CN105221737A - A kind of plunger hydraulic shift control mechanism - Google Patents
A kind of plunger hydraulic shift control mechanism Download PDFInfo
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- CN105221737A CN105221737A CN201510721706.1A CN201510721706A CN105221737A CN 105221737 A CN105221737 A CN 105221737A CN 201510721706 A CN201510721706 A CN 201510721706A CN 105221737 A CN105221737 A CN 105221737A
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- chamber
- valve body
- piston rod
- control mechanism
- shift control
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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
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
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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
- F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
- F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
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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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid 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
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
- F16H2061/301—Hydraulic or pneumatic motors or related fluid control means therefor for power assistance, i.e. servos with follow up action
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Gear-Shifting Mechanisms (AREA)
Abstract
The present invention relates to a kind of plunger hydraulic shift control mechanism, comprise gearshift cylinder and two power assisted gearshift cylinders, gearshift cylinder comprises upper valve body (14), middle valve body (22) and lower valve body (1), lower valve body (1) is provided with the first chamber (F), the second chamber (B), the 3rd chamber (R) and the 4th chamber (L) four chambers, first chamber (F) is connected a power assisted gearshift cylinder with the second chamber (B), and the 3rd chamber (R) is connected another power assisted gearshift cylinder with the 4th chamber (L).Be provided with first piston bar (2), the second piston rod (30), the 3rd piston rod (34) and the 4th piston rod (35) in lower valve body (1), first piston bar (2) is identical with the length of the second piston rod (30); 3rd piston rod (34) is identical with the length of the 4th piston rod (35), adds comfortable feel and the symmetry properties of gear.Be equipped with double-way check valve (I) in gearshift cylinder, make corresponding chambers produce the function of supercharging, decompression smoothly.
Description
Technical field
The present invention relates to heavy vehicle gearshift technical field, in particular to a kind of plunger hydraulic shift control mechanism.
Background technique
The heavy vehicles such as existing truck generally adopt mechanical type shifting system to shift gears, and mechanical type shifting system, due to vibrations and zip fracture, easily causes gear to jump tooth and engage a gear difficulty, the shortcomings such as noise is large, therefore adopts mechanical type shifting system comparatively unstable; If adopt hydraulic type shifting system to put into gear comparatively stable, because the tonnage of truck is comparatively large, hydraulic type shifting system is for comparatively light during heavy vehicle gearshift, and can accomplish engage a gear and gearbox gear-shift synchronously, noise reduces, and greatly reduces the working strength of driver.And maintain and replace is simple, the features such as cost is light.But mechanical type shifting system is used for the heavy vehicles such as truck, then need gear to be hung up with larger labor intensity, maintenance more complicated, it is very inconvenient to regulate.
Such as Authorization Notice No. is the Chinese utility model patent of CN204127298U, it discloses a kind of truck hydraulic gear-shifting system, this model utility comprises gearshift cylinder and two power assisted gearshift cylinders, gearshift cylinder comprises gearshift cylinder body, and gearshift cylinder body is provided with four piston/cylinder inner chambers, wears piston cylinder in each piston/cylinder inner chamber, the upper end of piston/cylinder inner chamber is coordinated with piston cylinder by seal ring, piston cylinder upper end arranges push rod, and push rod is connected by pusher bar support, and pusher bar support is connected with gear level; Each piston/cylinder inner chamber sidepiece is provided with the through hole through with piston/cylinder inner chamber, is connected with hydraulic tube in through hole; Each power assisted gearshift cylinder is provided with two through holes, is provided with piston in power assisted gearshift cylinder inner chamber, and four hydraulic tube the other ends are connected on two through holes, and piston and truck gearbox are connected.This model utility make use of the principle of lever, by arranging longer hydraulic tube, can promote gearshift cylinder, realize the gears meshing work in gearbox with less active force, shift gears easy, manipulation strength is low.Although each power assisted gearshift cylinder is provided with two through holes, two through holes are positioned at one end of servo-cylinder, and the pressure in such cylinder body can not get balance, thus has influence on the supercharging of each chamber and the function of decompression; Adopt seal ring to seal in power assisted gearshift cylinder, wear resistance is poor.
Summary of the invention
In order to solve the above-mentioned technological deficiency that prior art exists, the object of the present invention is to provide a kind of plunger hydraulic shift control mechanism, by arranging double-way check valve in each power assisted gearshift cylinder, making corresponding chamber produce the function of supercharging, decompression.
In order to realize above-mentioned purpose of design, the scheme that the present invention adopts is as follows:
A kind of plunger hydraulic shift control mechanism, comprise gearshift cylinder and two power assisted gearshift cylinders, described gearshift cylinder comprises upper valve body, middle valve body and lower valve body, the bottom of lower valve body is provided with the first chamber, the second chamber, the 3rd chamber and the 4th chamber four chambers, first chamber F is connected a power assisted gearshift cylinder with the second chamber, and the 3rd chamber is connected another power assisted gearshift cylinder with the 4th chamber; First chamber is for moving back gear chamber, second chamber is for entering to keep off chamber, be provided with first piston bar, the second piston rod, the 3rd piston rod and the 4th piston rod in described lower valve body, first piston bar is identical with the length of the second piston rod, and the 3rd piston rod is identical with the length of the 4th piston rod; Double-way check valve is equipped with in gearshift cylinder.First piston bar is identical with the length of the second piston rod, the 3rd piston rod is identical with the length of the 4th piston rod, adds comfortable feel and the symmetry properties of gear.Be equipped with double-way check valve in gearshift cylinder, make corresponding chambers produce the function of supercharging, decompression smoothly.
Preferably, the top of described upper valve body is provided with operating handle.
In above-mentioned either a program preferably, the top of described lower valve body is provided with protective housing.
In above-mentioned either a program preferably, in described upper valve body, have cavity, in this cavity, be provided with vertical pin and horizontal pin.
In above-mentioned either a program preferably, the outer cover of described vertical pin has gear pedestal, gear seat and spring.
In above-mentioned either a program preferably, the lower end abutment of described vertical pin is on lower gear seat.
In above-mentioned either a program preferably, one end of described horizontal pin is positioned at gear pedestal; The horizontal pin the other end is positioned at the lower end of upper valve body.
In above-mentioned either a program preferably, the joint of described horizontal pin and upper valve body is provided with flange bearing.
In above-mentioned either a program preferably, be provided with connecting rod in described upper valve body, the two ends of connecting rod are spherical in shape.
In above-mentioned either a program preferably, one end of described connecting rod is fixed on the shoulder of upper valve body, and the other end of connecting rod is resisted against the top of piston rod.
In above-mentioned either a program preferably, spring sheet is provided with between described connecting rod and piston rod and ball is buckled.
In above-mentioned either a program preferably, described first piston bar, be provided with between the 3rd piston rod and lower valve body that the one 0 shape is enclosed, first piston, the first Y-shaped ring, the 2nd O shape are enclosed, the second piston, the second Y-shaped ring and piston pressing plate.
In above-mentioned either a program preferably, described second piston rod, be provided with the second piston pressing plate, the 3rd piston, the 3rd Y-shaped ring, the 4th Y-shaped ring and the 4th piston between the 4th piston rod and lower valve body.
In above-mentioned either a program preferably, the lower end of described lower gear seat is provided with reserve, and this reserve is divided into upper and lower two regions, by the 3rd seal with O ring between upper and lower two regions.
In above-mentioned either a program preferably, the lower end of described reserve is provided with star washer and filter screen.
In above-mentioned either a program preferably, be provided with out beam hanger in described reserve, the middle part going out beam hanger has through hole; The lower end going out beam hanger is provided with the 4th O shape circle.
In above-mentioned either a program preferably, the lower end going out beam hanger described in has a passage and is communicated with lubricating cup assembly.
In above-mentioned either a program preferably, described passage and lubricating cup assembly connection part are provided with connecting sleeve.
In above-mentioned either a program preferably, the top of described lubricating cup assembly is with filler opening, and filler opening is provided with protective hat.
In above-mentioned either a program preferably, described double-way check valve is positioned at the bottom of lower valve body; Double-way check valve comprises check valve body.
In above-mentioned either a program preferably, the joint of described check valve body and lower valve body is provided with the 5th O shape and encloses and the 6th O shape is enclosed.
In above-mentioned either a program preferably, steel ball, straight pin, the first check valve spring, the 7th O shape circle, one-way valve sealing column, the second check valve spring and hole back-up ring is provided with in described check valve body.
In above-mentioned either a program preferably, described steel ball is resisted against on the second check valve spring.
In above-mentioned either a program preferably, the inlet of described hole back-up ring is provided with filter screen.
In above-mentioned either a program preferably, when the second chamber builds pressure, the top place that driver promotes operating handle swings to B1, B2 angle direction, promoting connecting rod makes the second piston rod move downward along the second piston pressing plate and the 3rd piston axis direction, the volume of the second chamber reduces, hydraulic oil is squeezed and makes each point of the second chamber produce pressure, and oil pressure continues to walk downwards; Hydraulic oil acts on the end face of steel ball and one-way valve sealing column through filter screen, and one-way valve sealing column and steel ball produce displacement left, until with the end contact of check valve body after just no longer move; Hydraulic oil continues to export to the delivery outlet of the second chamber, and the system of meeting builds the needs of pressure, makes down-stream system complete gear shift operation, and now due to the needs of down-stream system, this operating mechanism can complete the pressure foundation that B1 gear and B2 keep off two gears.
In above-mentioned either a program preferably, when the second chamber builds pressure, the moving back gear chamber and the pressure in this chamber will be cut of the power assisted gearshift cylinder in downstream, steel ball in the check valve body of the second chamber moves to right building pressure, one-way valve sealing column props up check valve body, now, the second chamber, downstream power assisted gearshift cylinder enter to keep off chamber, move back gear chamber and the first chamber F all establish pressure; First piston bar moves release pressure, and now whole hydraulic gear-shifting system is in sealed vacuum state, and the first chamber communicates with the fuel reserve tank of lubricating cup assembly, to reach the object that be communicated with of short duration in air; First chamber and air are connected, and the pressure of the first chamber is not in vacuum state, move on first piston bar is unresisted, and the pressure of the first chamber cuts.
Accompanying drawing explanation
Fig. 1 is the structural representation of the preferred embodiment according to plunger hydraulic shift control mechanism of the present invention.
Fig. 2 is the side sectional view embodiment illustrated in fig. 1 according to plunger hydraulic shift control mechanism of the present invention.
Fig. 3 is the working state figure embodiment illustrated in fig. 1 according to plunger hydraulic shift control mechanism of the present invention.
Fig. 4 is the embodiment illustrated in fig. 3 middle II place enlarged view according to plunger hydraulic shift control mechanism of the present invention.
Fig. 5 is the polycrystalline substance schematic diagram embodiment illustrated in fig. 1 according to plunger hydraulic shift control mechanism of the present invention.
Fig. 6 is the sectional view of the embodiment illustrated in fig. 1 middle double-way check valve according to plunger hydraulic shift control mechanism of the present invention.
Fig. 7 is the phase diagram be moved to the left according to the embodiment illustrated in fig. 1 middle double-way check valve of plunger hydraulic shift control mechanism of the present invention.
Fig. 8 is the phase diagram moved right according to the embodiment illustrated in fig. 1 middle double-way check valve of plunger hydraulic shift control mechanism of the present invention.
Embodiment
The following description is only exemplary and be not to limit the disclosure, application or purposes in essence.Be further described below in conjunction with the embodiment of Figure of description to plunger hydraulic shift control mechanism of the present invention.
As shown in Figure 1-Figure 3, according to the structural representation of plunger hydraulic shift control mechanism of the present invention.A kind of plunger hydraulic shift control mechanism, comprise gearshift cylinder and two power assisted gearshift cylinders, described gearshift cylinder comprises upper valve body 14, middle valve body 22 and lower valve body 1, the bottom of lower valve body 1 is provided with the first chamber F, the second chamber B, the 3rd chamber R and the 4th chamber L tetra-chambers, first chamber F is connected a power assisted gearshift cylinder with the second chamber B, and the 3rd chamber R is connected another power assisted gearshift cylinder with the 4th chamber L; First chamber F is for moving back gear chamber, second chamber B is for entering to keep off chamber, first piston bar 2, second piston rod 30, the 3rd piston rod 34 and the 4th piston rod 35 is provided with in described lower valve body 1, first piston bar 2 is identical with the length of the second piston rod 30, and the 3rd piston rod 34 is identical with the length of the 4th piston rod 35; Double-way check valve I is equipped with in gearshift cylinder.First piston bar 2 is identical with the length of the second piston rod 30, the 3rd piston rod 34 is identical with the length of the 4th piston rod 35, adds comfortable feel and the symmetry properties of gear.Be equipped with double-way check valve I in gearshift cylinder, make corresponding chambers produce the function of supercharging, decompression smoothly.
First piston bar 2 is major diameter bar, the second piston rod 30 is smaller diameter rods, the 3rd piston rod 34 is major diameter bar, the 4th piston rod 35 is smaller diameter rods.
In the present embodiment, the top of described upper valve body 14 is provided with operating handle a.
When operating handle a swings to B2 gear, when namely the centerlines of operating handle a and upper valve body 14 is 375 °, the lower end of first piston bar 2 arrives h1 position; Swing to B1 angle at operating handle a, when namely the centerlines of operating handle a and upper valve body 14 is 21 °, the lower end of first piston bar 2 arrives h2 position, and the second piston rod 30 arrives h3 position; When operating handle a swings to B1 gear, when namely the centerlines of operating handle a and upper valve body 14 is 375 °, the lower end of first piston bar 2 arrives h1 position, the second piston rod 30 h4 position on earth.
In the present embodiment, the top of described lower valve body 1 is provided with protective housing 15.
In the present embodiment, in described upper valve body 14, have cavity, in this cavity, be provided with vertical pin 16 and horizontal pin 18.
In the present embodiment, the outer cover of described vertical pin 16 has gear pedestal 17, gear seat 20 and spring.
In the present embodiment, the lower end abutment of described vertical pin 16 is on lower gear seat 21.
In the present embodiment, one end of described horizontal pin 18 is positioned at gear pedestal 17; Horizontal pin 18 the other end is positioned at the lower end of upper valve body 14.When R gear, L keep off work, around Fig. 1 place, horizontal straight pin 18 rotates; When F gear, B keep off work, around Fig. 2 place, horizontal straight pin 18 rotates.
In the present embodiment, described horizontal pin 18 is provided with flange bearing 19 with the joint of upper valve body 14.
In the present embodiment, be provided with connecting rod 13 in described upper valve body 14, the two ends of connecting rod 13 are spherical in shape.
In the present embodiment, one end of described connecting rod 13 is fixed on the shoulder of upper valve body 14, and the other end of connecting rod 13 is resisted against the top of piston rod.
In the present embodiment, spring sheet 10 is provided with between described connecting rod 13 and piston rod and ball buckles 11.
In the present embodiment, described first piston bar 2, be provided with between the 3rd piston rod 34 and lower valve body 1 that the one 0 shape encloses 3, first piston 4, first Y-shaped ring 5, the 2nd O shape enclose the 6, second piston 7, second Y-shaped ring 8 and piston pressing plate 9.
In the present embodiment, described second piston rod 30, be provided with the second piston pressing plate 23, the 3rd piston 24, the 3rd Y-shaped ring 25, the 4th Y-shaped ring 26 and the 4th piston 27 between the 4th piston rod 35 and lower valve body 1.
In the present embodiment, the lower end of described lower gear seat 21 is provided with reserve, and this reserve is divided into upper and lower two regions, by the 3rd O shape circle 12 sealing between upper and lower two regions.
In the present embodiment, the lower end of described reserve is provided with star washer 28 and filter screen 29.
In the present embodiment, be provided with out beam hanger 36 in described reserve, the middle part going out beam hanger 36 has through hole; The lower end going out beam hanger 36 is provided with the 4th O shape circle 37.
As shown in Figure 5, in the present embodiment, the lower end going out beam hanger 36 described in has a passage and is communicated with lubricating cup assembly 39.
In the present embodiment, described passage and lubricating cup assembly 39 connection part are provided with connecting sleeve 38.
In the present embodiment, the top of described lubricating cup assembly 39 is with filler opening, and filler opening is provided with protective hat 40.Because dust cap 40 does not seal completely itself, but there is certain gap identical with air, so the hydraulic oil of the first chamber F can communicate with air, relieve the vacuum state in F chamber.
Next consult shown in Fig. 1, Fig. 3, Fig. 6, describe the process of build-up pressure when shifting system enters to keep off.
When the second chamber B builds pressure, driver promotes the top place of operating handle a to B1, B2 angle direction, now upper valve body 14, vertical straight pin 16, gear pedestal 17 each other Integral synchronous rotate (straight pin 1 totally 4 around horizontal straight pin 18, now 2 straight pins rotations in Fig. 2 view), promote connecting rod 13 and second piston rod 30 is moved downward along the second piston pressing plate 23 and the 4th piston 24 axial direction.
Now the shoe cream room of the second chamber B reduces the volume of the second chamber B due to moving downward of first piston bar 2, hydraulic oil makes each point of whole second chamber B produce pressure owing to being squeezed, because O shape circle the 3, a 4th Y shape circle 26 serves the effect of sealing, so oil pressure continues to walk downwards.As shown in Figure 5, hydraulic oil acts on the end face of steel ball 42 and one-way valve sealing column 47 through filter screen 29, because the pressure acting on one-way valve sealing column 47 end face is greater than the spring force of the first check valve spring 44, so one-way valve sealing column 47 and steel ball 42 produce displacement left, until with the end contact of check valve body 50 after move (now double-way check valve assembly second chamber B has worked) with regard to no longer carrying out, as shown in Figure 5.Now the second piston rod 30 promotes hydraulic oil and the hydraulic coupling that produces in one-way valve place constricted flow owing to moving down, so the delivery outlet continued to the second chamber B outputs, the system of meeting builds the needs of pressure, makes down-stream system complete gear shift operation.Now due to the needs of down-stream system, this operating mechanism can complete B1 gear and B2 keep off two gears pressure set up.
As shown in Figure 3, the power assisted gearshift cylinder in this shift control mechanism downstream is all full of hydraulic oil before operation too in product and pipeline, while B gear carries out building pressure, moving back gear chamber and the pressure in this chamber will being cut of the power assisted gearshift cylinder in downstream, can ensure that downstream power assisted gearshift piston moves forward.
As shown in Figure 6, the process of release pressure when shifting system plucks gear.
The one-way valve steel ball 42 of the second chamber B moves to right building pressure, and one-way valve sealing column 47 props up check valve body 50, now, and the entering to keep off chamber, move back gear chamber and the first chamber F establishes pressure of the second chamber B, downstream power assisted gearshift cylinder.The feature of this hydraulic gear-shifting operating mechanism is, the second piston rod 30 wants to move down build-up pressure, first piston bar 2 must on move release pressure.Now whole hydraulic gear-shifting system is in sealed vacuum state, want to make first piston bar 2 moves, the first chamber F must be made to communicate with the fuel reserve tank of lubricating cup assembly 39, to reach the object that be communicated with of short duration in air, as long as the first chamber F and air are connected, the pressure of the first chamber F is not just in vacuum state, first piston bar 2 just can unresisted on move.
The following describes, F chamber be in equally build pressure condition time, how to communicate with air:
When second piston rod 30 of the second chamber B starts to build pressure, the second chamber part B of double-way check valve I is first started working, and state as shown in Figure 5.Now steel ball 42 and one-way valve sealing column 47 produce and seal, and the hydraulic oil of the second chamber B can not be flowed in lubricating cup assembly 39 and the first chamber F by double-way check valve I.As shown in Figure 7, when the first chamber F produces pressure by the power assisted gearshift cylinder in downstream, oil pressure acts on one-way valve sealing column 47 surface and produces pressure in the first chamber chamber, overcome the spring force of the first check valve spring 44 and move right, one-way valve sealing column 47 is made to prop up check valve body 50, the X2 size vanishing now in Fig. 5.Meanwhile steel ball 42 is under the spring-force driven dual of the second check valve spring 48, props up straight pin 43, now the vanishing of X1 size.Oil return gap X3(is to produced as Fig. 7) because X2 is greater than X1, the hydraulic oil of the second chamber F is communicated with the hydraulic oil inside lubricating cup assembly 39 by this oil return gap, because dust cap 40 does not seal completely itself, but have certain gap identical with air, so the hydraulic oil of the first chamber F can communicate with air, relieve the vacuum state in F chamber, first piston bar 2 is continued to move up, under second piston rod 30 of the second chamber B acts on, power assisted gearshift cylinder piston (shown in Fig. 6) has been moved to the left corresponding actions.When gear is in F1 gear, the oil-return groove of first piston bar 2 and the seal lip place of the first Y-shaped ring 5 produce an oil return gap X4(as shown in Figure 8), the hydraulic oil of the first chamber F the spill port of gap from this gap, between first piston bar 2 and the second piston 7 and the second piston 7 can be back to lubricating cup, now enters gear process and terminates.Shift handle onto F1 when to move back grade to keep off, its principle is identical with the principle that B1 keeps off.
Same principle, also can realize the R gear shown in Fig. 2 and L gear.When operating handle a swings to R2 gear, namely the centerlines of operating handle a and upper valve body 14 is 24 °; Swing to R1 angle at operating handle a, namely the centerlines of operating handle a and upper valve body 14 is 11 °; When operating handle a swings to L gear, namely the centerlines of operating handle a and upper valve body 14 is 24 °.
In the present embodiment, described double-way check valve I is positioned at the bottom of lower valve body 1; Double-way check valve I comprises check valve body 50.Lower valve body 1 is provided with oil return cup liquid storage cylinder, thus hydraulic oil is got back in oil return cup.
In the present embodiment, described check valve body 50 and the joint of lower valve body 1 be provided with the 5th O shape enclose 41 and the 6th O shape enclose 45.
In the present embodiment, steel ball 42, straight pin 43, first check valve spring 44, the 7th O shape circle 46, one-way valve sealing column 47, second check valve spring 48 and hole back-up ring 49 is provided with in described check valve body 50.
In the present embodiment, described steel ball 42 is resisted against on the second check valve spring 48.
In the present embodiment, the inlet of described hole back-up ring 49 is provided with filter screen 29, thus ensure that product normally works.
Plunger hydraulic Gear shift operation mechanism of the present invention has the following advantages:
The first, working medium is hydraulic oil, compares air inflated structure, specific product volume is little, the transmission of power fast, feature accurately;
The second, adopt plunger-type structure, piston does not directly contact with steel body inwall, reduces the processing cost of cylinder body, too increases life of product simultaneously;
Three, adopt hydraulic structure to compare pneumatic structure, when discharging internal pressure, compare pneumatic structure, dry sound is little, does not almost have sound;
Four, double-way check valve inside adopts stainless steel steel ball sealing, has feature that is corrosion-resistant, that increase the service life;
Five, double-way check valve utilizes the design of pressure balance principle, and corresponding chamber can be made smoothly to produce the work function increasing, reduce pressure;
Six, enter gear, with move back the design that gear two chamber adopts the plunger diameter of two kinds of different-diameters, make in gear shifting action operating process, produce difference in flow, be conducive to gearshift carry out smoothly.As: entering to keep off what adopt when chamber B builds pressure is the piston of minor diameter, move back gear chamber F and adopt large diameter piston, when the piston of such first chamber F and the second chamber B produces displacement at the same time, due to the first chamber F diameter more greatly, compare during same displacement the second chamber B less plug can abdicate larger space, can make like this piston displacement of the second chamber B more smooth and easy (this require according to customer requirement and design);
Seven, in order to ensure the clean of interiors of products working medium, both increasing filter screen design 5 key points, ensure that product normally works;
Eight, each piston both increases the design of oil-return groove, and the Position Design of oil-return groove accurately, rationally;
Nine, as shown in Figure 5, the Precise spraying of X2, X1 size is the key producing oil return gap X3 as shown in Figure 7.
It will be apparent to those skilled in the art that plunger hydraulic shift control mechanism of the present invention comprises the combination in any of each several part in this specification.As space is limited and in order to make specification simple and clear, these combinations are not introduced one by one in detail at this, but after having seen this specification, the scope of the present invention that the combination in any of each several part be made up of this specification is formed is self-evident.
Claims (10)
1. a plunger hydraulic shift control mechanism, comprise gearshift cylinder and two power assisted gearshift cylinders, described gearshift cylinder comprises upper valve body (14), middle valve body (22) and lower valve body (1), the bottom of lower valve body (1) is provided with the first chamber (F), the second chamber (B), the 3rd chamber (R) and the 4th chamber (L) four chambers, first chamber (F) is connected a power assisted gearshift cylinder with the second chamber (B), and the 3rd chamber (R) is connected another power assisted gearshift cylinder with the 4th chamber (L); First chamber (F) is for moving back gear chamber, second chamber (B) is for entering to keep off chamber, it is characterized in that: in lower valve body (1), be provided with first piston bar (2), the second piston rod (30), the 3rd piston rod (34) and the 4th piston rod (35), first piston bar (2) is identical with the length of the second piston rod (30), and the 3rd piston rod (34) is identical with the length of the 4th piston rod (35); Double-way check valve (I) is equipped with in gearshift cylinder.
2. plunger hydraulic shift control mechanism as claimed in claim 1, is characterized in that: the top of upper valve body (14) is provided with operating handle (a).
3. plunger hydraulic shift control mechanism as claimed in claim 1, is characterized in that: the top of lower valve body (1) is provided with protective housing (15).
4. plunger hydraulic shift control mechanism as claimed in claim 1, is characterized in that: upper valve body has cavity in (14), is provided with vertical pin (16) and horizontal pin (18) in this cavity.
5. plunger hydraulic shift control mechanism as claimed in claim 4, is characterized in that: the outer cover of vertical pin (16) has gear pedestal (17), gear seat (20) and spring.
6. plunger hydraulic shift control mechanism as claimed in claim 4, is characterized in that: the lower end abutment of vertical pin (16) is on lower gear seat (21).
7. plunger hydraulic shift control mechanism as claimed in claim 4, is characterized in that: one end of horizontal pin (18) is positioned at gear pedestal (17); Horizontal pin (18) the other end is positioned at the lower end of upper valve body (14).
8. plunger hydraulic shift control mechanism as claimed in claim 4, is characterized in that: horizontal pin (18) is provided with flange bearing (19) with the joint of upper valve body (14).
9. plunger hydraulic shift control mechanism as claimed in claim 1, it is characterized in that: be provided with connecting rod (13) in upper valve body (14), the two ends of connecting rod (13) are spherical in shape.
10. plunger hydraulic shift control mechanism as claimed in claim 9, it is characterized in that: one end of connecting rod (13) is fixed on the shoulder of upper valve body (14), the other end of connecting rod (13) is resisted against the top of piston rod.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510721706.1A CN105221737A (en) | 2015-08-10 | 2015-10-30 | A kind of plunger hydraulic shift control mechanism |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2015104849002 | 2015-08-10 | ||
| CN201510484900 | 2015-08-10 | ||
| CN201510721706.1A CN105221737A (en) | 2015-08-10 | 2015-10-30 | A kind of plunger hydraulic shift control mechanism |
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| CN105221737A true CN105221737A (en) | 2016-01-06 |
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| CN201510721706.1A Pending CN105221737A (en) | 2015-08-10 | 2015-10-30 | A kind of plunger hydraulic shift control mechanism |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4074531A (en) * | 1974-03-08 | 1978-02-21 | Lamborghini Oleodinamica S.P.A. | Oleodynamic servo control |
| FR2545160A1 (en) * | 1983-04-26 | 1984-11-02 | Lalanne Jean Claude | Safety hydraulic-control device for a gearbox |
| CN2648150Y (en) * | 2003-03-26 | 2004-10-13 | 中国第一汽车集团公司 | Gearshifting oil cylinder |
| CN201137692Y (en) * | 2007-11-08 | 2008-10-22 | 彪马集团浙江汽车研究院有限公司 | Integral shifting operation device for speed variator |
| CN204127298U (en) * | 2014-08-27 | 2015-01-28 | 绍兴市嘉坤汽车配件有限公司 | Truck hydraulic gear-shifting system |
| CN205118222U (en) * | 2015-08-10 | 2016-03-30 | 瑞立集团瑞安汽车零部件有限公司 | Plunger type hydraulic pressure operating mechanism that shifts |
-
2015
- 2015-10-30 CN CN201510721706.1A patent/CN105221737A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4074531A (en) * | 1974-03-08 | 1978-02-21 | Lamborghini Oleodinamica S.P.A. | Oleodynamic servo control |
| FR2545160A1 (en) * | 1983-04-26 | 1984-11-02 | Lalanne Jean Claude | Safety hydraulic-control device for a gearbox |
| CN2648150Y (en) * | 2003-03-26 | 2004-10-13 | 中国第一汽车集团公司 | Gearshifting oil cylinder |
| CN201137692Y (en) * | 2007-11-08 | 2008-10-22 | 彪马集团浙江汽车研究院有限公司 | Integral shifting operation device for speed variator |
| CN204127298U (en) * | 2014-08-27 | 2015-01-28 | 绍兴市嘉坤汽车配件有限公司 | Truck hydraulic gear-shifting system |
| CN205118222U (en) * | 2015-08-10 | 2016-03-30 | 瑞立集团瑞安汽车零部件有限公司 | Plunger type hydraulic pressure operating mechanism that shifts |
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Application publication date: 20160106 |