CN104088681A - Variable driver - Google Patents
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- CN104088681A CN104088681A CN201410134300.9A CN201410134300A CN104088681A CN 104088681 A CN104088681 A CN 104088681A CN 201410134300 A CN201410134300 A CN 201410134300A CN 104088681 A CN104088681 A CN 104088681A
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Abstract
The invention provides a variable valve driver. The variable valve driver comprises a driver casing, a driving cylinder, a driving piston, a piston rod, a driving cylinder first cavity, a driving cylinder second cavity, a spring system, a first opening, a second opening, a driving switching valve, a first runner, a supercharger and supercharge switching valve, wherein the driving cylinder is provided with a driving cylinder first end part and a driving cylinder second end part; the driving piston can slide between the driving cylinder first end part and the driving cylinder second end part; the first opening and the second opening are respectively connected with fluid of the driving cylinder first cavity and the driving cylinder second cavity; the driving switching valve is respectively connected with the supercharger and the driving cylinder first cavity through the supercharge switching valve and the first runner connected with the supercharge switching valve in parallel; the supercharge switching valve opens the first runner when being at a first position, so that the variable driver realizes a normal driving function; the supercharge switching valve opens the supercharger when being at a second position, so that the variable driver realizes a cylinder pressure braking function.
Description
Technical field
The invention relates to a kind of control technique of driver, and relate to especially a kind of with pressurized machine without cam variable valve actuation device.
Background technique
In prior art, can adopt various variable valve actuation (Variable Valve Actuation or abbreviation VVA) system effectively to control timing and the lift of 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 cam (cam-based) and the form without cam (camless).
In the case of the system that has cam, keep traditional engine cam system and amendment a little, to indirectly control valve timing and/or valve lift.In without camming, traditional engine cam system is with directly driving electric liquid or the electromagnetic driver of each valve to replace completely.With respect to the system that has cam, there is more control freedom degree or advantage without camming, particularly: 1) the abundant control freedom degree in time domain without camming, can realize (cycle to cycle) between the thermal cycle of adjacent heat mechanics arbitrarily, Instantaneous Control; 2) can realize the personalization control at each cylinder of motor without camming, or (the cylinder to cylinder) that be called between cylinder controls.Between this circulation and cylinder between control ability be to help to realize support technology or the key technology of various new energy-saving and emission-reduction combustion process, such as the homogeneous compression-ignition in petrol engine (HCCI) and the homogeneous charge compression ignition in diesel engine (PCCI) all need between circulation and cylinder between effective control could be stably, in larger condition range, implement, realize more than 10% fuel consumption reduction.
In addition in the application of the commercial car of similar truck, in order to realize effectively, the braking of safety and low wearing and tearing, modern diesel engine generally adopts cylinder compacting braking technique, particularly cylinder to press releasing brake technology.Cylinder presses releasing braking device to have the ability near compression stroke proceeds to top dead center (TDC), and the air high pressure (such as up to 70bar) overcoming in cylinder is opened exhaust valve, discharges artificially and consumes the air potential energy in cylinder, realizes braking function.It is a kind of optional equipment of costliness that cylinder is pressed releasing braking device.In diesel applications, people wish cylinder to press releasing brake function to be integrated in without in cam variable valve actuation device, to reduce total fringe cost, improve cost performance.Major function designing requirement without cam variable valve actuation device is agility, and cylinder to press the major function designing requirement of releasing brake device be large retrothrust, this retrothrust is approximately five times of general valve opening power or more.Generally speaking, high thrust needs larger piston action area or higher system pressure or both to have concurrently.In order to keep simplification and the low cost of electric liquid without cam variable valve actuation device system, cylinder presses releasing braking device preferably to utilize the driven plunger of driver itself.Excessive piston can affect negatively and drive function or agility; Too high hydraulic system pressure can have negative impact to the intensity of system, reliability and cost again.
In sum, need one without cam variable valve actuation device, it had both had the characteristics such as the required agility of common changeable air valve, needed again effective cylinder to press releasing brake function, both integrated simplicity and feasibilities of wanting holding structure simultaneously.
Summary of the invention
For the problems referred to above, the object of this invention is to provide a kind of with pressurized machine without cam variable valve actuation device, its driven function comprises the lift control of stepless timing control and one-level or two-stage, integrated pressurized machine can help to press when releasing brake the working pressure in driven plunger is amplified to many times of system pressure at cylinder, is enough to open near exhaust valve top dead center.Amplify by this pressure is local, do not need to adopt expensive high-pressure service pump and high-pressure solenoid valve, the appropriate design size that has kept again driven plunger to be determined by agility simultaneously.
For reaching above-mentioned advantage, the technological scheme that the present invention adopts is to provide a kind of variable actuator, and it comprises:
Actuator housing;
Drive cylinder, in described actuator housing, limits and has the longitudinal axis of the first and second directions, and have drive cylinder first end in one end of first direction, has drive cylinder the second end in one end of second direction;
Driven plunger can slide between described drive cylinder first end and described drive cylinder the second end in described drive cylinder, has respectively driven plunger the first end face and driven plunger the second end face at the two ends of the first and second directions;
Piston rod, can be operatively connected to described driven plunger the second end face;
Drive cylinder the first chamber is space in drive cylinder, between described drive cylinder first end and described driven plunger the first end face;
Drive cylinder the second chamber is the space between described driven plunger the second end face and described drive cylinder the second end;
Spring system, can operatively act on described piston rod;
The first port and the second port, in described actuator housing, be connected with described drive cylinder the second chamber fluid with described drive cylinder the first chamber respectively; And
Drive switching valve, first flow, pressurized machine and supercharging switching valve, described driving switching valve is connected with described drive cylinder the first chamber with described pressurized machine by described supercharging switching valve and described first flow in parallel successively, described supercharging switching valve is opened described first flow so that described variable actuator is carried out driven function in the time of first of its supercharging switching valve, and described supercharging switching valve is opened described pressurized machine and pressed releasing brake function so that described variable actuator is carried out cylinder in the time of its supercharging switching valve second.
In a preferred embodiment of the present invention, described pressurized machine comprises:
Supercharging body;
Large tank and small oil tank, be built in described supercharging body;
Large piston and small piston, can be built in respectively in described large tank and described small oil tank slidably;
Hyperbaric chamber, in described small oil tank, with described first flow fluid communication;
Low-pressure cavity and intermediate cavity, two chambeies that are separated by by large piston in described large tank, wherein close described small piston is described intermediate cavity, described low-pressure cavity and described supercharging switching valve fluid communication; And
Drain tap.
In a preferred embodiment of the present invention, described pressurized machine further comprises pressurized machine return spring, to help the returning movement of described large piston and small piston.
In a preferred embodiment of the present invention, described pressurized machine further comprises repairing one-way valve, its entrance and exit respectively with described low-pressure cavity and described hyperbaric chamber fluid communication, flow from described low-pressure cavity to the unidirectional repairing of described hyperbaric chamber allowing.
In a preferred embodiment of the present invention, described variable actuator has driver supercharging and drives stroke;
Described driven plunger first end mask has driven plunger the first face area;
Described pressurized machine has intensifier piston stroke, and stroke two ends are all mechanical position limitations;
Described small piston has small piston acting surface area;
Described variable actuator has leakage compensation volume; And
Product=described driven plunger first face area of described small piston acting surface area and described intensifier piston stroke and described driver supercharging drive the product+described leakage compensation volume of stroke.
In a preferred embodiment of the present invention, described variable actuator has driver supercharging and drives stroke, and its numerical value is between 1 millimeter to 4 millimeters.
In a preferred embodiment of the present invention, comprise brake control pressure source, described supercharging switching valve is two-position three-way valve, its switching function is controlled by described brake control pressure source.
In a preferred embodiment of the present invention, comprise mechanical braking COMM communication, described supercharging switching valve is two-position three-way valve, its switching function is switched by described mechanical braking COMM communication.
In a preferred embodiment of the present invention, there are high pressure and two grades of pressure of low pressure in described brake control pressure source;
When described brake control pressure source is during in low pressure, described supercharging switching valve is communicated with described driving switching valve with described first flow; And
When described brake control pressure source is during at high pressure, described supercharging switching valve is communicated with described driving switching valve with the described low-pressure cavity of described pressurized machine.
In a preferred embodiment of the present invention, at least two described variable actuator are controlled in described brake control pressure source simultaneously.
In a preferred embodiment of the present invention, described large piston and small piston are structurally one.
In a preferred embodiment of the present invention, comprising:
Lift control cylinder, in described actuator housing, extends to second direction from described drive cylinder, and has respectively lift control cylinder first end and lift control cylinder the second end at the two ends of the first and second directions;
Lift control cover, in described lift control cylinder, can slide between described lift control cylinder first end and described lift control cylinder the second end, and there is respectively lift control cover first end and lift control cover the second end at the two ends of the first and second directions;
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 switched pressure source, be connected with described lift control chamber fluid, be enclosed within the switching between described lift control cylinder first end and described lift control cylinder the second end to control described lift control, control thus the switching of described variable actuator between little lift and high-lift;
Described drive cylinder the second end is arranged on described lift control cover first end, floating with described lift control cover; With
Described piston rod can pass described lift control cover slidably.
In a preferred embodiment of the present invention, described lift control cover first end is provided with the groove with certain depth, and this groove is the second buffer area, and the bottom of this groove is described drive cylinder the second end.
In a preferred embodiment of the present invention, described lift switching pressure source fluid is connected in the described lift control chamber of at least two described variable actuator
In a preferred embodiment of the present invention, comprising:
Low pressure runner; Drive switching valve refluxing opening; Drive switching valve backflow road, connect described driving switching valve refluxing opening to described low pressure runner; Drive switching valve influent stream mouth; High pressure runner, is connected with described driving switching valve influent stream mouth fluid; The direct fluid of described the second port is connected to described driving switching valve backflow road, to form differential function.
In a preferred embodiment of the present invention, also comprise: drive switching valve refluxing opening; Fuel tank; Drive switching valve backflow road, connect described driving switching valve refluxing opening to described fuel tank; Back pressure apparatus, is arranged in described driving switching valve backflow road; Drive switching valve influent stream mouth; High pressure runner, is connected with described driving switching valve influent stream mouth fluid; The direct fluid of described the second port is connected to described driving switching valve backflow road, and tie point is between described driving switching valve refluxing opening and described back pressure apparatus, to form differential function.
In a preferred embodiment of the present invention, also comprise:
Engine valve, it further comprises valve stem, this valve stem can operatively connect described piston rod;
Wherein, described spring system acts on described piston rod through described valve stem.
In a preferred embodiment of the present invention, also comprise:
Engine exhaust port, it further comprises valve stem, this valve stem can operatively connect described piston rod;
Wherein, described spring system acts on described piston rod through described valve stem.
In a preferred embodiment of the present invention, also comprise:
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, also comprise:
The first chamber feeder current one-way valve, its delivery outlet fluid is connected in described drive cylinder the first chamber, to help described variable actuator to open the quick startup of stroke; And
Throttling arrangement, fluid is connected in described drive cylinder the first chamber, the buffering when helping described driven plunger to approach described drive cylinder first end.
In a preferred embodiment of the present invention, effective restriction of described throttling arrangement can regulate.
In a preferred embodiment of the present invention, each described driving switching valve is connected in the described drive cylinder of at least two described variable actuator.
In a preferred embodiment of the present invention, each described pressurized machine and described supercharging switching valve are connected in the described drive cylinder of at least two described variable actuator.
In a preferred embodiment of the present invention, the diameter of described large piston and small piston is 1.5-5.0 than scope.
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.
Brief description of the drawings
Fig. 1 is the variable actuator of the embodiment of the present invention one structural representation in the time of high-lift operating mode.
Fig. 2 is the structural representation of variable actuator shown in Fig. 1 in the time of little lift operating mode.
Fig. 3 is the structural representation of the variable actuator of the embodiment of the present invention two.
In accompanying drawing, the mark of each parts is as follows:
21, actuator housing; 30, driven plunger; 31, piston rod; 34, driven plunger the first end face; 36, driven plunger the second end face; 40, the first chamber feeder current one-way valve; 41, throttling arrangement; 50, pressurized machine (pressure booster); 51, large piston; 52, small piston; 53, supercharging body; 54, large piston action face; 55, low-pressure cavity; 56, hyperbaric chamber; 57, small piston acting surface; 58, pressurized machine return spring; 59, the first confined planes; 60, the second confined planes; 61, intermediate cavity; 62, large tank; 63, small oil tank; 64, drain tap; 65, drive switching valve; 66, drive first of switching valve; 67, drive switching valve second; 70, spring system; 71, cotter seat; 72, valve return; 73, valve guide bushing; 74, cylinder body; 80, valve; 81, valve stem; 82, valve head; 83, valve seat; 85, repairing one-way valve; 90, supercharging switching valve; 91, first of supercharging switching valve; 92, supercharging switching valve second; 94, lift is switched restriction; 96, lift is switched one-way valve; 110, high pressure runner; 112, low pressure runner; 114, brake control pressure source; 116, lift pilot pressure source; 210, the first through hole; 211, drive cylinder (actuation cylinder); 212, the first notch; 213, the first port; 214, power internal orifice; 216, the second notch; 217, the second port; 220, lift control cylinder (stroke control chamber); 221, lift control chamber (stroke control chamber); 222, tappet influent stream mouth; 223, piston rod hole; 224, lift control mouth; 226, the 3rd port; 227, lift control cylinder first end; 228, lift control cylinder the second end; 232, drive cylinder the first chamber; 234, drive cylinder the second chamber; 236, drive cylinder first end; 237, drive cylinder the second end; 240, seal ring; 250, lift control cover; 251, lift control cover first end; 252, lift control cover the second end; 253, the second buffer area; 254, the first buffer area; 255, the second buffer area head piece; 651, drive switching valve the first valve port; 652, drive switching valve the second valve port; 653, drive switching valve the 3rd valve port; 901, supercharging switching valve the first valve port; 902, supercharging switching valve the second valve port; 903, supercharging switching valve the 3rd valve port;
The area of Aa1, driven plunger the first end face; Abs, small piston acting surface area; Lb, intensifier piston stroke; Ls1, the first buffer length; Ls2, the second buffer length; S1, little lift; S2, high-lift; Sb, driver supercharging drive stroke; Vloss, leakage compensation volume; X1, first flow; X2, the second runner; X3, the 3rd runner; X4, the 4th runner; X5, the 5th runner; X6, the 6th runner.
Embodiment
Below in conjunction with accompanying drawing, embodiments of the invention are described in detail, so that advantages and features of the invention can be easier to be it will be appreciated by those skilled in the art that, protection scope of the present invention is not limited with this embodiment.Term " top " in this specification and " end " or " on " and the orientation such as D score or " left side " and " right side " and directivity term be just used for being convenient to show driver each several part relative position in the drawings, and do not limit mounting point or the direction of variable valve actuation device itself.
As shown in Figure 1, the variable valve actuation device of first embodiment of the invention comprises actuator housing 21, in described actuator housing, 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.In this actuator housing 21, along second direction, be provided with drive cylinder 211, the first port 213, power internal orifice 214, the second port 217, lift control cylinder 220 and piston rod hole 223.Variable valve actuation device also comprises the driven plunger 30 being arranged in drive cylinder 211; Be arranged in piston rod hole 223, with driven plunger 30 one or piston rod 31 rigidly connected or that can operatively be connected; Be arranged on the lift control cover 250 in lift control cylinder 220; And the spring system 70 being connected with piston rod 31.Variable valve actuation device also comprises driving switching valve 65, pressurized machine 50 and supercharging switching valve 90.Variable valve actuation device also comprises that as the valve 80(of its load be engine valve or engine valve).
Driven plunger 30 has respectively driven plunger the first end face 34 and driven plunger the second end face 36 up and down.Due to the existence of piston rod 31, the area of Area Ratio first end face 34 of driven plunger the second end face 36 is little.
The part of drive cylinder the first chamber 232 between upper edge and the drive cylinder first end 236 of power internal orifice 214 is the first buffer area 254, and its length is Ls1.In the time that driven plunger 30 enters the first buffer area 254, drive cylinder the first chamber 232 cannot directly or unimpededly be discharged working liquid body and cause cushioning effect through the first port 213.
Lift control cover 250 comprises lift control cover first end 251 and lift control cover the second end 252, and to be wherein provided with the degree of depth be that the groove of Ls2 is the second buffer area 253 to lift control cover first end 251.In the time that driven plunger 30 enters the second buffer area 253, drive cylinder the second chamber 234 cannot directly or unimpededly be discharged working liquid body and cause cushioning effect through the second port 217.
Be arranged on the side of driven plunger 30, with have respectively at least one first notch 212 and at least one the second notch 216 near driven plunger the first end face 34 and the second end face 36 intersections, think that driven plunger 30 provides release of fluid and deceleration progressively while entering respectively the first buffer area 254 and the second buffer area 253.The shape of notch can be traditional triangular groove, also can other shape of comparatively optimizing.The first notch 212 also can be replaced by least one the notch (not shown) that is arranged on power internal orifice 214 tops.The second notch 216 also can be replaced by least one the notch (not shown) being arranged on the second buffer area 253 sidewalls.
Lift control cylinder 220 comprises lift control cylinder first end 227 and lift control cylinder the second end 228.Lift control cover 250 can move between lift control cylinder first end 227 and the second end 228.Lift control cylinder 220 also comprises lift control chamber 221, it be between lift control cylinder the second end 228 and lift control cover the second end 252 and near the fluid space that communicates.Pressure-acting in lift control chamber 221 overlaps 250 position in lift control cover the second end 252 to control lift control.Lift control chamber 221 is communicated with by lift control mouth 224 the lift pilot pressure source 116 of controlling its pressure.
Lift pilot pressure source 116 itself can be the output (not shown) of a two-bit triplet electromagnetic switching valve, an input of this valve can be high pressure runner 110, and another input can be system fuel tank or atmosphere or have the more runner of low-pressure like lowpressure stream road 112.The lift control chamber 221 of two or more drivers can be controlled in a lift pilot pressure source 116 simultaneously.
Drive cylinder 211 has respectively drive cylinder first end 236 and drive cylinder the second end 237 up and down; Wherein, drive cylinder the second end 237 is provided in a side of the bottom of the second buffer area 253 of lift control cover first end 251, and it is along with lift control cover 250 floats.In drive cylinder 211, there is drive cylinder the first chamber 232 being limited by drive cylinder first end 236 and driven plunger the first end face 34 and drive cylinder the second chamber 234 being limited by drive cylinder the second end 237 and driven plunger the second end face 36.
Drive cylinder the first chamber 232 is connected with the first port 213 by power internal orifice 214.Power internal orifice 214 is selectable; The structural type that it can adopt 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.
Variable valve actuation device also comprises delivery outlet and the throttling arrangement 41 of the first chamber feeder current one-way valve 40, by two the first through holes 210 respectively (also can save described the first through hole 210, directly) be communicated with the first buffer area 254.First inlet opening of chamber feeder current one-way valve 40 and the other end of throttling arrangement 41 are connected to supercharging switching valve 90 and are driven switching valve 65 by the 3rd runner X3 and first flow X1.Throttling arrangement 41 for the first buffer area 254 provide controlled or confined go out stream, the pooling feature while entering the first buffer area 254 to help realizing driven plunger 30.But due to the amphicheirality of its throttling function, throttling arrangement 41 also hinders driven plunger 30 and leaves rapidly the first buffer area 254.In order to make up the defect of throttling arrangement 41 in the time that valve is opened, the first chamber feeder current one-way valve 40 in parallel can help to realize unobstructed influent stream with it.Due to its one-way, the throttling function of throttling arrangement 41 can not released and interfere to the first chamber feeder current one-way valve 40 in the time that driven plunger 30 enters the first buffer area 254.
Driving switching valve 65 shown in Fig. 1 and supercharging switching valve 90 are all two-position three-way valves, drive switching valve 65 to be responsible for the switching of driving direction or the switch of valve; And supercharging switching valve 90 is responsible for driving the switching of character, determine that driver carries out normal valve driving or cylinder is pressed releasing brake.
Drive the first valve port 651(of switching valve 65 or claim influent stream mouth) through the 5th runner X5(or title influent stream road) communicate with high pressure runner 110.High pressure runner 110 itself is general former in a certain pump, and additional pressure control structure more conventionally, adds accumulation of energy function even again.Drive the second valve port 652(of switching valve 65 also to claim refluxing opening) drive switching valve backflow road through the 4th runner X4(or title) communicate with low pressure runner 112.Low pressure runner 112 is connected system fuel tank (not shown) directly, also can be communicated with fuel tank by a certain back pressure apparatus (not shown), to set up metastable pressure again.Drive the 3rd valve port 653(of switching valve 65 also to claim delivery outlet, or working hole) be connected with the first valve port 901 of supercharging switching valve 90.The second valve port 902 of supercharging switching valve 90 communicates with the first port 213 by first flow X1.The 3rd valve port 903 of supercharging switching valve 90 is by being connected with the first port 213 after the 6th runner X6 and pressurized machine 50.
Pressurized machine 50 comprises: supercharging body 53; Large tank 62 and small oil tank 63, be built in described supercharging body 53; Large piston 51 and small piston 52, can be built in respectively in large tank 62 and small oil tank 63 slidably; Hyperbaric chamber 56, in small oil tank 63, with first flow X1 fluid communication; Low-pressure cavity 55 and intermediate cavity 61, two chambeies that are separated by the large piston 51 of the interior quilt of large tank 62, wherein close small piston 52 is intermediate cavity 61, low-pressure cavity 55 is passed through the 6th runner X6 fluid communication with supercharging switching valve 90; And selectable drain tap 64, to ensure that intermediate cavity 61 keeps lower pressure.Drain tap 64 can communicate with a certain low pressure runner or fuel tank (not shown) or atmosphere.
Large piston 51 and small piston 52 structurally can separate, and can be also structurally one.Function of increasing pressure is to realize by the equilibrium of forces of large piston 51 and small piston 52, large piston action face 54 is greater than small piston acting surface 57, therefore in the time of hydrostatic equilibrium, the pressure of small piston 52 place hyperbaric chambers 56 is greater than the pressure of large piston 51 place low-pressure cavity 55.If the diameter of large and small piston ratio is 1.5 times, the Area Ratio of large and small piston is 2.25 times, and the static pressure in high and low pressure chamber is 2.25 times than also.If the diameter of large and small piston ratio is 5 times, the Area Ratio of large and small piston is 25 times, and the static pressure in high and low pressure chamber is 25 times than also.
After the high-pressure liquid of next self-driven switching valve 65 and supercharging switching valve 90 enters low-pressure cavity 55, promote large piston 51 and the left of small piston 52 in Fig. 1 to movement, at the fluid of hyperbaric chamber 56, with higher Output pressure, the interior unnecessary fluid of intermediate cavity 61 overflows from drain tap 64 simultaneously.Pressurization is carried out until large piston 51 is encountered the second confined planes 60, and now, the driver in downstream also loses the power that continues motion, is controlled to certain displacement.As Fig. 1, design is depicted as Lb to intensifier piston stroke, be all to carry out mechanical position limitation by large piston 51, and the left end of small piston 52 in Fig. 1 is unrestricted at stroke two ends.In design, also can allow small piston 52 and large piston 51 define intensifier piston stroke (not shown) at left end and right-hand member mechanical position limitation respectively.As needed, also can in pressurized machine, add damping device, to limit the striking speed of large small piston in addition.
If definition
Sb: driver supercharging drives stroke, i.e. driver stroke in the time that pressurized machine is worked
Aa1: the area of driven plunger the first end face
Lb: intensifier piston stroke
Abs: small piston acting surface area
Vloss: leakage compensation volume
And supposition working medium or liquid are compressible hardly, have following design relation:
Abs?*Lb?=?Aa1*Sb?+?Vloss
Leakage compensation volume is wherein to press the part or all of fluid leakage in releasing brake process for making up cylinder, such as the under high pressure leakage from hyperbaric chamber 56 to intermediate cavity 61.If need, also the Volume Loss causing due to the compressibility of working medium can be included in to leakage compensation volume.Press in releasing brake application at cylinder of diesel engine, the lift of exhaust valve when driver supercharging drives stroke to be exactly cylinder pressure releasing brake, its numerical value is generally between 1 millimeter to 4 millimeters.
Pressurized machine 50 further comprises pressurized machine return spring 58, and it can be built in intermediate cavity 61 as shown in Figure 1, and its one end heads on large piston 51, helps large piston 51 and small piston 52 returning movements.Returning movement refers to that pressurized machine 50 is after low-pressure cavity 55 loses high pressure, and large piston 51 and small piston 52 move (be in Fig. 1 direction) to the right towards the direction that reduces low-pressure cavity 55 volumes, until large piston 51 is encountered the first confined planes 59.Under many operating modes, also enough promote the returning movement of large piston 51 and small piston 52 from the hydrodynamic pressure in drive cylinder the first chamber 232, but pressurized machine return spring 58 can ensure more fast or return more thoroughly.While permission in space, pressurized machine return spring 58 also can be built in hyperbaric chamber 56, and its right-hand member heads on small piston acting surface 57.
Pressurized machine 50 further comprises repairing one-way valve 85, its entrance and exit respectively with low-pressure cavity 55 and hyperbaric chamber 56 fluid communication, allow the unidirectional repairing from low-pressure cavity 55 to hyperbaric chamber 56 to flow, and limit rightabout mobile, so that pressurized machine 50 in return process or return supplement working solution for hyperbaric chamber 56 and adjacent channels after finishing, avoid inhaling sky or cavitation phenomenon.
Supercharging switching valve 90 can be as shown in Fig. 1 hydraulic operated valve, controlled by brake control pressure source 114, in the time that the pressure in brake control pressure source 114 is low pressure and high pressure, supercharging switching valve 90 is respectively in first 91 and second 92.Brake control pressure source 114 itself can be the output (not shown) of a two-bit triplet electromagnetic switching valve, and the input of this valve is high pressure runner 110 and low pressure runner 112.Two or more supercharging switching valves 90 can be controlled in a brake control pressure source 114 simultaneously.
Supercharging switching valve 90 was first shown in Fig. 1 91 o'clock, and pressurized machine 50 does not participate in the operation of driver, and driver carries out normal valve driving under the control that drives switching valve 65.In the time driving switching valve 65 first 66 shown in Fig. 1, the first port 213 is arranged working solution to low pressure runner 112.In the time driving switching valve 65 at second 67, high pressure runner 110 supplies working solution to the first port 213.
The 4th runner X4 communicates with the second port 217 through the second runner X2 halfway.Therefore, the second port 217 directly communicates with driving switching valve backflow road, and with this, drive cylinder 211 has formed an effective differential mechanics.In the time that high pressure runner 110 enters working solution through the 5th runner X5, X1 and X3 to drive cylinder the first chamber 232, drive cylinder the second chamber 234 is arranged working solution through the second port 217, the second runner X2 and the 4th runner X4 toward low pressure runner 112.In the time that drive cylinder the first chamber 232 is arranged working solution through first flow X1 and X4 etc. toward low pressure runner 112, some work liquid separates, mends working solution through the second runner X2 to drive cylinder the second chamber 234 from the 4th runner X4, and wherein low pressure runner 112 can suitably keep certain pressure with to improve the efficiency of differential feeder current.
Supercharging switching valve 90 is in the time of second 92, and pressurized machine 50 participates in operation, and driver carries out cylinder and presses releasing brake under the control that drives switching valve 65.In the time driving switching valve 65 at second 67, high-pressure liquid is from high pressure runner 110 low-pressure cavity 55 that supercharging switching valve 90 and the 6th runner X6 enter pressurized machine 50 of flowing through successively, promote large piston 51 and small piston 52 towards left motion in Fig. 1, the fluid being pressurized flows out into drive cylinder the first chamber 232 from hyperbaric chamber 56.Meanwhile, drive cylinder the second chamber 234 is arranged working solution through the second port 217, the second runner X2 and the 4th runner X4 toward low pressure runner 112.In the time driving switching valve 65 at first 66, drive cylinder the first chamber 232 is arranged working solution through first flow X1 and the 4th runner X4 etc. toward low pressure runner 112, some work liquid separates, mends working solution through the second runner X2 to drive cylinder the second chamber 234 from the 4th runner X4, and wherein low pressure runner 112 can suitably keep certain pressure with to improve the efficiency of differential feeder current.
Spring system 70 comprises cotter seat 71, valve return 72, valve guide bushing 73 and cylinder body 74.Described valve 80 comprises valve stem 81, valve head 82 and valve seat 83.Valve return 72 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 is supported by cylinder body 74 and cotter seat 71 simultaneously.In Fig. 1, due to the upwards driving force of valve return springs 72, valve 80 taken a seat (being that valve head 82 is pasting valve seat 83); Basic its tip position that arrives of driven plunger 30; Driven plunger the first end face 34 is near to or in contact with drive cylinder first end 236; Drive cylinder the first chamber 232 discharge opeings are to low pressure runner 112, and reach its minimum volume.
Spring system 70 also can be substituted by other driver return mechanism (not shown), such as having the pneumatic spring (not shown) of similar return function.Their point of force application can be on valve stem 81, indirectly acts on piston rod 31, also can be directly on piston rod 31.
As shown in Figure 1, valve head 82 just in time contacts valve seat 83, in closed condition.Number in the figure S2 represents high-lift, is substantially equal to the distance between driven plunger the second position of end face 36 in Fig. 1 to the position in the time that valve high-lift is opened.
When variable valve actuation device is during in high-lift operating mode (shown in Fig. 1), lift is switched pressure source 116 and lift control chamber 221 in lower pressure, and therefore lift control cover the second end 252 does not almost have hydrodynamic pressure.And drive cylinder the second chamber 234 on lift control cover maintains certain back pressure at least in the ordinary course of things, such as the pressure of low pressure runner 112.Although this back pressure is far below system high pressure PH, but it can produce enough hydrodynamic pressures on lift control cover first end 251, so that lift control cover 250 is controlled to the second place, that is, lift control cover the second end 252 contacts lift control cylinder the second end 228.Certainly, also can increase extra locking or spring reverse motion (not shown) and ensure that lift control cover 250 is in the second place.
In Fig. 1, valve is in closed condition, because drive switching valve 65 at first 66, the first port 213 and drive cylinder the first chamber 232 connect low pressure, and the hydrodynamic pressure of driven plunger the first end face 34 is lower, and driven plunger and valve keep its closed condition under the effect of valve return 72.
Switch pressure source 116 when lift and continue to keep low-pressure state, changeable air valve driver continues under high-lift operating mode, and drives switching valve 65 to switch to second 67, and valve starts to open and remain on the state of standard-sized sheet.The first port 213 and drive cylinder the first chamber 232 connect the system high pressure PH of high pressure runner 110, and high-pressure work liquid enters drive cylinder the first chamber 232.When valve has just started to open, (driven plunger 30 or driven plunger the first end face 34 are also in the first buffer area 254, in Fig. 1, do not show), working solution can enter drive cylinder the first chamber 232 by drive cylinder the first chamber feeder current one-way valve 40, to make up throttling arrangement 41 and the first restriction of notch 212 to flow velocity.After driven plunger 30 is walked out the first buffer area 254, working solution mainly unimpededly enters drive cylinder the first chamber 232 by the first port 213.In valve opening procedure, the working solution in drive cylinder the second chamber 234 is discharged to low pressure runner 112 by the second port 217, the second runner X2 and the 4th runner X4 successively.
In order to realize the little lift of valve, lift is switched pressure source 116, therefore lift control chamber 221 is in high pressure conditions, force and drive lift control cover 250 to primary importance, as shown in Figure 2, lift control cover first end 251 heads on lift control cylinder first end 227.In the state shown in Fig. 2, drive switching valve 65 to be positioned at first 66, the first port 213 and to connect low pressure, on driven plunger the first end face 34, there is no large hydrodynamic pressure, therefore valve 80 under the dominant force of spring force in closed condition.
Connect high pressure if drive switching valve 65 to switch to its second 67, the first ports 213, on driven plunger the first end face 34, have enough large hydrodynamic pressure to overcome spring force and open valve 80.The aperture of valve equals little lift S1, driven plunger the second end face 36 from its among Fig. 2 when valve-closing position to the distance of position in the time that the little lift of valve is opened.The stroke of driven plunger 30 is subject to the restriction of lift control cover 250.In design, the area of lift control cover the second end 252 ideally should be enough large, ensure on this area hydrodynamic pressure under high pressure and spring force (both are all upwards) from spring system 70 make a concerted effort to be enough to overcome downwards make a concerted effort so that lift control cover 250 keeps its control positions and loosening.This makes a concerted effort downwards to comprise: hydrodynamic pressure under high pressure on driven plunger the first end face 34, lift control cover first end 251 hydrodynamic pressure under low pressure, and the transient force that produces at drive cylinder the second end 237 while entering the second buffer area 253 fast of driven plunger 30.In design, also can only ensure upwards make a concerted effort only enough overcome static making a concerted effort downwards, allow lift control cover 250 to have the loosening of transient state downwards, the little lift motion of valve has the overshoot of transient state thus.
The variable actuator of second embodiment of the invention shown in Fig. 3, comprising: actuator housing 21; Drive cylinder 211, in described actuator housing 21, limits and has the longitudinal axis of the first and second directions, and have drive cylinder first end 236 in one end of first direction, has drive cylinder the second end 237 in one end of second direction; Driven plunger 30 can slide between described drive cylinder first end 236 and described drive cylinder the second end 237 in described drive cylinder 211, has respectively driven plunger the first end face 34 and driven plunger the second end face 36 at the two ends of the first and second directions; Piston rod 31, can be operatively connected to described driven plunger the second end face 36; Drive cylinder the first chamber 232 is space in drive cylinder 211, between described drive cylinder first end 236 and described driven plunger the first end face 34; Drive cylinder the second chamber 234 is the space between described driven plunger the second end face 36 and described drive cylinder the second end 237; Spring system 70, can operatively act on described piston rod 31; The first port 213 and the second port 217, in described actuator housing 21, be connected with described drive cylinder the second chamber 234 fluids with described drive cylinder the first chamber 232 respectively; And driving switching valve 65, first flow X1, pressurized machine 50 and supercharging switching valve 90, described driving switching valve 65 is connected with described drive cylinder the first chamber 232 with described pressurized machine 50 by described supercharging switching valve 90 and described first flow X1 in parallel successively, described supercharging switching valve 90 is opened described first flow X1 at 91 o'clock so that described variable valve actuation device carries out driven function first of its supercharging switching valve, and described supercharging switching valve 90 is opened described pressurized machine 50 and pressed releasing brake function so that described variable actuator is carried out cylinder in the time of its supercharging switching valve second 92.
Again as shown in Figure 3, the present embodiment two is with embodiment one main difference part: the present embodiment two does not comprise (as depicted in figs. 1 and 2) lift control cover 250, lift control cylinder 220, lift control chamber 221, lift control mouth 224 and the lift pilot pressure source 116 in embodiment one.Therefore, the present embodiment two only has a lift (S in Fig. 3), there is no high-lift (S2 in Fig. 1) and little lift (S1 in Fig. 2) in embodiment one.
Comprise with main identical point of the embodiment one: the present embodiment two also can carry out cylinder and press releasing brake function, its stroke is that driver supercharging drives stroke (or Sb).
Certainly, in design, lift S can have numerical value close or that equate with high-lift S2.In some engine application, a lift S meets normal valve actuation function substantially.In some engine application, also can adopt driver supercharging to drive stroke Sb to carry out other little lift function, be not limited to cylinder and press releasing brake function.The application of driver of the present invention is also not limited to aspect motor or engine valve.
In addition, the spring system 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 of variable valve actuation device return mechanism, will not enumerate herein.In addition, in the present invention, various switching valves and control valve are not limited to structure, combination or the control form of above-mentioned switching valve and control valve, can be replaced by other structure, combination or control form.Such as, drive the two-bit triplet valve arrangement of switching valve 65 in Fig. 1 to substitute (not shown) by two 2/2-way valves; Drive the electromagnetism of switching valve 65 in Fig. 1 directly to move control form and can add that the two-stage valve of the main valve that surges replaces (not shown) by electromagnetic priority valve; A normally open valve can be replaced by a normally close valve, otherwise or; The valve of Single electromagnet control can be replaced by the valve of double electromagnet control.The electrichydraulic control form of supercharging switching valve 90 in Fig. 1 also can be replaced by Mechanical Driven form, on driver module such as whole row's engine exhaust port, a mechanical braking COMM communication (not shown) can be installed, can stir or switch simultaneously the spool of all supercharging switching valves by mechanical means (instead of the means of surging), and the action of mechanical braking COMM communication itself can be realized by a certain electric liquid or Electric actuator.
In the present invention, same lift is switched pressure source 116 also can control at least two variable actuator simultaneously, and the working hole of this lift switching control valve is connected with the lift control mouth of all controlled variable actuator.Such as in a motor, same lift switching pressure source 116 can be controlled the variable actuator of all intake valves and/or exhaust valve.
In the present invention, same driving switching valve 65 also can be controlled two or more variable actuator (not shown) simultaneously, and the working hole of this driving switching valve is connected with the second port 217 with all the first ports 213 of being controlled variable actuator respectively with refluxing opening.Such as on a cylinder, same driving switching valve 65 can two intake valves of synchronization control or the variable actuator of two exhaust valves.
In the present invention, many runners (such as runner X1, X2, X3, X4, X5, X6) are structurally not necessarily independent of actuator housing 21, shown independence of structure or the just convenience in order to describe or to illustrate of presentation of independence in each figure.If needed, they any can directly be combined in actuator housing 21, coupled like this port (such as the first port 213, the second port 217, the 3rd port 226) can be also the part continuous with runner, instead of artificial openning (port).
Lift control in the present invention is enclosed between primary importance and the second place switches.In the time of primary importance and the second place, variable actuator also can adopt machinery, electromechanics, machine liquid or mechanical electronic hydraulic locking device (not shown) to help or replace the control of above-mentioned hydraulic type lift, to stablize lift control cover, ensures the precision of valve lift.
Throttling arrangement 41 shown in Fig. 1 to Fig. 3 can be replaced by (not shown in the figures) variable throttling device thereof.Effective restriction of a variable throttling device thereof can change or regulate according to the variation of operating mode (similar operating temperature) or system requirements (rotating speed of similar motor).Effectively the regulative mode of restriction comprises: regulate the area of single or multiple restrictions, such as passing ratio valve or proportional throttle valve; Change the series and parallel combination relation of multiple restrictions; And partial throttling mouth in the combination of the multiple restrictions of shutoff, such as insertion switch valve in restriction combination.
Variable actuator of the present invention 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 ensure reliability and the low cost in application.In the present invention, valve is by lift control cover mechanical position limitation in the position of opening, the therefore 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, therefore combustion efficiency and discharge quality.Also can reduce the possibility of valve and internal combustion engine collision to the control of lift overshoot.
The present invention is further integrated in pressurized machine in variable valve actuation device, can help to press when releasing brake the working pressure in driven plunger is amplified to many times of system pressure at cylinder, is enough to open near exhaust valve top dead center.Amplify by this pressure is local, do not need to adopt expensive high-pressure service pump and high-pressure solenoid valve, the appropriate design size that has kept again driven plunger to be determined by agility simultaneously.
Be appreciated that variable actuator of the present invention (also can be described as variable valve actuation device) can be used on valve control, also can be used in other has the occasion of similar motion control.
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, but 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 (24)
1. a variable actuator, is characterized in that, it comprises:
Actuator housing;
Drive cylinder, in described actuator housing, limits and has the longitudinal axis of the first and second directions, and have drive cylinder first end in one end of first direction, has drive cylinder the second end in one end of second direction;
Driven plunger can slide between described drive cylinder first end and described drive cylinder the second end in described drive cylinder, has respectively driven plunger the first end face and driven plunger the second end face at the two ends of the first and second directions;
Piston rod, can be operatively connected to described driven plunger the second end face;
Drive cylinder the first chamber is space in drive cylinder, between described drive cylinder first end and described driven plunger the first end face;
Drive cylinder the second chamber is the space between described driven plunger the second end face and described drive cylinder the second end;
Spring system, can operatively act on described piston rod;
The first port and the second port, in described actuator housing, be connected with described drive cylinder the second chamber fluid with described drive cylinder the first chamber respectively; And
Drive switching valve, first flow, pressurized machine and supercharging switching valve, described driving switching valve is connected with described drive cylinder the first chamber with described pressurized machine by described supercharging switching valve and described first flow in parallel successively, described supercharging switching valve is opened described first flow so that described variable actuator is carried out driven function in the time of first of its supercharging switching valve, and described supercharging switching valve is opened described pressurized machine and pressed releasing brake function so that described variable actuator is carried out cylinder in the time of its supercharging switching valve second.
2. variable actuator according to claim 1, is characterized in that, described pressurized machine comprises:
Supercharging body;
Large tank and small oil tank, be built in described supercharging body;
Large piston and small piston, can be built in respectively in described large tank and described small oil tank slidably;
Hyperbaric chamber, in described small oil tank, with described first flow fluid communication;
Low-pressure cavity and intermediate cavity, two chambeies that are separated by by large piston in described large tank, wherein close described small piston is described intermediate cavity, described low-pressure cavity and described supercharging switching valve fluid communication; And
Drain tap.
3. variable actuator according to claim 2, is characterized in that, described pressurized machine further comprises pressurized machine return spring, to help the returning movement of described large piston and small piston.
4. variable actuator according to claim 2, it is characterized in that, described pressurized machine further comprises repairing one-way valve, its entrance and exit respectively with described low-pressure cavity and described hyperbaric chamber fluid communication, flow from described low-pressure cavity to the unidirectional repairing of described hyperbaric chamber allowing.
5. variable actuator according to claim 2, is characterized in that,
Described variable actuator has driver supercharging and drives stroke;
Described driven plunger first end mask has driven plunger the first face area;
Described pressurized machine has intensifier piston stroke, and stroke two ends are all mechanical position limitations;
Described small piston has small piston acting surface area;
Described variable actuator has leakage compensation volume; And
Product=described driven plunger first face area of described small piston acting surface area and described intensifier piston stroke and described driver supercharging drive the product+described leakage compensation volume of stroke.
6. variable actuator according to claim 1, is characterized in that,
Described variable actuator has driver supercharging and drives stroke, and its numerical value is between 1 millimeter to 4 millimeters.
7. variable actuator according to claim 1, is characterized in that, comprises brake control pressure source, and described supercharging switching valve is two-position three-way valve, and its switching function is controlled by described brake control pressure source.
8. variable actuator according to claim 1, is characterized in that, comprises mechanical braking COMM communication,
Described supercharging switching valve is two-position three-way valve, and its switching function is switched by described mechanical braking COMM communication.
9. variable actuator according to claim 7, is characterized in that,
There are high pressure and two grades of pressure of low pressure in described brake control pressure source;
When described brake control pressure source is during in low pressure, described supercharging switching valve is communicated with described driving switching valve with described first flow; And
When described brake control pressure source is during at high pressure, described supercharging switching valve is communicated with described driving switching valve with the described low-pressure cavity of described pressurized machine.
10. variable actuator according to claim 7, is characterized in that, at least two described variable actuator are controlled in described brake control pressure source simultaneously.
11. variable actuator according to claim 2, is characterized in that, described large piston and small piston are structurally one.
12. variable actuator according to claim 1, is characterized in that, comprising:
Lift control cylinder, in described actuator housing, extends to second direction from described drive cylinder, and has respectively lift control cylinder first end and lift control cylinder the second end at the two ends of the first and second directions;
Lift control cover, in described lift control cylinder, can slide between described lift control cylinder first end and described lift control cylinder the second end, and there is respectively lift control cover first end and lift control cover the second end at the two ends of the first and second directions;
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 switched pressure source, be connected with described lift control chamber fluid, be enclosed within the switching between described lift control cylinder first end and described lift control cylinder the second end to control described lift control, control thus the switching of described variable actuator between little lift and high-lift;
Described drive cylinder the second end is arranged on described lift control cover first end, floating with described lift control cover; With
Described piston rod can pass described lift control cover slidably.
13. variable actuator according to claim 12, is characterized in that, described lift control cover first end is provided with the groove with certain depth, and this groove is the second buffer area, and the bottom of this groove is described drive cylinder the second end.
14. variable actuator according to claim 12, is characterized in that, described lift switching pressure source fluid is connected in the described lift control chamber of at least two described variable actuator.
15. variable actuator according to claim 1, is characterized in that, comprising:
Low pressure runner; Drive switching valve refluxing opening; Drive switching valve backflow road, connect described driving switching valve refluxing opening to described low pressure runner; Drive switching valve influent stream mouth; High pressure runner, is connected with described driving switching valve influent stream mouth fluid; The direct fluid of described the second port is connected to described driving switching valve backflow road, to form differential function.
16. variable actuator according to claim 1, is characterized in that, also comprise: drive switching valve refluxing opening; Fuel tank; Drive switching valve backflow road, connect described driving switching valve refluxing opening to described fuel tank; Back pressure apparatus, is arranged in described driving switching valve backflow road; Drive switching valve influent stream mouth; High pressure runner, is connected with described driving switching valve influent stream mouth fluid; The direct fluid of described the second port is connected to described driving switching valve backflow road, and tie point is between described driving switching valve refluxing opening and described back pressure apparatus, to form differential function.
17. variable actuator according to claim 1, is characterized in that, also comprise:
Engine valve, it further comprises valve stem, this valve stem can operatively connect described piston rod;
Wherein, described spring system acts on described piston rod through described valve stem.
18. variable actuator according to claim 1, is characterized in that, also comprise:
Engine exhaust port, it further comprises valve stem, this valve stem can operatively connect described piston rod;
Wherein, described spring system acts on described piston rod through described valve stem.
19. variable actuator according to claim 1, is characterized in that, also comprise:
Power internal orifice, on described drive cylinder, is connected with described drive cylinder the first chamber fluid with described the first port.
20. variable actuator according to claim 1, is characterized in that, also comprise:
The first chamber feeder current one-way valve, its delivery outlet fluid is connected in described drive cylinder the first chamber, to help described variable actuator to open the quick startup of stroke; And
Throttling arrangement, fluid is connected in described drive cylinder the first chamber, the buffering when helping described driven plunger to approach described drive cylinder first end.
21. variable actuator according to claim 20, is characterized in that, effective restriction of described throttling arrangement can regulate.
22. variable actuator according to claim 1, is characterized in that, each described driving switching valve is connected in the described drive cylinder of at least two described variable actuator.
23. variable actuator according to claim 1, is characterized in that, each described pressurized machine and described supercharging switching valve are connected in the described drive cylinder of at least two described variable actuator.
24. variable actuator according to claim 2, is characterized in that, the diameter of described large piston and small piston is 1.5-5.0 than scope.
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| CN201410134300.9A CN104088681B (en) | 2014-04-04 | 2014-04-04 | Variable actuator |
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| CN201410134300.9A CN104088681B (en) | 2014-04-04 | 2014-04-04 | Variable actuator |
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Cited By (6)
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| CN105485407A (en) * | 2015-12-29 | 2016-04-13 | 沪东重机有限公司 | Gas exhaust valve drive system with stroke capable of being compensated and regulated |
| CN105781662A (en) * | 2016-05-04 | 2016-07-20 | 哈尔滨工程大学 | Double-electromagnetism cooperative control boosting-type air distribution system |
| CN106703928A (en) * | 2016-12-28 | 2017-05-24 | 沪东重机有限公司 | Exhaust valve control execution system directly driven by servo oil |
| CN106848587A (en) * | 2017-03-10 | 2017-06-13 | 京信通信系统（中国）有限公司 | Multichannel transmission mechanism and antenna |
| CN107476841A (en) * | 2017-08-10 | 2017-12-15 | 中国北方发动机研究所(天津) | A kind of gear-type hydraulic variable valve actuator for air based on rotor control |
| CN111156064A (en) * | 2019-12-25 | 2020-05-15 | 浙江吉利新能源商用车集团有限公司 | Electric control valve structure and engine |
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| CN111156064A (en) * | 2019-12-25 | 2020-05-15 | 浙江吉利新能源商用车集团有限公司 | Electric control valve structure and engine |
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|---|---|
| CN104088681B (en) | 2016-08-17 |
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Owner name: NINGBO HUAYE MACHINE MANUFACTURE CO., LTD. Free format text: FORMER OWNER: JIANGSU GONGDA POWER TECHNOLOGY CO., LTD. Effective date: 20150518 |
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Effective date of registration: 20150518 Address after: 315131 Zhejiang city of Ningbo Province Wang town Yinzhou District week Jiacun Applicant after: Ningbo Hoyea Machine Manufacturing 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. |
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Granted publication date: 20160817 Termination date: 20210404 |
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