CN2477453Y - Electrohydraulic controlled speed controlling and dispensing valve - Google Patents
Electrohydraulic controlled speed controlling and dispensing valve Download PDFInfo
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- CN2477453Y CN2477453Y CN 01236787 CN01236787U CN2477453Y CN 2477453 Y CN2477453 Y CN 2477453Y CN 01236787 CN01236787 CN 01236787 CN 01236787 U CN01236787 U CN 01236787U CN 2477453 Y CN2477453 Y CN 2477453Y
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Abstract
The utility model relates to a new electrohydraulic controlled variable speed controlling and dispensing valve of the hydraulic transmission power gear shifting gear box used for loader transmission and variable speed fluid system, which is characterized in that: the adjusting valve, the upper valve and the lower valve are organically piled together. The utility model is of a compact structure and good reliability. Adopting the electrohydraulic control for steering and shifting, and the operation is light and flexible, which greatly reduces the working intensity of the driver; the utility model has good shifting and steering buffer capacity, and power transmission can not be interrupted, and the operation efficiency of the whole machine is high. The main pressure stability of the system is good, and shifting is not accompanied with runout. The utility model has the function of emergency hand controlled steering when the system powers down.
Description
The utility model relates to a kind of engineering machinery hydraulic valve, exactly is that the novel electric liquid that is used for the hydraulic transmission Powershift transmission of loader transmission and compensator pressure system is handled the variable speed control distributing valve.
At present, the change speed gear box hydraulic efficiency pressure system of engineering machinery vehicles such as domestic and international loader generally adopts single oil pump feed, through being divided into two-way behind the speed change main pressure regulator valve, wherein one the tunnel for carrying out the lubricated of circulation cooling and change speed gear box toward tor-con, and another road is for past change speed gear box maneuvering system.The hydraulic efficiency pressure system of this form should have following function:
1, should guarantee to have in the tor-con use charge oil pressure of the cavitation erosion of not producing and the fuel supply flow rate that can take away tor-con, heat that change speed gear box produces.
2, should preferentially guarantee to prevent that to handling the oil circuit fuel feeding maneuvering system is malfunctioning.
3, the pressure that should preferentially guarantee to supply with working connection should have the superpressure overflow within the specific limits, and basic unmodified function keep-ups pressure.
4, should guarantee the quality requirements of compensator pressure system in the gearshift procedure, promptly guarantee commutation, gearshift procedure steadily, do not have and impact, guarantee that the gear shift oil pressure grows steadily, it is overlapping to have a suitable gear shift, and the power transmission is not interrupted as far as possible.
At present, the applied variable speed control distributing valve of available dynamic shift transmission generally adopts hand shift, and the shift control handle links in connecting rod mechanism and operator's compartment.Owing to adopt connecting rod mechanism, understeer is lived.The compensator pressure system has only adopted the buffering energy storage on the reversing oil circuit that moves forward and backward, the shift control inconvenience easily produces shifting shock, and reduces the service life of friction lining.The energy storage volume is big, complex process, manufacturing cost height.Main pressure regulator valve adopts Direct Action Type, opens than big.During buty shifting, pressure runout, system pressure poor stability.
The purpose of this utility model is for overcoming the deficiency that above-mentioned distributing valve exists, provide a kind of manipulation light, flexible, main pressure regulator valve superior performance, commutation, the electric liquid manipulation variable speed control distributing valve that the gear shift cushion characteristic is good, nothing is impacted, integrated level is high.
The purpose of this utility model is achieved in that with compensator pressure system pressure-gradient control valve, main pressure regulator valve, speed change guide's reducing valve, stopping brake valve, change-over valve, command valve, the fast control cock of height, tor-con back pressure valve and control cock, rapid release valve, emergent hand change over valve, speed change electromagnetic valve, the organic integration of stopping brake electromagnetic valve together, is fixed on the change speed gear box side.
The utility model has saved many complicated pipelines and has connected because the above-mentioned functions valve is organically integrated and be superimposed.Adopt electric liquid to handle commutation, gear shift, light and flexible greatly reduces driver's labour intensity.Adopt control cock, rapid release valve to gear shift, the buffer action that commutated, cushion characteristic is good, and transmission of power does not interrupt, complete machine operating efficiency height, and the main pressure regulator valve pressure stability is good, and gear shift does not have runout.
Concrete structure of the present utility model is provided by following examples and accompanying drawing thereof.
Fig. 1 handles the speed change control valve outside drawing according to the electric liquid that the utility model proposes.
Fig. 2 is a control cock section-drawing of handling speed change control valve according to the electric liquid that the utility model proposes.
Fig. 3 is a upper valve section-drawing of handling speed change control valve according to the electric liquid that the utility model proposes.
Fig. 4 is a lower valve section-drawing of handling speed change control valve according to the electric liquid that the utility model proposes.
Describe details, service condition and dynamic duty process in detail below in conjunction with Fig. 1, Fig. 2, Fig. 3, Fig. 4 according to the concrete device that the utility model proposes.
The utility model electricity liquid is handled speed change control valve by control cock (34), upper valve (31) and lower valve (29) three partial function valve pieces and upper valve seal pad (30), control cock packing seal (33) connect the formation that is superimposed by bolt (32), (35) as shown in Figure 1.One as shown in Figure 2, constitutes control cock (34) by end cap (1), spring (2), spool (3), valve pocket (4), spring perch (5), spring (6), spring (7), energy storage plunger (8), valve body (9), end cap (10), spring (11).Spool (3) adopts free-running fit with valve pocket (4) relative motion.Spool (3) adopts free-running fit with valve body (9), and its relative motion is a straight-line motion.Accumulation of energy plunger (8) adopts free-running fit with valve body (9), and its relative motion is a straight-line motion.Oil duct d communicates with the q chamber through the damping hole i of spool (3).Oil duct a communicates with Fig. 3 oil duct c, and oil duct d communicates with Fig. 4 oil duct e and Fig. 3 oil duct B, and oil duct f communicates with Fig. 3 oil duct g, and oil duct Ne communicates with t chamber among Fig. 3.
Its two, as shown in Figure 3, upper valve (31) organic integration emergent hand change over valve (12), speed change guide's reducing valve (13), rapid release valve (14), main pressure regulator valve (15) and tor-con back pressure valve (16).Steel ball (17), spring (18), spool (19), plug screw (20), damping plug (21), spring (22) constitute rapid release valve (14).Upper body (23) is a straight-line motion with spool (19) relative motion, and adopts free-running fit.Oil duct B communicates with oil duct g through damping hole h, and oil duct J communicates with oil return, and Z communicates with oil duct B through damping hole R for the sealing oil duct, and the R1 chamber communicates with Fig. 4 oil duct L.Oil duct R2 communicates with oil duct X5, and X1 and X2 annular groove oil duct communicate with X6 and X7 among Fig. 4 respectively.
Its three, as shown in Figure 4, lower valve (29) organic integration change-over valve (28), high low speed valve (24), command valve (25), pressure-gradient control valve (26), stopping brake valve (27), solenoid directional control valve D1, D2, D3, D4 and stopping brake electromagnetic valve D5.Oil duct L is the speed-variable pump oil input channel, oil duct K with 3 oil duct c Fig. 2 oil duct a, communicate, oil duct M communicates with the change speed gear box parking brake clutch.Hydraulic fluid port N is 2 grades, and hydraulic fluid port P is 1 grade, and hydraulic fluid port U is 3 grades, and hydraulic fluid port V is 4 grades, and hydraulic fluid port Y is a D Drive, and hydraulic fluid port X is for retreating shelves.
The service condition that the utility model electricity liquid is handled the variable speed control distributing valve is as follows:
(1) service condition of commutation of control cock (34) and rapid release valve (14) or gear shift:
When retreating grade as being transformed into from D Drive, the pressure of oil duct B is owing to clutch pressure reduces, and oil duct g pressure reduces simultaneously.Rapid release valve left end enclosed cavity Z pressure oil is pushed steel ball (17) overflow open, and under the effect of pull back spring (22), spool (19) is moved to the left, oil duct g communicates with oil duct J, the whole oil sump tanks of oil pocket f pressure oil, spool (3) moves under spring (2) effect, opens hydraulic fluid port S.After the gear conversion, the pressure oil of oil duct a enters oil duct d through decompression, and the You Yilu of oil duct d enters power-transfer clutch, and one the tunnel enters oil duct B.Oil duct B enters accumulation of energy chamber f through damping plug (21) damping hole h and oil duct g.Clutch pressure is pressure (pressure in q chamber) P2 and spring (2) pressure P 3 and oil duct f pressure P 1 balance in d chamber.Along with promoting energy storage plunger (8), oil duct f pressure P 1 compression spring (6), spring (7) move to left.Be accompanied by energy storage plunger (8) and move to left, original balance is broken, and P2 is that the pressure of power-transfer clutch raises gradually, makes the gear shift slow pressure build-up, realizes pooling feature so repeatedly.Because oil duct Ne communicates with oil duct t among Fig. 3 among Fig. 2, so during engine speed change, pressure P 4 risings of oil duct Ne.Spool (3) is positioned at annular groove W both sides, and to be provided with a diameter difference be Δ D, its downside is greater than upside, so pressure P 4 applies a pressure P that moves downward 4 at annular groove W place to spool (3), d cavity pressure P2, spring (2) pressure P 3, oil duct f pressure P 1 and annular groove W place pressure P 4 have following relational expression: P2=P1+P3+P4 at this moment, so clutch pressure is complementary with engine speed in control process, avoid transmission of power lagging influence operating efficiency, get 0.7-1.2 for mating general Δ D preferably.The gear shift action step is identical with the commutation step.
(2) service condition 1 grade time of advancing: (other gear engaged situation is similar)
Oil pump comes oil content to become two-way, wherein one the tunnel enter the R1 chamber, after speed change guide reducing valve (13) decompression, reach emergent hand change over valve (12) from the R2 chamber for past each solenoid directional control valve, another road is for past pressure-gradient control valve (26) oil duct L, enter oil duct K after opening pressure-gradient control valve (26), supply respectively again toward oil duct C and oil duct a.Oil duct C pressure oil is opened main pressure regulator valve (15) back and is supplied toward tor-con from oil duct C1, and the tor-con oil return is opened tor-con back pressure valve (16) back from oil duct t oil sump tank.Oil duct a pressure oil is through control cock, rapid release valve (14), change-over valve (28), high low speed valve (24), command valve (25) laggard oil inlet port Y D Drive and hydraulic fluid port PI shelves clutch oil cylinder, because the effect of control cock, pressure rises gradually, when reaching rated pressure, D Drive and the complete combination of I shelves power-transfer clutch.Solenoid directional control valve D1, D3 are charged during this operating mode.
(3) stopping brake service condition:
When stopping brake electromagnetic valve D5 was charged, stopping brake valve (27) valve rod was under the guide oil effect, and compression spring makes oil duct M communicate with oil duct L, and pressure oil for toward parking brake, removes stopping brake by oil duct M.
(4) emergent hand change over valve service condition: (D Drive)
When electric system breaks down, push emergent manual reverse of direction valve rod (12), at this moment, oil duct X3, oil duct X5 communicate with X6 chamber among Fig. 4, and X2, X7 chamber communicate with the X4 chamber and oil return, and commutation valve rod (28) is moved to the left, then oil pocket Y communicates with oil pocket e, and pressure oil liquid enters forward clutch.The backward gear service condition is as the same.
Claims (5)
1, the novel electric liquid of the applied hydraulic transmission Powershift transmission of a kind of transmission of single oil pump feed and compensator pressure system is handled the variable speed control distributing valve, it is characterized in that control cock (34), upper valve (31), lower valve (29) and upper valve seal pad (30), control cock packing seal (33) is by bolt (32), (35) connect the formation that is superimposed, by end cap (1), spring (2), spool (3), valve pocket (4), spring perch (5), spring (6), spring (7), energy storage plunger (8), valve body (9), end cap (10), spring (11) constitutes control cock (34); Constitute upper valve (31) by emergent hand change over valve (12), speed change guide's reducing valve (13), rapid release valve (14), main pressure regulator valve (15), tor-con back pressure valve (16); Constitute lower valve (29) by high low speed valve (24), command valve (25), pressure-gradient control valve (26), stopping brake valve (27), change-over valve (28), solenoid directional control valve D1, D2, D3, D4, stopping brake electromagnetic valve D5; Control cock (34) oil duct a communicates with upper valve (31) oil duct c, control cock (34) oil duct d communicates with lower valve (29) oil duct e and upper valve (31) oil duct B, control cock (34) oil duct f communicates with upper valve (31) oil duct g, control cock (34) oil duct Ne communicates with t chamber in the upper valve (31), upper valve (31) oil duct J communicates with oil return, upper valve (31) R1 chamber with communicate with lower valve (29) oil duct L, upper valve (31) X1 and X2 annular groove oil duct communicate lower valve (29) oil duct K and upper valve (31) oil duct c with middle X6 of lower valve (29) and X7 respectively, control cock (34) oil duct a communicates.
2, electric liquid according to claim 1 is handled the variable speed control distributing valve, it is characterized in that both sides, control cock (34) spool (3) annular groove W place are provided with diameter difference Δ D, and Δ D gets 0.7～1.2, and its downside is greater than upside; The W annular groove communicates with tor-con oil back chamber t by oil duct Ne; Spool (3) links to each other with valve pocket (4) by spring (2); Spring (6) one ends are supported in spool (3) upper end, and the other end is supported on the spring perch (5); Spring (7) two ends link to each other with spring perch (5) and energy storage plunger (8) respectively.
3, electric liquid according to claim 1 is handled the variable speed control distributing valve, it is characterized in that rapid release valve Z chamber is an enclosed cavity, and the Z chamber communicates with oil duct B by damping hole K; Damping plug is provided with damping hole h in (21); Steel ball (17) is pressed in spool (19) with spring (18) and goes up and seal.
4, electric liquid according to claim 1 is handled the variable speed control distributing valve, it is characterized in that being provided with emergent hand change over valve (12) on the top of upper valve, and between its valve rod and valve body free-running fit.
5, electric liquid according to claim 1 is handled the variable speed control distributing valve, it is characterized in that being provided with stopping brake valve (27) in the bottom of lower valve, and between its valve rod and valve body free-running fit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01236787 CN2477453Y (en) | 2001-04-29 | 2001-04-29 | Electrohydraulic controlled speed controlling and dispensing valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01236787 CN2477453Y (en) | 2001-04-29 | 2001-04-29 | Electrohydraulic controlled speed controlling and dispensing valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2477453Y true CN2477453Y (en) | 2002-02-20 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01236787 Expired - Fee Related CN2477453Y (en) | 2001-04-29 | 2001-04-29 | Electrohydraulic controlled speed controlling and dispensing valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2477453Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094441A (en) * | 2010-12-23 | 2011-06-15 | 山东临工工程机械有限公司 | Hydraulic system of loader |
| CN104712751A (en) * | 2015-03-26 | 2015-06-17 | 第一拖拉机股份有限公司 | Tractor electric hydraulic control gear shift mechanism |
| CN107339416A (en) * | 2017-07-11 | 2017-11-10 | 山东临工工程机械有限公司 | A kind of gearbox manual shift control valve |
-
2001
- 2001-04-29 CN CN 01236787 patent/CN2477453Y/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094441A (en) * | 2010-12-23 | 2011-06-15 | 山东临工工程机械有限公司 | Hydraulic system of loader |
| CN104712751A (en) * | 2015-03-26 | 2015-06-17 | 第一拖拉机股份有限公司 | Tractor electric hydraulic control gear shift mechanism |
| CN107339416A (en) * | 2017-07-11 | 2017-11-10 | 山东临工工程机械有限公司 | A kind of gearbox manual shift control valve |
| CN107339416B (en) * | 2017-07-11 | 2022-10-14 | 山东临工工程机械有限公司 | Manual gear shifting control valve for gearbox |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee |
Owner name: SHANDONG CONSTRUCTION MACHINERY GROUP CO., LTD. Free format text: FORMER NAME OR ADDRESS: SHANDONG ENGINEERING MACHINERY PLANT |
|
| CP01 | Change in the name or title of a patent holder |
Patentee after: Shandong SEM Machinery Co., Ltd. Patentee before: Shandong Engineering Machiner Factory |
|
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20020220 Termination date: 20100429 |