CN103696822A - Driver with hydraulic tappet - Google Patents
Driver with hydraulic tappet Download PDFInfo
- Publication number
- CN103696822A CN103696822A CN201310712877.9A CN201310712877A CN103696822A CN 103696822 A CN103696822 A CN 103696822A CN 201310712877 A CN201310712877 A CN 201310712877A CN 103696822 A CN103696822 A CN 103696822A
- Authority
- CN
- China
- Prior art keywords
- tappet
- piston
- driver
- valve
- hydraulic tappet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Abstract
The invention discloses a driver with a hydraulic tappet. The driver comprises a driver shell, a driving cylinder, a first piston, a second piston, a piston rod and the hydraulic tappet, wherein the hydraulic tappet further comprises a tappet plunger, a tappet body, a tappet high-pressure chamber, a tappet inflow channel, a discharge channel, a tappet one-way valve and a plunger return spring. The hydraulic tappet is optimized in design, and the driver with the hydraulic tappet has comprehensive advantages in terms of spatial size, high-pressure chamber pressure and cost, and is particularly applicable to valve clearance control of a variable valve driver. The hydraulic tappet is combined among the wall of the driving cylinder and the two pistons of the driver, the tappet body includes a tappet body end and a tappet body wall, the first piston serves as the tappet body end, the wall of the driving cylinder serves as the tappet body wall, so that the tappet high-pressure chamber can have a diameter as large as that of the driving cylinder to reduce the internal high pressure of the tappet high-pressure chamber, a normal air distribution function, low noise and reasonable service life are ensured, an additional tappet body wall structure and an additional high-precision matching structure are omitted, and manufacturing cost is reduced.
Description
Technical field
The invention relates to a kind of control technique of driving machine, and particularly relevant for a kind of driver with hydraulic tappet, this driver is specially adapted to engine variable-valve driver, valve wherein can be the traditional intake valve of motor and exhaust valve, can be to be also specifically designed to the device of controlling gas shape fuel.
Background technique
People are using and are developing timing and the lift that various variable valve systems are effectively controlled valve, improve performance, fuel economy, injection and other characteristics of motor.According to device or the driver controlled, these systems mainly can be divided into (electrohydraulic) and electromagnetism (electromagnetic) form machinery, electric liquid.According to the scope of controlling, can be divided into the form of lift range variable and timing, Variable Valve Time and lift range variable.They also can be divided into strap cam (cam-based) and without the form of cam (camless).The design of these variable valve systems also needs to consider the control of valve clearance, to guarantee normal distribution function, less noise and rational life-span.
When valve is during in closed condition, the gap between valve and driving component is called valve clearance.Due to component expand with heat and contract with cold, wear and tear, process the reasons such as accumulated error, desirable zero clearance is impossible; And negative clearance can cause valve and valve seat to be not closed completely, thereby produce gas leak phenomenon.Many Modern Internal-Combustion Engine distribution devices adopt hydraulic tappet to control valve clearance, guarantee that at whole internal-combustion engine, in working life and under different operating mode, each valve, in the moment of taking a seat, has a less valve clearance.Noise, the problem such as life-span are even caused in gap too conference.
Such as what show in Chinese patent application 201310120949.0 and 201310163910.7, without cam variable valve system, adopted respectively hydraulic tappet to control valve clearance, wherein gone back handlebar hydraulic tappet and be combined in the preferred embodiment in actuator piston.
Hydraulic tappet comprises tappet plunger, tappet body and tappet hyperbaric chamber between the two conventionally.In valve switch course of action, the liquid of tappet hyperbaric chamber can produce the high pressure of transient state conventionally.The value of this high pressure is directly proportional to the power of hydraulic tappet transmission, is inversely proportional to the cross section of tappet plunger.The parts of tappet hyperbaric chamber periphery need in structural strength, to bear this high pressure.
Chinese patent application 201310163910.7 has been shown may designing or embodiment of a kind of hydraulic tappet and piston in combination, a part for tappet plunger wherein is built in tappet body slidably, between the end of tappet plunger and tappet body, formed tappet hyperbaric chamber, conventionally to guarantee that tappet intracoelomic cavity has enough large diameter to reduce inner high pressure, and the outer wall of tappet body has enough thickness to guarantee its structural life-time, in this embodiment, internal diameter and the outer wall of tappet body superpose.Meanwhile, for rapidity and the low energy consumption without cam variable valve actuation device, in scope of design, the piston of driver will be tried one's best little or compact.
In sum, the hydraulic tappet of optimum organization in piston has very large meaning to variable valve actuation device.
Summary of the invention
The technical problem that the present invention mainly solves is to provide a kind of driver with hydraulic tappet, hydraulic tappet design wherein has reasonable comprehensive advantage on bulk and hyperbaric chamber pressure, and at least reduce a pair of highi degree of accuracy fitting surface to cut down finished cost, be particularly useful for variable valve actuation device.Briefly: this hydraulic tappet is combined between the driving casing wall and two pistons of driver, and traditionally the tappet body structure of one is divided into the tappet end of body being served as by first piston of relative sliding and by the tappet body wall that drives casing wall to serve as.At drive cylinder diameter according to driving under the prerequisite of requirements set, do not need again a built-in tappet body wall (by driving casing wall to substitute, reduce a pair of highi degree of accuracy fitting surface), the internal diameter and the cross-section area that have guaranteed tappet hyperbaric chamber maximize, so the in the situation that of same valve thrust, reduced tappet hyperbaric chamber internal pressure, to guarantee normal distribution function, less noise and rational life-span.
For solving the problems of the technologies described above, the technological scheme that the present invention adopts is: a kind of driver with hydraulic tappet is provided, comprises
Actuator housing;
Drive cylinder, in described actuator housing, limits and has the longitudinal axis of the first and second directions, and have respectively drive cylinder first end and drive cylinder the second end at the two ends of its first direction and second direction, at it, radially has driving casing wall;
First piston and the second piston, can along second direction, be built in respectively in described drive cylinder slidably, described first piston has respectively first piston upper-end surface and first piston lower end surface at the two ends of its first and second direction, and the second piston has respectively the second piston upper-end surface and the second piston lower surface at the two ends of its first and second direction;
Piston rod, can be operatively connected to described the second piston lower surface; And
Hydraulic tappet, described hydraulic tappet further comprises:
Tappet plunger, is served as by described the second piston;
Tappet body, is served as by described first piston and described driving casing wall;
Tappet hyperbaric chamber, is border radially take described driving casing wall, axially take respectively described first piston lower end surface and described the second piston upper-end surface, is border;
Tappet influent stream road, to provide described tappet hyperbaric chamber to be communicated with the fluid between low pressure runner;
Earial drainage road, to provide the passage of described tappet hyperbaric chamber to external leakage;
Tappet one-way valve, to control from described tappet influent stream road to the one-way flow of described tappet hyperbaric chamber; And
Plunger return spring, is arranged between described first piston and the second piston.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises spring system and valve, and described valve further comprises valve stem, and valve stem one end is connected with piston rod energy place of working, wherein, described spring system acts on described piston rod through described valve stem.
In a preferred embodiment of the present invention, described earial drainage road further comprises
The first earial drainage road, described the first earial drainage road is the radial clearance between described tappet plunger and described driving casing wall;
The second earial drainage road, described the second earial drainage road is the radial clearance between first piston and described driving casing wall.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises
Drive cylinder the first chamber is space in drive cylinder, between described drive cylinder first end and described first piston upper-end surface;
Drive cylinder the second chamber is the space between described the second piston lower surface and described drive cylinder the second end;
The first port, in described actuator housing, is connected with described drive cylinder the first chamber fluid; And
The first port, in described actuator housing, is connected with described drive cylinder the second chamber fluid.
In a preferred embodiment of the present invention, described tappet influent stream road further comprises
Axially tappet influent stream road, is communicated with described tappet hyperbaric chamber; And
Radially tappet influent stream road, is communicated with described axial tappet influent stream road and described drive cylinder the second chamber.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises driving switching valve, and described driving switching valve and described the first port fluid-phase connect, and to control working solution, pass in and out described drive cylinder the first chamber.
In a preferred embodiment of the present invention, described driving switching valve further drives high pressure switching valve and a driving low pressure switching valve to form by one.
In a preferred embodiment of the present invention, the refluxing opening of described driving switching valve is communicated with low pressure runner fluid, drives the influent stream mouth of switching valve to be communicated with high pressure runner fluid, wherein, the direct fluid of described the second port is communicated to the refluxing opening of described driving switching valve, to form differential function.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises power internal orifice, and described power internal orifice, on described drive cylinder, is connected with described drive cylinder the first chamber fluid with described the first port.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises
At least one first notch, is arranged on the top of first piston;
At least one second notch, is arranged on the bottom of the second piston.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises
The first chamber feeder current one-way valve, its delivery outlet fluid is communicated in described drive cylinder the first chamber;
Throttling arrangement, fluid is communicated in described drive cylinder the first chamber, the buffering when helping described first piston to approach described drive cylinder first end.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises at least one through hole, and described at least one through hole is communicated to described drive cylinder the first chamber described the first chamber feeder current one-way valve and described throttling arrangement.
In a preferred embodiment of the present invention, described throttling arrangement is variable throttling device thereof.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises
Lift control cylinder is placed in the bottom of the second piston in described actuator housing, extends, and have respectively lift control cylinder first end and lift control cylinder the second end at the two ends of its first and second direction from described drive cylinder to second direction;
Lift is controlled cover, in described lift control cylinder, can slide between described lift control cylinder first end and described lift control cylinder the second end, and at the two ends of its first and second direction, there is respectively lift control cover first end and lift control cover the second end.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises
Lift control chamber is the fluid space between described lift control cylinder the second end and described lift control cover the second end;
Lift is controlled mouth, is connected with described lift control chamber fluid.
In a preferred embodiment of the present invention, the described driver with hydraulic tappet also comprises lift switching valve, described lift switching valve is connected with described lift control chamber fluid, to control described lift control, be enclosed within the switching between described lift control cylinder first end and described lift control cylinder the second end, control thus the switching of the described driver with hydraulic tappet between little lift and high-lift.
In a preferred embodiment of the present invention, described lift switching valve is the two-position three-way valve of often opening.
The invention has the beneficial effects as follows: the driver with hydraulic tappet of the present invention, it is a kind of hydraulic tappet design of optimization, on bulk and hyperbaric chamber pressure, there is reasonable comprehensive advantage, be particularly useful for variable valve actuation device, wherein, hydraulic tappet is combined between two pistons of driver, by hydraulic tappet, control valve clearance, guaranteed that tappet hyperbaric chamber has enough large diameter to reduce inner high pressure, to guarantee normal distribution function, less noise and rational life-span simultaneously.
Above-mentioned explanation is only the general introduction of technical solution of the present invention, in order to better understand technological means of the present invention, and can be implemented according to the content of specification, and for above and other objects of the present invention, feature and advantage can be become apparent, below especially exemplified by embodiment, and coordinate accompanying drawing, be described in detail as follows.
Accompanying drawing explanation
In order to be illustrated more clearly in the technological scheme in the embodiment of the present invention, below the accompanying drawing of required use during embodiment is described is briefly described, apparently, accompanying drawing in the following describes is only some embodiments of the present invention, for those of ordinary skills, do not paying under the prerequisite of creative work, can also according to these accompanying drawings, obtain other accompanying drawing, wherein:
Fig. 1 is the structural representation of driver one preferred embodiment with hydraulic tappet of the present invention;
Fig. 2 is the structural representation of another preferred embodiment of driver with hydraulic tappet of the present invention;
Being labeled as in accompanying drawing: 1, actuator housing, 2, drive cylinder, 3, first piston, 4, the second piston, 5, piston rod, 6, hydraulic tappet, 7, spring system, 8, valve, 9, drive switching valve, 10, the first chamber feeder current one-way valve, 11, through hole, 12, drive casing wall (being also tappet body wall), 20, throttling arrangement, 21, drive cylinder first end, 22, drive cylinder the second end, 23, drive cylinder the first chamber, 24, drive cylinder the second chamber, 25, the first port, 26, the second port, 27, power internal orifice, 28, the first buffer area, 29, the second buffer area, 30, lift control cylinder, 31, first piston upper-end surface, 32, first piston lower end surface, 33, the first notch, 40, lift is controlled cover, 41, the second piston upper-end surface, 42, the second piston lower surface, 43, the second notch, 50, lift control chamber, 60, lift switching valve, 61, tappet plunger, 62, tappet end of body, 63, tappet hyperbaric chamber, 64, axial tappet influent stream road, 65, tappet influent stream road radially, 66, tappet one-way valve, 67, plunger return spring, 68, the first earial drainage road, 69, the second earial drainage road, 70, lift is controlled mouth, 71, cotter seat, 72, valve return, 73, valve guide bushing, 74, cylinder body, 80, fuel tank, 81, valve stem, 82, valve head, 83, valve seat, 301, lift control cylinder first end, 302, lift control cylinder the second end, 401, lift is controlled cover first end, 402, lift is controlled cover the second end, S, lift, S1, little lift, S2, high-lift, X1 ~ 7, runner.
Embodiment
Below the technological scheme in the embodiment of the present invention is clearly and completely described, obviously, described embodiment is only a part of embodiment of the present invention, rather than whole embodiments.Embodiment based in the present invention, those of ordinary skills, not making all other embodiments that obtain under creative work prerequisite, belong to the scope of protection of the invention.
In this specification
term "top " and
"the end " or
"on " and
"under " etc. orientation term be just used for showing driver each several part relative position in the drawings, and not mounting point or the direction of the driver of check strap hydraulic tappet itself.
As shown in Figure 1, the driver with hydraulic tappet of the present invention's the first preferred embodiment comprises actuator housing 1.In this actuator housing 1, be provided with drive cylinder 2, first piston 3, the second piston 4, piston rod 5 and hydraulic tappet 6,
Drive cylinder 2, in described actuator housing 1, restriction has the longitudinal axis of the first and second directions, along being second direction from the direction of the portion end of to, top (or) (or under) portion in accompanying drawing, along being first direction from the direction of (or) portion to top, the end (or on) portion in accompanying drawing.And there is respectively drive cylinder first end 21 and drive cylinder the second end 22 at the two ends of its first and second direction (or upper and lower), at it, radially there is the casing wall 12 of driving;
Piston rod 5, can be operatively connected to described the second piston lower surface 42, and with the second piston 4 one or rigidly connected or can operatively be connected, due to the existence of piston rod 5, the area of the Area Ratio second piston upper-end surface 41 of the second piston lower surface 42 is little; And
Tappet body, further has tappet end of body 62(to be served as by described first piston 3) and tappet body wall (being served as by described driving casing wall 12), the parts of these two relative slidings serve as the tappet body structure of one traditionally.Under the prerequisite of having set according to driving demand at drive cylinder diameter, do not need again a built-in extra tappet body wall (by driving casing wall to substitute, therefore reduce a pair of highi degree of accuracy fitting surface), the internal diameter and the cross-section area that have guaranteed tappet hyperbaric chamber 63 maximize, so the in the situation that of same valve thrust, reduced the internal pressure of tappet hyperbaric chamber 63, to guarantee normal distribution function, less noise and rational life-span;
Tappet hyperbaric chamber 63, to drive casing wall 12 be border radially take, in axial first direction and second direction respectively with first piston lower end surface 32 and the second 41Wei border, piston upper-end surface;
Tappet influent stream road, to provide described tappet hyperbaric chamber 63 to be communicated with the fluid between low pressure runner, such as in Fig. 1, tappet influent stream road further comprises and connects the axial tappet influent stream road 64 of described tappet hyperbaric chamber 63 and be communicated with described axial tappet influent stream road 64 and the radially tappet influent stream road 65 in drive cylinder the second chamber 24.
Tappet one-way valve 66, to control from described tappet influent stream road to the one-way flow of described tappet hyperbaric chamber 63; And
In above-mentioned, described hydraulic tappet 6 also comprises earial drainage road, so that the passage of tappet hyperbaric chamber 63 to external leakage to be provided.Can there be different designs in earial drainage road, and in Fig. 1, the design in described earial drainage road comprises the first earial drainage road 68 and the second earial drainage road 69; Described the first earial drainage road 68 is the radial clearance between described tappet plunger 61 and described driving casing wall 12, and the current by pass from tappet hyperbaric chamber 63 to described drive cylinder the second chamber 24 or the second port 26 is provided; Described the second earial drainage road 69 is the radial clearance between first piston 3 and described driving casing wall 12, and the current by pass from tappet hyperbaric chamber 63 to drive cylinder the first chamber 23 or the first port 25 is provided.
Leakage flow in above-mentioned current by pass is general relevant to some design parameter, such as, leakage flow and gap length are inversely proportional to, be directly proportional to gap width or driving casing wall girth, be directly proportional to the cube of radial clearance size, be inversely proportional to the viscosity of working solution, be directly proportional to the pressure reduction at current by pass two ends.Generally need suitably control leakage flow, so that in the process of as far as possible opening at each valve, because leaking the hydraulic tappet decrement (be the displacement of axially drawing close between first and second piston, be also called valve clearance) that causes within the specific limits.Such as, the target valve clearance of gasoline engine is generally between 0.05mm to 0.10mm.
In the present invention, the described driver with hydraulic tappet also comprises the spring system 7 that is connected with piston rod 5 and is engine valve or engine valve as the valve 8(of its load).
Wherein, described spring system 7 comprises cotter seat 71, valve return 72, valve guide bushing 73 and cylinder body 74.Described valve 8 comprises valve stem 81, valve head 82 and valve seat 83.Cotter seat 71 is connected with valve stem 81 one end, and valve stem 81 the other ends are connected with valve head 82.Described cylinder body 74 is between cotter seat 71 and valve head 82, and valve guide bushing 73 is set on cylinder body 74.Valve stem 81 passes from valve guide bushing 73, and described valve return 72 is sleeved on valve stem 81 and simultaneously and is supported by cylinder body 74 and cotter seat 71.
In above-mentioned, described spring system 7 also can be substituted by other driver return mechanism (not showing in Fig. 1), such as having the pneumatic spring (not showing in Fig. 1) of similar return function.Their point of force application can (indirectly act on piston rod 5) on valve stem 81, also can directly on piston rod 5, (in Fig. 1, not show).
Further, the described driver with hydraulic tappet also comprises:
Drive cylinder the first chamber 23 is space in drive cylinder 2, between described drive cylinder first end 21 and described first piston upper-end surface 31;
Drive cylinder the second chamber 24 is the space between described the second piston lower surface 42 and described drive cylinder the second end 22;
The first port 25, in described actuator housing 1, is connected with described drive cylinder the first chamber 23 fluids;
The second port 26, in described actuator housing 1, is connected with described drive cylinder the second chamber 24 fluids;
Power internal orifice 27, on described drive cylinder 2, is connected with described drive cylinder the first chamber 23 fluids with described the first port 25;
At least one first notch 33, is arranged on the top of first piston 3, if more than one, preferably along even circumferential or symmetrical, in order to flowing and the symmetry properties of pressure distribution; And
At least one second notch 43, is arranged on the bottom of the second piston 4, if more than one, preferably along even circumferential or symmetrical, in order to flowing and the symmetry properties of pressure distribution.
In above-mentioned, power internal orifice 27 is selectable, and its effect is to provide transition runner between the first port 25 and drive cylinder the first chamber 23.Power internal orifice 27 can adopt the structural type of the undercut groove shown in Fig. 1, so that the fluid energy of flow distributes comparatively evenly along drive cylinder periphery, reduces flow resistance and lateral force.
Drive cylinder the first chamber 23 is the first buffer area 28 in upper edge and the part between drive cylinder first end 21 of power internal orifice 27.When first piston 3 enters the first buffer area 28, the fluid in the first buffer area 28 cannot directly or unimpededly be discharged and formation cushioning effect through the first port 25.
Equally, the connectivity part of drive cylinder the second chamber 24 and the second port 26 also can include the structural type of undercut groove resemble shown in Fig. 1, so that the fluid energy of flow distributes comparatively evenly along drive cylinder periphery, reduces flow resistance and lateral force.This undercut groove below to the part between drive cylinder the second end 22 be the second buffer area 29.When the second piston 4 enters the second buffer area 29, the fluid in the second buffer area 29 cannot directly or unimpededly cause cushioning effect through the second port 26 discharges.
When first piston 3 and the second piston 4 enter respectively the first buffer area 28 and the second buffer area 29, the first notch 33 and the second notch 43 provide respectively release of fluid and deceleration progressively.The shape of the first notch 33 and the second notch 43 can be traditional triangular groove, also can other shape of comparatively optimizing.The first notch 33 also can be replaced by least one the notch (not shown) that is arranged on power internal orifice 27 top edge.The second notch 43 also can be replaced by least one the notch (not shown) being arranged on the second buffer area 29 sidewalls.
Further, the described driver with hydraulic tappet also comprises:
Drive switching valve 9, described driving switching valve 9 is connected with described the first port 25 fluids, to control working solution, passes in and out described drive cylinder the first chamber 23;
The first chamber feeder current one-way valve 10, its delivery outlet fluid is communicated in described drive cylinder the first chamber 23;
Throttling arrangement 20, fluid is communicated in described drive cylinder the first chamber 23, the buffering when helping described first piston 3 to approach described drive cylinder first end 21, described throttling arrangement 20 also can be designed to variable throttling device thereof; And
Two through holes 11, connect respectively the first chamber feeder current one-way valve 10 and throttling arrangement 20, and are installed on the top of drive cylinder first end 21.
The refluxing opening of described driving switching valve 9 is communicated with low pressure runner PL fluid, drives the influent stream mouth of switching valve 9 to be communicated with high pressure runner PH fluid, and wherein, the direct fluid of described the second port 26 is communicated to the refluxing opening of described driving switching valve 9, to form differential function.
The delivery outlet of the first chamber feeder current one-way valve 10 and throttling arrangement 20, be communicated with the first buffer area 28 respectively by two through holes 11; Also can share a through hole 11, even save through hole 11 and be directly communicated with.First inlet opening of chamber feeder current one-way valve 10 and the other end of throttling arrangement 20 are connected to and are driven switching valve 9 by runner X3 and runner X1.Throttling arrangement 20 provides the controlled or confined stream that goes out, the pooling feature while entering the first buffer area 28 to help realizing first piston 3 for the first buffer area 28.But due to the amphicheirality of its throttling function, throttling arrangement 20 also hinders first piston 3 and leaves rapidly the first buffer area 28.In order to make up the defect of throttling arrangement 20 when valve is opened, the first chamber feeder current one-way valve 10 in parallel can help to realize unobstructed influent stream with it.Due to its one-way, the throttling function of throttling arrangement 20 can not released and interfere to the first chamber feeder current one-way valve 10 when first piston 3 enters the first buffer area 28.
Driving switching valve 9 shown in Fig. 1 is Normally closed type two-position three-way valves.So-called three links: link of trade，travel and post represent that it has three valve ports, its delivery outlet (also can be called working hole or A mouth) communicates with the first port 25 through runner X1, its refluxing opening is through runner X4(or be called driving switching valve backflow road) communicate with low-pressure channel PL, its influent stream mouth is through runner X5(or be called influent stream road) communicate with high pressure runner PH.High pressure runner PH itself is generally derived from a certain oil hydraulic pump, and additional pressure control structure again, adds accumulation of energy function even more conventionally.So-called " two " represent that it has two working positions or state: enable possition and closed position.Shown in Fig. 1 is the closed position of valve, and it is according to the annexation of three valve ports of circulation logic control of the right position of its schematic symbols; Wherein influent stream mouth is cut off (therefore claiming closed position), and working hole can only communicate with refluxing opening.Enable possition (not shown) in contrast, it is according to the annexation of three valve ports of circulation logic control of the left position of its schematic symbols; Wherein influent stream mouth communicates with working hole (therefore claiming enable possition), and refluxing opening is cut off.So-called " normally closed " (normally-closed) represents that this valve or its electromagnetic coil when no electric circuit (acquiescence or normality position) are (states that Fig. 1 represents) of closing, and during energising when abnormal () in enable possition.In above-mentioned, the two-bit triplet structure of described driving switching valve 9 also can be further drives high pressure switching valve (figure depending on) and two two-way to drive the combination of low pressure switching valve (figure depending on) to substitute by two two-way.Two two-ways wherein drive high pressure switching valve to control the on off state of runner X1 and high pressure runner PH, and two two-ways drive low pressure switching valve to control the on off state of runner X1 and low-pressure channel PL.
Drive switching valve 9 when the closed position shown in Fig. 1, the first port 25 is to low pressure runner PL row working solution; When driving switching valve 9 in left position (figure does not look), high pressure runner PH supplies working solution to the first port 25.Runner X4 communicates with the second port 26 through runner X2 halfway.Therefore, the second port 26 directly communicates with driving switching valve backflow road, and with this, drive cylinder 2 has formed an effective differential mechanics.When high pressure runner PH enters working solution through runner X5, X1 and X3 to drive cylinder the first chamber 23, drive cylinder the second chamber 24 through the second port 26, runner X2 and runner X4 toward low pressure runner PL row working solution.When drive cylinder the first chamber 23 is arranged working solution through runner X1 and X4 etc. toward low pressure runner PL, some work liquid separates, through runner X2, to drive cylinder the second chamber 24, mends working solutions from runner X4.
In Fig. 1, valve head 82 just in time contacts valve seat 83, in closed condition.Number in the figure S represents lift.
Working principle
(1) keep valve-closing state: as shown in Figure 1, drive switching valve 9 to remain on closed condition, drive cylinder the first chamber 23 and the second chamber 24 are all communicated with low pressure runner PL fluid.On first piston upper-end surface 31 and the second piston lower surface 42, all there is no large hydraulic coupling.Mainly due to the upwards driving force of valve return springs 72, valve 8 taken a seat (being that valve head 82 is pasting valve seat 83).It is also tappet end of body 62 to first piston 3(that plunger return spring 67 keeps) and the second piston 4(be also tappet plunger 61) thrust, piston rod 5 keeps and the contacting of valve stem 81; Basic its tip position that arrives of first piston 3, first piston upper-end surface 31 approaches and contacts drive cylinder first end 21.During this time, the pressure of tappet hyperbaric chamber 63 approaches or is less than low pressure PL, and tappet one-way valve 66 guarantees to supplement working solution to tappet hyperbaric chamber 63.
(2) open valve: drive switching valve 9 to switch to opening state (not showing in Fig. 1), drive cylinder the first chamber 23 starts to be communicated with high pressure runner PH fluid, drive cylinder the second chamber 24 keeps being communicated with the fluid of low pressure runner PL, first piston upper-end surface 31 starts there is large action of hydraulic force, and first piston 3 starts to move downward; The pressure of tappet hyperbaric chamber 63 starts to raise simultaneously, close tappet one-way valve 66, hydraulic coupling on first piston 3 is also given the second piston 4 by hyperbaric chamber 63 going downs, and further passes to successively piston rod 5, valve stem 81 and valve head 82, when these parts start, progressively accelerates.The upwards driving force of valve return springs 72 attempts to resist downward motion simultaneously, and resistance power also increases and increases along with the displacement of valve, so valve can generally can experience the first process of acceleration, rear acceleration in whole opening process.Until the power of last hydraulic thrust and valve return springs 72 reaches balance or the second piston 4 arrives drive cylinder the second end 22, valve opening process finishes.During this time, under high pressure, a little liquid in tappet hyperbaric chamber 63 can, by the first earial drainage road 68 and the second earial drainage road 69 to external leakage, marginally shorten the length of tappet hyperbaric chamber 63.In addition, before first piston 3 is walked out the first buffer area 28, the first notch 33 and throttling arrangement 20 can not allow enough flows; Now, the first chamber feeder current one-way valve 10 can be opened and carry out feeder current function.Also have, when the second piston 4 enters behind the second buffer area 29, the second notch 43 provides release of fluid and deceleration progressively.
(3) keep the open mode of valve: drive switching valve 9 to remain on opening state (not showing in Fig. 1), drive cylinder the first chamber 23 keeps being communicated with high pressure runner PH fluid, drive cylinder the second chamber 24 keeps being communicated with the fluid of low pressure runner PL, keeps thus the open mode of valve.During this time, under high pressure, tappet hyperbaric chamber 63 continues outwards marginally to leak.Concrete valve stays open the time of state to be determined by requirement (as air inflow or air displacement) and the operating mode of internal-combustion engine.Under some operating mode, may not need the retention time.
(4) close valve: drive switching valve 9 to switch back closed condition, drive cylinder the first chamber 23 is got back to the fluid of low pressure runner PL and is communicated with.On first piston upper-end surface 31 and the second piston lower surface 42, all there is no large hydraulic coupling.Under the upwards driving force of valve return springs 72, valve 8, the second piston 4 and first piston 3 start to move upward, until valve 8 is taken a seat (being that valve head 82 starts to contact valve seat 83).During this time, tappet hyperbaric chamber 63 has the pressure being almost directly proportional to valve return springs power, therefore continues outwards marginally to leak.When first piston 3 enters behind the first buffer area 28, the first notch 33 and throttling arrangement 20 provide release of fluid and deceleration progressively, and the first chamber feeder current one-way valve 10 keeps closed condition.
(5) after valve is taken a seat: the moment of just having taken a seat at valve, owing to leaking accumulation, the volume of tappet hyperbaric chamber 63 has diminished or length has shortened, so first piston upper-end surface 31 also has some distances, i.e. valve clearance from drive cylinder first end 21.After valve is taken a seat, under the effect of plunger return spring 67, first piston 3 continues to move up until valve clearance is zero.During this time, tappet one-way valve 66 supplies required working solution to tappet hyperbaric chamber 63.
In addition, the spring system 7 in the present invention can be to be had identically, quite or other structures of similar functions, such as pneumatic spring (not shown), realizes the function with the driver return mechanism of hydraulic tappet, will not enumerate herein.In addition, in the present invention, various switching valves are not limited to structure, combination or the control form of above-mentioned switching valve, can be replaced by other structure, combination or control form.
In the present invention, same driving switching valve 9 also can be controlled at least two with the driver (not shown) of hydraulic tappet simultaneously, and the working hole of this driving switching valve 9 and refluxing opening are respectively with all by control, the first port 25 with the driver of hydraulic tappet is connected with the second port 26.Such as on a cylinder, same driving switching valve 9 can two intake valves of synchronization control or the driver with hydraulic tappet of two exhaust valves.
As shown in Figure 2, in another preferred embodiment, in the present invention, the driver with hydraulic tappet described above also further comprises the structure that lift control cylinder 30, lift control cover 40, lift control chamber 50, lift switching valve 60 and lift control mouth 70 etc. are controlled for lift.
Lift is controlled cover 40, in described lift control cylinder 30, can slide between described lift control cylinder first end 301 and described lift control cylinder the second end 302, and at the two ends of its first and second direction, there is respectively lift control cover first end 401 and lift control cover the second end 402.
Lift control chamber 50, for described lift control cylinder the second end 302 and described lift control between cover the second end 402 and near the fluid space that communicates, the pressure-acting in this lift control chamber 50 is controlled cover the second end 402 in lift and to control lift, is controlled the position of cover 40.
Lift is controlled mouth 70, is connected with described lift control chamber 50 fluids.
Lift switching valve 60, be connected with described lift control chamber 50 fluids, to control described lift, control the switching of cover 40 between described lift control cylinder first end 301 and described lift control cylinder the second end 302, control thus the switching of the described driver with hydraulic tappet between little lift S1 and high-lift S2.
The groove that lift control cover first end 401 in lift control cover 40 is provided with the degree of depth is the second buffer area 29.When the second piston 4 enters the second buffer area 29, the fluid in the second buffer area 29 cannot directly or unimpededly cause cushioning effect through the second port 26 discharges.
Drive cylinder 2 has respectively drive cylinder first end 21 and drive cylinder the second end 22 up and down.Wherein, drive cylinder the second end 22 is provided in a side of the bottom of the second buffer area 29, and it is along with lift control cover 40 floats.In drive cylinder 2, there is drive cylinder the first chamber 23 being limited by drive cylinder first end 21 and first piston upper-end surface 31 and drive cylinder the second chamber 24 being limited by drive cylinder the second end 22 and the second piston lower surface 42.
Lift switching valve 60 shown in Fig. 2 is Normally closed type two-position three-way valves.So-called three links: link of trade，travel and post represent that it has three valve ports, and its working hole communicates with lift control chamber 50 through runner X6 and lift control mouth 70; Its refluxing opening communicates and realizes backflow functionality with fuel tank 80; Its influent stream mouth communicates with high pressure runner PH through runner X7.So-called " two " represent that it has two working positions or state: enable possition and closed position.Shown in Fig. 2 is the closed position of valve, and it is according to the annexation of three valve ports of circulation logic control on its schematic symbols left side; Wherein influent stream mouth is cut off (therefore claiming closed position), and working hole can only communicate with refluxing opening.Enable possition (not shown) in contrast, it is according to the annexation of three valve ports of circulation logic control on its schematic symbols the right; Wherein influent stream mouth communicates with working hole (therefore claiming enable possition), and refluxing opening is cut off.So-called " normally closed " (normally-closed) represents that it is (state that Fig. 2 represents) of closing that this valve or its electromagnetic coil (also claim default location) when no electric circuit, and during energising in enable possition.
In order to realize the little lift of valve, lift switching valve 60 energising, contrary with shown in Fig. 2 of its valve port state, provide high pressure in lift control chamber 50, to drive lift to control cover 40 to primary importance, that is, lift is controlled cover first end 401 and is headed on lift control cylinder first end 301.In Fig. 2, drive switching valve 9 in closed condition, the first port 25 connects low pressure, there is no large hydrodynamic pressure on first piston upper-end surface 31, thus valve 8 under the dominant force of spring force in closed condition.If drive switching valve 9 to switch to its opening state (Fig. 2 does not show), the first port 25 meets high-pressure channel PH, has enough large hydrodynamic pressure to overcome spring force and open valve 8 on first piston upper-end surface 31.The aperture of valve 8 equals little lift S1, the second piston lower surface 42 when from it, valve 8 is closed in the drawings position to the distance of position when the little lift of valve is opened.The stroke of first piston 3 and the second piston 4 is subject to the restriction that lift is controlled cover 40.In design, the area of lift control cover the second end 402 ideally should be enough large, guarantee on this area hydrodynamic pressure under high pressure and spring force (both all make progress) from spring system 7 make a concerted effort to be enough to overcome downwards make a concerted effort so that lift is controlled cover 40, keep its control positions and do not become flexible.This makes a concerted effort downwards to comprise: hydrodynamic pressure under high pressure on first piston upper-end surface 31, lift is controlled cover first end 401 hydrodynamic pressure under low pressure, and the transient force that produces at drive cylinder the second end 22 while entering the second buffer area 29 fast of the second piston 4.In design, also can only guarantee upwards make a concerted effort only enough overcome static making a concerted effort downwards, allowing lift to control cover 40 has the loosening of transient state downwards, the little lift motion of valve 8 has the overshoot of transient state thus.In Fig. 2, valve head 82 just in time contacts valve seat 83, in closed condition.Number in the figure S1 represents that little lift and S2 represent high-lift.
In order to realize high-lift, lift switching valve 60 is (state shown in Fig. 2) in off position, and lift control chamber 50 is communicated in fuel tank 80 and roughly in atmospheric pressure, so lift is controlled cover the second end 402 and almost be there is no hydrodynamic pressure.And control in lift drive cylinder the second chamber 23 of overlapping above 40, maintain at least in the ordinary course of things certain back pressure.Although this back pressure is far below the pressure of high-pressure channel PH, but it can be controlled on cover first end 401 and produce enough hydrodynamic pressures in lift, so that lift is controlled to cover 40, be controlled at the second place, that is, lift is controlled cover the second end 402 contact lift control cylinder the second ends 302.Certainly, also can increase extra locking or spring reverse motion (not shown) and guarantee that lift control cover 40 is in the second place.
Except above-mentioned big or small lift switching function or working principle, the driver with hydraulic tappet shown in Fig. 2 and the driver shown in Fig. 1 have essentially identical function or working principle, can drive switching valve 9 to change the on off state of valve by switching.
In force, (arranging shown in Fig. 2 is contrary) that lift switching valve 60 also can be designed to often open, when this valve or its electromagnetic coil no electric circuit, lift control chamber 50 is communicated in high pressure runner PH, to realize little lift.Particularly, when most of operating mode is little lift, the default location design that realizes little lift can reduce the total energy consumption of electromagnetic coil.
Lift switching valve 60 is shared a high pressure runner PH with driving switching valve 9.In system, the pressure of high pressure runner PH is to be controlled at a fixing target or design load, also can maybe need to carry out variable control according to operating mode.Such as, can improve system pressure and improve valve switch speed; Also can come the system performance that compensator fluid viscosity-temperature characteristics cause to change by change system pressure.
In the present invention, same lift switching control valve 60 also can be controlled at least two with the driver of hydraulic tappet simultaneously, and the working hole of this lift switching control valve 60 is controlled mouth 70 with the lift of all controlled drivers with hydraulic tappet and is connected.Such as in a motor, same lift switching control valve 60 can be controlled the driver with hydraulic tappet of all intake valves or all exhaust valves, also can control the driver with hydraulic tappet of all inlet and outlet doors.
In the present invention, many runners (such as runner X1, X2, X3, X4, X5, X6, X7) are structurally not necessarily independent of actuator housing 1, the presentation of shown independence of structure or independence convenience in order to describe or to illustrate just in each figure.If needed, they any can directly be combined in actuator housing 1, coupled like this port (such as the first port 25, the second port 26 or lift are controlled mouth 70) can be also the part continuous with runner, rather than artificial openning (port).
Lift control cover 40 in the present invention switches between primary importance and the second place.When primary importance and the second place, with the driver of hydraulic tappet, can adopt machinery, electromechanics, machine liquid or mechanical electronic hydraulic locking device (not shown) to help or replace above-mentioned hydraulic type lift and control, to stablize lift, control cover 40, guarantee the precision of valve 8 lifts.
The driver with hydraulic tappet that the present invention discloses, can realize two switchings between lift by simple lift COMM communication, and lift COMM communication controlled by lift switching control valve, and this control is digital.The structure of the simplification of this structure can guarantee reliability and the low cost in application.In the present invention, valve is to control cover mechanical position limitation by lift in the position of opening, so the basic non-overshoot of valve lift, and lift itself is also more accurate.The accuracy of valve lift directly has influence on the accuracy of the engine combustion process of intake and exhaust amount, so combustion efficiency and discharge quality.To the control of lift overshoot, also can reduce the possibility of valve and internal combustion engine collision.
The driver with hydraulic tappet that the present invention discloses is a kind of hydraulic tappet design of optimization, on bulk and hyperbaric chamber pressure, there is reasonable comprehensive advantage, be particularly useful for variable valve actuation device, wherein, hydraulic tappet is combined between two pistons of driver, by hydraulic tappet, control valve clearance, guaranteed that tappet hyperbaric chamber has enough large diameter to reduce inner high pressure simultaneously, to guarantee normal distribution function, less noise and rational life-span.
Be appreciated that the driver with hydraulic tappet of the present invention can be used on valve and controls, also can be used in other applicable occasions.
The above, only embodiments of the invention, not the present invention is done to any pro forma restriction, although the present invention discloses as above with embodiment, yet not in order to limit the present invention, any those skilled in the art, do not departing within the scope of technical solution of the present invention, when can utilizing the technology contents of above-mentioned announcement to make a little change or being modified to the equivalent embodiment of equivalent variations, in every case be not depart from technical solution of the present invention content, any simple modification of above embodiment being done according to technical spirit of the present invention, equivalent variations and modification, all still belong in the scope of technical solution of the present invention.
Claims (17)
1. with a driver for hydraulic tappet, it is characterized in that, comprise
Actuator housing;
Drive cylinder, in described actuator housing, limits and has the longitudinal axis of the first and second directions, and have respectively drive cylinder first end and drive cylinder the second end at the two ends of its first direction and second direction, at it, radially has driving casing wall;
First piston and the second piston, can along second direction, be built in respectively in described drive cylinder slidably, described first piston has respectively first piston upper-end surface and first piston lower end surface at the two ends of its first and second direction, and the second piston has respectively the second piston upper-end surface and the second piston lower surface at the two ends of its first and second direction;
Piston rod, can be operatively connected to described the second piston lower surface; And
Hydraulic tappet, described hydraulic tappet further comprises:
Tappet plunger, is served as by described the second piston;
Tappet body, is served as by described first piston and described driving casing wall;
Tappet hyperbaric chamber, is border radially take described driving casing wall, axially take respectively described first piston lower end surface and described the second piston upper-end surface, is border;
Tappet influent stream road, to provide described tappet hyperbaric chamber to be communicated with the fluid between low pressure runner;
Earial drainage road, to provide the passage of described tappet hyperbaric chamber to external leakage;
Tappet one-way valve, to control from described tappet influent stream road to the one-way flow of described tappet hyperbaric chamber; And
Plunger return spring, is arranged between described first piston and the second piston.
2. the driver with hydraulic tappet according to claim 1, it is characterized in that, the described driver with hydraulic tappet also comprises spring system and valve, described valve further comprises valve stem, valve stem one end is connected with piston rod energy place of working, wherein, described spring system acts on described piston rod through described valve stem.
3. the driver with hydraulic tappet according to claim 1, is characterized in that, described earial drainage road further comprises
The first earial drainage road, described the first earial drainage road is the radial clearance between described tappet plunger and described driving casing wall;
The second earial drainage road, described the second earial drainage road is the radial clearance between first piston and described driving casing wall.
4. the driver with hydraulic tappet according to claim 1, is characterized in that, the described driver with hydraulic tappet also comprises
Drive cylinder the first chamber is space in drive cylinder, between described drive cylinder first end and described first piston upper-end surface;
Drive cylinder the second chamber is the space between described the second piston lower surface and described drive cylinder the second end;
The first port, in described actuator housing, is connected with described drive cylinder the first chamber fluid; And
The first port, in described actuator housing, is connected with described drive cylinder the second chamber fluid.
5. the driver with hydraulic tappet according to claim 4, is characterized in that, described tappet influent stream road further comprises
Axially tappet influent stream road, is communicated with described tappet hyperbaric chamber; And
Radially tappet influent stream road, is communicated with described axial tappet influent stream road and described drive cylinder the second chamber.
6. the driver with hydraulic tappet according to claim 4, it is characterized in that, the described driver with hydraulic tappet also comprises driving switching valve, and described driving switching valve and described the first port fluid-phase connect, and to control working solution, pass in and out described drive cylinder the first chamber.
7. the driver with hydraulic tappet according to claim 6, is characterized in that, described driving switching valve further drives high pressure switching valve and a driving low pressure switching valve to form by one.
8. according to the driver with hydraulic tappet described in claim 6 or 7, it is characterized in that, the refluxing opening of described driving switching valve is communicated with low pressure runner fluid, drive the influent stream mouth of switching valve to be communicated with high pressure runner fluid, wherein, the direct fluid of described the second port is communicated to the refluxing opening of described driving switching valve, to form differential function.
9. the driver with hydraulic tappet according to claim 1, is characterized in that, the described driver with hydraulic tappet also comprises power internal orifice, and described power internal orifice, on described drive cylinder, is connected with described drive cylinder the first chamber fluid with described the first port.
10. the driver with hydraulic tappet according to claim 1, is characterized in that, the described driver with hydraulic tappet also comprises
At least one first notch, is arranged on the top of first piston;
At least one second notch, is arranged on the bottom of the second piston.
11. drivers with hydraulic tappet according to claim 1, is characterized in that, the described driver with hydraulic tappet also comprises
The first chamber feeder current one-way valve, its delivery outlet fluid is communicated in described drive cylinder the first chamber;
Throttling arrangement, fluid is communicated in described drive cylinder the first chamber, the buffering when helping described first piston to approach described drive cylinder first end.
12. drivers with hydraulic tappet according to claim 11, it is characterized in that, the described driver with hydraulic tappet also comprises at least one through hole, and described at least one through hole is communicated to described drive cylinder the first chamber described the first chamber feeder current one-way valve and described throttling arrangement.
13. drivers with hydraulic tappet according to claim 11, is characterized in that, described throttling arrangement is variable throttling device thereof.
14. according to the driver with hydraulic tappet one of claim 1-13 Suo Shu, it is characterized in that, the described driver with hydraulic tappet also comprises
Lift control cylinder is placed in the bottom of the second piston in described actuator housing, extends, and have respectively lift control cylinder first end and lift control cylinder the second end at the two ends of its first and second direction from described drive cylinder to second direction;
Lift is controlled cover, in described lift control cylinder, can slide between described lift control cylinder first end and described lift control cylinder the second end, and at the two ends of its first and second direction, there is respectively lift control cover first end and lift control cover the second end.
15. drivers with hydraulic tappet according to claim 14, is characterized in that, the described driver with hydraulic tappet also comprises
Lift control chamber is the fluid space between described lift control cylinder the second end and described lift control cover the second end;
Lift is controlled mouth, is connected with described lift control chamber fluid.
16. drivers with hydraulic tappet according to claim 14, it is characterized in that, the described driver with hydraulic tappet also comprises lift switching valve, described lift switching valve is connected with described lift control chamber fluid, to control described lift control, be enclosed within the switching between described lift control cylinder first end and described lift control cylinder the second end, control thus the switching of the described driver with hydraulic tappet between little lift and high-lift.
17. drivers with hydraulic tappet according to claim 16, is characterized in that, described lift switching valve is the two-position three-way valve of often opening.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310712877.9A CN103696822B (en) | 2013-12-23 | 2013-12-23 | A kind of driver with hydraulic tappet |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310712877.9A CN103696822B (en) | 2013-12-23 | 2013-12-23 | A kind of driver with hydraulic tappet |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103696822A true CN103696822A (en) | 2014-04-02 |
| CN103696822B CN103696822B (en) | 2016-04-06 |
Family
ID=50358465
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310712877.9A Expired - Fee Related CN103696822B (en) | 2013-12-23 | 2013-12-23 | A kind of driver with hydraulic tappet |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103696822B (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104454066A (en) * | 2014-11-05 | 2015-03-25 | Lgd技术有限责任公司 | Continuous and variable lift driver |
| CN106640257A (en) * | 2015-10-29 | 2017-05-10 | 上海尤顺汽车部件有限公司 | Load-controllable engine braking device and engine braking method |
| CN107060935A (en) * | 2017-03-24 | 2017-08-18 | 中国北方发动机研究所(天津) | A kind of hydraulic pressure variable valve device |
| CN107143393A (en) * | 2017-06-02 | 2017-09-08 | 中国北方发动机研究所(天津) | A kind of internal combustion engine hydraulic variable valve mechanism |
| CN107355276A (en) * | 2017-06-02 | 2017-11-17 | 中国北方发动机研究所(天津) | A kind of variable valve actuator for air of high hydraulic-driven |
| CN107975395A (en) * | 2016-10-22 | 2018-05-01 | 浙江师范大学 | A kind of tappet formula of Piezoelectric Driving is without camshaft valve actuating mechanism |
| CN109790764A (en) * | 2016-08-05 | 2019-05-21 | 优特卡洛股份公司 | Hydraulic tappet |
| CN109779714A (en) * | 2019-03-21 | 2019-05-21 | 深圳职业技术学院 | A kind of engine air valve controlling mechanism |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070181087A1 (en) * | 2006-02-03 | 2007-08-09 | Zheng Lou | Electromechanical variable valve actuator with a spring controller |
| US20070272180A1 (en) * | 2006-05-26 | 2007-11-29 | Zheng Lou | Variable valve actuator with latch at one end |
| CN201284672Y (en) * | 2008-10-17 | 2009-08-05 | 奇瑞汽车股份有限公司 | Hydraulic tappet of engine |
| CN103216290A (en) * | 2013-04-09 | 2013-07-24 | 江苏公大动力技术有限公司 | Variable lift driver |
| CN103277163A (en) * | 2013-05-07 | 2013-09-04 | 江苏公大动力技术有限公司 | Variable-lift driver |
-
2013
- 2013-12-23 CN CN201310712877.9A patent/CN103696822B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070181087A1 (en) * | 2006-02-03 | 2007-08-09 | Zheng Lou | Electromechanical variable valve actuator with a spring controller |
| US20070272180A1 (en) * | 2006-05-26 | 2007-11-29 | Zheng Lou | Variable valve actuator with latch at one end |
| CN201284672Y (en) * | 2008-10-17 | 2009-08-05 | 奇瑞汽车股份有限公司 | Hydraulic tappet of engine |
| CN103216290A (en) * | 2013-04-09 | 2013-07-24 | 江苏公大动力技术有限公司 | Variable lift driver |
| CN103277163A (en) * | 2013-05-07 | 2013-09-04 | 江苏公大动力技术有限公司 | Variable-lift driver |
Non-Patent Citations (1)
| Title |
|---|
| 林波 李兴虎: "《内燃机构造》", 31 January 2012, 北京大学出版社 * |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104454066A (en) * | 2014-11-05 | 2015-03-25 | Lgd技术有限责任公司 | Continuous and variable lift driver |
| CN106640257A (en) * | 2015-10-29 | 2017-05-10 | 上海尤顺汽车部件有限公司 | Load-controllable engine braking device and engine braking method |
| CN106640257B (en) * | 2015-10-29 | 2019-09-27 | 上海尤顺汽车部件有限公司 | Load controllable engine braking apparatus and engine braking methods |
| CN109790764A (en) * | 2016-08-05 | 2019-05-21 | 优特卡洛股份公司 | Hydraulic tappet |
| CN107975395A (en) * | 2016-10-22 | 2018-05-01 | 浙江师范大学 | A kind of tappet formula of Piezoelectric Driving is without camshaft valve actuating mechanism |
| CN107060935A (en) * | 2017-03-24 | 2017-08-18 | 中国北方发动机研究所(天津) | A kind of hydraulic pressure variable valve device |
| CN107060935B (en) * | 2017-03-24 | 2018-11-02 | 中国北方发动机研究所(天津) | A kind of hydraulic pressure variable valve device |
| CN107143393A (en) * | 2017-06-02 | 2017-09-08 | 中国北方发动机研究所(天津) | A kind of internal combustion engine hydraulic variable valve mechanism |
| CN107355276A (en) * | 2017-06-02 | 2017-11-17 | 中国北方发动机研究所(天津) | A kind of variable valve actuator for air of high hydraulic-driven |
| CN107355276B (en) * | 2017-06-02 | 2018-11-02 | 中国北方发动机研究所(天津) | A kind of variable valve actuator for air of high hydraulic-driven |
| CN109779714A (en) * | 2019-03-21 | 2019-05-21 | 深圳职业技术学院 | A kind of engine air valve controlling mechanism |
| CN109779714B (en) * | 2019-03-21 | 2024-02-06 | 深圳职业技术学院 | Engine valve control mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103696822B (en) | 2016-04-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103696822B (en) | A kind of driver with hydraulic tappet | |
| CN103277163B (en) | Variable-lift driver | |
| EP2261471B1 (en) | Internal combustion engine with two hydraulically actuated intake valves with different return springs for each cylinder | |
| CN100375696C (en) | Power steering system | |
| CN105626258B (en) | Hydraulic drive type variable-compression-ratio piston link assembly | |
| EP2597276B1 (en) | Internal combustion engine having a system for variable actuation of the intake valves, provided with a three-way solenoid valve | |
| CN103216290B (en) | Variable lift driver | |
| CN104088681B (en) | Variable actuator | |
| CN1287069C (en) | Pressure differential style air valve variation control system | |
| CN101457678A (en) | Novel lift range valve mechanism for variable valve | |
| CN107676142B (en) | Hydraulic drive variable valve mechanism with low pressure control and high pressure | |
| CN1295441C (en) | Proportional differential pressure control valve | |
| CN205089460U (en) | Compression release type engine brake device | |
| CN104454066A (en) | Continuous and variable lift driver | |
| CN205908328U (en) | Four properties door engine variable valve mechanism | |
| US8607751B2 (en) | Electro-hydraulic variable valve lift system | |
| CN104314635B (en) | Variable driver | |
| CN202251197U (en) | Loading feedback control valve | |
| CN205331509U (en) | A vehicle that is used for control valve of vehicle and has it | |
| CN201275860Y (en) | Opening and closing die hydraulic circuit system of injection moulding machine | |
| CN103993925B (en) | Variable actuator | |
| CN203285507U (en) | Driver with variable lift ranges | |
| CN206071668U (en) | A kind of variable valve actuator for air | |
| CN104061037A (en) | Actuating fluid supply system for variable valve | |
| CN113530693B (en) | Control valve, control oil way and variable compression ratio engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| ASS | Succession or assignment of patent right |
Owner name: NINGBO HUAYE MACHINE MANUFACTURE CO., LTD. Free format text: FORMER OWNER: JIANGSU GONGDA POWER TECHNOLOGY CO., LTD. Effective date: 20150521 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20150521 Address after: 315131 Zhejiang city of Ningbo Province Wang town Yinzhou District week Jiacun Applicant after: NINGBO HOYEA MACHINERY MANUFACTURE Co.,Ltd. Address before: Four road 215513 Jiangsu Branch Park City in Suzhou Province, Changshu economic and Technological Development Zone No. 11 Room 303 Applicant before: JIANGSU GONGDA POWER TECHNOLOGIES Co.,Ltd. |
|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160406 Termination date: 20211223 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |