CN103994218B - Hydraulic regulating valve - Google Patents
Hydraulic regulating valve Download PDFInfo
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- CN103994218B CN103994218B CN201410045570.2A CN201410045570A CN103994218B CN 103994218 B CN103994218 B CN 103994218B CN 201410045570 A CN201410045570 A CN 201410045570A CN 103994218 B CN103994218 B CN 103994218B
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- Prior art keywords
- pressure
- spring
- valve
- signal pressure
- guiding valve
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4008—Control of circuit pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H2061/66204—Control for modifying the ratio control characteristic
- F16H2061/66218—Control for modifying the ratio control characteristic dependent on control input parameters other than ambient conditions or driver's choice
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66231—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed
- F16H61/66236—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed using electrical or electronical sensing or control means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention provides a hydraulic regulating valve which can reduce the pipeline pressure without reducing the resistance to the adherence of impurity. The regulating valve possesses an oil chamber (42d) which is communicated to the input port supplying the pipeline pressure (PH) and the output port (42e) supplying the control pressure (DR); a slide valve (42a) is received within the oil chamber (42d) in a manner of moving axially and controls the communication volume of the input port (42f) and the output port (42e); a signal pressure (42g) chamber has a signal pressure port (42h) supplying the signal voltage (DRC); a first spring (42) is positioned within the signal pressure chamber (42) and has a signal pressure port (42h) which is supplied with the signal pressure (DRC); a first spring (42b) is positioned within the signal pressure chamber (42g) and applies force to the slide valve (42a) along the direction where the communication volume is increased; and a second spring (42c) is positioned within the oil chamber (42d) which is contrary to the signal pressure chamber (42g) and applies force to the slide valve (42a) along the direction where the communication volume is decreased.
Description
Technical field
The present invention relates to hydraulic regulating valve.
Background technology
In the past, it is known that following variable v-belt drive, it was by the most movable driving (DR) belt wheel of halfbody and driven
(DN) belt wheel and be wound in these 2 belt wheels metal tape constitute.
In this variable v-belt drive, in order to control to the cylinder body room supply for making drawer at movable side pulley half move
Pressure, is provided with regulation valve (hydraulic regulating valve).
Supply the pipeline pressure generated by working oil to this regulation valve, this working oil is by being driven source to drive by electromotor etc.
Hydraulic pump carrys out force feed.And, regulation valve makes guiding valve move according to the signal pressure come from linear solenoid valve supply, thus defeated
Go out to control pressure.Guiding valve is exerted a force by spring, even if signal pressure is 0, also produces the MIN pressure that controls and (such as, joins
According to patent documentation 1).Pipeline pressure must be at the hydraulic pressure controlling to press the minimal surplus of additional necessity and formed.
Patent documentation 1: No. 3524751 publications of Japanese Patent Publication No.
Owing to utilizing the driving sources such as electromotor to drive hydraulic pump, therefore pipeline pressure is the highest, the shifting efficiency of buncher
The lowest.Its result is, decrease in fuel efficiency.Accordingly, it would be desirable to pipeline forces down.
But, in the technology of above-mentioned patent documentation 1, need to produce MIN control all the time and press above control
Pressure.Thus, even if in the case of pressure-drop in pipeline can being made low according to operational situation, also cannot by pressure-drop in pipeline as little as
Below the hydraulic pressure pressing the minimal surplus of additional necessity in MIN control and formed.
If it addition, reduce the active force of spring, then pressing the minimal surplus of additional necessity in control and diminish, from
And pressure-drop in pipeline can be made low.
But, if reducing the active force of spring, then at guiding valve due to impurity such as attritive powders in the case of set, profit
It is difficult to release this set with the active force of spring.Therefore, the resistance for impurity set reduces.
Summary of the invention
In view of above-mentioned problem of the prior art point, it is an object of the invention to provide and do not make to drop for the resistance of impurity set
Low, it becomes possible to reduce the hydraulic regulating valve of pipeline pressure.
It is a feature of the present invention that and possess: grease chamber, the hydraulic pressure behind its input port being supplied to hydraulic pressure and supply pressure regulation
Delivery outlet connection get up；Guiding valve, it is being contained in the way of being axially moveable in described grease chamber, and controls institute
State the connection amount of input port and described delivery outlet；Signal pressure chamber, it has the signal pressure mouth being supplied to signal pressure；1st
Spring, it is configured at described signal pressure chamber, and exerts a force described guiding valve to the direction that described connection amount increases；With the 2nd
Spring, it is configured at the side contrary with described signal pressure chamber of described grease chamber, and the direction reduced to described connection amount
Described guiding valve is exerted a force.
In accordance with the invention it is possible to according to signal pressure and the difference of the spring load of 2 springs, the liquid to supply to input port
Pressure (following, by this hydraulic pressure also referred to as " pipeline pressure ") carries out pressure regulation, and (below, should from delivery outlet supply hydraulic pressure
Hydraulic pressure also referred to as " controls pressure ").Therefore, as long as suitably setting the spring load of 2 springs, it becomes possible to make signal
Initial pressure when pressure is 0 is desired value, or at random setup control pressure sets up signal pressure originally.
And, utilize 2 springs respectively guiding valve to be exerted a force in the opposite direction, even if therefore at guiding valve due to fine powder
End etc. impurity and in the case of set, it is also possible to make guiding valve return to predetermined position.
It addition, in the present invention, it is preferred that the spring load of described 1st spring is than the spring of described 2nd spring
Load is little.
In this case, by random setting the inactive area of signal pressure, improve being input to control signal pressure
The following of the current instruction value in linear solenoid valve.May validate that for as shown in Figure 5 when increasing electric current
During command value, signal pressure is the linear solenoid valve that constitutes of mode of 0, when signal pressure is 0, meeting when returning from here
Produce big sluggishness.If thus being set as the vicinity not using this signal pressure to be 0, then to current-order
Following improves.
It addition, in the present invention, it is preferred that the spring load of described 1st spring and the spring of described 2nd spring
Load is identical.
In this case, when signal pressure is 0, controlling pressure is 0, situation about therefore recording with above-mentioned patent documentation 1
Compare, it is possible to make relative to controlling to press the pressure-drop in pipeline that should add necessary minimal surplus low.
It addition, in the present invention, it is preferred that the spring load of described 1st spring is than the spring of described 2nd spring
Load is big.
In this case, the combination by making spring load is different, it is possible to realize the response that change is abundant, additionally it is possible to
Make pressure-drop in pipeline low.
Accompanying drawing explanation
Fig. 1 is the belt possessing the hydraulic control circuit with regulation valve schematically illustrating embodiments of the present invention
The explanatory diagram of buncher.
Fig. 2 is the explanatory diagram schematically illustrating hydraulic control circuit.
Fig. 3 is the explanatory diagram of the schematic configuration of the regulation valve illustrating embodiments of the present invention.
Fig. 4 is to illustrate the signal pressure under different spring loads and control the line chart of the relation pressed.
Fig. 5 is the line chart of an example of the output characteristics illustrating linear solenoid valve.
Label declaration
1: variable v-belt drive；
4: metal tape mechanism；
5:DR belt wheel；
5A: fixing side DR pulley half；
5B: drawer at movable side DR pulley half；
Cylinder body room, 6:DR side；
7: metal tape；
8:DN belt wheel；
8A: fixing side DN pulley half；
8B: drawer at movable side DN pulley half；
Cylinder body room, 9:DN side；
24: forward clutch；
25: retrogressing brake；
26: torque-converters；
31: hydraulic pump；
35: control unit；
40: hydraulic control circuit；
41:PH regulates valve；
42:DR regulation valve, regulation valve (hydraulic regulating valve)；
42a: guiding valve (sliding spool valve)；
42b: the 1 spring；
42c: the 2 spring；
42d: grease chamber；
42e: delivery outlet；
42f: input port；
42g: signal pressure chamber；
42h: signal pressure mouth；
43:DN regulation valve, regulation valve (hydraulic regulating valve)；
44:CR valve；
45:DRC linear solenoid valve；
46:DNC linear solenoid valve；
47:LCC linear solenoid valve；
48:CPC linear solenoid valve；
49:LC control valve；
50: hand-operated valve；
57:LC switches valve；
ENG: electromotor；
PGS: planetary gears.
Detailed description of the invention
[structure of variable v-belt drive]
Hereinafter, referring to the drawings the variable v-belt drive 1 of the hydraulic regulating valve using embodiments of the present invention is carried out
Explanation.As it is shown in figure 1, variable v-belt drive 1 is made up of such as lower component: transmission input shaft 2, it is via stream
The torque-converters 26 of body formula and be connected with the output shaft of the electromotor ENG as the source of driving；Variator counter axis 3, its
Configure abreast with transmission input shaft 2；Metal tape mechanism 4, it is configured between the two axle 2,3；And
Forward-reverse switching mechanism 20, it is disposed on transmission input shaft 2.
It is provided with hydraulic pump 31 and hydraulic control circuit 40 at variable v-belt drive 1.Hydraulic pump 31 is via oil circuit 32
To hydraulic control circuit 40 force feed working oil.
Metal tape mechanism 4 is made up of such as lower component: driving (DR) belt wheel 5, it is rotatably disposed in speed change
On device power shaft 2；Driven (DN) belt wheel 8, it is disposed in the way of rotating integrally with variator counter axis 3
In variator counter axis 3；And metal tape 7, it is wound in two belt wheels 5,8.
DR belt wheel 5 is made up of such as lower component: fixing side DR pulley half 5A, and it is with rotatable and can not be along axle
It is disposed on transmission input shaft 2 to the mode of movement；With drawer at movable side DR pulley half 5B, it can be relative to
This fixing side DR pulley half 5A moves axially relatively.Formed in the side of drawer at movable side DR pulley half 5B
There is cylinder body room, DR side 6, utilize the hydraulic pressure come via oil circuit 33 supply from hydraulic control circuit 40, produce and make movably
The axial thrust (DR belt wheel axial thrust) that side DR pulley half 5B is axially moveable.
DN belt wheel 8 is made up of such as lower component: fixing side DN pulley half 8A, it combines and be disposed in variator meter
On number axis 3；With drawer at movable side DN pulley half 8B, it can be relative to this fixing side DN pulley half 8A along axle
To relative movement.It is formed with cylinder body room, DN side 9 in the side of drawer at movable side DN pulley half 8B, utilizes from hydraulic pressure
Control the hydraulic pressure that loop 40 is come via oil circuit 34 supply, produce and make drawer at movable side DN pulley half 8B be axially moveable
Axial thrust (DN belt wheel axial thrust).
Utilize hydraulic control circuit 40, the hydraulic pressure supplied to cylinder body room 9, side, cylinder body room, DR side 6 and DN is controlled
System, it is possible to set and does not makes metal tape 7 that the belt shaft thrust skidded occurs, and can by DR belt wheel 5 and
The belt wheel width setup of DN belt wheel 8 is variable.Thus, variable v-belt drive 1 can make metal tape 7 relative to
The winding radius of two belt wheels 5,8 change continuously thus infinitely (continuously) control gear ratio.
Forward-reverse switching mechanism 20 is by planetary gears PGS, forward clutch 24 and retrogressing brake
25 are constituted.Planetary gears PGS is configured to single pinion type, and it is constituted by with lower part: be incorporated into variator
The central gear 21 of power shaft 2；It is incorporated into the gear ring 23 of fixing side DR pulley half 5A；And planet carrier 22,
The little gear 22a axle engaged with central gear 21 and gear ring 23 is supported to be free to rotation and revolution by it.
Retrogressing brake 25 is configured to be held in shell Ca by fixing for planet carrier 22.Forward clutch 24
It is configured to link central gear 21 and gear ring 23.When forward clutch 24 is engaged, central gear 21,
Planet carrier 22 and gear ring 23 rotate integrally with transmission input shaft 2, DR belt wheel 5 by transmission input shaft 2
Identical direction (direction of advance) drives.On the other hand, when retrogressing brake 25 is engaged, planet carrier 22
Fixing and be held in shell Ca, gear ring 23 is driven to the direction (direction of retreat) contrary with central gear 21.
And, planetary gears PGS can also be configured to double-pinion type.In this case, as long as making to fix
Side DR pulley half 5A is incorporated into planet carrier, and retrogressing brake is located at gear ring.
After the power of electromotor ENG is via metal tape mechanism 4, forward-reverse switching mechanism 20 speed change, it is passed to
Variator counter axis 3.Be transferred to the power of variator counter axis 3 via gear 27a, 27b, 28a, 28b quilt
It is transferred to differential attachment 29, and is the most separately transferred to not shown left and right wheels.
As it was previously stated, utilize hydraulic control circuit 40 to control cylinder body room, side, cylinder body room, DR side 6 and DN 9
Hydraulic pressure supply thus realize speed Control.The control signal come from control unit 35 transmission is utilized to carry out this hydraulic control
The action control in loop 40.In order to carry out this speed Control, input engine rotation signal to control unit 35, send out
Motivation throttle opening signal, GES, DR belt wheel rotating signal and DN belt wheel rotating signal etc..
[structure of hydraulic control circuit]
Hereinafter, the hydraulic control circuit 40 possessed variable v-belt drive 1 illustrates.As in figure 2 it is shown,
Hydraulic control circuit 40 possesses: PH regulation valve 41, DR regulation valve 42, DN regulate valve 43, CR valve 44,4
Individual linear solenoid valve (electromagnetic valve) 45～48, LC control valve 49 and hand-operated valve 50.
The working oil drawn from fuel tank by the hydraulic pump 31 driven by electromotor ENG via oil circuit 32 by force feed to
PH regulates valve 41.PH regulation valve 41 carries out pressure regulation to the working oil come from hydraulic pump 31 force feed, generates pipeline pressure
PH。
The working oil utilizing the pipeline pressure PH after PH regulation valve 41 pressure regulation is supplied to DR regulation via oil circuit 51
Valve 42 and DN regulates valve 43.It addition, utilize PH regulation valve 41 pressure regulation after pipeline pressure PH working oil via
The oil circuit 52 branched out from oil circuit 51 is supplied to CR valve 44.
The pipeline pressure PH decompression of the CR valve 44 working oil to coming from oil circuit 52 supply, generates and controls pressure CR.By
What CR valve 44 generated controls to press the working oil of CR to be supplied to 4 linear solenoid valves 45～48 via oil circuit 53.
Though DRC linear solenoid valve 45 illustrates the most in detail, but it is according to making guiding valve shift the turn on angle of electromagnetic valve,
Generate signal pressure DRC from by the post-decompression pressure CR that controls of CR valve 44 according to turn on angle, and supply via oil circuit 54
Valve 42 is regulated to DR.Though DNC linear solenoid valve 46 illustrates the most in detail, but it is according to the turn on angle to electromagnetic valve
Make guiding valve shift, generate signal pressure DNC, and warp from by the post-decompression pressure CR that controls of CR valve 44 according to turn on angle
Supplied to DN regulation valve 43 by oil circuit 55.
DR regulation valve 42 is applied in signal pressure DRC, and pipeline pressure PH is carried out pressure regulation, generates supply pressure DR.By
The working oil of the supply pressure DR that DR regulation valve 42 generates is supplied to cylinder body room, DR side 6 via oil circuit 33.DN
Regulation valve 43 is applied in signal pressure DNC, and pipeline pressure PH is carried out pressure regulation, generates supply pressure DN.Adjusted by DN
The working oil of the supply pressure DN that joint valve 43 generates is supplied to cylinder body room, DN side 9 via oil circuit 34.
So, by controlling the turn on angle to DRC, DNC linear solenoid valve 45,46, DR belt wheel 5 is increased and decreased
And the side pressure of DN belt wheel 8, and make the belt wheel change width of DR belt wheel 5 and DN belt wheel 8, thus metal tape 7
Winding radius change.Thereby, it is possible to the gear ratio making the output of electromotor ENG be transferred to driving wheel infinitely becomes
Change.And, based on the control signal exported from control unit 35, to DRC, DNC linear solenoid valve 45,46
Turn on angle be controlled.
Though LCC linear solenoid valve 47 illustrates the most in detail, but guiding valve is made to shift according to the turn on angle to electromagnetic valve, from
By CR valve 44 post-decompression control pressure CR according to turn on angle generate signal pressure LCC, and via oil circuit 56 supply to
LC control valve 49.
The working oil of signal pressure LCC supplied via oil circuit 56 is supplied to LC and switches valve 57 by LC control valve 49.
Though LC switching valve 57 illustrates the most in detail, but by being switched on and off to the energising of electromagnetic valve, controls torque-converters
The locking (connection) of 26 and relieving (cut-out).
So, the working oil of the LCC pressure come from LCC linear solenoid valve 47 supply is used for the control of torque-converters 26.
The joint capacity (slippage) of torque-converters 26 is by adjusting the solenoidal turn on angle of LCC linear solenoid valve 47
Joint.And, based on the control signal exported from control unit 35, the turn on angle of LCC linear solenoid valve 47 is entered
Row controls.
Though CPC linear solenoid valve 48 illustrates the most in detail, but guiding valve is made to shift according to the turn on angle to electromagnetic valve, from
Generated signal pressure CPC corresponding to turn on angle by the post-decompression pressure CR that controls of CR valve 44, and supply via oil circuit 58
Give to hand-operated valve 50.And, based on the control signal exported from control unit 35 to CPC linear solenoid valve 48
Turn on angle is controlled.The operation of not shown gear level is moved by the guiding valve of hand-operated valve 50 by driver.
When gear level be operated to D(advance) shelves time, discharge working oil, and hydraulic pressure from retrogressing brake 25
Being supplied to forward clutch 24, forward clutch 24 is locked (connection).On the other hand, gear level is worked as
Be operated to R(retreat) shelves time, discharge working oil from forward clutch 24, and hydraulic pressure be supplied to retreat
With brake 25, retrogressing brake 25 is locked.So, the signal come from CPC linear solenoid valve 47 supply
The working oil of pressure CPC is used for forward clutch 24 and the locking of retrogressing brake 25, decontrols control.
[DR, DN regulate valve]
Hereinafter, DR, DN regulation valve 42,43 of the embodiment of the hydraulic regulating valve of the present invention is illustrated.
DR, DN regulation valve 42,43 is same structure, therefore, illustrates below as a example by DR regulation valve 42.
It addition, below, also DR is regulated valve 42 referred to as " regulation valve 42 ".
As it is shown on figure 3, regulation valve 42 possess: can in valve body guiding valve (sliding spool valve) 42a of movement；1st bullet
Spring 42b, it is located at right in the figure of guiding valve 42a, and in figure, guiding valve 42a is exerted a force by left all the time；And the 2nd
Spring 42c, it is located at left in the figure of guiding valve 42a, and exerts a force guiding valve 42a the most to the right.
Central part at regulation valve 42 has been formed about grease chamber 42d.Grease chamber 42d is delivery outlet 42e and input port 42f
Connection is got up, and described delivery outlet 42e is connected with the oil circuit 33 being connected to cylinder body room, DR side 6, described input port 42f
It is connected with the oil circuit 51 being connected to PH regulation valve 41.Guiding valve 42a is can (left and right directions in figure) move vertically
Dynamic mode is contained in grease chamber 42d, and is controlled the connection amount of input port 42f and delivery outlet 42e.
In the figure of regulation valve 42, right side is formed with signal pressure chamber 42g.Signal pressure chamber 42g has and is connected to DRC
The signal pressure mouth 42h that the oil circuit 54 of linear solenoid valve 45 is connected.And, the 1st spring 42b is with shorter than natural length
State be configured between the side of sidewall portion of signal pressure chamber 42g and the right sidewall portion of guiding valve 42a.More particularly,
1 spring 42b is configured to the state shorter than natural length, the sidewall of its one end (right-hand end) and signal pressure chamber 42g
Portion abuts, and its other end (left-hand end) abuts with the right sidewall portion of guiding valve 42a.In this embodiment,
The right sidewall portion of guiding valve 42a is made up of the recess caved in the left, and the side face of this recess is formed as and the 1st spring
The outer peripheral face of 42b is fitted together to.
And, regulation valve 42 possess: feedback port 42i, its with from oil circuit 33 branch and midway be provided with throttle orifice
Oil circuit 59 is connected；Leakage fluid dram 42j, it is connected with not shown discharging tube；And outlet 42k, it is used for discharging
Unnecessary working oil in signal pressure chamber 42g.And, the 2nd spring 42c is configured at the state shorter than natural length
The side contrary with signal pressure chamber 42g of grease chamber 42d, here, is configured at the grease chamber 421 being provided with leakage fluid dram 42j
Side of sidewall portion and the left side side of sidewall portion of guiding valve 42a between.More particularly, the 2nd spring 42c is with shorter than natural length
State be configured to, its one end (left-hand end) abuts with the side of sidewall portion of grease chamber 421, and its other end (right-hand end)
Abut with the left side side of sidewall portion of guiding valve 42a.In this embodiment, the left side side of sidewall portion of guiding valve 42a is by the most recessed
The recess fallen into is constituted, and the side face of this recess is formed as chimeric with the outer peripheral face of the 2nd spring 42c.
So, at least 1 in the both sides arm of guiding valve 42a is made up of the recess caved in, and the side face of this recess is with right
The outer peripheral face of the spring answered is fitted together to, therefore, it is possible to reliably keep at least the 1st spring 42b and the 2nd spring 42c
Any one, and, it is made up of the protuberance highlighted with the side of sidewall portion of guiding valve as described in Patent Document 1 and this protuberance
Compared with the structure that outer peripheral face and the inner peripheral surface of spring are chimeric, it can be ensured that the region abutted with valve body of guiding valve 42a and
Realize guiding valve 42a miniaturization in the axial direction, thereby, it is possible to realize regulation valve 42 miniaturization in the axial direction.
It addition, utilize 2 springs 42b, 42c of guiding valve 42a to exert a force to the left and right, though therefore guiding valve 42a by
In the case of being bonded to valve body in impurity such as attritive powders, it is also possible to make guiding valve 42a return to predetermined position.
In the regulation valve 42 so constituted, PH regulation valve 41 pipeline supplied press the working oil of PH via
Grease chamber 42d flows to cylinder body room, DR side 6, but from DRC linear solenoid valve 45 via oil circuit 54 entering signal pressure chamber
Guiding valve 42a is paid active force to the left by the working oil of signal pressure DRC of 42g.Therefore, guiding valve 42a is at this work
Firmly, spring load (active force) P1 to the left and the 2nd spring 42c of the 1st spring 42b to the right
The position of spring load P2 three balance, makes input port 42f connect with delivery outlet 42e.
Thus, the working oil supplied to cylinder body room 6, DR side via oil circuit 33 from delivery outlet 42e is by pressure regulation Cheng Yuxin
Number pressure DRC and corresponding for the spring load difference Δ P control pressure DR of 2 springs 42b, 42c.
So, pipeline, according to signal pressure DRC and spring load difference Δ P, is pressed PH pressure regulation to become to control by regulation valve 42
Pressure DR, and supply to cylinder body room, DR side 6.Therefore, if the spring suitably setting 2 springs 42b, 42c carries
Lotus P1, P2, it becomes possible to carry out pressure regulation to controlling pressure DR relative to signal pressure DRC.
Such as, as shown in the line L1 of Fig. 4, in the feelings that spring load P1, P2 of 2 springs 42b, 42c are identical
Under condition, when signal pressure DRC is 0, guiding valve 42a is positioned at and the connection of delivery outlet 42e and input port 42f is closed
Position (position at guiding valve 42a place in figure 3, below, by this position be referred to as " closed position "), control pressure
DR becomes 0.
And, when signal pressure DRC becomes big, the pressure of the working oil in signal pressure chamber 42g increases, along with this pressure
The increase of power, guiding valve 42a moves to the left.Thus, become big along with signal pressure DRC, control pressure DR and become big.
So, in the case of spring load P1, P2 are identical, when signal pressure DRC is 0, controlling pressure DR is
0, therefore compared with the technology described in above-mentioned patent documentation 1, it is possible to reduce pipeline pressure PH.Thus, it is possible to reduction liquid
The driving torque of press pump 31, it is possible to increase the efficiency of variable v-belt drive 1.It addition, when input signal presses DRC
Time, guiding valve 42a moves at once, and therefore response is sharp, and span of control also becomes big.
As shown in the line L2 of Fig. 4, at the spring load P1 of the 1st spring 42b spring load than the 2nd spring 42c
In the case of P2 is big, even if signal pressure DRC is 0, due to the spring load difference Δ P that guiding valve 42a is exerted a force to the left,
Guiding valve 42a is positioned at the position than the closed position side of keeping left, and therefore controls pressure DR and will not become 0, but has predetermined
Minimal pressure DR0.
And, when signal pressure DRC becomes big, the pressure of the working oil in signal pressure chamber 42g increases, along with this pressure
The increase of power, guiding valve 42a moves the most to the left.Thus, become big along with signal pressure DRC, control pressure DR
Become big.
So, in the case of spring load P1 is bigger than spring load P2, it is possible to obtain having with at above-mentioned patent literary composition
Offer the regulation valve of the identical response of the regulation valve described in 1.And, by making the combination of spring load P1, P2
Different, it is possible to realize the response that change is abundant.Thereby, it is possible to reduce pipeline pressure PH, therefore, it is possible to reduce hydraulic pressure
The driving torque of pump 31, additionally it is possible to improve the efficiency of variable v-belt drive 1.
On the other hand, as shown in the line L3 of Fig. 4, at the spring load P1 of the 1st spring 42b than the 2nd spring 42c
Spring load P2 little in the case of, when signal pressure DRC is little, due to the spring that guiding valve 42a is exerted a force to the right
Load difference Δ P, guiding valve 42a is positioned at closed position, therefore controls pressure DR and becomes 0.
And, when signal pressure DRC exceedes threshold DR C0, guiding valve 42a moves to the left, produces and controls pressure DR.
Then, become big along with signal pressure DRC, control pressure DR and become big.
So, in the case of spring load P1 is less than spring load P2, until signal pressure DRC exceedes threshold value
DRC0, controlling pressure DR is all 0, compared with the technology described in above-mentioned patent documentation 1, it is possible to reduce pipeline pressure PH.
Thus, it is possible to reduce the driving torque of hydraulic pump 31, it is possible to increase the efficiency of variable v-belt drive 1.
It addition, in this case, even if controlling pressure DR is 0, also by the 1st spring 42b to the left to guiding valve 42a
Force.Therefore, even if in the case of guiding valve 42a is bonded to valve body due to impurity such as attritive powders, working as signal pressure
When DRC exceedes threshold DR C0, it is also possible to release set at once, guiding valve 42a is made to move to the left.
Above, referring to the drawings embodiments of the present invention are illustrated, but the invention is not restricted to this.Such as, right
Hydraulic control circuit 40 is illustrated.But, the hydraulic control circuit with regulation valve of the present invention is not limited to liquid
Voltage-controlled loop processed 40, as long as controlling variable v-belt drive 1 iso-variable velocity device, other hydraulic control
Loop, then comprise arbitrary hydraulic control circuit.
It addition, variable v-belt drive 1 is illustrated.But, the belt continuous variable possessing regulation valve of the present invention
Variator is not limited to variable v-belt drive 1, it is also possible to be variable v-belt drive known to other.
Claims (1)
1. a hydraulic regulating valve, it is characterised in that possess:
Grease chamber, the delivery outlet of its input port and the hydraulic pressure after supply pressure regulation of being supplied to hydraulic pressure connects；
Guiding valve, it is being contained in the way of being axially moveable in described grease chamber, and controls described input port with described
The connection amount of delivery outlet；
Signal pressure chamber, it has the signal pressure mouth being supplied to signal pressure；
1st spring, it is configured at described signal pressure chamber, and exerts a force described guiding valve to the direction that described connection amount increases；
With
2nd spring, it is configured at the side contrary with described signal pressure chamber of described grease chamber, and subtracts to described connection amount
Described guiding valve is exerted a force by few direction,
The spring load of described 1st spring is less than the spring load of described 2nd spring, when described signal pressure is predetermined
Time below threshold value, owing to the spring load of described 1st spring is poor with the load of the spring load of described 2nd spring, institute
State guiding valve and be positioned at the closed position connection of described input port with described delivery outlet closed, control buckling and become 0, work as institute
Stating signal pressure when exceeding described predetermined threshold value, described guiding valve moves, and produces and described controls pressure, hereafter, along with letter
Number buckling is big, controls buckling big.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013029522A JP6405079B2 (en) | 2013-02-18 | 2013-02-18 | Hydraulic control circuit |
| JP2013-029522 | 2013-02-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103994218A CN103994218A (en) | 2014-08-20 |
| CN103994218B true CN103994218B (en) | 2017-01-11 |
Family
ID=51308475
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410045570.2A Active CN103994218B (en) | 2013-02-18 | 2014-02-08 | Hydraulic regulating valve |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6405079B2 (en) |
| CN (1) | CN103994218B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6397295B2 (en) * | 2014-09-29 | 2018-09-26 | 株式会社Ｓｕｂａｒｕ | Hydraulic circuit device |
| JP2017053397A (en) * | 2015-09-08 | 2017-03-16 | 日本電産トーソク株式会社 | Hydraulic control system |
| JP2020051623A (en) * | 2019-12-16 | 2020-04-02 | 日本電産トーソク株式会社 | Hydraulic control system |
| CN117450251B (en) * | 2023-12-25 | 2024-05-14 | 中国第一汽车股份有限公司 | Transmission hydraulic system and vehicle |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1491329A (en) * | 2001-11-09 | 2004-04-21 | ���＼�й�ҵ��ʽ���� | Hydraulic valve |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06288470A (en) * | 1993-03-31 | 1994-10-11 | Toyota Motor Corp | Hydraulic control device for vehicular automatic transmission |
| US5509448A (en) * | 1994-11-15 | 1996-04-23 | General Motors Corporation | Control valve with integral accumulator |
| DE19721036B4 (en) * | 1996-05-24 | 2006-09-14 | Luk Gs Verwaltungs Kg | Control valve for a vehicle with a pressure medium system |
| US5908098A (en) * | 1997-12-12 | 1999-06-01 | General Motors Corporation | Regulating valve for engagement control of friction drive devices |
| US6155949A (en) * | 1999-06-14 | 2000-12-05 | General Motors Corporation | Multiple gain trim valve for a selectively engageable friction device |
| US20080182709A1 (en) * | 2007-01-29 | 2008-07-31 | Gm Global Technology Operations, Inc. | Valve configuration for a lubrication circuit of a latched pump applied clutch transmission |
| WO2011021421A1 (en) * | 2009-08-21 | 2011-02-24 | 本田技研工業株式会社 | Hydraulic control device |
-
2013
- 2013-02-18 JP JP2013029522A patent/JP6405079B2/en not_active Expired - Fee Related
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2014
- 2014-02-08 CN CN201410045570.2A patent/CN103994218B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1491329A (en) * | 2001-11-09 | 2004-04-21 | ���＼�й�ҵ��ʽ���� | Hydraulic valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103994218A (en) | 2014-08-20 |
| JP2014156925A (en) | 2014-08-28 |
| JP6405079B2 (en) | 2018-10-17 |
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