment, the utility model is described in detail as follows.

The utility model provides a kind of cooling and lubricating system of automatic transmission, can be to the cooling and lubricating of automatic transmission Flow carries out two-step evolution so that the supply of flow is more accurate, reduces the energy consumption of speed changer.

[first embodiment]

Fig. 1 is the schematic diagram of the hydraulic gear-shifting system of automatic transmission in the utility model first embodiment, please join Fig. 1, The hydraulic gear-shifting system includes first pressure control magnetic valve 11, second pressure control magnetic valve 12, first flow control electromagnetism Valve 21, second flow control magnetic valve 22, first switch magnetic valve 31, second switch magnetic valve 32, the first driving switch valve 41, Second driving switch valve 42, third gear switch valve 43, fourth speed bit switch valve 44, the first shift cylinder 51, second are shifted gears oily Cylinder 52, the 3rd shift cylinder 53 and the 4th shift cylinder 54.

First pressure control magnetic valve 11 have entrance A1 and outlet B1, first pressure control magnetic valve 11 entrance A1 with Working connection 10 is connected, and the outlet B1 of first pressure control magnetic valve 11 is connected with first flow control magnetic valve 21, makes the first pressure The pressure oil of the outlet B1 outputs of power control magnetic valve 11 can be opened via first flow control magnetic valve 21 into the first gear Close valve 41 to promote the first shift cylinder 51 to carry out gear shift operation, or third gear is entered via first flow control magnetic valve 21 Bit switch valve 43 carries out gear shift operation to promote the 3rd shift cylinder 53.

When different gears carry out gear shift operation, required gearshift pressure would generally be different.To realize first pressure The gearshift pressure of the outlet B1 outputs of control magnetic valve 11 can meet the gearshift demand under different gears, in the present embodiment, First pressure control magnetic valve 11 is the Stress control proportion magnetic valve of side valve type, and first pressure controls the outlet of magnetic valve 11 The pressure of B1 feeds back to one end that first pressure controls magnetic valve 11 by oil circuit (Fig. 1 show and feeds back to spring terminal).Therefore, Operationally, the valve element of first pressure control magnetic valve 11 is in electromagnetic force, spring force and hydraulic pressure for first pressure control magnetic valve 11 The output pressure of outlet B1 can be adjusted and be controlled under the collective effect of feedback force.That is, by control input to first Current value size in the electromagnet of electromagnetic pressure control valve 11, it is possible to achieve the outlet B1 of first pressure control magnetic valve 11 exists Different gearshift pressure are exported under different gearshift demands.

Second pressure control magnetic valve 12 have entrance A2 and outlet B2, second pressure control magnetic valve 12 entrance A2 with Working connection 10 is connected, and the outlet B2 of second pressure control magnetic valve 12 is connected with second flow control magnetic valve 22, makes the second pressure The pressure oil of the outlet B2 outputs of power control magnetic valve 12 can be opened via second flow control magnetic valve 22 into the second gear Close valve 42 to promote the second shift cylinder 52 to carry out gear shift operation, or fourth speed is entered via second flow control magnetic valve 22 Bit switch valve 44 carries out gear shift operation to promote the 4th shift cylinder 54.

When different gears carry out gear shift operation, required gearshift pressure would generally be different.To realize second pressure The gearshift pressure of the outlet B2 outputs of control magnetic valve 12 can meet the gearshift demand under different gears, in the present embodiment, Second pressure control magnetic valve 12 is the Stress control proportion magnetic valve of side valve type, and second pressure controls the outlet of magnetic valve 12 The pressure of B2 feeds back to one end that second pressure controls magnetic valve 12 by oil circuit (Fig. 1 show and feeds back to spring terminal).Therefore, Operationally, the valve element of second pressure control magnetic valve 12 is in electromagnetic force, spring force and hydraulic pressure for second pressure control magnetic valve 12 The output pressure of outlet B2 can be adjusted and be controlled under the collective effect of feedback force.That is, by control input to second Current value size in the electromagnet of electromagnetic pressure control valve 12, it is possible to achieve the outlet B2 of second pressure control magnetic valve 12 exists Different gearshift pressure are exported under different gearshift demands.

First flow control magnetic valve 21 has entrance A3 and two outlet B3, B4 (or referred to as first outlets B3 and second Outlet B4), the outlet B1 that the entrance A3 of first flow control magnetic valve 21 controls magnetic valve 11 with first pressure is connected, first-class Two outlets B3, B4 of amount control magnetic valve 21 are connected with the first driving switch valve 41 and third gear switch valve 43, make first The pressure oil exported in two outlets B3, B4 of flow control electromagnetic valve 21 can promote first via the first driving switch valve 41 Shift cylinder 51 carries out gear shift operation, or promotes the 3rd shift cylinder 53 to carry out gearshift behaviour via third gear switch valve 43 Make.Specifically, first flow control magnetic valve 21 can switch between the first working position and the second working position, when first flow control When magnetic valve processed 21 is in the first working position, the entrance A3 of first flow control magnetic valve 21 controls magnetic valve 21 with first flow Two outlet B3, B4 in one of connection；It is first-class when first flow control magnetic valve 21 is in the second working position What entrance A3 and the first flow of amount control magnetic valve 21 controlled that two of magnetic valve 21 are exported in B3, B4 another connects.This reality In applying example, when first flow control magnetic valve 21 is in the first working position (right position as shown in Figure 1), first flow control electricity First outlet B3 that the entrance A3 of magnet valve 21 controls magnetic valve 21 with first flow is connected；When first flow control magnetic valve 21 is cut When shifting to the second working position (left position as shown in Figure 1), the entrance A3 of first flow control magnetic valve 21 is controlled with first flow The second outlet B4 connection of magnetic valve 21.That is, controlling the working position of magnetic valve 21, Ke Yixuan by changing first flow Selecting property is directed to pressure oil on this two outlets one of B3, B4 from entrance A3.

At present, realize most of technical scheme of hydraulic gear-shifting control all based on Stress control, it is impossible to which precise control is changed Gear executing agency (i.e. shift cylinder) rate travel to realize shift process in precise control.In order to realize gearshift control On the basis of, make hydraulic gear-shifting system more accurate to process control of shifting gears, in the present embodiment, first flow control magnetic valve 21 is The flow control proportion magnetic valve of side valve type.Therefore, operationally, first flow controls electromagnetism to first flow control magnetic valve 21 The valve element of valve 21 can carry out a tentering under the collective effect of electromagnetic force and spring force to the output flow of two outlets B3, B4 The regulation and control of degree.That is, first flow controls magnetic valve 21 under each working position (left position or right position), by adjusting input The current value size in the electromagnet of magnetic valve 21 is controlled to first flow, thus it is possible to vary first flow controls magnetic valve 21 and working as Valve port opening under front working position, so as to the output flow in two outlets B3, B4 adjusting first flow control magnetic valve 21, And then realize controlling the rate travel of shift cylinder, to realize the precise control of shift process.

Second flow control magnetic valve 22 has entrance A4 and two outlet B5, B6 (or referred to as first outlets B5 and second Outlet B6), the outlet B2 that the entrance A4 of second flow control magnetic valve 22 controls magnetic valve 12 with second pressure is connected, second Two outlets B5, B6 of amount control magnetic valve 22 are connected with the second driving switch valve 42 and fourth speed bit switch valve 44, make second The pressure oil exported in two outlets B5, B6 of flow control electromagnetic valve 22 can promote second via the second driving switch valve 42 Shift cylinder 52 carries out gear shift operation, or promotes the 4th shift cylinder 54 to carry out gearshift behaviour via fourth speed bit switch valve 44 Make.Specifically, second flow control magnetic valve 22 can switch between the first working position and the second working position, when second flow control When magnetic valve processed 22 is in the first working position, the entrance A4 of second flow control magnetic valve 22 controls magnetic valve 22 with second flow Two outlet B5, B6 in one of connection；When second flow control magnetic valve 22 is in the second working position, second What entrance A4 and the second flow of amount control magnetic valve 22 controlled that two of magnetic valve 22 are exported in B5, B6 another connects.This reality In applying example, when second flow control magnetic valve 22 is in the first working position (right position as shown in Figure 1), second flow control electricity First outlet B5 that the entrance A4 of magnet valve 22 controls magnetic valve 22 with second flow is connected；When second flow control magnetic valve 22 is cut When shifting to the second working position (left position as shown in Figure 1), the entrance A4 of second flow control magnetic valve 22 is controlled with second flow The second outlet B6 connection of magnetic valve 22.That is, controlling the working position of magnetic valve 22, Ke Yixuan by changing second flow Selecting property is directed to pressure oil on this two outlets one of B5, B6 from entrance A4.

At present, realize most of technical scheme of hydraulic gear-shifting control all based on Stress control, it is impossible to which precise control is changed Gear executing agency (i.e. shift cylinder) rate travel to realize shift process in precise control.In order to realize gearshift control On the basis of, make hydraulic gear-shifting system more accurate to process control of shifting gears, in the present embodiment, second flow control magnetic valve 22 is The flow control proportion magnetic valve of side valve type.Therefore, operationally, second flow controls electromagnetism to second flow control magnetic valve 22 The valve element of valve 22 can carry out a tentering under the collective effect of electromagnetic force and spring force to the output flow of two outlets B5, B6 The regulation and control of degree.That is, second flow controls magnetic valve 22 under each working position (left position or right position), by adjusting input The current value size in the electromagnet of magnetic valve 22 is controlled to second flow, thus it is possible to vary second flow controls magnetic valve 22 and working as Valve port opening under front working position, so as to the output flow in two outlets B5, B6 adjusting second flow control magnetic valve 22, And then realize controlling the rate travel of shift cylinder, to realize the precise control of shift process.

First switch magnetic valve 31 has entrance A5 and outlet B7, and second switch magnetic valve 32 has entrance A6 and outlet B8.First driving switch valve 41 has two entrances A7, A8, two outlet B9, B10 and control end C1.Second gear is opened Close valve 42 and there is two entrances A9, A10, two outlet B11, B12 and control end C2.Third gear switch valve 43 has two Individual entrance A11, A12, two outlet B13, B14 and control end C3.Fourth speed bit switch valve 44 have two entrances A13, A14, two outlet B15, B16 and control end C4.

The entrance A5 of first switch magnetic valve 31 is connected with working connection 10, the outlet B7 of first switch magnetic valve 31 simultaneously with Control end C2 of control end C1 of the first driving switch valve 41 and the second driving switch valve 42 is connected.Second switch magnetic valve 32 Entrance A6 is connected with working connection 10, and the outlet B8 of second switch magnetic valve 32 is while control end C3 with third gear switch valve 43 It is connected with control end C4 of fourth speed bit switch valve 44.

Two entrances A7, A8 of the first driving switch valve 41 control respectively two outlets of magnetic valve 21 with first flow B3, B4 are connected.Two entrances A9, A10 of the second driving switch valve 42 go out respectively with two of second flow control magnetic valve 22 Mouth B5, B6 are connected.Two entrances A11, A12 of third gear switch valve 43 control respectively two of magnetic valve 21 with first flow Outlet B3, B4 are connected.Two entrances A13, A14 of fourth speed bit switch valve 44 control respectively the two of magnetic valve 22 with second flow Individual outlet B5, B6 are connected.

Two outlets B9, B10 of first driving switch valve 41 are connected respectively with two oil pockets of the first shift cylinder 51.The Two outlets B11, B12 of two driving switch valves 42 are connected respectively with two oil pockets of the second shift cylinder 52.Third gear is opened Two outlets B13, B14 for closing valve 43 are connected respectively with two oil pockets of the 3rd shift cylinder 53.Fourth speed bit switch valve 44 Two outlets B15, B16 are connected respectively with two oil pockets of the 4th shift cylinder 54.

First switch magnetic valve 31 can switch between cut-off working position and ON operation position, when first switch magnetic valve 31 In cut-off working position (right position as shown in Figure 1) when, the entrance A5 of first switch magnetic valve 31 and first switch magnetic valve 31 Outlet B7 disconnect；When first switch magnetic valve 31 is on working position (left position as shown in Figure 1), first switch electromagnetism The entrance A5 of valve 31 is connected with the outlet B7 of first switch magnetic valve 31, and now the pressure oil from working connection 10 is opened via first Powered-down magnet valve 31 is applied in control end C2 of control end C1 of the first driving switch valve 41 and the second driving switch valve 42, to push away Dynamic first driving switch valve 41 and the second driving switch valve 42 are commutated.

Second switch magnetic valve 32 can switch between cut-off working position and ON operation position, when second switch magnetic valve 32 In cut-off working position (right position as shown in Figure 1) when, the entrance A6 of second switch magnetic valve 32 and second switch magnetic valve 32 Outlet B8 disconnect；When second switch magnetic valve 32 is on working position (left position as shown in Figure 1), second switch electromagnetism The entrance A6 of valve 32 is connected with the outlet B8 of second switch magnetic valve 32, and now the pressure oil from working connection 10 is opened via second Powered-down magnet valve 32 is applied in control end C4 of control end C3 of third gear switch valve 43 and fourth speed bit switch valve 44, to push away Dynamic third gear switch valve 43 and fourth speed bit switch valve 44 are commutated.

In the present embodiment, the first driving switch valve 41 is the pilot operated directional control valve of side valve type.First driving switch valve 41 can be Switch between first working position and the second working position, when the first driving switch valve 41 is in the first working position (right side as shown in Figure 1 Position) when, two entrances A7, A8 of the first driving switch valve 41 are broken respectively with two outlets B9, B10 of the first driving switch valve 41 Open, now two outlets B9, B10 of the first driving switch valve 41 are communicated to fuel tank；Lead when first switch magnetic valve 31 is in Logical working position, the pressure oil from working connection 10 is applied to the control of the first driving switch valve 41 via first switch magnetic valve 31 When promoting the first driving switch valve 41 to switch to the second working position (left position as shown in Figure 1) on the C1 of end, the first driving switch valve 41 two entrances A7, A8 are connected respectively with two outlets B9, B10 of the first driving switch valve 41, now from first flow The pressure oil of control magnetic valve 21 just can be changed in the first shift cylinder 51 through the first driving switch valve 41 with promotion first Gear oil cylinder 51 carries out gear shift operation.

In the present embodiment, the second driving switch valve 42 is the pilot operated directional control valve of side valve type.Second driving switch valve 42 can be Switch between first working position and the second working position, when the second driving switch valve 42 is in the first working position (right side as shown in Figure 1 Position) when, two entrances A9, A10 of the second driving switch valve 42 export B11, B12 with two of the second driving switch valve 42 respectively Disconnect, now two outlets B11, B12 of the second driving switch valve 42 are communicated to fuel tank；When first switch magnetic valve 31 is in ON operation position, the pressure oil from working connection 10 is applied to the control of the second driving switch valve 42 via first switch magnetic valve 31 When promoting the second driving switch valve 42 to switch to the second working position (left position as shown in Figure 1) on end C2 processed, the second driving switch Two entrances A9, A10 of valve 42 are connected respectively with two outlets B11, B12 of the second driving switch valve 42, now from second The pressure oil of flow control electromagnetic valve 22 just can enter in the second shift cylinder 52 to promote the through the second driving switch valve 42 Two shift cylinders 52 carry out gear shift operation.

In the present embodiment, third gear switch valve 43 is the pilot operated directional control valve of side valve type.Third gear switch valve 43 can be Switch between first working position and the second working position, when third gear switch valve 43 is in the first working position (right side as shown in Figure 1 Position) when, two entrances A11, A12 of third gear switch valve 43 two outlet B13 respectively with third gear switch valve 43, B14 disconnects, and now the two of third gear switch valve 43 outlet B13, B14 are communicated to fuel tank；When second switch magnetic valve 32 Working position is on, the pressure oil from working connection 10 is applied to third gear switch valve 43 via second switch magnetic valve 32 Control end C3 on when promoting third gear switch valve 43 to switch to the second working position (left position as shown in Figure 1), third gear Two entrances A11, A12 of switch valve 43 are connected respectively with two of third gear switch valve 43 outlet B13, B14, now from The pressure oil of first flow control magnetic valve 21 just can through third gear switch valve 43 in the 3rd shift cylinder 53 pushing away Dynamic 3rd shift cylinder 53 carries out gear shift operation.

In the present embodiment, fourth speed bit switch valve 44 is the pilot operated directional control valve of side valve type.Fourth speed bit switch valve 44 can be Switch between first working position and the second working position, when fourth speed bit switch valve 44 is in the first working position (right side as shown in Figure 1 Position) when, two entrances A13, A14 of fourth speed bit switch valve 44 two outlet B15 respectively with fourth speed bit switch valve 44, B16 disconnects, and now the two of fourth speed bit switch valve 44 outlet B15, B16 are communicated to fuel tank；When second switch magnetic valve 32 Working position is on, the pressure oil from working connection 10 is applied to fourth speed bit switch valve 44 via second switch magnetic valve 32 Control end C4 on when promoting fourth speed bit switch valve 44 to switch to the second working position (left position as shown in Figure 1), fourth speed position Two entrances A13, A14 of switch valve 44 are connected respectively with two of fourth speed bit switch valve 44 outlet B15, B16, now from The pressure oil of second flow control magnetic valve 22 just can through fourth speed bit switch valve 44 in the 4th shift cylinder 54 pushing away Dynamic 4th shift cylinder 54 carries out gear shift operation.

As described above, the entrance that the outlet of first pressure control magnetic valve 11 controls magnetic valve 21 with first flow is connected, The entrance that the outlet of second pressure control magnetic valve 12 controls magnetic valve 22 with second flow is connected, first flow control magnetic valve 21 outlet is connected with the entrance of the first driving switch valve 41 and the entrance of third gear switch valve 43, second flow control electricity The outlet of magnet valve 22 is connected with the entrance of the second driving switch valve 42 and the entrance of fourth speed bit switch valve 44, and the first gear is opened The outlet for closing valve 41 is connected with the oil pocket of the first shift cylinder 51, the outlet of the second driving switch valve 42 and the second shift cylinder 52 Oil pocket connection, the outlet of third gear switch valve 43 is connected with the oil pocket of the 3rd shift cylinder 53, fourth speed bit switch valve 44 Outlet be connected with the oil pocket of the 4th shift cylinder 54, outlet and the control of the first driving switch valve 41 of first switch magnetic valve 31 The control end connection of end processed and the second driving switch valve 42, the first driving switch valve 41 and the second driving switch valve 42 are by first The control of switch electromagnetic valve 31 is commutated, the outlet of second switch magnetic valve 32 and the control end of third gear switch valve 43 and The control end connection of fourth speed bit switch valve 44, third gear switch valve 43 and fourth speed bit switch valve 44 are by second switch electromagnetism The control of valve 32 is commutated, and the entrance of first pressure control magnetic valve 11, the entrance of second pressure control magnetic valve 12, first is opened The entrance of powered-down magnet valve 31 and the entrance of second switch magnetic valve 32 are connected with working connection 10.

First pressure control magnetic valve 11 can adjust the inlet pressure that first flow controls magnetic valve 21, first flow control Magnetic valve processed 21 can be according to the pressure of inlet pressure precise control outlet and flow, and first flow control magnetic valve 21 also simultaneously The commutation control of oil circuit can be carried out to convert pressure oil port and drain tap.Second pressure control magnetic valve 12 can adjust second The inlet pressure of flow control electromagnetic valve 22, second flow control magnetic valve 22 can be according to the outlet of inlet pressure precise control Pressure and flow, second flow control magnetic valve 22 can also carry out the commutation control of oil circuit to convert pressure oil port and let out simultaneously Hydraulic fluid port.First switch magnetic valve 31 can control the opening and closing of the first driving switch valve 41 and the second driving switch valve 42, and second opens Powered-down magnet valve 32 can control the opening and closing of third gear switch valve 43 and fourth speed bit switch valve 44, make the He of the first shift cylinder 51 The pressure oil port and drain tap that 3rd shift cylinder 53 controls magnetic valve 21 with first flow is connected, and makes the He of the second shift cylinder 52 The pressure oil port and drain tap that 4th shift cylinder 54 controls magnetic valve 22 with second flow is connected.

Therefore, magnetic valve 11, first flow control magnetic valve 21 and first switch electromagnetism are controlled by controlling first pressure Valve 31, can cause the first shift cylinder 51 to move by certain speed between the first position and the second position.The present embodiment It is middle to assume that the first shift cylinder 51 is used to control reverse gear and 6 grades, when first pressure controls magnetic valve 11 and first switch magnetic valve 31 conducting and first flow control magnetic valve 21 be in the first working position (right position as shown in Figure 1) when, from working connection 10 Pressure oil controls magnetic valve 11 and first flow control magnetic valve 21 via first pressure to carry out being reached after pressure and Flow-rate adjustment First flow controls first outlet B3 of magnetic valve 21, because the first driving switch valve 41 is in the control of first switch magnetic valve 31 Under commutated to conduction position, therefore first flow control magnetic valve 21 first outlet B3 in pressure oil will be via first grade First entrance A7 of bit switch valve 41 reaches first outlet B9, then reaches the left chamber of the first shift cylinder 51, promotes first to change Gear oil cylinder 51 is moved to right and hangs up 6 grades；When first pressure control magnetic valve 11 and first switch magnetic valve 31 are turned on and first flow When control magnetic valve 21 is in the second working position (left position as shown in Figure 1), the pressure oil from working connection 10 is via the first pressure Power controls magnetic valve 11 and first flow control magnetic valve 21 to be carried out reaching first flow control electromagnetism after pressure and Flow-rate adjustment Second outlet B4 of valve 21, because the first driving switch valve 41 has commutated to conducting position under the control of first switch magnetic valve 31 Put, therefore the pressure oil in second outlet B4 of first flow control magnetic valve 21 is by via the second of the first driving switch valve 41 Entrance A8 reaches second outlet B10, then reaches the right chamber of the first shift cylinder 51, promotes the first shift cylinder 51 to move to left and hang Upper reverse gear.

Magnetic valve 12, second flow control magnetic valve 22 and first switch magnetic valve 31 are controlled by controlling second pressure, The second shift cylinder 52 can be caused to move by certain speed between the first position and the second position.Assume in the present embodiment Second shift cylinder 52 is used to control 7 grades and 3 grades, turn on when second pressure control magnetic valve 12 and first switch magnetic valve 31 and When second flow control magnetic valve 22 is in the first working position (right position as shown in Figure 1), from the pressure oil Jing of working connection 10 Controlling magnetic valve 12 and second flow control magnetic valve 22 by second pressure carries out reaching second flow after pressure and Flow-rate adjustment First outlet B5 of control magnetic valve 22, because the second driving switch valve 42 commutates under the control of first switch magnetic valve 31 To conduction position, therefore the pressure oil in first outlet B5 of second flow control magnetic valve 22 will be via the second driving switch valve 42 first entrance A9 reaches first outlet B11, then reaches the left chamber of the second shift cylinder 52, promotes the second shift cylinder 52 Move to right and hang up 3 grades；When second pressure control magnetic valve 12 and first switch magnetic valve 31 are turned on and second flow control electromagnetism When valve 22 is in the second working position (left position as shown in Figure 1), the pressure oil from working connection 10 is via second pressure control electricity Magnet valve 12 and second flow control magnetic valve 22 carry out reaching the of second flow control magnetic valve 22 after pressure and Flow-rate adjustment Two outlet B6, because the second driving switch valve 42 commutates to conduction position under the control of first switch magnetic valve 31, therefore Pressure oil in second outlet B6 of second flow control magnetic valve 22 is by via second entrance A10 of the second driving switch valve 42 Second outlet B12 is reached, the right chamber of the second shift cylinder 52 is then reached, is promoted the second shift cylinder 52 to move to left and is hung up 7 grades.

Magnetic valve 11, first flow control magnetic valve 21 and second switch magnetic valve 32 are controlled by controlling first pressure, The 3rd shift cylinder 53 can be caused to move by certain speed between the first position and the second position.Assume in the present embodiment 3rd shift cylinder 53 is used to control 5 grades and 1 grade, turn on when first pressure control magnetic valve 11 and second switch magnetic valve 32 and When first flow control magnetic valve 21 is in the first working position (right position as shown in Figure 1), from the pressure oil Jing of working connection 10 Controlling magnetic valve 11 and first flow control magnetic valve 21 by first pressure carries out reaching first flow after pressure and Flow-rate adjustment First outlet B3 of control magnetic valve 21, because third gear switch valve 43 commutates under the control of second switch magnetic valve 32 To conduction position, therefore the pressure oil in first outlet B3 of first flow control magnetic valve 21 will be via third gear switch valve 43 first entrance A11 reaches first outlet B13, then reaches the left chamber of the 3rd shift cylinder 53, promotes the 3rd shift cylinder 53 move to right and hang up 1 grade；When first pressure control magnetic valve 11 and second switch magnetic valve 32 are turned on and first flow control electricity When magnet valve 21 is in the second working position (left position as shown in Figure 1), the pressure oil from working connection 10 is via first pressure control Magnetic valve 11 and first flow control magnetic valve 21 carry out reaching first flow control magnetic valve 21 after pressure and Flow-rate adjustment Second outlet B4, because third gear switch valve 43 has commutated to conduction position under the control of second switch magnetic valve 32, because Pressure oil in second outlet B4 of this first flow control magnetic valve 21 is by via the second entrance of third gear switch valve 43 A12 reaches second outlet B14, then reaches the right chamber of the 3rd shift cylinder 53, promotes the 3rd shift cylinder 53 to move to left and hang up 5 Shelves.

Magnetic valve 12, second flow control magnetic valve 22 and second switch magnetic valve 32 are controlled by controlling second pressure, The 4th shift cylinder 54 can be caused to move by certain speed between the first position and the second position.Assume in the present embodiment 4th shift cylinder 54 is used to control 4 grades and 2 grades, turn on when second pressure control magnetic valve 12 and second switch magnetic valve 32 and When second flow control magnetic valve 22 is in the first working position (right position as shown in Figure 1), from the pressure oil Jing of working connection 10 Controlling magnetic valve 12 and second flow control magnetic valve 22 by second pressure carries out reaching second flow after pressure and Flow-rate adjustment First outlet B5 of control magnetic valve 22, because fourth speed bit switch valve 44 commutates under the control of second switch magnetic valve 32 To conduction position, therefore the pressure oil in first outlet B5 of second flow control magnetic valve 22 will be via fourth speed bit switch valve 44 first entrance A13 reaches first outlet B15, then reaches the left chamber of the 4th shift cylinder 54, promotes the 4th shift cylinder 54 move to right and hang up 2 grades；When second pressure control magnetic valve 12 and second switch magnetic valve 32 are turned on and second flow control electricity When magnet valve 22 is in the second working position (left position as shown in Figure 1), the pressure oil from working connection 10 is via second pressure control Magnetic valve 12 and second flow control magnetic valve 22 carry out reaching second flow control magnetic valve 22 after pressure and Flow-rate adjustment Second outlet B6, because fourth speed bit switch valve 44 has commutated to conduction position under the control of second switch magnetic valve 32, because Pressure oil in second outlet B6 of this second flow control magnetic valve 22 is by via the second entrance of fourth speed bit switch valve 44 A14 reaches second outlet B16, then reaches the right chamber of the 4th shift cylinder 54, promotes the 4th shift cylinder 54 to move to left and hang up 4 Shelves.

So as in the utility model embodiment, adopt as few as possible magnetic valve and spool valve combinations, eight gears are realized Automatic transmission shift control, and by two electromagnetic pressure control valves 11,12 and two flow control electromagnetic valves 21, 22, on the basis of shift of transmission control is realized, the two ore control of gearshift pressure and flow is realized, make hydraulic gear-shifting system To shifting gears, process control is more accurate, and the precise control of shift process can be better achieved.

In addition, the work characteristics based on double-clutch automatic gearbox, synchronization there may be while being linked into odd number gear Position and even number gear situation (when being such as currently at a certain odd number gear, can the next even number gear of pre-hung；Or be currently at a certain During even number gear, can the next odd number gear of pre-hung), but synchronization is not allowed while being linked into multiple odd number gears or while hanging Enter multiple even number gears.In the present embodiment, reverse gear and 6 grades are by first pressure control magnetic valve 11, first flow control magnetic valve 21 and 31 3 solenoid valve controls of first switch magnetic valve, 4 grades and 2 grades by second pressure control magnetic valve 12, second flow control 32 3 solenoid valve controls of magnetic valve processed 22 and second switch magnetic valve, it can be seen that, control reverse gear and the three of 6 grades magnetic valves It is different with 4 grades and 2 grades of three magnetic valves of control, therefore while the possibility for being linked into multiple even number gears drops significantly It is low；In addition, 7 grades and 3 grades by second pressure control magnetic valve 12, second flow control magnetic valve 22 and first switch magnetic valve 31 Three solenoid valve controls, 5 grades and 1 grade by first pressure control magnetic valve 11, first flow control magnetic valve 21 and second switch 32 3 solenoid valve controls of magnetic valve, it can be seen that, control 7 grades and 3 grades of three magnetic valves and three of 5 grades and 1 grade of control Magnetic valve is different, therefore while the possibility for being linked into multiple odd number gears is greatly reduced.Therefore, the present embodiment is also carried The high security in terms of preventing from hanging shelves by mistake.

The hydraulic gear-shifting system of the present embodiment also includes main pump 61, auxiliary pump 62 and fuel tank 63.Main pump 61 and auxiliary pump 62 via Oil absorption filter 64 from oil suction in fuel tank 63, so as to provide the pressure needed for work in the working connection 10 to the hydraulic gear-shifting system Oil.In the present embodiment, main pump 61 is moved by the engine direct tape splicing of automobile, and auxiliary pump 62 is driven by motor, and the one side of auxiliary pump 62 can be with The assistance main pump 61 in the case of the output oil amount deficiency of main pump 61, on the other hand can be in engine stop and therefore main pump 61 stops The supply of pressure oil in system is guaranteed in the case of only.Fuel tank symbol is used at multiple positions of Fig. 1, these fuel tank symbols should It is interpreted as by related pipeline connection to fuel tank 63.

In order to the outlet for preventing fluid reverse flow, main pump 61 and auxiliary pump 62 is connected with check valve 65.For control system In maximum pressure, the outlet of main pump 61 is also associated with system safety valve 66, system safety valve 66 can for safety overflow valve or Check valve, in the present embodiment, system safety valve 66 is check valve, is connected between the outlet of main pump 61 and fuel tank 63, by list The maximum pressure allowed in valve initialization system, when the pressure in system exceedes the maximum pressure, check valve is opened and let out Oil.

The hydraulic gear-shifting system of the present embodiment also include first clutch magnetic valve 71, second clutch magnetic valve 72 and from Clutch safety valve 73.

First clutch magnetic valve 71 is used to control the engagement or separation of first clutch T1.First clutch magnetic valve 71 With entrance A15 and outlet B17, the entrance A15 of first clutch magnetic valve 71 is connected with working connection 10, first clutch electromagnetism The outlet B17 of valve 71 is connected with clutch safety valve 73.First clutch magnetic valve 71 can be in cut-off working position and ON operation Switch between position, when first clutch magnetic valve 71 is in cut-off working position (right position as shown in Figure 1), first clutch electricity The entrance A15 of magnet valve 71 disconnects with the outlet B17 of first clutch magnetic valve 71, and the outlet of first clutch magnetic valve 71 B17 is communicated to fuel tank 63, and now first clutch T1 is separated；When first clutch magnetic valve 71 is on working position (such as Fig. 1 Shown left position) when, the entrance A15 of first clutch magnetic valve 71 is connected with the outlet B17 of first clutch magnetic valve 71, this When pressure oil on working connection 10 drive first clutch via first clutch magnetic valve 71 and clutch safety valve 73 T1 is engaged.

Second clutch magnetic valve 72 is used to control the engagement or separation of second clutch T2.Second clutch magnetic valve 72 With entrance A16 and outlet B18, the entrance A16 of second clutch magnetic valve 72 is connected with working connection 10, second clutch electromagnetism The outlet B18 of valve 72 is connected with clutch safety valve 73.Second clutch magnetic valve 72 can be in cut-off working position and ON operation Switch between position, when second clutch magnetic valve 72 is in cut-off working position (right position as shown in Figure 1), second clutch electricity The entrance A16 of magnet valve 72 disconnects with the outlet B18 of second clutch magnetic valve 72, and the outlet of second clutch magnetic valve 72 B18 is communicated to fuel tank 63, and now second clutch T2 is separated；When second clutch magnetic valve 72 is on working position (such as Fig. 1 Shown left position) when, the entrance A16 of second clutch magnetic valve 72 is connected with the outlet B18 of second clutch magnetic valve 72, this When pressure oil on working connection 10 drive second clutch via second clutch magnetic valve 72 and clutch safety valve 73 T2 is engaged.

Clutch safety valve 73 when clutch T1, T2 break down, for disconnect towards clutch T1, T2 oil circuit. Clutch safety valve 73 has two entrances A17, A18, two outlet B19, B20 and control end C5, clutch safety valve 73 two entrances A17, A18 respectively with the outlet B17 of first clutch magnetic valve 71 and going out for second clutch magnetic valve 72 Mouthful B18 is connected, two outlets B19, B20 of clutch safety valve 73 respectively with first clutch T1 and second clutch T2 phases Even, the outlet B7 of the first switch magnetic valve 31 and outlet B8 of second switch magnetic valve 32 is connected to clutch safety valve 73 simultaneously Control end C5.Clutch safety valve 73 can switch between open and closed positions, when clutch safety valve 73 is in During open position (left position as shown in Figure 1), two entrances A17, A18 of clutch safety valve 73 respectively with clutch safety valve 73 two outlet B19, B20 connections, now can realize first by controlling the switch operation of first clutch magnetic valve 71 The engagement or separation of clutch T1, by controlling the switch operation of second clutch magnetic valve 72 second clutch T2 can be realized Engagement or separation；When clutch T1, T2 break down, while opening first switch magnetic valve 31 and second switch magnetic valve 32, first switch magnetic valve 31 and the pressure oil of the output of second switch magnetic valve 32 are made while being applied to clutch safety valve 73 In control end C5, promote clutch safety valve 73 to switch to closed position (right position as shown in Figure 1) from open position, now from Two entrances A17, A18 of clutch safety valve 73 disconnect respectively with two outlets B19, B20 of clutch safety valve 73, so as to cut The open close oil circuit toward clutch T1, T2, now first clutch T1 and second clutch T2 is by the off-load of clutch safety valve 73.

The hydraulic gear-shifting system of the present embodiment also includes the 3rd switch electromagnetic valve 33, park control valve 81 and parking oil cylinder 82.3rd switch electromagnetic valve 33 has entrance A19 and outlet B21.The entrance A19 of the 3rd switch electromagnetic valve 33 and the phase of working connection 10 Even, the outlet B21 of the 3rd switch electromagnetic valve 33 is connected with control end C6 of park control valve 81.3rd switch electromagnetic valve 33 can be Switch between cut-off working position and ON operation position, when the 3rd switch electromagnetic valve 33 is in the cut-off working position (right side as shown in Figure 1 Position) when, the entrance A19 of the 3rd switch electromagnetic valve 33 and outlet B21 of the 3rd switch electromagnetic valve 33 disconnects；When the 3rd switch electromagnetism When valve 33 is on working position (left position as shown in Figure 1), the switch electromagnetism of the entrance A19 of the 3rd switch electromagnetic valve 33 and the 3rd The outlet B21 connections of valve 33, now the pressure oil from working connection 10 is applied to parking control via the 3rd switch electromagnetic valve 33 In control end C6 of valve 81, to promote park control valve 81 to be commutated.

In the present embodiment, park control valve 81 is the pilot operated directional control valve of side valve type.Park control valve 81 have entrance A20, Two outlet B22, B23 and control end C6, the entrance A20 of park control valve 81 is connected with working connection 10, park control valve 81 Two outlets B22, B23 are connected respectively with two oil pockets of parking oil cylinder 82, and control end C6 of park control valve 81 is opened with the 3rd The outlet B21 of powered-down magnet valve 33 is connected.Park control valve 81 can switch between the first working position and the second working position, work as parking When control valve 81 is in the first working position (right position as shown in Figure 1), entrance A20 and the park control valve 81 of park control valve 81 First outlet B22 connection, second outlet B23 of park control valve 81 is connected with fuel tank 63, now from the pressure of working connection 10 Power oil enters in one of oil pocket of parking oil cylinder 82 to promote parking oil cylinder 82 to a side shifting through park control valve 81； When the 3rd switch electromagnetic valve 33 is on working position, the pressure oil from working connection 10 applies through the 3rd switch electromagnetic valve 33 Park control valve 81 is promoted to switch to the second working position (left position as shown in Figure 1) in control end C6 of park control valve 81 When, the entrance A20 of park control valve 81 is connected with second outlet B23 of park control valve 81, and the first of park control valve 81 goes out Mouth B22 is connected with fuel tank 63, and now the pressure oil from working connection 10 enters the another of parking oil cylinder 82 through park control valve 81 With promotion parking oil cylinder 82 to another side shifting in one oil pocket.So as to by the 3rd switch electromagnetic valve 33, park control valve 81 With the automatic parking and unlocking function that parking oil cylinder 82 realizes vehicle.

The hydraulic gear-shifting system of the present embodiment also includes the 3rd electromagnetic pressure control valve 13 and working connection pressure-regulating valve 18.

3rd electromagnetic pressure control valve 13 has entrance A21 and outlet B24.Working connection pressure-regulating valve 18 has entrance A22, two outlets B25, B26 (or referred to as first outlet B25 and second outlet B26) and two control ends C7, C8 (or referred to as the One control end C7 and the second control end C8).The entrance A21 of the 3rd electromagnetic pressure control valve 13 is connected with working connection 10, the 3rd pressure The outlet B24 of power control magnetic valve 13 is connected with the first control end C7 of working connection pressure-regulating valve 18, and working connection pressure is adjusted The entrance A22 and the second control end C8 of valve 18 is connected with working connection 10 simultaneously, first outlet B25 of working connection pressure-regulating valve 18 It is connected with fuel tank 63, second outlet B26 of working connection pressure-regulating valve 18 leads to lubricating and cooling system 90, lubricating and cooling system 90 For being lubricated and cooling down to the related elements of the automatic transmission such as (not shown) such as bearing, gear, clutch.

In the present embodiment, the 3rd electromagnetic pressure control valve 13 for side valve type Stress control proportion magnetic valve, and the 3rd pressure The pressure of the outlet B24 of power control magnetic valve 13 feeds back to one end of the 3rd electromagnetic pressure control valve 13 (shown in Fig. 1 by oil circuit To feed back to electromagnet end).Therefore, the 3rd electromagnetic pressure control valve 13 operationally, the valve of the 3rd electromagnetic pressure control valve 13 Core can be adjusted and control under the collective effect of electromagnetic force, spring force and hydraulic feedback power to the output pressure of outlet B24 System, and then change the active force being applied in the first control end C7 of working connection pressure-regulating valve 18, adjust working connection pressure Valve 18 progressively switches from closed position to open position, so as to realize the regulation to oil liquid pressure in working connection 10, while making master Unnecessary fluid can transfer to lubricating and cooling system 90 via working connection pressure-regulating valve 18 in oil circuit 10, cold to fluid to meet But the needs and to related elements being lubricated.

In the present embodiment, working connection pressure-regulating valve 18 has three working positions.When the 3rd electromagnetic pressure control valve 13 When the output pressure of outlet B24 is larger, act on active force in the first control end C7 of working connection pressure-regulating valve 18 also compared with Greatly, now working connection pressure-regulating valve 18 is in the first working position (right position as shown in Figure 1), working connection pressure-regulating valve 18 Entrance A22 disconnects with two outlets B25, B26 of working connection pressure-regulating valve 18；With the 3rd electromagnetic pressure control valve 13 The output pressure of outlet B24 reduces, and the active force acted in the first control end C7 of working connection pressure-regulating valve 18 also reduces, Now act on the power in the second control end C8 of working connection pressure-regulating valve 18 to will be greater than acting in the first control end C7 Power, promotes working connection pressure-regulating valve 18 to commutate to the second working position (middle position as shown in Figure 1), now working connection pressure regulation The entrance A22 of valve 18 is connected with second outlet B26 of working connection pressure-regulating valve 18, and fluid can be adjusted via working connection pressure Valve 18 leads to lubricating and cooling system 90；It is main as the output pressure of the outlet B24 of the 3rd electromagnetic pressure control valve 13 continues to reduce Oil circuit pressure regulating valve 18 will commutate to the 3rd working position (left position as shown in Figure 1), now working connection pressure-regulating valve 18 Entrance A22 is connected with two outlets B25, B26 of working connection pressure-regulating valve 18, and a part of fluid can be via working connection pressure Force regulating valve 18 leads to lubricating and cooling system 90, and another part fluid can return fuel tank via working connection pressure-regulating valve 18 63。

Lubricating and cooling system 90 includes cooling flow flow-limiting valve 91, oil cooler 92, filter 93, check valve 94, rill Adjustable valve 95 and large flux control valve 96.The entrance of cooling flow flow-limiting valve 91 and the second of working connection pressure-regulating valve 18 Outlet B26 is connected, and the entrance for making cooling flow flow-limiting valve 91 is connected by working connection pressure-regulating valve 18 with the outlet of main pump 61, Cooling flow flow-limiting valve 91 is used to automatically adjust towards the fluid flow in lubricating and cooling system 90.Control valve for small flows 95 and big Flow control valve 96 is connected with the outlet of cooling flow flow-limiting valve 91.Oil cooler 92 and filter 93 are connected to cooling flow Between flow-limiting valve 91 and two flow control valves 95,96, to be cooled down to fluid and be filtered.Check valve 94 is connected in parallel on oil cooling but On device 92 and filter 93, the setting of the Opening pressure of check valve 94 it is larger, under normal circumstances fluid is from oil cooler 92 and mistake Filter 93 flows through, and only in the case where oil cooler 92 and filter 93 have larger resistance (as blocked), fluid is just from list Flow through to the bypass of valve 94.Fluid is distributed to after cooling and filtration via control valve for small flows 95 and large flux control valve 96 The related elements (such as bearing, gear, clutch) of automatic transmission are lubricated and cool down.

The hydraulic gear-shifting system of the present embodiment also includes the 4th electromagnetic pressure control valve 14.4th electromagnetic pressure control valve 14 With entrance A23 and outlet B27.The entrance A23 of the 4th electromagnetic pressure control valve 14 is connected with working connection 10, the 4th Stress control The outlet B27 of magnetic valve 14 control ends C9 and the control end C10 phase of large flux control valve 96 simultaneously with control valve for small flows 95 Even.

In the present embodiment, the 4th electromagnetic pressure control valve 14 for side valve type Stress control proportion magnetic valve, and the 4th pressure The pressure of the outlet B27 of power control magnetic valve 14 feeds back to one end of the 4th electromagnetic pressure control valve 14 (shown in Fig. 1 by oil circuit To feed back to electromagnet end).Therefore, the 4th electromagnetic pressure control valve 14 operationally, the valve of the 4th electromagnetic pressure control valve 14 Core can be adjusted and control under the collective effect of electromagnetic force, spring force and hydraulic feedback power to the output pressure of outlet B27 System, and then change the effect being applied in control end C10 of control end C9 of control valve for small flows 95 and large flux control valve 96 Power, so as to promote control valve for small flows 95 and large flux control valve 96 to be commutated.In the present embodiment, low discharge is promoted to adjust Valve 95 commutated needed for active force less than the active force needed for promoting large flux control valve 96 to be commutated, therefore only needing When wanting the lubrication and cooling requirement of low discharge, smaller current, the 4th pressure control are passed through to the electromagnet of electromagnetic pressure control valve 14 The outlet B27 of magnetic valve processed 14 exports less pressure, adjusts control end C9 for being applied to control valve for small flows 95 and big flow Active force in control end C10 of valve 96 only promotes opening control valve for small flows 95 (now large flux control valve 96 is not opened), Meet the lubrication under low discharge demand and cooling；When the lubrication and cooling requirement of big flow is needed, to electromagnetic pressure control valve 14 electromagnet is passed through larger current, increases the output pressure of the outlet B27 of the 4th electromagnetic pressure control valve 14, makes to be applied to little Active force in control end C9 of flow control valve 95 and control end C10 of large flux control valve 96 is promoted and opens low discharge simultaneously Regulating valve 95 and large flux control valve 96, meet the lubrication under big flow demand and cooling.I.e. in the present embodiment, low discharge is controlled The guide proportion magnetic valve of regulating valve 95 and large flux control valve 96 is same (i.e. the 4th electromagnetic pressure control valve 14), is passed through Control is applied to two sections of electric currents of the electromagnet of electromagnetic pressure control valve 14, can respectively realize the lubrication of low discharge and big flow Cooling requirement.

Specifically, the entrance of control valve for small flows 95 is connected by pipeline with main pump 61, and control valve for small flows 95 is main pump 61 flow Directed cooling lubricating element.Control valve for small flows 95 has the first working position and the second working position, and low discharge is adjusted Control end C9 of valve 95 is connected with the outlet B27 of the 4th electromagnetic pressure control valve 14, in the control of the 4th electromagnetic pressure control valve 14 Under system, control valve for small flows 95 can be made to commutate between the first working position and the second working position, to control the stream of cooling and lubricating Amount continuous variable.When control valve for small flows 95 is in its first working position (bottom in such as Fig. 1), without flow rill is passed through The Directed cooling lubricating element of adjustable valve 95, now the flow of main pump 61 be cut off in control valve for small flows 95；When low discharge is adjusted When section valve 95 is in its second working position (as upper in Fig. 1), control valve for small flows 95 can be oriented to the flow of main pump 61 Cooling and lubricating element, now the flow of main pump 61 be turned on to cooling and lubricating element in control valve for small flows 95.

The two entrances of large flux control valve 96 are connected respectively with main pump 61 and auxiliary pump 62, and large flux control valve 96 is main pump 61 and the flow Directed cooling lubricating element of auxiliary pump 62.Because auxiliary pump 62 is driven by motor, therefore the output flow of auxiliary pump 62 It is continuous controllable.Large flux control valve 96 has the first working position, the second working position and the 3rd working position, large flux control valve 96 Control end C10 is connected with the outlet B27 of the 4th electromagnetic pressure control valve 14, under the control of the 4th electromagnetic pressure control valve 14, Large flux control valve 96 can be made to commutate between the first working position, the second working position and the 3rd working position, to control cooling profit Sliding flow continuous variable.When large flux control valve 96 is in its first working position (bottom in such as Fig. 1), lead to without flow The Directed cooling lubricating element of large flux control valve 96 is crossed, now the flow of main pump 61 is in the return oil switched on of large flux control valve 96 Case 63, the flow of auxiliary pump 62 is cut off in large flux control valve 96；When large flux control valve 96 is in its second working position (as schemed Middle position in 1) when, large flux control valve 96 can be the flow Directed cooling lubricating element of main pump 61, the now stream of main pump 61 Amount is simultaneously turned on to cooling and lubricating element in large flux control valve 96 and is returned fuel tank 63, and the flow of auxiliary pump 62 is adjusted in big flow Section valve 96 is cut off；When large flux control valve 96 is in its 3rd working position (upper in such as Fig. 1), large flux control valve 96 Can be the flow of main pump 61 and auxiliary pump 62 simultaneously Directed cooling lubricating element, now the flow of main pump 61 and auxiliary pump 62 is flowing greatly Adjustable valve 96 is simultaneously turned on to cooling and lubricating element, so as to increase cooling and lubricating flow, while the output flow of auxiliary pump 62 Continuously adjustabe, so as to realize the two-step evolution of cooling and lubricating flow, makes the supply of flow more accurate, reduces the energy of speed changer Consumption so that the performance of system more optimizes.

[second embodiment]

Fig. 2 be the utility model second embodiment in automatic transmission hydraulic gear-shifting system schematic diagram, the present embodiment It is that in the present embodiment, first switch magnetic valve 31 and second switch magnetic valve 32 are whole with the difference of above-mentioned first embodiment The switch electromagnetic valve 34 of a 3-position 4-way is combined into, the entrance A5 and second switch magnetic valve 32 of first switch magnetic valve 31 is made Entrance A6 is integrated into an entrance A24 of the switch electromagnetic valve 34 of the 3-position 4-way and is connected with working connection 10, first switch electricity The outlet B7 of the magnet valve 31 and outlet B8 of second switch magnetic valve 32 is respectively two of the switch electromagnetic valve 34 of the 3-position 4-way Outlet.

The switch electromagnetic valve 34 of the 3-position 4-way can switch in cut-off position, between the first working position and the second working position, this In embodiment, when switch electromagnetic valve 34 be located at cut-off position (middle position as shown in Figure 2) when, the entrance A24 of switch electromagnetic valve 34 with First outlet B7 of switch electromagnetic valve 34 disconnects with second outlet B8 and not connecting, now first outlet B7 of switch electromagnetic valve 34 Fuel tank is communicated to second outlet B8；When switch electromagnetic valve 34 switches to the first working position (right position as shown in Figure 2), switch The entrance A24 of magnetic valve 34 is connected with first outlet B7 of switch electromagnetic valve 34, now second outlet B8 of switch electromagnetic valve 34 It is communicated to fuel tank；When switch electromagnetic valve 34 switches to the second working position (left position as shown in Figure 2), switch electromagnetic valve 34 enters Mouth A24 is connected with second outlet B8 of switch electromagnetic valve 34, and first outlet B7 of switch electromagnetic valve 34 is communicated to fuel tank.Namely Say, by the working position for changing switch electromagnetic valve 34, selectively pressure oil can be directed to into this two outlets from entrance A24 On one of B7, B8, therefore the first switch magnetic valve 31 and second switch magnetic valve 32 in above-mentioned first embodiment can be integrated For a switch electromagnetic valve, the quantity and reduces cost of guiding valve are further simplified.

In addition, the present embodiment is also resided in the difference of above-mentioned first embodiment, and in the above-described first embodiment, first switch The outlet B7 of the magnetic valve 31 and outlet B8 of second switch magnetic valve 32 is connected to control end C5 of clutch safety valve 73 simultaneously. And in the present embodiment, the outlet B1 of first pressure control magnetic valve 11 and the outlet B2 of second pressure control magnetic valve 12 are simultaneously Control end C5 of clutch safety valve 73 is connected to, therefore when clutch T1, T2 break down, while opening first pressure control Magnetic valve processed 11 and second pressure control magnetic valve 12, make first pressure control magnetic valve 11 and second pressure control magnetic valve 12 The pressure oil of output is applied in control end C5 of clutch safety valve 73 simultaneously, to promote clutch safety valve 73 to carry out jointly Commutation.

The other structures and operation principle of the present embodiment can join above-mentioned first embodiment, will not be described here.

The above, is only preferred embodiment of the present utility model, not makees any formal to the utility model Restriction, although the utility model is disclosed above with preferred embodiment, but is not limited to the utility model, any ripe Professional and technical personnel is known, in the range of without departing from technical solutions of the utility model, when in the technology using the disclosure above Appearance is made a little change or is modified to the Equivalent embodiments of equivalent variations, as long as being without departing from technical solutions of the utility model Hold, above example is made any simple modification, equivalent variations and modification according to technical spirit of the present utility model, still Belong in the range of technical solutions of the utility model.

Claims (10)

1. a kind of cooling and lubricating system of automatic transmission, it is characterised in that adjust including main pump (61), auxiliary pump (62), low discharge Section valve (95) and large flux control valve (96), the entrance of the control valve for small flows (95) is connected with the main pump (61), the big flow One of entrance of regulating valve (96) is connected with the main pump (61), and another entrance is connected with the auxiliary pump (62)；The low discharge Regulating valve (95), when the control valve for small flows (95) is in the first working position, does not have with the first working position and the second working position There is flow by control valve for small flows (95) the Directed cooling lubricating element, when the control valve for small flows (95) is in the second work During position, flow Directed cooling lubricating element of the control valve for small flows (95) the main pump (61)；The large flux control valve (96) With the first working position, the second working position and the 3rd working position, when the large flux control valve (96) is in the first working position, do not have There is flow by large flux control valve (96) the Directed cooling lubricating element, when the large flux control valve (96) is in the second work During position, the large flux control valve (96) the flow Directed cooling lubricating element of the main pump (61), when the large flux control valve (96) when being in three working positions, the large flux control valve (96) is simultaneously oriented to the flow of the main pump (61) and the auxiliary pump (62) Cooling and lubricating element.

2. cooling and lubricating system as claimed in claim 1, it is characterised in that the control valve for small flows (95) is with control end (C9), the large flux control valve (96) is with control end (C10), the control end (C9) and the big stream of the control valve for small flows (95) The control end (C10) of adjustable valve (96) while be connected with the outlet (B27) of same electromagnetic pressure control valve (14), by the pressure Power control magnetic valve (14) changes the control end (C9) and the large flux control valve (96) for being applied to the control valve for small flows (95) Control end (C10) on active force, promote the control valve for small flows (95) between its first working position and the second working position Commutation, and promote the large flux control valve (96) to commutate in its first working position, between the second working position and the 3rd working position.

3. cooling and lubricating system as claimed in claim 2, it is characterised in that promote the control valve for small flows (95) to be commutated Required active force is less than the active force needed for promoting the large flux control valve (96) to be commutated, the electromagnetic pressure control valve (14) when electromagnet is passed through smaller current, the control end (C9) and the big flow for being applied to the control valve for small flows (95) is adjusted Active force in the control end (C10) of valve (96) only promotes the control valve for small flows (95) to be commutated, the electromagnetic pressure control When the electromagnet of valve (14) is passed through larger current, the control end (C9) and the big flow for being applied to the control valve for small flows (95) is adjusted Active force in the control end (C10) of section valve (96) promotes the control valve for small flows (95) and the large flux control valve (96) simultaneously Commutated.

4. cooling and lubricating system as claimed in claim 1, it is characterised in that the main pump (61) by driven by engine, the auxiliary pump (62) driven by motor, the output flow continuously adjustabe of the auxiliary pump (62).

5. the hydraulic gear-shifting system of a kind of automatic transmission, it is characterised in that include as described in any one of Claims 1-4 Cooling and lubricating system.

6. hydraulic gear-shifting system as claimed in claim 5, it is characterised in that the hydraulic gear-shifting system also includes first pressure control Magnetic valve (11) processed, second pressure control magnetic valve (12), first flow control magnetic valve (21), second flow control magnetic valve (22), first switch magnetic valve (31), second switch magnetic valve (32), the first driving switch valve (41), the second driving switch valve (42), third gear switch valve (43), fourth speed bit switch valve (44), the first shift cylinder (51), the second shift cylinder (52), The outlet of the 3rd shift cylinder (53) and the 4th shift cylinder (54), the wherein first pressure control magnetic valve (11) with this The entrance connection of one flow control electromagnetic valve (21), the outlet of second pressure control magnetic valve (12) and the second flow control The entrance connection of magnetic valve (22), the outlet of first flow control magnetic valve (21) and entering for the first driving switch valve (41) The entrance connection of mouth and the third gear switch valve (43), outlet and second gear of second flow control magnetic valve (22) The entrance of switch valve (42) and fourth speed bit switch valve (44) entrance connection, the outlet of first driving switch valve (41) with The oil pocket connection of first shift cylinder (51), the outlet of second driving switch valve (42) and second shift cylinder (52) Oil pocket connects, and the outlet of the third gear switch valve (43) is connected with the oil pocket of the 3rd shift cylinder (53), the fourth speed position The outlet of switch valve (44) is connected with the oil pocket of the 4th shift cylinder (54), the outlet of the first switch magnetic valve (31) with should The control end of the first driving switch valve (41) and the control end connection of second driving switch valve (42), the first driving switch valve (41) commutated by first switch magnetic valve (31) control with second driving switch valve (42), the second switch magnetic valve (32) outlet is connected with the control end of the third gear switch valve (43) and the control end of fourth speed bit switch valve (44), should Third gear switch valve (43) and fourth speed bit switch valve (44) are commutated by second switch magnetic valve (32) control, should Entrance, first switch magnetic valve of the entrance of first pressure control magnetic valve (11), second pressure control magnetic valve (12) (31) entrance and the entrance of the second switch magnetic valve (32) is connected with working connection (10).

7. hydraulic gear-shifting system as claimed in claim 6, it is characterised in that first pressure control magnetic valve (11) have into Mouth (A1) and outlet (B1), second pressure control magnetic valve (12) is with entrance (A2) and outlet (B2), the first flow control , with entrance (A3) and two outlets (B3, B4), second flow control magnetic valve (22) is with entrance for magnetic valve (21) processed (A4) and two outlets (B5, B6), the entrance (A1) of first pressure control magnetic valve (11) and the second pressure control electromagnetism The entrance (A2) of valve (12) is connected with the working connection (10), the outlet (B1) of first pressure control magnetic valve (11) with this The entrance (A3) of one flow control electromagnetic valve (21) is connected, the outlet (B2) of second pressure control magnetic valve (12) with this second The entrance (A4) of flow control electromagnetic valve (22) is connected, two outlets (B3, B4) of first flow control magnetic valve (21) with First driving switch valve (41) and the third gear switch valve (43) are connected, two of second flow control magnetic valve (22) Outlet (B5, B6) is connected with second driving switch valve (42) and fourth speed bit switch valve (44).

8. hydraulic gear-shifting system as claimed in claim 7, it is characterised in that first flow control magnetic valve (21) can be the Switch between one working position and the second working position, first flow control magnetic valve (21) in the first working position when, this first The entrance (A3) of flow control electromagnetic valve (21) controls its in two outlets (B3, B4) of magnetic valve (21) with the first flow One of connection, first flow control magnetic valve (21) in the second working position when, first flow control magnetic valve (21) Entrance (A3) connect with another in two outlets (B3, B4) of first flow control magnetic valve (21)；The second flow Control magnetic valve (22) can switch between the first working position and the second working position, and second flow control magnetic valve (22) is in During the first working position, the entrance (A4) of second flow control magnetic valve (22) and the two of second flow control magnetic valve (22) Connection one of in individual outlet (B5, B6), second flow control magnetic valve (22) in the second working position when, this second The entrance (A4) of flow control electromagnetic valve (22) is another with what two of second flow control magnetic valve (22) exported in (B5, B6) One connection.

9. hydraulic gear-shifting system as claimed in claim 7, it is characterised in that the first switch magnetic valve (31) is with entrance (A5) and outlet (B7), the second switch magnetic valve (32) with entrance (A6) and export (B8), the first driving switch valve (41) with two entrances (A7, A8), two outlets (B9, B10) and a control end (C1), second driving switch valve (42) With two entrances (A9, A10), two outlets (B11, B12) and a control end (C2), third gear switch valve (43) tool There are two entrances (A11, A12), two outlets (B13, B14) and a control end (C3), fourth speed bit switch valve (44) tool There are two entrances (A13, A14), two outlets (B15, B16) and a control end (C4), the first switch magnetic valve (31) The entrance (A6) of entrance (A5) and the second switch magnetic valve (32) is connected with the working connection (10), the first switch magnetic valve (31) outlet (B7) at the same with the control end (C1) of first driving switch valve (41) and second driving switch valve (42) Control end (C2) is connected, and the outlet (B8) of the second switch magnetic valve (32) is while the control with the third gear switch valve (43) End (C3) is connected with the control end (C4) of fourth speed bit switch valve (44), the two entrances of first driving switch valve (41) (A7, A8) is connected respectively with two outlets (B3, B4) of first flow control magnetic valve (21), the second driving switch valve (42) two entrances (A9, A10) are connected respectively with two outlets (B5, B6) of second flow control magnetic valve (22), should The two entrances (A11, A12) of third gear switch valve (43) are exported respectively with two of first flow control magnetic valve (21) (B3, B4) is connected, and the two entrances (A13, A14) of fourth speed bit switch valve (44) control magnetic valve with the second flow respectively (22) two outlets (B5, B6) are connected, two outlets (B9, B10) of first driving switch valve (41) respectively with this first Two oil pockets of shift cylinder (51) are connected, two outlets (B11, B12) of second driving switch valve (42) respectively with this Two oil pockets of two shift cylinders (52) are connected, two outlets (B13, B14) of the third gear switch valve (43) respectively with this Two oil pockets of the 3rd shift cylinder (53) are connected, two outlets (B15, B16) of fourth speed bit switch valve (44) respectively with Two oil pockets of the 4th shift cylinder (54) are connected.

10. hydraulic gear-shifting system as claimed in claim 9, it is characterised in that the first switch magnetic valve (31) and this second Switch electromagnetic valve (32) is integrated into the switch electromagnetic valve (34) of a 3-position 4-way, the entrance of the first switch magnetic valve (31) (A5) that the switch electromagnetic valve (34) of the 3-position 4-way is integrated into the entrance (A6) of the second switch magnetic valve (32) enters Mouthful (A24) and be connected with the working connection (10), the outlet (B7) of the first switch magnetic valve (31) and the second switch magnetic valve (32) outlet (B8) is respectively two outlets of the switch electromagnetic valve (34) of the 3-position 4-way.