CN1920347A - Hydraulic control system for 7-gear automatic speed variator of vehicle - Google Patents
Hydraulic control system for 7-gear automatic speed variator of vehicle Download PDFInfo
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- CN1920347A CN1920347A CNA2005100929536A CN200510092953A CN1920347A CN 1920347 A CN1920347 A CN 1920347A CN A2005100929536 A CNA2005100929536 A CN A2005100929536A CN 200510092953 A CN200510092953 A CN 200510092953A CN 1920347 A CN1920347 A CN 1920347A
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Abstract
The invention relates to a hydraulic control system of seven-shift automatic speed-changer of vehicle, wherein it comprises: the first clutch control part; the first brake; the third clutch control part; the second clutch control part; the second brake control part; and the fourth clutch control part; the first, second, third, fourth, and the fifth pressure control electromagnetic valves are arranged reasonably, to realize accurate control; and it at least supplies two methods to avoid mistake, to strengthen the total function.
Description
Technical field
The present invention relates to a kind of hydraulic control system that is used for the 7-speed automatic transmission of Motor Vehicle.More particularly, the present invention relates to a kind of hydraulic control system of 7-speed automatic transmission of Motor Vehicle of the overall performance with enhancing, thus the enhancing of the overall performance of this Motor Vehicle by the fail-safe function be provided in two ways realize accurately and effectively control reduce the gear shift vibration and improve fuel economy and realize.
Background technique
Typical automatic transmission comprises torque converter and the multi-stage gear mechanism driving system that links to each other with torque converter.In addition, automatic transmission also has hydraulic control system, is used for the operating element according at least one power train of travelling state selection operation of Motor Vehicle.
This automatic transmission comprises power train and hydraulic control system.Power train comprises the combined type planetary gear set, and it forms by combination two common planetary gear set and a plurality of friction element at least, and wherein planetary gear set is used to obtain required many grades.Hydraulic control system is optionally operated the friction element of power train according to drive condition.
Each Motor Vehicle manufactory has released multiple such power train and hydraulic control system according to plan separately.Nowadays, fourth gear automatic transmission the most commonly on market.Yet, developed the g.p.m number that five grades and 6-speed automatic transmission improve the power transmission performance and increase Motor Vehicle.
Recently, on the basis of 6-speed automatic transmission, begin to further develop the research 7-speed automatic transmission, in the hope of improving the power transmission performance of automatic transmission, thereby further increased the g.p.m number of Motor Vehicle.
Disclosed content only is used to strengthen the understanding to background of the present invention in the background technique part of the present invention, thereby foregoing may comprise such information: this information does not constitute those of ordinary skills' known systems for this country.
Summary of the invention
Thereby, the present invention is devoted to provide a kind of hydraulic control system, it can be applicable in the power train of the Motor Vehicle 7-speed automatic transmission with six friction elements, thereby realize accurately and effectively control by the failure safe function that dual mode is provided, make the gear shift minimum vibration, and the optimization fuel consume, improve overall performance.
According to this purpose, the hydraulic control system that is used for the Motor Vehicle 7-speed automatic transmission of an exemplary embodiment comprises first clutch control section, first break and three-clutch control section, second clutch control section, second break control section and the four clutches control section according to the present invention.The first clutch control section is controlled forward gears slewing range pressure according to the control of first proportional electromagnetic valve, forward gears slewing range pressure is fed to first clutch when the first, second, third, fourth, the 5th forward gears, when the first proportional control solenoid valve when the 4th, the 5th, the 6th and the 7th forward gears is closed, prevent that hydraulic pressure is fed to first clutch.In the 4th, the 5th, the 6th and the 7th forward gears, low-grade L slewing range, reverse gear R slewing range, first break and three-clutch control section are controlled according to the control of second proportional electromagnetic valve and optionally forward gears slewing range pressure are fed to first break or three-clutch, and at guiding valve of an ON/OFF electromagnetic valve, the hydraulic pipe line of three-clutch is led in this guiding valve control, and under the situation that this solenoid valve cuts out owing to fault, keep leading to the hydraulic pipe line of three-clutch at the 4th, the 5th, the 6th and the 7th forward gears.
In the 3rd, the 5th and the 6th forward gears and reverse gear, the second clutch control section is fed to second clutch according to the control of the 3rd proportional control solenoid valve with loine pressure.
At the second and the 7th forward gears, the second break control section is fed to second break according to the control of the 4th proportional control solenoid valve with forward gears slewing range pressure, and controls second break and make it in the working pressure of the 7th forward gears working pressure greater than second forward gears.
When the first, second, third, fourth, the 6th and the 7th forward gears and reverse gear, the four clutches control section is fed to four clutches according to the control of the 5th proportional control solenoid valve with working pressure.
In another embodiment, the first, second, third and the 5th proportional control solenoid valve is the duty control valve, and it is time output maximum hydraulic pressure in off position; The 4th proportional control solenoid valve is the duty control valve, and it is control valve output minimum hydraulic pressure in off position the time.
In another embodiment, the first clutch control section comprises: by the first clutch side switch valve and the first clutch side pressure control valve of the control of first proportional control valve; With first switch valve, it controls the hydraulic pipe line by the forward gears slewing range pressure of hand control valve supply, and by first clutch side pressure control valve working pressure is fed to first clutch.
In another embodiment, first clutch side switch valve comprises: valve body and guiding valve, and wherein valve body comprises first port of reception from the pilot pressure of the first proportional control solenoid valve; Be formed in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port of the working pressure that is fed to first clutch; With the 4th port, it will optionally be fed to the first clutch pressure controlled valve as its pilot pressure by the hydraulic pressure that the 3rd port receives; Guiding valve comprises the second step that reception is passed through the pilot pressure of second port supply from the first step and the reception of the pilot pressure of first port, and second step optionally makes third and fourth port be communicated with first step, wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
In another embodiment, the first clutch pressure controlled valve comprises: valve body and guiding valve, wherein valve body comprises first port of reception from the pilot pressure of first clutch side switch valve, reception is from second port of the first proportional control electromagnetic valve pressure, reception is from the 3rd port of the first clutch working pressure of first switch valve, optionally will be fed to the 4th port of first clutch by the hydraulic pressure that the 3rd port receives, with the five-port that will return by the hydraulic pressure that the 4th port receives, guiding valve comprises the first step of optionally cutting out the 3rd port by the pilot pressure of first port reception, can make third and fourth port or the 4th and the second step that is communicated with of five-port with first step, receive the 3rd step by the pilot pressure of second port supply, wherein elastic element is arranged between first step and the valve body.
In another embodiment, wherein first switch valve comprises: valve body and guiding valve, wherein valve body comprises first port that receives forward gears slewing range pressure, receive second port of loine pressure as its pilot pressure, to be fed to the 3rd port of first clutch side pressure control valve by the hydraulic pressure that first port receives, receive four port of the working pressure of the second clutch and second break as its pilot pressure, receive the five-port of the working pressure of four clutches as its pilot pressure, receive six port of the working pressure of three-clutch as its pilot pressure, with the 7th port of discharging the hydraulic pressure that receives by the 3rd port, guiding valve comprises the first step of the pilot pressure that receives the supply of second port; Receive the second step of the hydraulic pressure of five-port supply, and it makes optionally the 3rd port be communicated with the first and the 6th port; Receive the 3rd step of the pilot pressure of five-port supply; Receive the 4th step of the pilot pressure of the 4th port supply; Wherein elastic element is arranged between the 3rd step and the valve body.
In another embodiment, first switch valve so constitutes, and makes that only when all the 4th, the 5th and the 6th ports were all supplied pilot pressure, guiding valve just moved towards first port by first port supply pilot pressure time.
In another embodiment, first break and three-clutch control section comprise: by the three-clutch side switch valve of the second proportional control electromagnetic valve and three-clutch side pressure control valve; By the control valve of loine pressure and ON/OFF electromagnetic valve, it makes hydraulic pipe line change hydraulic pressure from three-clutch side pressure control valve into; By the second switch valve of ON/OFF electromagnetic valve, its hydraulic pressure with the control valve supply is fed to three-clutch.
In another embodiment, three-clutch side switch valve comprises: valve body and guiding valve, and wherein valve body comprises first port of reception from the second proportional control solenoid valve; Be formed in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port of the working pressure that is fed to first break or three-clutch; Optionally will be fed to four port of three-clutch side pressure control valve as its pilot pressure by the hydraulic pressure that the 3rd port receives, guiding valve comprises the first step that receives by the pilot pressure of first port supply; With the second step that receives by the pilot pressure of second port supply, it optionally makes third and fourth port be communicated with, and wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
In another embodiment, three-clutch side pressure control valve comprises: valve body and guiding valve, wherein valve body comprises first port of reception from the second proportional control electromagnetic valve pressure, reception is from second port of three-clutch side on-off valve control pressing pressure, reception is from the 3rd port of the forward gears slewing range pressure of hand control valve, to be fed to the 4th port of control valve and three-clutch side switch valve by the hydraulic pressure that the 3rd port receives, with the five-port that will return by the hydraulic pressure that the 4th port receives, guiding valve comprises the first step of optionally cutting out the 3rd port by the pilot pressure of second port reception, can make third and fourth port or the 4th and the second step that is communicated with of five-port with first step, with the 3rd step that receives by the pilot pressure of second port supply, wherein elastic element is arranged between first step and the valve body.
In another embodiment, control valve comprises: valve body and guiding valve, wherein valve body comprises first port that receives loine pressure, reception is from second port of the second ON/OFF electromagnetic valve pressure, reception is from the 3rd port of the hydraulic pressure of three-clutch side pressure control valve, to be fed to four port of first break by the hydraulic pressure that the 3rd port receives as its working pressure, to be fed to the five-port of second switch valve by the hydraulic pressure that the 3rd port receives, discharge the 6th port of the hydraulic pressure that receives by five-port, receive seven port of the working pressure of three-clutch as its pilot pressure, guiding valve comprises the first step of the pilot pressure that receives the supply of second port, the second step that the 4th port and exhaust port are communicated with, the 3rd step that the 3rd port is communicated with the 4th and five-port, optionally open the 4th step of five-port by the pilot pressure of the first port supply, receive the 5th step of the pilot pressure of the 7th port supply.
In another embodiment, the second switch valve comprises: valve body and guiding valve, wherein valve body comprises first port of reception from the pilot pressure of the 4th proportional control solenoid valve, to be fed to second port of the second break side pressure control valve by the pilot pressure that first port receives, receive three port of the hydraulic pressure of control valve as the working pressure of three-clutch, to be fed to the 4th port of three-clutch by the hydraulic pressure that the 3rd port receives, discharge five-port by the hydraulic pressure of the 4th port supply, as the 4th branch ports and with the hydraulic pressure of the 4th port output the 6th and the 7th port as the pilot pressure of second switch valve, receive the 8th mouthful of the first ON/OFF electromagnetic valve pressure, guiding valve comprises the first step of optionally opening first port, the second step that first and second ports is communicated with first step, the 3rd step that third and fourth port is communicated with second step, the 4th step of the pilot pressure that reception is answered by the 8th confession, wherein the 3rd step and the 4th step separately are shaped, and elastic element is arranged between first step and the valve body.
In another embodiment, third and fourth step so separately is shaped, thereby when guiding valve moved right, disconnected position was positioned on the 6th port, and when guiding valve was mobile to the left, disconnected position was positioned on the 7th port.
In another embodiment, the second clutch control section comprises that hydraulic pressure can be fed to second clutch like this by the second clutch side switch valve of three proportional control electromagnetic valve and second clutch side pressure control valve.
In another embodiment, second clutch side switch valve comprises: valve body and guiding valve, and wherein valve body comprises first port of reception from the pilot pressure of the 3rd proportional control solenoid valve; Be arranged in second port of the opposite side of first port, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port by the second clutch working pressure of second clutch side pressure control valve supply; Optionally will be fed to four port of second clutch side pressure control valve as its pilot pressure by the hydraulic pressure that the 3rd port receives, guiding valve comprises the first step that receives by the pilot pressure of first port supply; With the second step that receives by the pilot pressure of second port supply, this second step optionally makes third and fourth port be communicated with first step, wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
In another embodiment, second clutch side pressure control valve comprises: valve body and guiding valve, wherein valve body comprises first port of reception from the pilot pressure of the 3rd proportional control solenoid valve, reception is from second port of the pilot pressure of second clutch side switch valve, receive the 3rd port of loine pressure, to be fed to the 4th port of second clutch by the hydraulic pressure that the 3rd port receives, discharge five-port by the hydraulic pressure of the 4th port supply, guiding valve comprises the first step that receives pilot pressure by first port, the second step of opening/closing five-port optionally, with the 3rd step that the 4th port is communicated with the 3rd and five-port, wherein elastic element is arranged between the 3rd step and the valve body.
In another embodiment, the second break control section comprises that such second break can receive hydraulic pressure by the second break side switch valve of the 4th proportional control electromagnetic valve and the second break side pressure control valve.
In another embodiment, the second break side switch valve comprises: valve body and guiding valve, and wherein valve body comprises first port of reception from the pilot pressure of the 4th proportional control solenoid valve; Be arranged in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive by the 3rd port of the second break working pressure of the second break side pressure control valve supply, the hydraulic pressure of the 3rd port is fed to four port of the second break side pressure control valve as its pilot pressure, guiding valve comprises the first step of reception from the pilot pressure of first port; Receive second step by the pilot pressure of second port supply, this second step optionally makes third and fourth port be communicated with first step, wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
In another embodiment, the second break side pressure control valve comprises: valve body and guiding valve, wherein valve body comprises first port of reception from the pilot pressure of the 4th proportional control solenoid valve, reception is from second port of the pilot pressure of the second break side switch valve, receive the 3rd port of loine pressure, to be fed to the 4th port of second break by the hydraulic pressure that the 3rd port receives, discharge five-port by the hydraulic pressure of the 4th port supply, the 6th port that is communicated with second port of second switch valve, guiding valve comprises the first step that receives by the pilot pressure of first port supply, the second step of opening/closing five-port optionally, the 3rd step that the 4th port is communicated with second step with the 3rd and five-port, with the 4th step that receives by the pilot pressure of second port supply, wherein elastic element is arranged between the 4th step and the valve body.
In another embodiment, first switch valve is connected the upstream side of the second clutch and second break by second reciprocable valve, and the hydraulic pressure that is fed to the second clutch and second break like this can partly be fed in first switch valve.
In another embodiment, the four clutches control section comprises that by the four clutches side switch valve and the four clutches pressure controlled valve of the 5th proportional control electromagnetic valve such second break can receive hydraulic pressure.
In another embodiment, four clutches side switch valve comprises: valve body and guiding valve, and wherein the valve body of four clutches side switch valve comprises first port of reception from the pilot pressure of the 5th proportional control solenoid valve; Be arranged in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port by the four clutches working pressure of four clutches side pressure control valve supply; Optionally will be fed to four port of four clutches side pressure control valve as its pilot pressure by the hydraulic pressure that the 3rd port receives, guiding valve comprises the first step that receives the first port controlling pressure; With the second step that receives by the pilot pressure of second port supply, this second step optionally makes third and fourth port be communicated with first step, and wherein elastic element is arranged between first step and the valve body.
In another embodiment, the four clutches pressure controlled valve comprises: valve body and guiding valve, wherein the valve body of four clutches pressure controlled valve comprises first port of reception from the pilot pressure of the 5th proportional control solenoid valve, receive second port of four clutches side on-off valve control pressing pressure, receive the 3rd port of loine pressure, to be fed to the 4th port of four clutches by the hydraulic pressure that the 3rd port receives, with the five-port of discharging by the hydraulic pressure of the 4th port supply, guiding valve comprises the first step of the pilot pressure that receives the supply of first port, the second step of opening/closing five-port optionally, with the 3rd step that the 4th port is communicated with second step with the 3rd and five-port, wherein elastic element is arranged between the 3rd step and the valve body.
Description of drawings
Fig. 1 is the schematic representation of power train one example, and the hydraulic control system of an exemplary embodiment can be operated this power train according to the present invention.
Fig. 2 is the operating chart of the friction element of power train shown in Figure 1.
Fig. 3 is the schematic representation of the hydraulic control system of an exemplary embodiment according to the present invention.
Fig. 4 is the detail drawing of the first clutch control section of the exemplary embodiment according to the present invention.
Fig. 5 is first break of the exemplary embodiment according to the present invention and the detail drawing of three-clutch control section.
Fig. 6 is the detail drawing of the second clutch control section of the exemplary embodiment according to the present invention.
Fig. 7 is the detail drawing of the second break control section of an exemplary embodiment according to the present invention.
Fig. 8 is the detail drawing of the four clutches control section of an exemplary embodiment according to the present invention.
Embodiment
Describe one embodiment of the invention in detail below with reference to accompanying drawing.
Fig. 1 is the schematic representation of an example of seven grades of power trains, and the hydraulic control system of an exemplary embodiment can be operated this power train according to the present invention.These seven grades of power trains are formed by the first planetary gear set PG1 and the second planetary gear set PG2, wherein first planetary gear set is double pinion planetary gear set (double pinion planetary gear set), and second planetary gear set is La Weilie AUX (Ravingneaux) formula combined planetary gear group.The first and second planetary gear set PG1 and PG2 combine by four clutch C1, C2, C3, C4 and two break B1 and B2.
The sun gear 2 of the first planetary gear set PG1 is fixedly connected on the case of transmission H, thereby always serves as reaction member, and its planetary carrier 4 directly links to each other with input shaft 6, thereby always serves as input element.
The gear ring 8 of the first planetary gear set PG1 always serves as the output element of the first planetary gear set PG1.The output of gear ring 8 after through four clutches C4 by along separate routes.That is to say that by four clutches C4, gear ring 8 links to each other with first sun gear 10 of the second planetary gear set PG2 by first clutch C1, also links to each other with second sun gear 12 of the second planetary gear set PG2 by second clutch C2.
The planetary carrier 14 of the second planetary gear set PG2 is connected with input shaft 6 changeably by three-clutch C3, and is connected changeably with case of transmission H by the first break B1.The overrunning clutch F and first break be arranged in abreast case of transmission H and between.
In addition, case of transmission H links to each other with an element by the second break B2, and this element connects second sun gear 12 of the second clutch C2 and the second planetary gear set PG2.The gear ring 16 of the second planetary gear set PG2 links to each other with output gear 16, thereby always serves as output element.
Can operate the power train of this structure by operating chart shown in Figure 2, to realize seven forward gearss and a reverse gear.That is to say the operation first of first forward gears and four clutches C1 and C4.The operation first of second forward gears and four clutches C1 and the C4 and the second break B2.The 3rd forward gears is operated first, second and four clutches C1, C2 and C4.The 4th forward gears operation first, the third and fourth clutch C1, C3 and C4.The 5th forward gears is operated first, second and three-clutch C1, C2 and C3.The 6th forward gears is operated second, third and four clutches C2, C3 and C4.The 7th forward gears is operated the third and fourth clutch C3 and the C4 and the second break B2.Reverse gear operation second and four clutches C2 and the C4 and the first break B1.
Carry out gear-change operation according to operating chart actuating friction element shown in Figure 2 and be readily appreciated that for those skilled in the art, so no longer described in detail.
Figure 3 illustrates the hydraulic control system that is used to operate this power train, the hydraulic control system of an exemplary embodiment comprises loine pressure control section A, starting control section B, decompression control section C, hand shift control section D, first clutch control section E, first break and three-clutch control section F, second clutch control section G, the second break control section H and four clutches control section I according to the present invention, thus hydraulic pressure supply and the release of may command friction element C1, C2, C3, C4, B1 and B2.
Loine pressure control section A, starting control section B and decompression control section C can be traditional structure.According to an exemplary embodiment of the present invention, loine pressure control section A comprises modulating valve 32 and proportional control solenoid valve S1, is used to control the former.Therefore, can stablize the hydraulic pressure of control oil hydraulic pump 30 supplies, loine pressure can change according to the change of drive condition.Thereby can optimize the fuel consume of Motor Vehicle.
Starting control section B comprises torque converter control valve 34, damping clutch control valve 36 and proportional control solenoid valve S2.Torque converter control valve 34 reduces loine pressure, suitably to control damping clutch, optimizes fuel consume when high speed, and utilizes the torsion of torque converter TC to increase effect when quickening.The engagement and the release of damping clutch control valve 36 control damping clutchs.Proportional control solenoid valve S2 is according to the electrical signal control damping clutch control valve 36 from transmission control unit TCU.
Decompression control section C comprises reduction valve 38.Decompression control section C reduces the hydraulic pressure that oil hydraulic pump 30 provides, and then the hydraulic pressure that reduces is fed among solenoid valve S1 and the S2 as their pilot pressure, also is fed to the pilot pressure of clutch/brake control section as them respectively.
Hand shift control section D comprises hand control valve 40, and it can be according to hand shift conversion hydraulic pipe line.
First clutch control section E comprises first clutch side switch valve 50, first clutch side pressure control valve 52 and first switch valve 54.First clutch side switch valve 50 and first clutch side pressure control valve 52 are controlled by the first proportional control solenoid valve DS1.First switch valve 54 is according to the working pressure of the hydraulic control first clutch C1 of the pilot pressure of loine pressure and the second clutch C2 or the second break B2.
First break and three-clutch control section F comprise three-clutch side switch valve 56, three-clutch side pressure control valve 58, control valve 60, second switch valve 62 and first and second ON/OFF solenoid valve SS1 and the SS2.Three-clutch side switch valve 56 and three-clutch side pressure control valve 58 are controlled by the second proportional control solenoid valve DS2.Control valve 60 can make hydraulic pipe line change hydraulic pressure from three-clutch side pressure control valve 58 into.Second switch valve 62 will be fed among the three-clutch C3 from the hydraulic pressure of control valve 60.The first and second ON/OFF solenoid valve SS1 and SS2 control second switch valve 62 and control valve 60.
Second clutch control section G comprises second clutch side switch valve 64 and second clutch side pressure control valve 66, the three proportional control solenoid valve DS3 control second clutch side pressure control valve 66.
The second break control section H comprises that the second break side switch valve 68 and the second break side pressure control valve, 70, the four proportional control solenoid valve DS4 control the second break side pressure control valve 70.
In addition, four clutches control section I comprises that four clutches side switch valve 72 and four clutches pressure controlled valve 74, the five proportional control solenoid valve DS5 control four clutches pressure controlled valve 74.
In more detail, as shown in Figure 3, hand control valve 40 optionally will be fed to reverse gear slewing range pressure piping 82 and forward gears slewing range pressure piping 84 from the hydraulic pressure of loine pressure 80 pipelines that link to each other with modulating valve 32 according to the change that drives slewing range.
Reverse gear slewing range pressure piping 82 links to each other with modulating valve 32, and the loine pressure with control reverse gear R slewing range also links to each other with the first break B1, to supply reverse gear slewing range pressure to first break.
Each control section that forward gears slewing range pressure piping 84 can be the control friction element provides working pressure.
Fig. 4 is the detail drawing of first clutch control section E.
First clutch side switch valve 50 comprises valve body and the guiding valve that is installed in wherein.
The valve body of first clutch side switch valve 50 comprises first to the 4th port 90,92,94 and 96.First port 90 receives the pilot pressure of the first proportional control solenoid valve DS1.Second port 92 is formed in the opposite side of first port 90, and the low pressure of reception reduction valve 38 is as its pilot pressure.The 3rd port 94 partly receives the working pressure that is fed to first clutch C1.The 4th port 96 optionally will be fed on the first clutch side pressure control valve 52, as its pilot pressure by the hydraulic pressure that the 3rd port 94 receives.
The guiding valve that is installed in the valve body of first clutch side switch valve 50 comprises first and second steps 98 and 100.The pilot pressure that first step 98 receives from first port 90.Second step 100 receives the pilot pressure by 92 supplies of second port, and with first step 98 third and fourth port 94 and 96 is communicated with.First step 98 has elastic element 102, and it applies an elastic force, and this elastic force is left direction biased spool valve in the figure always.
By the low pressure of second port 92 supply, guiding valve right direction in the figure moves, and such third and fourth port 94 and 96 can communicate with each other.When the duty pilot pressure of the first proportional control solenoid valve DS1 was fed in the valve by first port 90, guiding valve left direction in the figure moved a certain distance, and this distance is corresponding with the duty pilot pressure.In this case, the cross-section area of the communication passage between third and fourth port 94 and 96 is correspondingly regulated, thereby regulates the pilot pressure that is fed in the first clutch side pressure control valve 52.
First clutch side pressure control valve 52 comprises valve body and the guiding valve that is installed in wherein.
The valve body of first clutch side pressure control valve 52 comprises first to five-port 110,112,114,116 and 118.First port one 10 receives the pilot pressure of first clutch side switch valve 50.Second port one 12 receives the pilot pressure of the first proportional control solenoid valve DS1.The 3rd port one 14 receives the working pressure that is fed to first clutch C1 from first switch valve 54.The 4th port one 16 optionally is fed to the hydraulic pressure that the 3rd port one 14 receives on the first clutch C1.Five-port 118 is returned the hydraulic pressure that the 4th port one 16 receives.
The guiding valve of first clutch side pressure control valve 52 comprises first to the 3rd step 120,122 and 124.First step 120 is optionally closed the 3rd port one 14 by the pilot pressure that first port one 10 receives.Second step 122 with first step 120 make third and fourth port one 14 and 116 or the 4th and five-port 116 and 118 be communicated with.The 3rd step 124 receives the pilot pressure by 12 supplies of second port one.In addition, elastic element 126 is arranged between first step 132 and the valve body.
When pilot pressure was fed in the valve by first port one 10, guiding valve right direction in the figure moved, thereby closes the 3rd port one 14, and make the 4th and five-port 116 and 118 be communicated with.When the duty pilot pressure of the first proportional control solenoid valve DS1 was fed in the valve by second port one 12, guiding valve left direction in the figure moved a certain distance, and this distance is corresponding with the duty pilot pressure, thereby third and fourth port one 14 and 116 is communicated with.
The valve body of first switch valve 54 comprises first to the 6th port one 30,132,134,136,138,140 and 142.First port one 30 receives forward gears slewing range pressure as its pilot pressure.Second port one 32 receives loine pressure.The 3rd port one 34 will be fed in the first clutch side pressure control valve 52 by the hydraulic pressure that second port one 32 receives.The 4th port one 36 receives the working pressure of the second clutch C2 and the second break B2 as its pilot pressure.Five-port 138 receives the working pressure of four clutches C4 as its pilot pressure.The 6th port one 40 receives the working pressure of three-clutch C3 as its pilot pressure.The 7th port one 42 will be discharged by the pressure of the 3rd port one 34 supplies.
The guiding valve that is installed in first switch valve, 54 valve bodies comprises first to the 4th step 144,146,148 and 150.First step 144 receives the pilot pressure by 30 supplies of first port one.Second step 146 receives the hydraulic pressure by 40 supplies of the 6th port one, and optionally is communicated with the 3rd port one 34 and the first and the 6th port one 30 and 142 with first step 144.The pilot pressure that the 3rd step 148 receives by five-port 138 supplies.The 4th step 150 receives the pilot pressure by 36 supplies of the 4th port one.In addition, elastic element 152 is arranged between the 4th step 150 and the valve body.
Fig. 5 is the detail drawing of first break and three-clutch control section F.
Three-clutch side switch valve 56 comprises valve body and the guiding valve that is installed in wherein.
The valve body of three-clutch side switch valve 56 comprises first to the 4th port one 60,162,164 and 166.First port one 60 receives the pilot pressure of the second proportional control solenoid valve DS2.Second port one 62 is formed in the opposite side of first port one 60, and the low pressure of reception reduction valve 38 is as its pilot pressure.The 3rd port one 64 partly receives the working pressure that is fed to the first break B1 or three-clutch C3.The 4th port one 66 optionally will be fed on the three-clutch side pressure control valve 58 by the hydraulic pressure that the 3rd port one 64 receives, as its pilot pressure.
The guiding valve that is installed in the valve body of three-clutch side switch valve 56 comprises first and second steps 168 and 170.The pilot pressure that first step 168 receives from first port one 60.Second step 170 receives the pilot pressure by 62 supplies of second port one, and third and fourth port one 64 and 166 is communicated with.First step 168 has elastic element 172, and it applies an elastic force, and this elastic force is left direction biased spool valve in the figure always.
By the low pressure of second port one 62 supply, guiding valve right direction in the figure moves, and such third and fourth port one 64 and 166 can communicate with each other.When the duty pilot pressure of the second proportional control solenoid valve DS2 was fed in the valve by first port one 60, guiding valve left direction in the figure moved a certain distance, and this distance is corresponding with the duty pilot pressure.In this case, the cross-section area of the communication passage between third and fourth port one 64 and 166 is conditioned, thereby regulates the pilot pressure that is fed in the three-clutch side pressure control valve 58.
Three-clutch side pressure control valve 58 comprises valve body and the guiding valve that is installed in wherein.
The valve body of three-clutch side pressure control valve 58 comprises first to five-port 180,182,184,186 and 188.First port one 80 receives the pilot pressure of the second proportional control solenoid valve DS2.Second port one 82 receives the pilot pressure of three-clutch side switch valve 56.The 3rd port one 84 receives the forward gears slewing range pressure of hand control valve 40.The 4th port one 86 is fed to the hydraulic pressure that the 3rd port one 84 receives on control valve 60 and the three-clutch side switch valve 56.Five-port 188 is returned the hydraulic pressure that the 4th port one 86 receives.
The guiding valve of three-clutch side pressure control valve 58 comprises first to the 3rd step 190,192 and 194.First step 190 is optionally closed the 3rd port one 84 by the pilot pressure that second port one 82 receives.Second step 192 with first step 190 make third and fourth port one 84 and 186 or the 4th and five-port 186 and 188 be communicated with.The 3rd step 194 receives the pilot pressure by 82 supplies of second port one.In addition, elastic element 196 is arranged between first step 190 and the valve body.
When pilot pressure was fed in the valve by first port one 80, guiding valve right direction in the figure moved, thereby closes the 3rd port one 84, and make the 4th and five-port 186 and 188 be communicated with.When the duty pilot pressure of the second proportional control solenoid valve DS2 was fed in the valve by first port one 80, guiding valve left direction in the figure moved a certain distance, and this distance is corresponding with the duty pilot pressure, and third and fourth port one 84 and 186 is communicated with each other.
Control valve 60 comprises valve body and the guiding valve that is installed in wherein.The valve body of control valve 60 comprises first to the 7th port 200,202,204,206,208,210 and 212.First port 200 receives loine pressure.Second port 202 receives the pilot pressure of the second ON/OFF solenoid valve SS2.The 3rd port 204 receives the hydraulic pressure of three-clutch side pressure control valve 58.The 4th port 206 is fed to the hydraulic pressure that the 3rd port 204 receives on the first break B1, as its working pressure.Five-port 208 is fed to the hydraulic pressure that the 3rd port 204 receives on the second switch valve 62.The 6th port 210 is discharged the hydraulic pressure that receives by five-port 208.The 7th port 212 receives the working pressure of three-clutch C3 as its pilot pressure.
The guiding valve that is installed in control valve 60 valve bodies comprises first to the 5th step 214,216,218,220 and 222.First step 214 receives the pilot pressure by 202 supplies of second port.Second step 216 optionally is communicated to exhaust port EX with the 4th port 206.The 3rd step 218 optionally is communicated to the 3rd port 204 the 4th and five-port 206 and 208.The 4th step 220 is optionally opened five-port 208 by the pilot pressure of first port, 200 supplies.The 5th step 222 receives the pilot pressure by 212 supplies of the 7th port.
When hydraulic pressure was fed in the valve by second port 202, guiding valve right direction in the figure moved, thereby third and fourth port 204 and 206 is communicated with each other.When second port 202 not during sap pressure supply, the hydraulic pressure of guiding valve by 200 supplies of first port left direction in the figure moves, thus make the 3rd and five-port 204 and 208 communicate with each other.
In addition, the first reciprocable valve SV1 is arranged in the upstream side of the first break B1, such first break B1 can receive forward gears slewing range pressure in the low-grade L slewing range of engine brake enable position, and receives reverse gear slewing range pressure in the reverse gear slewing range.
The guiding valve that is installed in second switch valve 62 valve bodies comprises first to the 4th step 246,248,250 and 252.First step 246 is optionally opened first port 230.Second step 248 optionally makes first and second ports 230 and 232 be communicated with first step 246.The 3rd step 250 optionally makes third and fourth port 234 and 236 be communicated with second step 248.The pilot pressure that the 4th step 252 receives by the 8th mouthful of 244 supply.The 3rd step 250 and the 4th step 252 separately are shaped.In addition, elastic element 254 is arranged between first step 246 and the valve body.
Third and fourth step 250 and opened shaping in 252 minutes, when guiding valve moved right, disconnected position was positioned on the 6th port 240 like this, and when guiding valve was mobile to the left, disconnected position was positioned on the 7th port 242.
Therefore, when three-clutch C3 received working pressure, even the first ON/OFF solenoid valve SS1 fault, guiding valve 62 still moved right.
When first ON/OFF solenoid valve SS1 supply pilot pressure is to valve, guiding valve right direction in the figure moves, and the hydraulic pressure that receives by the 3rd port 234 can be fed on the three-clutch C3 by the 4th port 236 like this.
According to the scheme of this seven forward gearss, the pilot pressure of the 4th proportional control solenoid valve DS4 is fed to the second break side pressure control valve 70, and guiding valve can move towards right direction among the figure like this.That is to say, can control the second break B2 with high-grade different controls path by low-grade, thereby can obtain accurate control.
Fig. 6 is the detail drawing of second clutch control section G.
Second clutch side switch valve 64 comprises valve body and the guiding valve that is installed in wherein.
The valve body of second clutch side switch valve 64 comprises first to the 4th port 260,262,264 and 266.First port 260 receives the pilot pressure of the 3rd proportional control solenoid valve DS3.Second port 262 is arranged in the opposite side of first port 260, and the low pressure of reception reduction valve 38 is as its pilot pressure.The 3rd port 264 partly receives the working pressure by the second clutch C2 of second clutch side pressure control valve 66 supplies.The 4th port 266 optionally will be fed on the second clutch side pressure control valve 66, as its pilot pressure by the hydraulic pressure that the 3rd port 264 receives.
The guiding valve that is installed in the valve body of second clutch side switch valve 64 comprises first and second steps 268 and 270.First step 268 receives the pilot pressure by 260 supplies of first port.Second step 270 receives the pilot pressure by 262 supplies of second port, and with first step 268 third and fourth port 264 and 266 is communicated with.First step 268 has elastic element 272, and it applies an elastic force, and this elastic force is left direction biased spool valve in the figure always.
When not having the duty pilot pressure, the pilot pressure of guiding valve by the supply of second port 262 right direction in the figure moves, thereby third and fourth port 264 and 266 is communicated with each other.When receiving the duty pilot pressure of the 3rd proportional control solenoid valve DS3 by first port 260, guiding valve left direction in the figure moves a certain distance, and this distance is corresponding with the duty pilot pressure, closes the 3rd port 264 simultaneously.
Second clutch side pressure control valve 66 comprises valve body and the guiding valve that is installed in wherein.The valve body of second clutch side pressure control valve 66 comprises first to five-port 280,282,284,286 and 288.First port 280 receives the pilot pressure of the 3rd proportional control solenoid valve DS3.Second port 282 receives the pilot pressure of second clutch side switch valve 64.The 3rd port 284 receives loine pressure.The 4th port 286 is fed to the hydraulic pressure that the 3rd port 284 receives on the second clutch C2.Five-port 288 is discharged the hydraulic pressure of the 4th port 286 supplies.
The guiding valve that is installed in second clutch side pressure control valve 66 valve bodies comprises first to the 3rd step 290,292 and 294.First step 290 receives pilot pressure by first port 280.Second step 292 is opening/closing five-port 288 optionally.The 3rd step 294 with second step 292 make the 4th port 286 and the 3rd and five-port 284 and 288 be communicated with.In addition, elastic element 296 is arranged between the 3rd step 294 and the valve body.
When pilot pressure was fed in the valve by first port 280, guiding valve left direction in the figure moved, and third and fourth port 284 and 286 is communicated with, thereby supplied working pressure for second clutch C2.During when the pilot pressure of discharging first port 280 and by second port, 282 supply pilot pressures, guiding valve right direction in the figure moves, thereby can discharge the working pressure of second clutch C2 by being communicated with the 4th and five-port 286 and 288.
Fig. 7 is the detail drawing of the second break control section F.
The second break side switch valve 68 comprises valve body and the guiding valve that is installed in wherein.
The valve body of the second break side switch valve 68 comprises first to the 4th port 300,302,304 and 306.First port 300 receives the pilot pressure of the 4th proportional control solenoid valve DS4.Second port 302 is arranged in the opposite side of first port 300, and the low pressure of reception reduction valve 38 is as its pilot pressure.The 3rd port 304 partly receives the working pressure by the second break B2 of the second break side pressure control valve, 70 supplies.The 4th port 306 is fed to the hydraulic pressure of the 3rd port 304 on the second break side pressure control valve 70, as its pilot pressure.
The guiding valve that is installed in the valve body of the second break side switch valve 68 comprises first and second steps 308 and 310.The pilot pressure that first step 308 receives from first port 300.Second step 310 receives the pilot pressure by 302 supplies of second port, and with first step 308 third and fourth port 304 and 306 is communicated with.First step 308 has elastic element 312, and it applies an elastic force, and this elastic force is left direction biased spool valve in the figure always.
When not having the duty pilot pressure, the pilot pressure of guiding valve by the supply of second port 302 right direction in the figure moves, thereby third and fourth port 304 and 306 is communicated with each other.When receiving the duty pilot pressure of the 4th proportional control solenoid valve DS4 by first port 300, guiding valve left direction in the figure moves a certain distance, and this distance is corresponding with the duty pilot pressure, and the while is correspondingly closed the 3rd port 304.
The second break side pressure control valve 70 comprises valve body and the guiding valve that is installed in wherein.
The valve body of the second break side pressure control valve 70 comprises first to the 6th port 320,322,324,326,328 and 340.First port 320 receives the pilot pressure of the 4th proportional control solenoid valve DS4.Second port 322 receives the pilot pressure of the second break side switch valve 68.The 3rd port 324 receives loine pressure.The 4th port 326 is fed to the hydraulic pressure that the 3rd port 324 receives on the second break B2.Five-port 328 is discharged the hydraulic pressure of the 4th port 326 supplies.The 6th port 330 is communicated with second port 232 of second switch valve 62.
The guiding valve that is installed in the second break side pressure control valve, 70 valve bodies comprises first to the 4th step 332,333,336 and 338.First step 332 receives the pilot pressure of first port 320.Second step 334 is opening/closing five-port 328 optionally.The 3rd step 336 with second step 334 make the 4th port 326 and the 3rd and five-port 324 and 328 be communicated with.The 4th step 338 receives the pilot pressure of second port 322.In addition, elastic element 340 is arranged between the 4th step 338 and the valve body.Elastic element 340 is arranged between the 3rd step 336 and the valve body.
When pilot pressure was fed in the valve by first port 320, guiding valve left direction in the figure moved, and third and fourth port 324 and 326 is communicated with, thereby was second break B2 supply working pressure.When the pilot pressure of discharging first port 320, and during by second port, 322 supply pilot pressures, guiding valve right direction in the figure moves, thereby can discharge the working pressure of the second break B2 by being communicated with the 4th and five-port 326 and 328.
Fig. 8 is the detail drawing of four clutches control section I.
Four clutches side switch valve 72 comprises valve body and the guiding valve that is installed in wherein.
The valve body of four clutches side switch valve 72 comprises first port 350, and it receives the pilot pressure of the 5th proportional control solenoid valve DS5; Second port 352, it is arranged in the opposite side of first port 350, and the low pressure of reception reduction valve 38 is as its pilot pressure; The 3rd port 354, it partly receives the working pressure by the four clutches C4 of four clutches side pressure control valve 74 supplies; With the 4th port 356, its hydraulic pressure with the 3rd port 354 optionally is fed on the four clutches side pressure control valve 74, as its pilot pressure.
The guiding valve that is installed in the valve body comprises first step 358, and it receives the pilot pressure from first port 350; With second step 360, it receives the pilot pressure by 352 supplies of second port, and with first step third and fourth port 354 and 356 is communicated with.
When not having the duty pilot pressure, the pilot pressure of guiding valve by the supply of second port 352 right direction in the figure moves, thereby third and fourth port 354 and 356 is communicated with each other.When receiving the duty pilot pressure of the 5th proportional control solenoid valve DS5 by first port 350, guiding valve left direction in the figure moves a certain distance, and this distance is corresponding with the duty pilot pressure, and the while is correspondingly closed the 3rd port 354.
Four clutches side pressure control valve 74 comprises valve body and the guiding valve that is installed in wherein.
The valve body of four clutches side pressure control valve 74 comprises first port 370, and it receives the pilot pressure of the 5th proportional control solenoid valve DS3; Second port 372, it receives the pilot pressure of four clutches side switch valve 72; The 3rd port 374, it receives loine pressure; The 4th port 376, it is fed to the hydraulic pressure that the 3rd port 374 receives on the four clutches C4; And five-port 378, it discharges the hydraulic pressure of the 4th port 376 supplies.
The guiding valve that is installed in the valve body comprises first step 380, and it receives the pilot pressure by 370 supplies of first port; Second step 382, it is opening/closing five-port 378 optionally; With the 3rd step 384, its with second step 382 optionally make the 4th port 376 and the 3rd and five- port 374 and 378 be communicated with.
When pilot pressure was fed in the valve by first port 370, guiding valve left direction in the figure moved, and third and fourth port 374 and 376 is communicated with, thereby was four clutches C4 supply working pressure.When the pilot pressure of discharging first port 370, and during by second port, 372 supply pilot pressures, guiding valve right direction in the figure moves.In this case, by make the 4th and five-port 376 and 378 be communicated with to discharge the working pressure of four clutches C4, this working pressure partly is fed in first switch valve 54 as its pilot pressure.
In addition, according to an exemplary embodiment of the present invention, accumulator AC1 is arranged in the driving pressure pipeline 84, but stabilized driving pressure like this.In addition, accumulator AC2 is arranged in the loop, the hydraulic pressure in the time of can stably keeping discharging like this.Similarly, first, second, third and the pipeline of four clutches C1, C2, C3 and C4 and the second break B2 in be furnished with an accumulator (referring to Fig. 3) respectively.
The first, second, third, fourth and the 5th proportional control solenoid valve DS1, DS2, DS3, DS4 and DS5 about control section in the exemplary embodiment of the present invention, output maximum hydraulic pressure when the first, second, third and the 5th proportional control solenoid valve DS1, DS2, DS3 and DS5 close, the 4th proportional control solenoid valve DS4 exports minimum hydraulic pressure when closing.
The hydraulic control system of an exemplary embodiment according to the present invention, the first and second ON/OFF solenoid valves and proportional control solenoid valve carry out according to following table 1 in the operation of each gear.
[table 1]
| SS1 | SS2 | DS1 | DS2 | DS3 | DS4 | DS5 | |
| Bottom gear | Low | High | High | High | High | ||
| 1 grade | Low | Low | High | High | |||
| 2 grades | Low | Low | High | High | High | ||
| 3 grades | Low | Low | High | High | High | ||
| 4 grades | High | Low | High | High | High | ||
| 5 grades | High | Low | High | High | High |
| 6 grades | High | Low | High | High | High | ||
| Seven grades | High | Low | High | High | High | ||
| Reverse gear | Low | Low | High | High |
Describe the operation of the hydraulic control system of an exemplary embodiment below in detail according to the present invention.
When pilot engine, when oil hydraulic pump 30 produces hydraulic pressure, loine pressure is fed to the first and second solenoid valve SS1 and SS2, hand control valve 40, first switch valve 54, the third and fourth clutch side pressure control valve 66 and 74 and control valve 60.In this case, the hydraulic pressure of reduction valve 38 control be fed to respectively proportional control solenoid valve DS1, DS2, DS3, DS4 and DS5, first, second, third and the four clutches side switch valve 50,64,56 and the 72 and second break side switch valve 68 on, as their pilot pressure.
When hand control valve 40 was transformed into D shelves slewing range with the starter motor motor-car, D shelves slewing range pressure was fed to first switch valve 54, three-clutch side pressure control valve 58 and the second break side pressure control valve 70 by forward gears slewing range pressure piping 84.In this case, first switch valve 54 receives loine pressures by its first port one 30, guiding valve left direction in the figure is moved, so that the second and the 3rd port one 32 and 134 communicates with each other.Therefore, the forward gears slewing range pressure that is fed to second port one 32 is delivered to first clutch side pressure control valve 52 by the 3rd port one 14.
When the control first proportional control solenoid valve DS1, the pilot pressure of the first proportional control solenoid valve DS1 is fed to first clutch side switch valve 50 by first port 90, also is fed to first clutch side pressure control valve 52 by second port one 12.Therefore, in this case, their guiding valve left direction in the figure moves, and the 3rd port 94 of first clutch side switch valve 50 is closed, and third and fourth port one 14 and 116 of first clutch side pressure control valve 52 communicates with each other.Thereby forward gears slewing range pressure is fed to first clutch C1, with the conversion (referring to Fig. 4) that realizes first forward gears.
In addition, the hydraulic pressure of the 5th proportional control solenoid valve DS5 is fed to four clutches side hydraulic control valve 74 by first port 370.Thereby under pilot pressure, right direction moves in the figure guiding valve left direction in the figure is moved.Thereby third and fourth port 374 and 376 communicates with each other, and the hydraulic pressure that is fed to the 3rd port 374 is fed on the four clutches C4 by the 4th port 376 now.
Meanwhile, the duty pilot pressure of the 5th proportional electromagnetic valve DS5 also is fed to four clutches side switch valve 72 by first port 350, as its pilot pressure.By this pilot pressure, the guiding valve that right direction moves in the figure begins to move to the left now.
At this moment, low pressure is acting on the guiding valve with first port, 350 opposite sides, as its pilot pressure, thereby reduces the travelling speed of guiding valve.The working pressure that is fed to four clutches C4 from four clutches side pressure control valve 74 is partly got back to four clutches side pressure control valve 74 by third and fourth port 354 and 356 at second port 372 of four clutches side pressure control valve 74.So guiding valve to the left travelling speed in four clutches side pressure control valve 74 reduces, thereby the hydraulic pressure that is fed to four clutches C4 increases gradually.
When four clutches side switch valve 72 fully moves to the right side, close the 3rd port 354.In this case, the pilot pressure that second port 372 by four clutches side pressure control valve 70 is fed to four clutches side pressure control valve 70 is discharged from now, makes the guiding valve of four clutches side pressure control valve 74 fully move to left side among the figure.Therefore forward gears slewing range pressure normally is fed among the four clutches C4, thereby finishes by first and the conversion of first forward gears realized of four clutches C1 and C4.
When the speed of a motor vehicle increased on the basis of first forward gears, speed change degree control unit (not shown) made the 4th proportional control solenoid valve DS4 begin control (referring to Fig. 7).
Then, the pilot pressure of the 4th proportional control solenoid valve DS4 is fed to the second break side pressure control valve 70 by first port 320 of the second break side pressure control valve 70, thereby and makes right direction moves in the figure guiding valve begin to move to the left by the effect of this duty pilot pressure.The result communicates with each other third and fourth port 324 and 326, and the hydraulic pressure that is fed to the 3rd port 324 begins to be fed to the second break B2 by the 4th port 326.
Meanwhile, the duty pilot pressure of the 4th proportional electromagnetic valve DS4 also is fed to the second break side switch valve 68 by first port 300 of the second break side switch valve 68, as its pilot pressure.By this pilot pressure, the guiding valve that right direction moves in the figure begins to move to the left.
At this moment, low pressure is acting on the guiding valve with first port, 300 opposite sides, as its pilot pressure, thereby reduces the travelling speed of guiding valve.The working pressure that is fed to the second break B2 from the second break side pressure control valve 70 is partly got back to the second break side pressure control valve 70 by third and fourth port 304 and 306 at second port 322 of the second break side pressure control valve 70.So guiding valve to the left travelling speed in the second break side pressure control valve 70 reduces, thereby the hydraulic pressure that is fed to the second break B2 increases gradually.
When the guiding valve of the second break side switch valve 68 fully moves to the right side, close the 3rd port 304.In this case, the pilot pressure that is fed to the second break side pressure control valve 70 is discharged from by its second port 322, thereby and makes the guiding valve of the second break side pressure control valve 70 fully move to left side among the figure.Therefore forward gears slewing range pressure normally is fed among the second break B2, thereby has finished by first and the conversion of second forward gears realized of four clutches C1 and C4 and the second break B2.
Be appreciated that from above, the second break side switch valve 68 and the second break side pressure control valve 70 are worked together, the working pressure that is fed to the second break B2 was reduced in the starting stage of gear shift, and normally supply working pressure in the gear shift stage of finishing.Thereby the validity of gear shift control is improved.
When the speed of a motor vehicle further increased on the basis of second forward gears, speed change degree control unit was closed the 4th proportional control solenoid valve DS4, made the 3rd proportional control solenoid valve DS3 begin control (referring to Fig. 6).
Thereby, discharge the hydraulic pressure that is fed to the second break B2, the pilot pressure of the 3rd proportional control solenoid valve DS3 is fed to second clutch side pressure control valve 66 by first port 280 of second clutch side pressure control valve 66.Thereby, make right direction moves in the figure guiding valve begin to move to the left by the effect of this duty pilot pressure.Third and fourth port 284 and 286 communicates with each other as a result, and the hydraulic pressure that is fed to the 3rd port 284 begins to be fed to second clutch C2 by the 4th port 286.
Meanwhile, the duty pilot pressure of the 3rd proportional electromagnetic valve DS3 also is fed to second clutch side switch valve 64 by first port 260 of second clutch side switch valve 64, as its pilot pressure.By this pilot pressure, the guiding valve that right direction moves in the figure begins to move to the left.
At this moment, low pressure is acting on the guiding valve with first port, 260 opposite sides, as its pilot pressure, thereby reduces the travelling speed of guiding valve.Correspondingly, the working pressure that is fed to second clutch C2 from second clutch side pressure control valve 66 is partly got back to second clutch side pressure control valve 66 by third and fourth port 264 and 266 at second port 282 of second clutch side pressure control valve 66.So guiding valve to the left travelling speed in second clutch side pressure control valve 66 reduces, thereby the hydraulic pressure that is fed to second clutch C2 increases gradually.
When the guiding valve of second clutch side switch valve 64 fully moves to the right side, close the 3rd port 264.In this case, the pilot pressure that is fed to second clutch side pressure control valve 66 is discharged from by its second port 282, thereby and makes the guiding valve of second clutch side pressure control valve 66 fully move to left side among the figure.Thereby forward gears slewing range pressure normally is fed among the second clutch C2, thereby has finished by first, second conversion with the 3rd forward gears of four clutches C1, C2 and C4 realization.
Be appreciated that from above, second clutch side switch valve 64 and second clutch side pressure control valve 66 are worked together, the working pressure that is fed to second clutch C2 was reduced in the starting stage of gear shift, and normally supply working pressure in the gear shift stage of finishing.Thereby the validity of gear shift control is improved.
When the speed of a motor vehicle further increased on the basis of the 3rd forward gears, speed change degree control unit was closed the control of the 3rd proportional control solenoid valve DS3.In addition, make the second proportional control solenoid valve DS2 begin control, and control the first ON/OFF solenoid valve SS1, make it to open (referring to Fig. 5).
Thereby, discharge the hydraulic pressure that is fed to second clutch C2, the duty pilot pressure of the second proportional control solenoid valve DS2 is fed to three-clutch side pressure control valve 58 by first port one 80 of three-clutch side pressure control valve 58.Thereby the guiding valve that right direction moves in the figure begins to move to the left by the effect of this duty pilot pressure.Third and fourth port one 84 and 186 communicates with each other as a result, and the hydraulic pressure that is fed to the 3rd port one 84 begins to be fed to by the 4th port one 86 the 3rd port 204 of control valve 60.
Meanwhile, the duty pilot pressure of the second proportional electromagnetic valve DS2 also is fed to three-clutch side switch valve 56 by first port one 60 of three-clutch side switch valve 56, as its pilot pressure.By this pilot pressure, the guiding valve that right direction moves in the figure begins to move to the left.
At this moment, low pressure is acting on the guiding valve with first port one, 60 opposite sides, as its pilot pressure, thereby reduces the travelling speed of guiding valve.Correspondingly, the working pressure that is fed to three-clutch C3 from three-clutch side pressure control valve 58 is partly got back to three-clutch side pressure control valve 58 by third and fourth port one 64 and 166 at second port one 82 of three-clutch side pressure control valve 58.So guiding valve to the left travelling speed in three-clutch side pressure control valve 58 reduces, thereby the hydraulic pressure that is fed to three-clutch C3 increases gradually.
When the guiding valve of three-clutch side switch valve 56 fully moves to the right side, close the 3rd port one 64.In this case, the pilot pressure that is fed to three-clutch side pressure control valve 58 is discharged from by its second port one 82, thereby and makes the guiding valve of three-clutch side pressure control valve 58 fully move to left side among the figure.Therefore forward gears slewing range pressure is fed among the three-clutch C3 by control valve 60 and second switch valve 62, thereby has finished the conversion of the 4th forward gears of realizing by first, the third and fourth clutch C1, C3 and C4.
In the process of this sap pressure supply, control valve 60 receives loine pressures by its first port 200, thereby makes guiding valve keep that left direction moves in the figure.Therefore, the hydraulic pressure that is fed to the 3rd port 204 outputs to the 3rd port 234 of second switch valve 62 by five-port 208.At this moment, the guiding valve of second switch valve 62 passes through the elastic force quilt of elastic element 254 towards the left side bias voltage, and receives pilot pressure by the 8th mouthful 244 when opening the first ON/OFF solenoid valve SS1.Therefore, guiding valve right direction in the figure moves, because third and fourth port 234 and 236 communicates with each other, hydraulic pressure can be supplied on the three-clutch C3 like this.
Be appreciated that from above the hydraulic part that is fed to three-clutch C3 is fed in first switch valve 54.In addition, three-clutch side switch valve 56 and three-clutch side pressure control valve 58 are worked together, the working pressure that is fed to three-clutch C3 was reduced in the starting stage of gear shift, and normally supply working pressure in the gear shift stage of finishing.Thereby the validity of gear shift control is improved.
When the speed of a motor vehicle further increased on the basis of the 4th forward gears, speed change degree control unit was closed the control of the 5th proportional control solenoid valve DS5, begins the control of the 3rd proportional control solenoid valve DS3.
Thereby the hydraulic pressure that is fed to four clutches C4 is discharged from, and first and three-clutch C1 and C3 keep work.The duty pilot pressure of the 3rd proportional control solenoid valve DS3 is fed to second clutch side pressure control valve 66 by first port 280 of second clutch side pressure control valve 66.Thereby make right direction moves in the figure guiding valve begin to move to the left by the effect of this duty pilot pressure.As a result, third and fourth port 284 and 286 communicates with each other, and the hydraulic pressure that is fed to the 3rd port 284 begins to be fed to second clutch C2 by the 4th port 286.
When the speed of a motor vehicle further increased on the basis of the 5th forward gears, speed change degree control unit (not shown) was closed the control of the first proportional control solenoid valve DS1, begins the control (referring to Fig. 8) of the 5th proportional control solenoid valve DS5.
Then, control according to the 5th proportional control solenoid valve DS5, four clutches C4 receives working pressure in the mode identical with mode in first forward gears, and realizes the conversion of the 6th forward gears by work of operating second, third and four clutches C2, C3 and C4.
When the speed of a motor vehicle further increased on the basis of the 6th forward gears, speed change degree control unit (not shown) was closed the control of the 3rd proportional control solenoid valve DS3, begins the control (referring to Fig. 7) of the 4th proportional control solenoid valve DS4.
Then, control according to the 4th proportional control solenoid valve DS4, the second break B2 receives working pressure in the mode identical with mode in second forward gears, and realizes the conversion of the 7th forward gears by the work of operating the third and fourth clutch C3 and C4 and the second break B2.
When reverse gear, reverse gear slewing range pressure directly is fed to the first break B1 by the reverse gear slewing range pressure piping 82 of hand control valve 40, meanwhile, begins the control of the 3rd and the 5th proportional control solenoid valve DS3 and DS5.
Then, the first break B1 and second receives working pressure with four clutches C2 and C4 in the mode identical with mode in the first and the 3rd forward gears, thereby realizes the conversion of reverse gear.
When carrying out the conversion of the 7th forward gears and a reverse gear, the hydraulic control system of an exemplary embodiment has the failure safe function of dual mode according to the present invention, promptly by cutting off and/or opening circuit, deal with malfunctioning such as the element of solenoid valve etc.
In more detail, when the low grade of first, second and the 3rd forward gears broke down, speed changer kept with the 3rd forward gears work.When the top grade of the 4th, the 5th, the 6th and the 7th forward gears broke down, speed changer kept with the 6th forward gears work.
This is because in off position down, the first, second, third and the 5th proportional control solenoid valve DS1, DS2, DS3 and DS5 output maximum flow hydraulic pressure, and in off position down, the 4th proportional control solenoid valve DS4 can not export hydraulic pressure.
In more detail, first and first forward gears of four clutches C1 and C4 work when breaking down, second, third and the 5th proportional control solenoid valve DS2, DS3 and DS5 close, and export maximum pilot pressures.Therefore, by the delivery pressure of the second proportional control solenoid valve DS2, the hydraulic pressure of three-clutch side pressure control valve 58 is fed to second switch valve 62 by control valve 60.
Yet because second switch valve 62 is not supplied pilot pressure, its guiding valve keeps that left direction moves in the figure.Therefore, the 3rd port 234 is closed, and hydraulic pressure is not fed to three-clutch C3.
In addition, by the delivery pressure of the 3rd proportional control solenoid valve DS3, the hydraulic pressure of second clutch side pressure control valve 66 is fed among the second clutch C2.Therefore, realize remaining on the 3rd forward gears by operating first, second work with four clutches C1, C2 and C4.
When first and second forward gears of four clutches C1 and C4 and second break B2 work when breaking down, the 3rd proportional control solenoid valve DS3 closes, and output hydraulic pressure.Thereby make second clutch C2 work, realize the first and the 3rd forward gears by operating first, second and four clutches C1, C2 and C4.
When the 4th forward gears in first, the third and fourth clutch C1, C3 and C4 work breaks down, the hydraulic pressure that is fed to three-clutch C3 is fed to the 3rd step 250 of guiding valve by the 6th port 240 parts, even the first ON/OFF solenoid valve SS1 stops to export hydraulic pressure.Thereby guiding valve can't be towards moving left, and make three-clutch C3 continue to receive hydraulic pressure.
In addition, because the 3rd proportional control solenoid valve DS3 output pressure maximum, second clutch C2 receives hydraulic pressure.Owing to be fed to the 4th, the 5th and the 6th port one 36,138 and 140 that second, third hydraulic pressure with four clutches C2, C3 and C4 is fed to first switch valve 54, second port one 32 of first switch valve 54 gets clogged, and is discharged from thereby be fed to first clutch C1 hydraulic pressure.Thereby, keep the 6th forward gears by operating second, third and four clutches C2, C3 and C4.
When first, second the 5th forward gears with three-clutch C1, C2 and C3 work breaks down, hydraulic pressure by the 5th proportional control solenoid valve DS5 makes four clutches C4 work, and first clutch C1 quits work when breaking down in the 4th forward gears.Thereby, keep the 6th forward gears by operating second, third and four clutches C2, C3 and C4.
When the 7th forward gears in the third and fourth clutch C3 and C4 and second break B2 work breaks down, because the 3rd proportional control solenoid valve DS3 closes, so second clutch C2 receives working pressure, because the 4th proportional control solenoid valve DS4 closes, so the second break B2 stops to receive working pressure.Thereby, keep the 6th forward gears by operating second, third and four clutches C2, C3 and C4.
So, when speed changer so that for example the the the 4th, the 5th, the 6th and the 7th grade top grade drives, can suddenly not drop into the 3rd forward gears, and this falls and will cause the gear shift vibration.When under the failure safe pattern, killing engine and restarting motor subsequently, certainly use the 3rd forward gears, and can realize the driving torque bigger than the driving torque of the 6th forward gears.
In addition, about the second break B2, the delivery pressure of the 4th proportional control solenoid valve DS4 is fed to the 6th port 340 of the second break side pressure control valve 70 by first and second ports 230 and 232 of second switch valve 62, when gear shift between high and low shift, can in the different pressures scope, control like this hydraulic control valve that is used for the control operation element.Thereby, improved the precision of hydraulic control.
In addition, the first break B1 and three-clutch C3 can only be controlled by a pressure controlled valve (three-clutch side pressure control valve 58 is with the control valve 60 and the second ON/OFF solenoid valve SS2).Therefore, can simplify the structure of hydraulic control system.
As mentioned above, the hydraulic control system that is applied in an exemplary embodiment of the present invention of 7-speed automatic transmission power train has six friction elements, and it prevents the vibration of losing rank suddenly by the failure safe function with dual mode is provided.
Exemplary embodiment according to the present invention, each friction element all has hydraulic control valve and switch valve, and specifically, the pilot pressure scope of second break can change according to high and low shift.Thereby, can obtain more accurate and more effective control, realized the gear shift minimum vibration, improved and driven the control performance, also optimized fuel consume.
In addition, first break and three-clutch are controlled by a pressure controlled valve, so, by simplifying the structure of hydraulic control system, can improve the overall performance of automatic transmission.
Though the present invention is set forth by being considered to the most practical exemplary embodiment at present, yet should be understood that, the present invention is not limited to disclosed embodiment, on the contrary, the present invention ought to be contained by the various distortion that spirit and scope covered of appended claim and equivalence design.
Claims (23)
1. hydraulic control system that is used for the 7-speed automatic transmission of Motor Vehicle comprises:
The first clutch control section, forward gears slewing range pressure is controlled in its control according to first proportional electromagnetic valve, forward gears slewing range pressure is fed to first clutch when the first, second, third, fourth, the 5th forward gears, and when the first proportional control solenoid valve when the 4th, the 5th, the 6th and the 7th forward gears is closed, prevent that hydraulic pressure is fed to first clutch;
First break and three-clutch control section, it is the 4th, the 5th, the the 6th and the 7th forward gears, low-grade L slewing range, reverse gear R slewing range, control forward gears slewing range pressure according to the control of second proportional electromagnetic valve, and optionally forward gears slewing range pressure is fed to first break or three-clutch, and at guiding valve of an ON/OFF electromagnetic valve, the hydraulic pipe line of three-clutch is led in this guiding valve control, and under the situation that this solenoid valve cuts out owing to fault, the 4th, the 5th, the the 6th and the 7th forward gears keeps leading to the hydraulic pipe line of three-clutch;
The second clutch control section, it is in the 3rd, the 5th and the 6th forward gears and reverse gear, and the control according to the 3rd proportional control solenoid valve is fed to second clutch with loine pressure;
The second break control section, it according to the control of the 4th proportional control solenoid valve, is fed to second break with forward gears slewing range pressure at the second and the 7th forward gears, and control second break, make it in the working pressure of the 7th forward gears working pressure greater than second forward gears; And
The four clutches control section, it is when the first, second, third, fourth, the 6th and the 7th forward gears and reverse gear, and the control according to the 5th proportional control solenoid valve is fed to four clutches with working pressure.
2. according to the hydraulic control system of claim 1, it is characterized in that:
The first, second, third and the 5th proportional control solenoid valve is the duty control valve, and it is time output maximum hydraulic pressure in off position; And
The 4th proportional control solenoid valve is the duty control valve, and it is time output minimum hydraulic pressure in off position.
3. according to the hydraulic control system of claim 1, it is characterized in that: the first clutch control section comprises:
By the first clutch side switch valve of the first proportional control electromagnetic valve and first clutch side pressure control valve; And
First switch valve, it controls the hydraulic pipe line by the forward gears slewing range pressure of hand control valve supply, thereby by first clutch side pressure control valve working pressure is fed to first clutch.
4. according to the hydraulic control system of claim 3, it is characterized in that: first clutch side switch valve comprises:
Valve body, it comprises first port of reception from the pilot pressure of the first proportional control solenoid valve; Be formed in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port of the working pressure that is fed to first clutch; With the 4th port, it will optionally be fed to the first clutch pressure controlled valve as its pilot pressure by the hydraulic pressure that the 3rd port receives; And
Guiding valve, it comprises reception from the first step of the pilot pressure of first port with receive second step by the pilot pressure of second port supply, and second step optionally makes third and fourth port be communicated with first step,
Wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
5. according to the hydraulic control system of claim 3, it is characterized in that: the first clutch pressure controlled valve comprises:
Valve body, it comprise reception from first port of the pilot pressure of first clutch side switch valve, receive second port, receive the 3rd port, optionally will be fed to the 4th port of first clutch and the five-port that will return by the hydraulic pressure that the 4th port receives by the hydraulic pressure that the 3rd port receives from the working pressure of the first clutch of first switch valve from the pilot pressure of the first proportional control solenoid valve; And
Guiding valve, it comprises that the pilot pressure that receives by first port optionally closes the first step of the 3rd port, can make third and fourth port or the 4th and the second step that is communicated with of five-port, receive the 3rd step by the pilot pressure of second port supply with first step
Wherein elastic element is arranged between first step and the valve body.
6. according to the hydraulic control system of claim 3, it is characterized in that: first switch valve comprises:
Valve body, it comprises first port that receives forward gears slewing range pressure, receive loine pressure as second port of its pilot pressure, will be fed to by the hydraulic pressure that first port receives first clutch side pressure control valve the 3rd port, receive the working pressure of the second clutch and second break as the 4th port of its pilot pressure, receive the working pressure of four clutches as the five-port of its pilot pressure, receive three-clutch working pressure as the 6th port of its pilot pressure with discharge the 7th port of the hydraulic pressure that receives by the 3rd port; And
Guiding valve, it comprises the first step of the pilot pressure that receives the supply of second port; Receive the second step of the hydraulic pressure of five-port supply, and this second step makes optionally the 3rd port be communicated with the first and the 6th port; Receive the 3rd step of the pilot pressure of five-port supply; And the 4th step that receives the pilot pressure of the 4th port supply;
Wherein elastic element is arranged between the 3rd step and the valve body.
7. according to the hydraulic control system of claim 6, it is characterized in that: first switch valve so constitutes, make that only when all the 4th, the 5th and the 6th ports were all supplied pilot pressure, guiding valve just moved towards first port by first port supply pilot pressure time.
8. according to the hydraulic control system of claim 1, it is characterized in that: first break and three-clutch control section comprise:
By the three-clutch side switch valve of the second proportional control electromagnetic valve and three-clutch side pressure control valve;
By the control valve of loine pressure and ON/OFF electromagnetic valve, it makes hydraulic pipe line change hydraulic pressure from three-clutch side pressure control valve into;
By the second switch valve of ON/OFF electromagnetic valve, its hydraulic pressure with the control valve supply is fed to three-clutch.
9. hydraulic control system according to Claim 8, it is characterized in that: three-clutch side switch valve comprises:
Valve body, it comprises first port of reception from the second proportional control solenoid valve; Be formed in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port of the working pressure that is fed to first break or three-clutch; Optionally will be fed to four port of three-clutch side pressure control valve by the hydraulic pressure that the 3rd port receives as its pilot pressure; And
Guiding valve, it comprises the first step that receives by the pilot pressure of first port supply; With the second step that receives by the pilot pressure of second port supply, this second step optionally makes third and fourth port be communicated with,
Wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
10. hydraulic control system according to Claim 8, it is characterized in that: three-clutch side pressure control valve comprises:
Valve body, it comprise reception from first port of the second proportional control electromagnetic valve pressure, receive second port, receive the 3rd port, will be fed to the 4th port of control valve and three-clutch side switch valve and the five-port that will return by the hydraulic pressure that the 4th port receives from the hydraulic pressure that the 3rd port receives from the forward gears slewing range pressure of hand control valve from the pilot pressure of three-clutch side switch valve; And
Guiding valve, it comprises that the pilot pressure that receives by second port optionally closes the first step of the 3rd port, can make third and fourth port or the 4th and the second step that is communicated with of five-port and receive the 3rd step by the pilot pressure of second port supply with first step
Wherein elastic element is arranged between first step and the valve body.
11. hydraulic control system according to Claim 8 is characterized in that: control valve comprises:
Valve body, it comprises first port that receives loine pressure, receive second port of the second ON/OFF electromagnetic valve pressure, receive the 3rd port from the hydraulic pressure of three-clutch side pressure control valve, will be fed to from the hydraulic pressure that the 3rd port receives first break as the 4th port of its working pressure, will be fed to from the hydraulic pressure that the 3rd port receives the second switch valve five-port, discharge the hydraulic pressure that receives by five-port the 6th port, receive seven port of the working pressure of three-clutch as its pilot pressure; And
Guiding valve, it comprise the first step of the pilot pressure that receives the second port supply, optionally make second step that the 4th port and exhaust port be communicated with, optionally make the 3rd step that the 3rd port is communicated with the 4th and five-port, optionally open the 4th step of five-port, the 5th step of pilot pressure that reception the 7th port is supplied by the pilot pressure of the first port supply.
12. hydraulic control system according to Claim 8 is characterized in that: the second switch valve comprises:
Valve body, it comprises first port of reception from the pilot pressure of the 4th proportional control solenoid valve, to be fed to second port of the second break side pressure control valve by the pilot pressure that first port receives, receive three port of the hydraulic pressure of control valve as the working pressure of three-clutch, to be fed to the 4th port of three-clutch by the hydraulic pressure that the 3rd port receives, discharge five-port by the hydraulic pressure of the 4th port supply, as the 4th branch ports and with the hydraulic pressure of the 4th port output the 6th and the 7th port as the pilot pressure of second switch valve, reception is from the 8th mouthful of the pilot pressure of the first ON/OFF solenoid valve; And
Guiding valve, it comprises the first step of optionally opening first port, optionally makes second step that first and second ports are communicated with, optionally makes the 3rd step that third and fourth port is communicated with, the 4th step that receives the pilot pressure of answering by the 8th confession with second step with first step
Wherein the 3rd step and the 4th step separately are shaped, and
Elastic element is arranged between first step and the valve body.
13. the hydraulic control system according to claim 12 is characterized in that: third and fourth step so separately is shaped, and makes that disconnected position is positioned on the 6th port when guiding valve moves right, and when guiding valve was mobile to the left, disconnected position was positioned on the 7th port.
14. hydraulic control system according to claim 1, it is characterized in that: the second clutch control section comprises second clutch side switch valve and the second clutch side pressure control valve of being controlled by the 3rd proportional control solenoid valve, thereby hydraulic pressure can be fed to second clutch.
15. the hydraulic control system according to claim 14 is characterized in that: second clutch side switch valve comprises:
Valve body, it comprises first port of reception from the pilot pressure of the 3rd proportional control solenoid valve; Be arranged in second port of the opposite side of first port, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port by the second clutch working pressure of second clutch side pressure control valve supply; Optionally will be fed to four port of second clutch side pressure control valve by the hydraulic pressure that the 3rd port receives as its pilot pressure; And
Guiding valve, it comprises the first step that receives by the pilot pressure of first port supply; With the second step that receives by the pilot pressure of second port supply, this second step optionally makes third and fourth port be communicated with first step,
Wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
16. the hydraulic control system according to claim 14 is characterized in that: second clutch side pressure control valve comprises:
Valve body, it comprise reception from first port of the pilot pressure of the 3rd proportional control solenoid valve, receive second port from the pilot pressure of second clutch side switch valve, receive loine pressure the 3rd port, will be fed to by the hydraulic pressure that the 3rd port receives second clutch the 4th port, discharge five-port by the hydraulic pressure of the 4th port supply; And
Guiding valve, it comprises by first port and receives the first step of pilot pressure, the optionally second step of opening/closing five-port and the 3rd step that the 4th port is communicated with second step with the 3rd and five-port,
Wherein elastic element is arranged between the 3rd step and the valve body.
17. hydraulic control system according to claim 1, it is characterized in that: the second break control section comprises the second break side switch valve and the second break side pressure control valve of being controlled by the 4th proportional control solenoid valve, thereby makes second break receive hydraulic pressure.
18. the hydraulic control system according to claim 17 is characterized in that: the second break side switch valve comprises:
Valve body, it comprises first port of reception from the pilot pressure of the 4th proportional control solenoid valve; Be arranged in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive by the 3rd port of the second break working pressure of the second break side pressure control valve supply, the hydraulic pressure of the 3rd port is fed to four port of the second break side pressure control valve as its pilot pressure; And
Guiding valve, it comprises the first step of reception from the pilot pressure of first port; Receive the second step by the pilot pressure of second port supply, this second step optionally makes third and fourth port be communicated with first step,
Wherein first step has elastic element, and its elastic force that applies is left direction biased spool valve in the figure always.
19. the hydraulic control system according to claim 17 is characterized in that: the second break side pressure control valve comprises:
Valve body, it comprise reception from first port of the pilot pressure of the 4th proportional control solenoid valve, receive second port, receive the 3rd port of loine pressure, the 4th port that will be fed to second break, the five-port of discharging the hydraulic pressure by the supply of the 4th port and the 6th port that is communicated with second port of second switch valve by the hydraulic pressure that the 3rd port receives from the pilot pressure of the second break side switch valve; And
Guiding valve, comprise reception by the first step of the pilot pressure of the first port supply, optionally the opening/closing five-port second step, make the 3rd step that the 4th port is communicated with the 3rd and five-port and receive the 4th step with second step by the pilot pressure of second port supply
Wherein elastic element is arranged between the 4th step and the valve body.
20. hydraulic control system according to claim 14, it is characterized in that: first switch valve is connected the upstream side of the second clutch and second break by second reciprocable valve, and the hydraulic pressure that is fed to the second clutch and second break like this can partly be fed in first switch valve.
21. the hydraulic control system according to claim 1 is characterized in that: the four clutches control section comprises by the four clutches side switch valve and the four clutches pressure controlled valve of the 5th proportional control electromagnetic valve, thereby makes second break receive hydraulic pressure.
22. the hydraulic control system according to claim 21 is characterized in that: four clutches side switch valve comprises:
The valve body of four clutches side switch valve, it comprises first port of reception from the pilot pressure of the 5th proportional control solenoid valve; Be arranged in second port of the first port opposite side, this second port receives the low pressure of reduction valve as its pilot pressure; Partly receive the 3rd port by the four clutches working pressure of four clutches side pressure control valve supply; Optionally will be fed to four port of four clutches side pressure control valve by the hydraulic pressure that the 3rd port receives as its pilot pressure; And
Guiding valve comprises the first step that receives the first port controlling pressure; With the second step that receives by the pilot pressure of second port supply, this second step optionally makes third and fourth port be communicated with first step,
Wherein elastic element is arranged between first step and the valve body.
23. the hydraulic control system according to claim 21 is characterized in that: the four clutches pressure controlled valve comprises:
The valve body of four clutches pressure controlled valve, it comprises that reception is from first port of the pilot pressure of the 5th proportional control solenoid valve, second port that receives the pilot pressure of four clutches side switch valve, the 3rd port that receives loine pressure, the 4th port that will be fed to four clutches by the hydraulic pressure that the 3rd port receives and the discharge five-port by the hydraulic pressure of the 4th port supply; And
Guiding valve comprises reception by the first step of the pilot pressure of the first port supply, the optionally second step of opening/closing five-port and the 3rd step that the 4th port is communicated with second step with the 3rd and five-port,
Wherein elastic element is arranged between the 3rd step and the valve body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100929536A CN100547268C (en) | 2005-08-24 | 2005-08-24 | The hydraulic control system that is used for 7 gear automatic speed variators of Motor Vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100929536A CN100547268C (en) | 2005-08-24 | 2005-08-24 | The hydraulic control system that is used for 7 gear automatic speed variators of Motor Vehicle |
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| CN1920347A true CN1920347A (en) | 2007-02-28 |
| CN100547268C CN100547268C (en) | 2009-10-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2005100929536A Expired - Fee Related CN100547268C (en) | 2005-08-24 | 2005-08-24 | The hydraulic control system that is used for 7 gear automatic speed variators of Motor Vehicle |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102454771A (en) * | 2010-10-14 | 2012-05-16 | 现代自动车株式会社 | Hydraulic control system of continuously variable transmission for vehicle |
| CN102808945A (en) * | 2012-08-12 | 2012-12-05 | 哈尔滨东安汽车发动机制造有限公司 | Hydraulic oil path for controlling reverse gear of six-speed automatic transmission |
-
2005
- 2005-08-24 CN CNB2005100929536A patent/CN100547268C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102454771A (en) * | 2010-10-14 | 2012-05-16 | 现代自动车株式会社 | Hydraulic control system of continuously variable transmission for vehicle |
| CN102454771B (en) * | 2010-10-14 | 2015-11-25 | 现代自动车株式会社 | For the hydraulic control system of the continuously variable transmission of vehicle |
| CN102808945A (en) * | 2012-08-12 | 2012-12-05 | 哈尔滨东安汽车发动机制造有限公司 | Hydraulic oil path for controlling reverse gear of six-speed automatic transmission |
Also Published As
| Publication number | Publication date |
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| CN100547268C (en) | 2009-10-07 |
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