CN204532541U

CN204532541U - Double-crankshaft variable compression ratio engine

Info

Publication number: CN204532541U
Application number: CN201520174693.6U
Authority: CN
Inventors: 唐明龙
Original assignee: TIANJIN QIANJING TECHNOLOGY CONSULTING Co Ltd
Current assignee: TIANJIN QIANJING TECHNOLOGY CONSULTING Co Ltd
Priority date: 2015-03-26
Filing date: 2015-03-26
Publication date: 2015-08-05
Anticipated expiration: 2025-03-26

Abstract

A kind of double-crankshaft variable compression ratio engine, comprise the structure that the double-crankshaft after optimization and variable-compression-ratio piston combine, it is characterized in that, variable-compression-ratio piston is using the cylinder sleeve (401) of outer piston as double-acting hydraulic cylinder, the cover plate (403) of stationary ring on the opening of cylinder sleeve (401), inner piston rod passes through in the middle of cover plate (403), the space of cylinder sleeve is divided into by the inner carrier (402) of double-acting hydraulic cylinder, lower oil hydraulic cylinder, the control valve pocket of center mounting hole (4023) the internal fixtion sliding valve style position control valve of inner carrier, install in undercrown surface center mounting hole (4011) rotational slide installation or nut-screw rod and control spool, twin crankshaft engine counterrotating bent axle by gear be coupled together synchronous backward rotate, each piston is connected with the pitman shaft of two bent axles, and the driveshaft (808,807) reserving variable-compression-ratio piston in the bent axle of twin crankshaft engine, the centre of connecting rod passes through position, piston control valve driving mechanism (800) is arranged between two bent axles.

Description

Double-crankshaft variable compression ratio engine

Technical field

The present invention relates to a kind of reciprocating-piston engine, especially can change the twin crankshaft engine of compression ratio.

Background technique

The upper and lower stop of known common engine is fixed, and compression ratio is fixed, and cause to adjust air inflow and carry out the petrol engine of Modulating Power when low-load, igniter pressure is low, and efficiency of heat engine is low, and the motor of Ratios can address this problem.

Known variable compression ratio engine has mobile cylinder cap, mobile bent axle, changes piston length by hydraulic pressure, and changes the modes such as piston length by spring and hydraulic pressure cooperation.Mobile cover type has formed product, and confirms that variable compression ratio engine significantly can save oil consumption.The variable compression ratio engine moving member of mobile cover type and mobile curved shaft type increases the driving cam of valve and the complexity of pto＝power take-off greatly, simultaneously, there is no large-scale promotion at present.Coordinate by hydraulic pressure and spring the scheme changing piston with hydraulic pressure, because piston is the parts of a high-speed motion, the difficulty reliably arranging hydraulic pipe line is very large.

The present inventor devises a kind of piston (2012204098128) of self-pump type's variable compression ratio in early stage, be double-acting oil hydraulic cylinder by plunger designs, be connected with connecting rod at the inner carrier of oil hydraulic cylinder, inner carrier and cylinder body are installed respectively and are controlled valve pocket and control spool, control spool and are divided into axial motion type and rotary.The inner cylinder of two kinds of control valve pockets all there is fluid passage respectively with upper, lower oil hydraulic cylinder communicates, controlling in the middle of valve pocket is seal section, revolving control spool outside cylinder has spirality fluid passage, there is annular fluid passage the centre of the control spool of axial motion type cylinder outside, control valve core ribbon central through bore, central through bore communicates with the fluid passage on outer cylinder, central through bore is respectively by one-way valve and upper, lower oil hydraulic cylinder communicates, the control spool of spirality fluid passage is had by rotating outer cylinder, or move axially the control spool that outer cylinder has annular fluid passage, the fluid passage on control spool outer cylinder and the upper fluid passage controlling valve pocket inner cylinder can be made, lower fluid passage communicates, when controlling the fluid passage on spool outer cylinder when communicating with fluid passage in inner cylinder on valve pocket, when upper oil hydraulic cylinder pressurized, the hydraulic oil of (typicalness is expansion stroke and lower) upper oil hydraulic cylinder is entered by upper oil hydraulic cylinder and controls spool by oil hydraulic cylinder under one-way valve inflow, promotion inner carrier moves upward, piston length shortens, inner carrier moves simultaneously, when the seal section that control valve puts is relative with the fluid passage on spool, fluid passage on spool and upper, lower oil hydraulic cylinder does not all communicate, inner carrier position is fixed, equally, when controlling the fluid passage on spool outer cylinder and communicating with fluid passage under control valve pocket inner cylinder, when lower oil hydraulic cylinder pressurized, under (typicalness suction stroke and exhaust stroke latter stage), the hydraulic oil of oil hydraulic cylinder is entered by lower oil hydraulic cylinder and controls spool and flow into upper oil hydraulic cylinder by one-way valve, promotion inner carrier moves downward, the upper of inner carrier is just achieved like this by moving valve core, lower movement, change the length of piston, do not need the transfer passage of hydraulic oil, do not increase again the configuration difficulty of other parts, but the connecting rod small end that routine is started is positioned at piston axis place, the controlling rod of spool must be arranged on side, piston is caused to be non-symmetry structure, the cylinder cap of the piston of double hydraulic cylinder formula is not suitable for adopting the better simply screw thread of structure to install, structure is more complicated, the piston (2012204098128) of self-pump type's variable compression ratio in early stage does not consider that working solution body heat is splashed swollen problem yet, one-way valve is have employed in the piston of self-pump type's variable compression ratio, but one-way valve is by the impact of piston movement acceleration, running parameter design difficulty is large.

Known motor is generally single shaft type, but the motor of double-crankshaft also has research and experiment, twin crankshaft engine motor has two bent axles, each piston is connected by connecting rod with two bent axles simultaneously, two crank teeth are combined, two bent axle anti-phase rotations respectively, the side pressure of piston can be eliminated, two crank spindles and connecting rod major axial diameter can reduce simultaneously, reduce frictional loss, but some data of tool introduce this motor may upper, lower two connecting rod asynchrony phenomenons, cause job insecurity, the problems referred to above solve by adopting increase coupling shaft, present inventor is found by research, when two bent axles are by gear coupling, when being exported by single drive shaft again, due to during engine operation be outwards export energy (expansion stroke) with alternately occur from outer absorption energy, coupling gear can be caused to be in positive and negative drive condition continually, coupling working gear state is very severe, gear life can be caused extremely short.

Summary of the invention

The technical problems to be solved in the utility model is: the problem that (1) pressure-variable piston is larger than piston difficulty of processing, and (2) double-crankshaft variable compression ratio engine control valve is by the problem of acceleration action; (3) the variable piston hydraulic cylinder works liquid problem of expanding with heat and contract with cold, (4) variable-compression-ratio piston controls the problem that spool upper and lower end face pressure reduction may cause the working state that controls large problem (5) the twin crankshaft engine coupling gear of spool steering force severe.

Concrete technological scheme is: twin crankshaft engine and variable-compression-ratio piston are combined, variable-compression-ratio piston is using the cylinder sleeve of outer piston as double-acting hydraulic cylinder, the cover plate of stationary ring on the opening of cylinder sleeve, inner piston rod passes through in the middle of cover plate, the space of cylinder sleeve is divided into by the inner carrier of double-acting hydraulic cylinder, lower oil hydraulic cylinder, the control valve pocket of the center mounting hole internal fixtion sliding valve style position control valve of inner carrier, install in the rotational slide installation of undercrown surface center mounting hole or nut-screw rod and control spool, the control spool of variable-compression-ratio piston sliding valve style directional control valve installs driveshaft, the sliding sleeve of linear slide is installed in driveshaft bottom, bottom rotary drive mechanism drives sliding sleeve, to be counterrotating bent axle rotated by the gear synchronous backward that is coupled together twin crankshaft engine, each piston is connected with the pitman shaft of two bent axles, reserve the driveshaft of variable-compression-ratio piston by position in the bent axle of twin crankshaft engine, the centre of connecting rod, piston control valve driving mechanism is arranged between two bent axles, difference Flywheel on each bent axle of twin crankshaft engine, position control valve is when state of equilibrium, and directional control valve is in closed condition, works as rotary spool, spool oil into and out of hydraulic fluid port relatively on move time, spool oil outlet and upper oil hydraulic cylinder company can lead to, and filler opening is communicated with lower oil hydraulic cylinder, upper oil hydraulic cylinder discharge opeing, lower oil hydraulic cylinder feed liquor, inner carrier moves, and drives on valve pocket simultaneously and moves, the relative position aftertaste of spool and valve pocket is to closed condition, motion stops, and piston overall length shortens, otherwise piston length is elongated, because motor is in movement process, it is stressed is periodicity pulling force and pressure, cause the pressure cycle change that two acting cylinder are, it is low pressure liquid that the variable-compression-ratio piston of the present invention's design controls working liquid body, and the lubrication of direct engine lubrication system controls working liquid body as variable-compression-ratio piston.

Flywheel distinguished by each bent axle to above-mentioned change in the twin crankshaft engine of compression ratio, the crankshaft-flywheel optimized adopts distributing, distributing flywheel adopts full symmetric structure, distribution two counterweight blocks on each cylinder of i.e. bent axle, the additional flywheels while of on each counterweight block, also can the dispersion flywheel of extraction Lightened structure, Lightened structure one is: on two bent axles that each cylinder is corresponding each a band balancer weight is installed crank arm and a crank arm not only with balancer weight but also with flywheel, Lightened structure two is: each crank arm installing a band balancer weight on two bent axles that each cylinder is corresponding, on two bent axles, different crank arm is alternately distributed.

The bent axle optimized adopts the structure being separated completely or being partly separated, being separated bent axle is completely main shaft, crank arm, connecting rod macro-axis is separated, part separation bent axle is connecting rod macro-axis is separated type, hot charging interference fit is adopted to link between main shaft and crank arm, or adopt the conical interference-fit of fastened by screw to link, interference fit is adopted to link between crank arm and connecting rod macro-axis, now to first connecting rod be arranged on bar macro-axis, interference fit links again, also sliding connection can be adopted between crank arm and connecting rod macro-axis, crank arm connecting rod macro-axis not containing flywheel is blind-hole type, crank arm flywheel containing flywheel is that edge is thick, intermediate thin, annular space is left between flywheel and cylinder body dividing plate, connecting rod macro-axis is not installing thrust mechanism containing the axle head of the crank arm of flywheel, rely on blind hole thrust, at the crank arm containing flywheel, thrust mechanism is installed, the cylinder body of the position corresponding with connecting rod macro-axis arranges connecting rod macro-axis mounting hole, for installing connecting rods macro-axis and thrust mechanism.

The piston rod Placement optimized is: three axles connect, the inner carrier push rod of piston is slidably matched by three hole connectors, wrist pin, connecting rod small end axle and is linked together by connecting rod, connnecting rod big end axis hole is slidably installed on connecting rod macro-axis, three hole connectors are two dihedral plates of distribution three axis holes, an entirety is formed by connecting plate, for controlling the passing hole of spool driveshaft in the middle of connecting plate, larger axis hole is piston pin hole, two less axis holes are connecting rod small end axis hole, and preferred three hole connector middle opening parts are the structure outwards increased.

The above-mentioned variable-compression-ratio piston changed in the twin crankshaft engine of compression ratio is double-acting hydraulic cylinder formula, the upper installation sliding valve style control valve of oil hydraulic cylinder, the valve pocket of control valve is fixed on inner carrier, the Spool rotating of control valve is slidably mounted on the internal surface of piston top, or the spool of control valve is arranged on the internal surface of piston top with feed screw nut, the driveshaft of spool adopts the sliding sleeve of axial sliding type to drive, the driveshaft of spool is hollow type, rotate slide core, slide core moves relative to outer piston axis, the replenisher of oil hydraulic cylinder or the working solution of oil hydraulic cylinder are carried by the driveshaft of hollow.Control valve is divided into six kinds of (1) 3-position-3-way axis to move self-pump type, (2) 3-position-3-way spiral chute self-pump type, the outer liquid formula of (3) three groove sliding sleeve 3-position 4-ways, the outer liquid formula of (4) two groove sliding sleeve 3-position 4-ways, (5) 3-position 4-way spiral chute genesis analysis formula, (6) 3-position 4-way spiral chute circle distribution formula.

The sliding valve style directional control valve control valve embodiment 1 of variable-compression-ratio piston is: 3-position-3-way axis moves self-pump type's variable-compression-ratio piston control valve, main control valve structure is equivalent to 3-position-3-way directional control valve, valve pocket there are two annular grooves, upper annular groove is that upper cylinder half annular groove communicates with upper oil hydraulic cylinder, lower annular groove is annular groove under lower cylinder, communicate with lower oil hydraulic cylinder, on, be valve pocket seal section between lower annular groove, spool is hollow type, there is hydraulic oil outflow opening at middle part, hydraulic oil outflow opening communicates with the center hole of spool, hydraulic oil outflow opening in the middle part of spool can be separately cellular type, also an annular groove can be established, hydraulic oil outflow opening diameter in the middle part of spool or be highly less than or equal to the height of valve pocket seal section, hydraulic oil ostium is established at spool two ends, hydraulic oil ostium installs one-way valve, one-way valve flow direction is to outflow by spool, the outlet of upper one-way valve communicates with upper oil hydraulic cylinder, lower one-way valve communicates with lower oil hydraulic cylinder, one-way valve is installed at the driveshaft top of spool, one-way valve liquid flow path direction from bottom to top, spool is slidably mounted in valve pocket, valve pocket is fixed on inner carrier, spool nut and screw mandrel are arranged in the internal surface center mounting hole of piston top, one-way valve adopts circlip type to move horizontally one-way valve, piston arranges safety installations, eliminate security risk when hydraulic oil heat is splashed swollen, control spool arranges decompression longitudinal hole and is in communication with the outside in the space of spool mounting hole, longitudinal hole does not communicate with center hole, reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force, the driveshaft of rotational valve core bottom, spool is upper and lower relative to outer piston to be moved axially, and valve pocket and spool relativeness have three kinds of states, and (1) valve pocket seal section is relative with core hydraulic oil tap hole, and the liquid between upper and lower oil hydraulic cylinder does not flow, (2) on valve pocket, annular groove is relative with core hydraulic oil tap hole, when the pressure of upper oil hydraulic cylinder is greater than the pressure of lower oil hydraulic cylinder, the liquid of upper oil hydraulic cylinder flows into spool, flows into lower oil hydraulic cylinder, when the pressure of upper oil hydraulic cylinder is less than or equal to the pressure of lower oil hydraulic cylinder through lower one-way valve, two cylinder liquid do not flow, along with oil hydraulic cylinder under the flow direction of upper oil hydraulic cylinder, inner carrier moves up, and piston total length shortens, when valve pocket seal section is relative with core hydraulic oil ostium, two oil hydraulic cylinder liquid do not flow, (3) under valve pocket, annular groove is relative with core hydraulic oil tap hole, instantly when the pressure of oil hydraulic cylinder is greater than the pressure of oil hydraulic cylinder, the liquid of lower oil hydraulic cylinder flows into spool, flows into upper oil hydraulic cylinder, when the pressure of oil hydraulic cylinder is less than or equal to the pressure of oil hydraulic cylinder instantly through upper one-way valve, two cylinder liquid do not flow, along with oil hydraulic cylinder on the flow direction of lower oil hydraulic cylinder, inner carrier moves down, and piston total length is elongated, valve pocket seal section is relative with core hydraulic oil tap hole, and two oil hydraulic cylinder liquid do not flow, during due to engine operation, the pressure alternately change of two oil hydraulic cylinders, always the fluid in two cylinders can rotate with driveshaft and flow, realizes piston length change.

3-position-3-way axis moves self-pump type's variable-compression-ratio piston control valve and arranges safety installations, eliminate security risk when hydraulic oil heat is splashed swollen, safety installations scheme 1, mounting safety valve on valve pocket, safety valve import communicates with lower oil hydraulic cylinder, outlet drain is to piston exterior, and opening pressure of safety valve is greater than the working pressure of engine peak speed oil hydraulic cylinder at present; Safety installations scheme 2 is the safety installations simplified, and changes the seal ring between inner piston rod and oil hydraulic cylinder cover plate into opening ring type, utilizes opening slowly to miss the safety ensureing to pacify oil hydraulic cylinder.

3-position-3-way axis moves the one-way valve in self-pump type's variable-compression-ratio piston control valve, is circlip type horizontal single-headed valve, and adopt the structure moving horizontally spool, the optional ball valve of spool, cone valve, column valve, the Returnning spring of one-way valve is open ring structure.

The unidirectional inflow valve at driveshaft top, be made up of spool and overcoat, spool is divided between center hole, lower center hole, upper and lower center hole and is not communicated with, lower horizontal installs one group (2 to 4) unidirectional outflow valve (flowing out from driveshaft center hole), unidirectional outflow valve is distributed on ring week, top arranges one group of (2 to 4) horizontal through hole, the outside interference fit of spool installs overcoat, between overcoat and spool, gap is stayed at middle part, be communicated with horizontal through hole by unidirectional outflow valve, unidirectional outflow valve is circlip type horizontal single-headed valve.

The sliding valve style position control valve embodiment 2 that variable-compression-ratio piston is installed is: 3-position-3-way spiral chute self-pump type variable-compression-ratio piston control valve, main control valve structure is equivalent to 3-position-3-way directional control valve, valve pocket there are two groups of cannelures, upper cannelure is that upper cylinder half cannelure communicates with upper oil hydraulic cylinder, lower cannelure is that under lower cylinder, cannelure communicates with lower oil hydraulic cylinder, on, be seal section between lower cannelure, spool is hollow type, it is hydraulic oil tap hole in the middle part of spool, communicate with the center hole of spool, in the middle part of spool, outer cylinder establishes spiral chute, in the middle part of spool, hydraulic oil tap hole is arranged in spiral chute, valve pocket cannelure and spiral chute phase cross surface place, when valve pocket seal section is in the middle of spiral chute, seal section can sealing screw groove completely, spool upper, under have hydraulic oil ostium, in hydraulic oil ostium, one-way valve is installed, one-way valve flow direction is to outflow by spool, the outlet of upper one-way valve communicates with upper oil hydraulic cylinder, lower one-way valve communicates with lower oil hydraulic cylinder, one-way valve is installed at the driveshaft top of spool, spool is slidably mounted in valve pocket, valve pocket is fixed on inner carrier, spool setscrew nut and positioning step rotational slide are arranged in the internal surface center mounting hole of piston top, one-way valve liquid flow path direction from bottom to top, one-way valve adopts circlip type to move horizontally one-way valve, piston arranges safety installations, eliminate security risk when hydraulic oil heat is splashed swollen, control spool arranges decompression longitudinal hole and is in communication with the outside in the space of mounting hole, decompression longitudinal hole does not communicate with center hole, reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.Rotate the driveshaft of bottom, spool is relative to outer piston rotary motion, and valve pocket cannelure and spool spiral chute relativeness change, and valve pocket and spool relativeness have three kinds of states, (1) valve pocket seal section just capping spool spiral chute, the liquid between upper and lower oil hydraulic cylinder does not flow; (2) on valve pocket, cannelure is communicated with spool spiral chute, when the pressure of upper oil hydraulic cylinder is greater than the pressure of lower oil hydraulic cylinder, the liquid of upper oil hydraulic cylinder flows into spool, flows into lower oil hydraulic cylinder, when the pressure of upper oil hydraulic cylinder is less than or equal to the pressure of lower oil hydraulic cylinder through lower one-way valve, two cylinder liquid do not flow, along with oil hydraulic cylinder under the flow direction of upper oil hydraulic cylinder, inner carrier moves up, and piston total length shortens, when valve pocket seal section is relative with core hydraulic oil ostium, two oil hydraulic cylinder liquid do not flow; (3) under valve pocket, cannelure is communicated with spool spiral chute, instantly when the pressure of oil hydraulic cylinder is greater than the pressure of oil hydraulic cylinder, the liquid of lower oil hydraulic cylinder flows into spool, flows into upper oil hydraulic cylinder, when the pressure of oil hydraulic cylinder is less than or equal to the pressure of oil hydraulic cylinder instantly through upper one-way valve, two cylinder liquid do not flow, along with oil hydraulic cylinder on the flow direction of lower oil hydraulic cylinder, inner carrier moves down, and piston total length is elongated, valve pocket seal section is relative with core hydraulic oil ostium, and two oil hydraulic cylinder liquid do not flow; During due to engine operation, the pressure alternately change of two oil hydraulic cylinders, always the fluid in two cylinders can rotate with driveshaft and flow, realizes piston length change.

3-position-3-way self-pump type variable-compression-ratio piston arranges safety installations, eliminate security risk when hydraulic oil heat is splashed swollen, safety installations scheme 1, mounting safety valve on valve pocket, safety valve import communicates with lower oil hydraulic cylinder, outlet drain is to piston exterior, and opening pressure of safety valve is greater than the working pressure of engine peak speed oil hydraulic cylinder at present; Safety installations scheme 2 is the safety installations simplified, change the seal ring between inner piston rod and oil hydraulic cylinder cover plate into opening ring type, opening is utilized slowly to miss the safety ensureing to pacify oil hydraulic cylinder, the variable-compression-ratio piston of other type can adopt the method for initiatively a small amount of moving valve core, ensure oil hydraulic cylinder not superpressure, also can adopt above-mentioned safety measure.

The sliding valve style position control valve embodiment 3 that variable-compression-ratio piston is installed is: the outer liquid formula variable-compression-ratio piston control valve of three groove sliding sleeve 3-position 4-ways, main valve structure is equivalent to three groove valve pocket 3-position 4-way guiding valves, valve pocket there are three annular grooves, middle annular groove is upper cylinder half annular groove, communicate with upper oil hydraulic cylinder, on lower cylinder, under annular groove and lower cylinder, annular groove communicates with lower oil hydraulic cylinder, spool is hollow structure, spool top is hydraulic oil inflow entrance, circlip type horizontal single-headed valve is installed, it is to outflow by center spool that one-way valve flows to, be communicated with center spool hole, middle part is hydraulic oil outflow opening, hydraulic oil outflow opening flows out piston, valve pocket is two seal sections between three annular grooves, upper seal section its be highly more than or equal to hydraulic oil inflow entrance annular groove height on spool, lower seal section is highly more than or equal to hydraulic oil outflow opening diameter in the middle part of spool, spool is slidably mounted in valve pocket, valve pocket is fixed on inner carrier, spool nut and screw mandrel are arranged in the internal surface center mounting hole of piston top, control spool arranges decompression longitudinal hole and is communicated with center spool hole in the space of mounting hole, reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.Rotate the driveshaft of bottom, spool is upper and lower relative to outer piston to be moved axially, and valve pocket and spool relativeness have three kinds of states, (1) valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, and the liquid between upper and lower oil hydraulic cylinder does not flow; (2) spool moves, on valve pocket, annular groove is communicated with spool liquid flow inlet, and in valve pocket, annular groove communicates with upper oil hydraulic cylinder, the outwards discharge of upper cylinder hydraulic oil, upper cylinder pressure reduces, when center spool hole pressure is greater than lower oil hydraulic cylinder, the liquid in spool flows into lower oil hydraulic cylinder through one-way valve, and inner carrier moves up, piston total length shortens, move along with on inner carrier, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow; (3) spool moves down, in valve pocket, annular groove is communicated with spool liquid flow inlet, and under valve pocket, annular groove communicates with upper oil hydraulic cylinder, the outwards discharge of lower cylinder hydraulic oil, lower cylinder pressure reduces, when center spool hole pressure is greater than upper oil hydraulic cylinder, the liquid in spool flows into upper oil hydraulic cylinder through one-way valve, and inner carrier moves down, piston total length is elongated, along with inner carrier moves down, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow.

The sliding valve style position control valve embodiment 4 that variable-compression-ratio piston is installed is: the outer liquid formula variable-compression-ratio piston control valve of two groove sliding sleeve 3-position 4-ways, main valve structure is equivalent to two groove valve pocket 3-position 4-way guiding valves, valve pocket there is annular groove on two annular grooves be that upper cylinder half annular groove communicates with upper oil hydraulic cylinder, lower annular groove is that under lower cylinder, annular groove communicates with lower oil hydraulic cylinder, spool is hollow structure, spool has two groups of hydraulic oil inflow entrances and one group of hydraulic oil outflow opening, liquid oil ostium is at two ends, hydraulic oil tap hole is in centre, there is jump ring annular groove hydraulic oil inflow entrance periphery, circlip type is installed and moves horizontally one-way valve, it is to outflow by center spool that one-way valve flows to, be communicated with center spool hole, valve pocket is seal section between two annular grooves, be seal spool section between spool three groups of runners, valve pocket seal section height is more than or equal to the height of hydraulic oil tap hole, the height of seal spool section is more than or equal to valve pocket annular groove height, spool nut and screw mandrel are arranged in the internal surface center mounting hole of piston top, control spool arranges decompression longitudinal hole and is communicated with by the center hole of the space spool of mounting hole, reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force, rotate the driveshaft of bottom, spool is upper and lower relative to outer piston to be moved axially, and valve pocket and spool relativeness have three kinds of states, (1) valve pocket seal section sealing through hole or annular groove, and the liquid between upper and lower oil hydraulic cylinder does not flow, (2) spool moves, on valve pocket, annular groove is communicated with fluid outlet in spool, and under valve pocket, annular groove communicates with annular groove under spool, the outwards discharge of upper cylinder hydraulic oil, upper cylinder pressure reduces, when center spool hole pressure is greater than lower oil hydraulic cylinder, the liquid in spool flows into lower oil hydraulic cylinder through one-way valve, and inner carrier moves up, piston total length shortens, move along with on inner carrier, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow, (3) spool moves down, on valve pocket, annular groove is communicated with annular groove on spool, and under valve pocket, annular groove communicates with middle hydraulic output, the outwards discharge of lower cylinder hydraulic oil, lower cylinder pressure reduces, when center spool hole pressure is greater than upper oil hydraulic cylinder, the liquid in spool flows into upper oil hydraulic cylinder through one-way valve, and inner carrier moves down, piston total length is elongated, along with inner carrier moves down, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow.

The sliding valve style position control valve embodiment 5 that variable-compression-ratio piston is installed is: 3-position 4-way spiral chute genesis analysis formula variable-compression-ratio piston control valve, main valve structure is equivalent to three groove valve pocket 3-position 4-way guiding valves, valve pocket there are three groups of cannelures, middle cannelure is upper cylinder half cannelure, communicate with upper oil hydraulic cylinder, on lower cylinder, under cannelure and lower cylinder, cannelure communicates with lower oil hydraulic cylinder, spool is band center hole structure, on spool outer cylinder, lower each distribution one group of spiral chute, upper spiral chute communicates with hydraulic oil inflow entrance, and be communicated with center spool hole, lower spiral chute communicates with hydraulic oil outflow opening, be communicated with space outerpace by longitudinal hole, valve pocket is two seal sections between longitudinal annular groove, valve pocket cannelure and spiral chute phase cross surface place, when valve pocket seal section is in the middle of spiral chute, seal section can sealing screw groove completely, spool is slidably mounted in valve pocket, valve pocket is fixed on inner carrier, spool setscrew nut and positioning step rotational slide are contained in the internal surface center mounting hole of piston top, circlip type horizontal single-headed valve is installed at driveshaft top, control spool arranges decompression longitudinal hole and is in communication with the outside in the space of mounting hole, decompression longitudinal hole does not communicate with center hole, reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.Rotate the driveshaft of bottom, spool rotates relative to outer piston, and valve pocket and spool relativeness change, and has three kinds of states, and (1) valve pocket seal section seals up spiral chute, and the liquid between upper and lower oil hydraulic cylinder does not flow; (2) on spool, spiral chute is communicated with cannelure on valve pocket, under spool, spiral chute is communicated with cannelure in valve pocket, now, lower oil hydraulic cylinder is communicated with liquid inflow port, upper oil hydraulic cylinder is communicated with liquid flowing outlet, the outwards discharge of upper cylinder hydraulic oil, upper cylinder pressure reduces, when driveshaft fluid pressure is greater than lower oil hydraulic cylinder, the liquid in spool is through flowing into lower oil hydraulic cylinder, and inner carrier moves up, piston total length shortens, move along with on inner carrier, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow; (3) on spool, spiral chute is communicated with cannelure in valve pocket, under spool, spiral chute is communicated with cannelure under valve pocket, now, lower oil hydraulic cylinder is communicated with liquid flowing outlet, upper oil hydraulic cylinder is communicated with liquid inflow port, the outwards discharge of lower cylinder hydraulic oil, lower cylinder pressure reduces, when center spool hole pressure is greater than upper oil hydraulic cylinder, the liquid in spool flows into upper oil hydraulic cylinder through one-way valve, and inner carrier moves down, piston total length is elongated, along with inner carrier moves down, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow.

The sliding valve style position control valve embodiment 6 that variable-compression-ratio piston is installed, 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston control valve, valve pocket has four groups of cannelures, upper and lower each distribution two groups of cannelures, upper cannelure is divided into cannelure on cannelure on the upper cylinder half that communicates with upper fluid cylinder and the lower cylinder that communicates with lower oil hydraulic cylinder, and lower cannelure is divided into cannelure under cannelure under the upper cylinder half communicated with upper oil hydraulic cylinder and the lower cylinder that communicates with lower oil hydraulic cylinder, spool outer cylinder circumference two groups of spiral chutes, wherein one group of spiral chute is hydraulic oil inflow entrance, be communicated with center spool hole, another group spiral chute is that hydraulic oil outflow opening is communicated with space outerpace, valve pocket is two seal sections between longitudinal annular groove, valve pocket cannelure and spiral chute phase cross surface place, when valve pocket seal section is in the middle of spiral chute, seal section can sealing screw groove completely, and spool is slidably mounted in valve pocket, on lower cylinder, cannelure is corresponding with the direction of cannelure under upper cylinder half and the hydraulic oil inflow entrance of spool, and under lower cylinder, cannelure is corresponding with the direction of cannelure on upper cylinder half and the hydraulic oil inflow entrance of spool, valve pocket is fixed on inner carrier, spool setscrew nut and positioning step rotational slide are contained in the internal surface center mounting hole of piston top, one-way valve is installed at driveshaft top, control spool arranges longitudinal hole and is in communication with the outside in the space of mounting hole, longitudinal hole does not communicate with center hole, eliminate the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force, rotate the driveshaft of bottom, spool rotates relative to outer piston, and valve pocket and spool relativeness change, and has three kinds of states, and (1) valve pocket seal section seals up spiral chute, and the liquid between upper and lower oil hydraulic cylinder does not flow, (2) spool outflow spiral chute is communicated with valve pocket top upper cylinder half cannelure, spool flows into spiral chute and is communicated with cylinder cannelure under valve pocket middle and lower part, now, lower oil hydraulic cylinder is communicated with liquid inflow port, upper oil hydraulic cylinder is communicated with liquid flowing outlet, the outwards discharge of upper cylinder hydraulic oil, upper cylinder pressure reduces, when driveshaft fluid pressure is greater than lower oil hydraulic cylinder, liquid in spool is through flowing into lower oil hydraulic cylinder, inner carrier moves up, piston total length shortens, move along with on inner carrier, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow, (3) spool outflow spiral chute is communicated with subordinate's cylinder cannelure under valve pocket, spool flows into spiral chute and is communicated with valve pocket top upper cylinder half cannelure, now, lower oil hydraulic cylinder is communicated with liquid flowing outlet, upper oil hydraulic cylinder is communicated with liquid inflow port, the outwards discharge of lower cylinder hydraulic oil, lower cylinder pressure reduces, when center spool hole pressure is greater than upper oil hydraulic cylinder, liquid in spool flows into upper oil hydraulic cylinder through one-way valve, inner carrier moves down, piston total length is elongated, along with inner carrier moves down, valve pocket seal section sealing fluid force feed inflow entrance and hydraulic oil outflow opening, two oil hydraulic cylinder liquid do not flow.

The control valve driveshaft of the self-pump type's variable-compression-ratio piston in the twin crankshaft engine of above-mentioned variable compression ratio is sliding bush type, and upper driveshaft is uniformly distributed semicircle spline; Lower driving casing is ring-shaped sleeve, top is uniformly distributed the corresponding hole of spline semicircle with upper driveshaft, the diameter in hole is identical with the diameter of the semicircle spline of upper driveshaft, in the hole of lower driving casing, steel ball is installed, steel ball half is exposed in driving casing, and the steel ball exposed is arranged in the semicircle spline of the driveshaft on top.

Above-mentioned control valve drive the steel ball in sliding sleeving hole to replace with band circular arc head with the bullet nose rod of screw thread, carry out simplified structure.

The beneficial effects of the utility model are: double-acting hydraulic cylinder formula variable-compression-ratio piston is combined with twin crankshaft engine, reduce variable-compression-ratio piston processing and installation difficulty, by disperseing the structure of flywheel, reducing the conversion of bent axle between energy input and output, alleviating the harsh state of coupling gear, compared with self-pump type's variable-compression-ratio piston (2012204098128) in early stage, setting up by safety installations, motor can be avoided when starting, in variable piston, working liquid body temperature raises the security risk caused, the circlip type of design moves horizontally one-way valve, eliminate engine operation process acceleration to open one-way valve, the impact of closing, the outer liquid formula variable-compression-ratio piston of the 3-position 4-way formula control valve newly increased, accelerate the exchange of liquid, working liquid body is avoided to exchange not enough, the problem that the working solution that may cause is rotten, when also solving low engine speed operation simultaneously, two oil hydraulic cylinder pressure reduction in variable-compression-ratio piston are not enough, reliably can not open the problem of one-way valve, improve the controllability of variable-compression-ratio piston.

Accompanying drawing explanation

Below in conjunction with the drawings and specific embodiments, the utility model is further illustrated:

Fig. 1 is double-crankshaft variable compression ratio engine, crankshaft-link rod and piston graphics,

Fig. 2 is the horizontal sectional drawing of double-crankshaft variable compression ratio engine along crank spindle,

Fig. 3 is double-crankshaft variable compression ratio engine piston, connecting rod, bent axle and piston drive mechanism location diagram,

Fig. 4 is double-crankshaft inside and outside gear ring coupling position graph of a relation,

Fig. 5 is that double-crankshaft variable compression ratio engine simplifies gear coupling schematic diagram,

Fig. 6 is triple axle connecting head stereogram,

Fig. 7 connecting rod stereogram,

Fig. 8 wrist pin stereogram

Fig. 9 is not with flywheel crankshaft arm stereogram

Figure 10 is the crank arm stereogram of band flywheel

Driveshaft on Figure 11 variable-compression-ratio piston control valve,

Sliding sleeve is driven under Figure 12 variable-compression-ratio piston control valve,

Figure 13 variable-compression-ratio piston control valve drives switching mechanism Local map,

Figure 14 is that 3-position-3-way moves axially self-pump type's variable-compression-ratio piston sectional drawing,

Figure 15 is that 3-position-3-way moves axially self-pump type's variable-compression-ratio piston control valve sectional drawing,

Figure 16 is that 3-position-3-way moves axially self-pump type's variable-compression-ratio piston control valve cored structure figure,

Figure 17 is that 3-position-3-way moves axially self-pump type's variable-compression-ratio piston control valve noose composition,

Figure 18 circlip type external fluid input one-way valve,

Figure 19 is 3-position-3-way spiral chute self-pump type variable-compression-ratio piston structural drawing,

Figure 20 is 3-position-3-way spiral chute self-pump type variable-compression-ratio piston control valve sectional drawing,

Figure 21 is that 3-position-3-way spiral chute self-pump type variable-compression-ratio piston controls valve pocket sectional drawing,

Figure 22 is that 3-position-3-way spiral chute self-pump type variable-compression-ratio piston controls spool stereogram,

Figure 23 is that 3-position-3-way spiral chute self-pump type variable-compression-ratio piston controls spool sectional drawing,

Figure 24 is the outer liquid formula variable-compression-ratio piston control valve sectional drawings of three groove sliding sleeve 3-position 4-ways,

Figure 25 is the outer liquid formula variable-compression-ratio piston control valve noose compositions of three groove sliding sleeve 3-position 4-ways,

Figure 26 is the outer liquid formula variable-compression-ratio piston control valve sectional drawings of two groove sliding sleeve 3-position 4-ways,

Figure 27 is the outer liquid formula variable-compression-ratio piston control valve noose compositions of two groove sliding sleeve 3-position 4-ways,

Figure 28 is the outer liquid formula variable-compression-ratio piston control valve cored structure figure of two groove sliding sleeve 3-position 4-ways,

Figure 29 is 3-position 4-way spiral chute genesis analysis formula variable-compression-ratio piston control valve sectional drawing,

Figure 30 is that 3-position 4-way spiral chute genesis analysis formula variable-compression-ratio piston controls valve pocket sectional drawing (in displaying oil hydraulic cylinder runner),

Figure 31 is that 3-position 4-way spiral chute genesis analysis formula variable-compression-ratio piston controls valve pocket sectional drawing (showing lower oil hydraulic cylinder runner),

Figure 32 is that 3-position 4-way spiral chute genesis analysis formula variable-compression-ratio piston controls spool stereogram,

Figure 33 is 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston control valve sectional drawing (liquid inflow),

Figure 34 is 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston control valve sectional drawing (liquid outflow),

Figure 35 is that 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston controls spool stereogram,

Figure 36 is 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston control valve noose composition (in displaying oil hydraulic cylinder runner),

Figure 37 is 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston control valve noose composition (showing lower oil hydraulic cylinder runner)

Embodiment

Fig. 1 ~ Fig. 3 illustrates the general structure of double-crankshaft variable compression ratio engine crankshaft-link rod and piston, in order to make simplified form, only draw a set of piston crank mechanism, the general structure of double-crankshaft crankshaft with variable compression-ratio connecting rod and piston: two covers flywheel crankshaft arranged side by side (200) are arranged on cylinder body (101), two covers flywheel crankshaft arranged side by side is coupled together by gear (300), triple axle connecting head (600) adopts axle, variable piston (400) bottom and two connecting rod (700) microcephalies link together by hole rotational slide formula, the major part rotational slide formula of two connecting rods is arranged on crankshaft connecting rod axle, be arranged between two connecting rods at variable piston driving mechanism (800).

Cylinder body (101) is separated four spaces by three central housing dividing plates (103), central housing dividing plate (103) and two end plates distribution two row's spindle mounting hole (104), the crank arm end of spindle mounting hole (104) band flywheel is tube-in-tube structure, the cylinder body of the position corresponding with connecting rod macro-axis is arranged connecting rod macro-axis mounting hole (102), for installing connecting rods macro-axis and thrust mechanism, cylinder body can be that two positions manufacture at main shaft place subdivision, also can be fabricated to integrated type by the present embodiment.

The main shaft (201) of two end band cone angles with not with flywheel crankshaft arm (203) and the center hole (2031) being with flywheel crankshaft arm (204), (2041) by main shaft fastening screw (205) interference fit together, not with flywheel crankshaft arm (203) and the connecting rod axis hole (2032) being with flywheel crankshaft arm (204), (2042) linked together by connecting rod macro-axis (202), fit system can be interference fit also can be slidably matched, what select in the present embodiment is be slidably matched, containing flywheel crank arm on (203) (Fig. 2) be blind-hole type, containing the crank arm (204) of flywheel flywheel (2043) for edge thick, intermediate thin, annular space (105) is left between flywheel and cylinder body dividing plate (103), at the crank arm containing flywheel, thrust screw (205) is installed, form complete bent axle, article two, the crankshaft installed that different crank arms are installed on the contrary is on the mounting hole (104) of cylinder body.

Gear (304) and gear (306) are fixed on main shaft respectively by fastening screw (305), (307), external toothing (301) and ring gear (302) are fixed together, form inside and outside gear ring, or make integrated type, external toothing (301) is meshing with gear (306), ring gear (302) is meshing with gear (304), external toothing (301) and the gear ratio of gear (306) equal ring gear (302) and the gear ratio of gear (304), inside and outside gear ring are established pto＝power take-off (303).

Fig. 5 illustrates double-crankshaft variable compression ratio engine and simplifies gear coupling schematic diagram, is reduced to two identical gear couplings by inside and outside gear ring coupling.

Fig. 6 describes the structure of three hole connectors (600), for two dihedral plates (601) of three axis holes that distribute, an entirety is formed by connecting plate (602), it is the passing hole (603) of spool driveshaft (808) in the middle of connecting plate (602), larger axis hole is piston pin hole (604), two less axis holes are connecting rod small end axis hole (605), and preferred three hole connector middle opening parts are the structure outwards increased.

Fig. 7 describes bar linkage structure, and its structure is similar to plain connecting rod, is divided into link arm (701), connecting rod small end axis hole (702) connnecting rod big end axis hole (703), and the connnecting rod big end of optimization is integrated type, and connecting rod small end is outside thin structure.

Fig. 8 describes wrist pin structure, is divided into wrist pin (611) main body, lightening hole (612), the passing hole (613) of spool driveshaft (808).

Fig. 9 describes and is not with flywheel crankshaft arm (203) structure, distribution main shaft attachment hole (2031), the large axis hole of connecting rod (2032), eccentric weight (2033).

Figure 10 describes crank arm (204) structure of band flywheel, distribution main shaft attachment hole (2041), the large axis hole of connecting rod (2042), eccentric weight (2043), and flywheel (2043) and crank arm are an entirety.

Figure 11 ~ Figure 13 describes the structure of variable-compression-ratio piston spool steering driving mechanism, with associated components coordinate referring to Fig. 1, Fig. 3, upper driveshaft (808) in figure, for having the tubular structure of central through bore (8081), be evenly distributed with arc groove (8082) in upper driveshaft (808) middle and upper part to bottom, lower driving sliding sleeve (807) is band driveshaft positioning step (8071), turbine positioning step (8071), with the fastening screw thread of turbine (8073), the tubular structure of band central through bore (8074), steel ball (or bullet nose rod) mounting hole (8075) corresponding with the arc groove (8082) on upper driveshaft (808) is furnished with in lower driving sliding sleeve (807) top portion, arc groove (8082) is identical with the diameter of mounting hole (8075), steel ball in mounting hole (8075) or bullet nose rod and arc groove (8082) are slidably matched, upper driveshaft (808) can slide axially in lower driving sliding sleeve (807), on when driving sliding sleeve (807) under rotation, driveshaft (808) also rotates.

Hydraulic oil rail (801) is the tubular structure of band center hole, level is arranged on cylinder base, the position relative with each piston centre arranges branched pipe (8011) upwards, branched pipe (8011) is the installation sleeve of lower driving sliding sleeve (807) simultaneously, lower driving sliding sleeve (807) is arranged in branched pipe (8011), lower driving sliding sleeve (807) coordinates with branched pipe (8011) rotational slide, rely on positioning step (8071) and set screw (804) location, turbine (805) is arranged on lower driving sliding sleeve (807), rely on positioning step (8071) location, fastening screw (806) is arranged on the fastening screw thread of turbine (8073), compress and fixed turbine (805), the scroll bar (803) that the upper distribution of horizontal driveshaft (802) is identical with number of pistons, level is arranged on cylinder body, scroll bar (803) coordinates with turbine (805) is meshing, rotating horizontal driveshaft (802) just can be with brake control valve core to rotate.

Hydraulic oil rail (801) communicates with engine lubricating oil, and lubricant oil passes through hydraulic oil rail (801), lower driving sliding sleeve (807), upper driveshaft (808), enters control spool center hole (5012).

The variable-compression-ratio piston spool steering driving mechanism of this enforcement have employed turbine, Worm-drive, according to same principle, turbine and scroll bar is replaced with gear and ratch, or is replaced by a pair umbrella tooth, also can realize the effect of the present embodiment, no longer describe in detail.

Control valve embodiment 1, Figure 14 ~ Figure 18 illustrates 3-position-3-way and moves axially self-pump type's variable-compression-ratio piston structure, variable-compression-ratio piston entirety is double-acting hydraulic cylinder, oil hydraulic cylinder comprises the cylinder body that outer piston (401) is oil hydraulic cylinder, the opening fixed hydraulic cylinder cap (401) of outer piston (401), oil hydraulic cylinder is divided into upper oil hydraulic cylinder (4021) and lower oil hydraulic cylinder (4022) by inner carrier (402), inner carrier (402) is installed seal ring (4024), hydraulic cylinder (401) is the cover plate of band center hole, inner piston rod (4026) and hydraulic cylinder are slidably installed, endoporus installs the sealing between rod seal circle (4031) realization (401) inner piston rod (4026) and hydraulic cylinder, inner carrier is set oil hydraulic cylinder oilhole (4025) to communicate with the lower cylinder oil circuit controlling valve pocket, mounting hole (4023) established by inner carrier, control valve pocket (502a) is fixed on inner carrier and establishes on mounting hole (4023), outer piston top inner surface is established and is controlled spool mounting hole (4011), the feed screw nut (4012) that axis movable type controls spool (501a) is fixed in spool mounting hole (4011), controlling spool screw mandrel (5018) is arranged in feed screw nut (4012), seal ring (4013) is established between feed screw nut (4012) and control spool.

3-position-3-way moves axially self-pump type's variable-compression-ratio piston and controls the tubular structure that spool (501b) is band center hole (5012), intermediate radial distributes one group of spool oil outlet (5011), filler opening (5013) on upper end radially direct one group of spool, lower end distribute filler opening (5014) under one group of spool, control upper filler opening (5013) peripheral distribution circlip type spring groove (5015) of spool, control lower filler opening (5013) peripheral distribution circlip type spring groove (5016) of spool; Control valve pocket (502a) endoporus and to establish under sliding sleeve upper cylinder half annular groove (5022) valve pocket annular groove (5023) under cylinder, valve pocket upper cylinder half annular groove (5022) is communicated with upper oil hydraulic cylinder (4021) by cannelure (5022a), and under valve pocket, under cylinder, annular groove (5023) is communicated with lower oil hydraulic cylinder by oil duct (5026,5027,5028,4025); Safety valve mounting hole (5029) mounting safety valve (506) on valve pocket, import communicates with lower oil hydraulic cylinder, and outlet drain is to piston exterior, and safety valve (506) cracking pressure is greater than the working pressure of engine peak speed oil hydraulic cylinder at present; Be valve pocket lower seal section (5025) between annular groove (5023) under upper cylinder half annular groove (5022) and lower cylinder, the height of valve pocket lower seal section (5025) is more than or equal to the height of spool oil outlet (5011), communicates in the upper filler opening (5013) controlling spool and lower filler opening (5014) working procedure controlling spool with annular groove (5023) under cylinder under valve pocket upper cylinder half annular groove (5022) and valve pocket always.

The interior circlip type of installing of upper and lower filler opening (5013,5014) controlling spool moves horizontally one-way valve (503,504), circlip type moves horizontally one-way valve (503,504) by valve seat (5031,5041), spool (5032,5042), and circlip type spring (5033,5034) is formed.

Control the unidirectional inflow valve (505) of installment work hydraulic oil bottom spool, working solution force feed way flow enters the upper circlip type of installing of valve (505) spool (5051) and moves horizontally one-way valve, move horizontally one-way valve and comprise valve opening (5055), valve seat (5054), spool (5057), circlip type spring (5056), the flow direction moving horizontally one-way valve is from inside to outside, radial hole (5059) is arranged at spool (5051) top, center hole (50511) and upper core bore (50510) is set in the middle of spool (5051), be not communicated with between lower center hole (50511) and upper core bore (50510), the external suit valve pocket (5052) of spool (5051), interference can be adopted to install between spool (5051) and valve pocket (5052), realize sealing, also can be as shown in figure 18, seal ring (5058) is installed, gap (5059) is stayed between spool (5051) and valve pocket (5052), realize working solution force feed flows into upper center hole through one-way valve object from lower center hole (50510).

Control spool (501a) arranges longitudinal hole (5017) and is in communication with the outside in the space of mounting hole (4011), and longitudinal hole (5017) does not communicate with center hole (5012), eliminates the pressure that generation missed on a small quantity by hydraulic oil, alleviates and control spool steering force.

Control valve embodiment 2, Figure 19 ~ Figure 23 illustrates 3-position-3-way spiral chute self-pump type variable-compression-ratio piston structure, overall structure is variable-compression-ratio piston entirety is double-acting hydraulic cylinder, control valve pocket (502b) is fixed on inner carrier and establishes on mounting hole (4023), outer piston top inner surface is established and is controlled spool mounting hole (4011), the positioning step (5018a) controlling spool (501b) relies on setscrew nut (4012a) to be fixed in spool mounting hole (4011), control spool top and thrust pad (4014) is installed, control spool (501b) to rotate in mounting hole (4011).

3-position-3-way spiral chute self-pump type variable-compression-ratio piston controls the tubular structure that spool (501b) is band center hole (5012), intermediate radial distributes one group of spool oil outlet (5011), filler opening (5013) in upper end radially direct one group, lower end distributes filler opening (5014) under a group, control upper filler opening (5013) peripheral distribution circlip type spring groove (5015) of spool, control lower filler opening (5013) peripheral distribution circlip type spring groove (5016) of spool, control spool (501b) periphery and one group of spiral chute (5011a) is set, spool oil outlet (5011) is positioned in the middle of spiral chute (5011a), control valve pocket (502b) endoporus and establish sliding sleeve upper cylinder half cannelure (5022a), cannelure (5023a) under cylinder under valve pocket, sliding sleeve upper cylinder half annular groove (5022a) communicates with upper oil hydraulic cylinder (4021), under sliding sleeve under cylinder annular groove (5023a) by oil duct (5026, 5027, 5028) communicate with lower oil hydraulic cylinder, safety valve mounting hole (5029) mounting safety valve (506) on valve pocket, import communicates with lower oil hydraulic cylinder, and outlet drain is to piston exterior, and safety valve (506) cracking pressure is greater than the working pressure of engine peak speed oil hydraulic cylinder at present, be valve pocket lower seal section (5025) between cannelure (5023a) under upper cylinder half cannelure (5022a) and lower cylinder, when valve pocket lower seal section (5025) is positioned at middle with spiral chute (5011a), valve pocket lower seal section (5025) can sealing screw groove (5011a) completely, controls to communicate with annular groove (5023a) under cylinder under sliding sleeve upper cylinder half annular groove (5022a) and sliding sleeve in the upper filler opening (5013) of spool and lower filler opening (5014) working procedure of control spool always.

Control the unidirectional inflow valve (505) of installment work hydraulic oil bottom spool, structure and 3-position-3-way move axially self-pump type's variable compressive to make hydraulic oil unidirectional inflow valve (505) structure identical.

Control spool (501b) arranges longitudinal hole (5017) and is in communication with the outside in the space of mounting hole (4011), and longitudinal hole (5017) does not communicate with center hole (5012), eliminates the pressure that generation missed on a small quantity by hydraulic oil, alleviates and control spool steering force.

Seen from the above description, control spool (501b) compared with control spool (501a), many spiral chute (5011a), mounting type is installed by nut-screw rod, become rotational slide to install, control valve pocket (502b) and control compared with valve pocket (502a), under upper cylinder half annular groove (5022) and lower cylinder, annular groove (5023) becomes cannelure (5023a) under upper cylinder half cannelure (5022a) and lower cylinder, and other structure is identical.

Control valve embodiment 3, Figure 24 ~ Figure 25 illustrates the outer liquid formula variable-compression-ratio piston control valve structure of three groove sliding sleeve 3-position 4-ways, controls spool (501c), adopts nut (4012) and screw mandrel (5018) to be arranged in mounting hole (4011), control spool (501c) and have one group of radial spool oil outlet (5011), and filler opening (5013) on one group of spool, radial spool oil outlet (5011) is not communicated with center hole (5012), and spool oil outlet (5011) communicates with longitudinal oil drain out (50111), and hydraulic oil is discharged piston by longitudinal oil drain out (50111), spool installs circlip type in filler opening (5013) and embodiment 1, the enterprising hydraulic fluid port of the identical spool of embodiment 2 (5013) and moves horizontally one-way valve (503), it is identical with the circlip type one-way valve of embodiment 1, embodiment 2 that circlip type moves horizontally one-way valve (503), by valve seat (5031), spool (5032), circlip type spring (5033) is formed, and the spool of control spool (501c) is seal section (50112) between filler opening (5013) and spool oil outlet (5011), control valve pocket (502c) endoporus and have three annular grooves, annular groove (5023) under cylinder under annular groove (5021), valve pocket upper cylinder half annular groove (5022), valve pocket on cylinder under valve pocket, two seal sections are had, upper valve sleeve seal section (5024), lower valve sleeve seal section (5025) between annular groove, valve pocket upper cylinder half annular groove (5022) is communicated with upper oil hydraulic cylinder by longitudinal hole 50221 and radial hole (50222), under valve pocket on cylinder under annular groove (5021) and valve pocket under cylinder annular groove (5023) by oil duct (5026, 5027, 5028) communicate with lower oil hydraulic cylinder, on valve pocket, seal section (5024) is highly more than or equal to filler opening on spool (5013) periphery circlip type spring groove (5015) highly, valve pocket lower seal section (5025) is highly more than or equal to spool oil outlet (5011) highly, on spool, seal section (50112) is highly more than or equal to valve pocket upper cylinder half annular groove (5022) highly, when controlling spool (501c) and moving up, under valve pocket, on cylinder, annular groove (5021) communicates with filler opening on spool (5013), valve pocket upper cylinder half annular groove (5022) communicates with spool oil outlet (5011), upper oil hydraulic cylinder oil extraction, lower oil hydraulic cylinder oil-feed, inner carrier moves, and drive valve pocket (502c) to move upward, final plant closure control valve, when controlling spool (501c) and moving down, under valve pocket, under cylinder, annular groove (5023) communicates with spool oil outlet (5011), valve pocket upper cylinder half annular groove (5022) communicates with spool filler opening (5013), upper oil hydraulic cylinder oil-feed, lower oil hydraulic cylinder oil extraction, inner carrier moves down, and drive valve pocket (502c) to move upward, final plant closure control valve, realize inner carrier to follow spool and move.

Control spool (501c) arranges longitudinal hole (5017a) and is communicated with center hole (5012) in the space of mounting hole (4011), eliminates the pressure that generation missed on a small quantity by hydraulic oil, alleviates and control spool steering force.

Control valve embodiment 4, Figure 26 ~ Figure 28 illustrates the outer liquid formula variable-compression-ratio piston control valve structure of two groove sliding sleeve 3-position 4-ways, controls spool (501d), adopts nut (4012) and screw mandrel (5018) to be arranged in mounting hole (4011), control spool (501c) and to have on one group of radial spool oil outlet (5011), one group of spool filler opening (5014) under filler opening (5013), one group of spool, under controlling the upper filler opening (5013) of spool (501d) and spool, filler opening (5014) installation circlip type moves horizontally one-way valve (503,504), radial spool oil outlet (5011) is not communicated with center hole (5012), spool oil outlet (5011) communicates with longitudinal oil drain out (50111), and hydraulic oil is discharged piston by longitudinal oil drain out (50111), the spool of control spool (501d) there are two seal sections (50112,50113) between filler opening (5014) under filler opening (5013), spool, control valve pocket (502d) endoporus and have two annular grooves, under valve pocket, under cylinder, between annular groove (5023), valve pocket upper cylinder half annular groove (5022), annular groove, have upper valve sleeve seal section (5024), valve pocket upper cylinder half annular groove (5022) is communicated with upper oil hydraulic cylinder by cannelure (5022a), under valve pocket, under cylinder, annular groove (5023) is communicated with lower oil hydraulic cylinder by oil duct (5028), valve pocket lower seal section (5024) is highly more than or equal to filler opening on spool (5013) periphery circlip type spring groove (5015) highly, valve pocket lower seal section (5025) is highly more than or equal to spool oil outlet (5011) highly, and on spool, seal section (50112) is highly more than or equal to valve pocket upper cylinder half annular groove (5022) highly, spool lower seal section (50113) to be highly more than or equal under valve pocket under cylinder annular groove (5023) highly, when controlling spool (501d) and moving up, on valve pocket, annular groove (5022) communicates with spool oil outlet (5013), under valve pocket, under cylinder, annular groove (5023) communicates with filler opening under spool (5014), upper oil hydraulic cylinder oil extraction, lower oil hydraulic cylinder oil-feed, inner carrier moves, and drive valve pocket (502d) to move upward, final plant closure control valve, when controlling spool (501d) and moving down, valve pocket upper cylinder half annular groove (5022) communicates with filler opening on spool (5013), under valve pocket, under cylinder, annular groove (5023) communicates with spool oil outlet (5011), upper oil hydraulic cylinder oil-feed, lower oil hydraulic cylinder oil extraction, inner carrier moves down, and drive valve pocket (502c) to move upward, final plant closure control valve, realize inner carrier to follow spool and move.

Control spool (501d) arranges longitudinal hole (5017a) and is communicated with center hole (5012) in the space of mounting hole (4011), eliminates the pressure that generation missed on a small quantity by hydraulic oil, alleviates and control spool steering force.

Control valve embodiment 5, Figure 29 ~ Figure 32 illustrates 3-position 4-way spiral chute genesis analysis formula variable-compression-ratio piston control valve structure, controls spool (501e), adopts setscrew nut (4012a) and positioning step (5018a) to be arranged in mounting hole (4011), control spool (501e) to distribute one group of radial spool oil outlet (5011e), filler opening (5013) on one group of spool, filler opening (5013) genesis analysis on spool oil outlet (5011e) and spool, spool peripheral distribution two groups of spiral chute (5011ae, 5013a), on radial spool oil outlet (5011e) and spool, filler opening (5013) is positioned at spiral chute (5011ae, 5013a), radial spool oil outlet (5011e) is not communicated with center hole (5012), spool oil outlet (5011e) communicates with longitudinal oil drain out (50111), hydraulic oil is discharged piston by longitudinal oil drain out (50111), the unidirectional inflow valve (505) of installment work liquid bottom spool, control valve pocket (502e) endoporus and have three groups of cannelures, cannelure (5023a) under cylinder under cannelure (5022a), valve pocket on annular groove (5021a), valve pocket on cylinder under valve pocket, two seal sections are had, upper valve sleeve seal section (5024), lower valve sleeve seal section (5025) between annular groove, valve pocket upper cylinder half cannelure (5022a) is by longitudinal hole 50221 and radial hole (50222), outer groove (50223) and radial hole (50224) communicate with upper oil hydraulic cylinder, under valve pocket on cylinder under annular groove (5021a) and valve pocket under cylinder annular groove (5023a) by oil duct (50231, 50232, 50233, 50234, 50235, 50236, 50215) communicate with lower oil hydraulic cylinder, on valve pocket, seal section (5024) is highly more than or equal to filler opening on spool (5013) highly, valve pocket lower seal section (5025) is highly more than or equal to spool oil outlet (5011) highly, on spool, seal section (50112) is highly more than or equal to valve pocket upper cylinder half annular groove (5022a) highly, when control spool (501e) is rotated, move on control spool spiral chute is relative with valve pocket cannelure intersection, under valve pocket, on cylinder, cannelure (5021a) communicates with filler opening on spool (5013), valve pocket upper cylinder half cannelure (5022a) communicates with spool oil outlet (5011e), upper oil hydraulic cylinder oil extraction, lower oil hydraulic cylinder oil-feed, inner carrier moves, and drive valve pocket (502e) to move upward, final plant closure control valve, when control spool (501e) is rotated, control spool spiral chute phase is relative with valve pocket cannelure intersection to be moved down, under valve pocket, under cylinder, cannelure (5023a) communicates with spool oil outlet (5011a), valve pocket upper cylinder half cannelure (5022a) communicates with spool filler opening (5013), upper oil hydraulic cylinder oil-feed, lower oil hydraulic cylinder oil extraction, inner carrier moves down, and drive valve pocket (502e) to move upward, final plant closure control valve, realize inner carrier to follow spool and move.

Control spool (501e) and arrange longitudinal hole (5017) by the connection of the outside space of mounting hole (4011), longitudinal hole (5017) is not communicated with center hole (5012), eliminates the pressure that generation missed on a small quantity by hydraulic oil, alleviates and control spool steering force.

Control valve embodiment 6, Figure 33 ~ Figure 37 illustrates 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston control valve nested structure, control spool (501f), adopt setscrew nut (4012a) and positioning step (5018a) to be arranged in mounting hole (4011), control spool (501f) to distribute a core assembly oil outlet (5011f), one group of spool filler opening (5013f), on spool oil outlet (5011f) and spool, filler opening (5013f) is circumferentially interspersed, spool peripheral distribution two groups of spiral chute (5011af, 5013af), radial spool oil outlet (5011f) and spool filler opening (5013f) are positioned at spiral chute (5011af, 5013af), radial spool oil outlet (5011f) is not communicated with center hole (5012), spool oil outlet (5011f) communicates with longitudinal oil drain out (50111f), hydraulic oil is discharged piston by longitudinal oil drain out (50111f), longitudinal oil drainage hole vertical communication spool top simultaneously, play the effect eliminating pressure in mounting hole (4011), the unidirectional inflow valve (505) of installment work liquid bottom spool, control that valve pocket (502f) valve pocket has four groups of cannelures, upper and lower each distribution two groups, two groups of circle distribution formula communicate with upper and lower oil hydraulic cylinder respectively, longitudinally upper and lower two groups are communicated with different oil hydraulic cylinders, two groups control inflow, two groups of controls are flowed out, and Figure 33 is the directional profile of ramp metering, and upper cannelure (5021af) communicates with lower oil hydraulic cylinder, lower cannelure (5022af) communicates with upper oil hydraulic cylinder, and this direction is relative with the control enterprising hydraulic fluid port of spool (5013f), Figure 34 flows out to control directional profile, upper cannelure (5022af1) communicates with upper oil hydraulic cylinder, lower cannelure (5021af1) communicates with lower oil hydraulic cylinder, this direction is relative with control spool oil outlet (5011f), upper oil hydraulic cylinder realizes communicating with upper cannelure (5022af), lower cannelure (5022f) by oil duct (50221,50222f, 50223f), and lower oil hydraulic cylinder is communicated with upper cannelure (5021af), lower cannelure (5021af1) by oil duct (50231f, 50232f, 50233f, 50234f, 50235f) realization, when control spool (501f) is rotated, move on control spool spiral chute is relative with valve pocket cannelure intersection, under valve pocket, on cylinder, cannelure (5021af) communicates with filler opening on spool (5013f), on valve pocket upper cylinder half, cannelure (5022af1) communicates with spool oil outlet (5011f), upper oil hydraulic cylinder oil extraction, lower oil hydraulic cylinder oil-feed, inner carrier moves, and drive valve pocket (502f) to move upward, final plant closure control valve, when control spool (501f) is rotated, control spool spiral chute is relative with valve pocket cannelure intersection to be moved down, under valve pocket, under cylinder, cannelure (5023af1) communicates with spool oil outlet (5011f), valve pocket upper cylinder half cannelure (5022af) communicates with spool filler opening (5013f), upper oil hydraulic cylinder oil-feed, lower oil hydraulic cylinder oil extraction, inner carrier moves down, and drive valve pocket (502f) to move upward, final plant closure control valve, realize inner carrier to follow spool and move.

Claims

1. a double-crankshaft variable compression ratio engine, comprise the structure that the double-crankshaft after optimization and variable-compression-ratio piston combine, it is characterized in that, variable-compression-ratio piston is using the cylinder sleeve (401) of outer piston as double-acting hydraulic cylinder, the cover plate (403) of stationary ring on the opening of cylinder sleeve (401), inner piston rod (4026) passes through in the middle of cover plate (403), and the space of cylinder sleeve is divided into by the inner carrier (402) of double-acting hydraulic cylinder, lower oil hydraulic cylinder (4021, 4022), the control valve pocket (502a of center mounting hole (4023) the internal fixtion sliding valve style position control valve of inner carrier, 502b, 502c, 502d, 502e, 502f), in undercrown surface center mounting hole (4011) rotational slide installation or nut-screw rod, control spool (501a is installed, 501b, 501c, 501d, 501e, 501f), the control spool of variable-compression-ratio piston sliding valve style directional control valve is installed driveshaft (808), the sliding sleeve (807) of linear slide is installed in driveshaft bottom, and bottom rotary drive mechanism (800) drives sliding sleeve (807), twin crankshaft engine counterrotating bent axle by gear be coupled together synchronous backward rotate, each piston is connected with the pitman shaft of two bent axles, and the driveshaft (808,807) reserving variable-compression-ratio piston in the bent axle of twin crankshaft engine, the centre of connecting rod passes through position, piston control valve driving mechanism (800) is arranged between two bent axles, difference Flywheel (204) on each bent axle of twin crankshaft engine, the working liquid body of variable-compression-ratio piston is low pressure liquid, directly adopts the working liquid body of lubricant oil as variable piston of engine lubrication system.

2. double-crankshaft variable compression ratio engine according to claim 1, is characterized in that, difference Flywheel (204) on each bent axle.

3. double-crankshaft variable compression ratio engine according to claim 1, is characterized in that, distributing flywheel adopts full symmetric structure, i.e. distribution two counterweight blocks on each cylinder of bent axle, additional flywheels simultaneously on each counterweight block.

4. double-crankshaft variable compression ratio engine according to claim 1, it is characterized in that, distributing flywheel adopts Lightened structure embodiment 1, namely on two bent axles that each cylinder is corresponding each a band balancer weight is installed crank arm (203) and a crank arm (204) not only with balancer weight but also with flywheel, on two bent axles, different crank arm is alternately distributed.

5. double-crankshaft variable compression ratio engine according to claim 1, it is characterized in that, distributing flywheel adopts Lightened structure embodiment 2, and each crank arm (203) installing a band balancer weight on two bent axles that namely each cylinder is corresponding, on two bent axles, different crank arm is alternately distributed.

6. double-crankshaft variable compression ratio engine according to claim 1, is characterized in that, piston, connecting rod adopt three axles to connect, and the inner carrier push rod (4026) of piston is slidably matched by three hole connectors (600) and connecting rod (701) and is linked together by connecting rod.

7. double-crankshaft variable compression ratio engine according to claim 1, it is characterized in that, the sliding valve style directional control valve control valve embodiment 1 of variable-compression-ratio piston is: 3-position-3-way axis moves self-pump type's variable-compression-ratio piston control valve, main control valve structure is equivalent to 3-position-3-way directional control valve, valve pocket (502a) there are two annular grooves (5022, 5023), upper annular groove is that upper cylinder half annular groove (5022) communicates with upper oil hydraulic cylinder, lower annular groove is that under lower ring, annular groove (5023) communicates with lower oil hydraulic cylinder, on, be valve pocket seal section (5025) between lower annular groove, spool (501a) is hollow type, there is hydraulic oil outflow opening (5011) at middle part, communicate with the center hole (5012) of spool, hydraulic oil inflow entrance in the middle part of spool can be separately cellular type, also an annular groove can be established, hydraulic oil outflow opening diameter in the middle part of spool or be highly less than or equal to the height (5025) of valve pocket seal section, hydraulic oil access aperture (5013 is established at spool two ends, 5014), hydraulic oil access aperture installs one-way valve (503, 504), one-way valve flow direction is to outflow by spool, the outlet of upper one-way valve (503) communicates with upper oil hydraulic cylinder, lower one-way valve (504) communicates with lower oil hydraulic cylinder, one-way valve (505) is installed at the driveshaft top of spool, one-way valve liquid flow path direction from bottom to top, spool is slidably mounted in valve pocket, valve pocket is fixed on inner carrier, spool (501a) nut (4012) and screw mandrel (5018) are arranged in the internal surface center mounting hole (4011) of piston top, one-way valve (503, 504, 505) circlip type is adopted to move horizontally one-way valve, piston arranges safety installations, eliminate security risk when hydraulic oil heat is splashed swollen, control spool (501a) arranges decompression longitudinal hole (5017) and is in communication with the outside in the space of mounting hole (4011), decompression longitudinal hole (5017) does not communicate with center hole (5012), reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.

8. double-crankshaft variable compression ratio engine according to claim 1, it is characterized in that, the sliding valve style position control valve embodiment 2 that variable-compression-ratio piston is installed is: 3-position-3-way spiral chute self-pump type variable-compression-ratio piston control valve, main control valve structure is equivalent to 3-position-3-way directional control valve, valve pocket (502b) there are two groups of cannelure (5022a, 5023a), upper cannelure is that upper cylinder half cannelure (5022a) communicates with upper oil hydraulic cylinder, lower cannelure is that under lower cylinder, cannelure (5023a) communicates with lower oil hydraulic cylinder, on, be seal section (5025) between lower annular groove, spool (501b) is hollow type, it is hydraulic oil tap hole (5011) in the middle part of spool, communicate with the center hole (5012) of spool, in the middle part of spool, outer cylinder establishes spiral chute (5011a), in the middle part of spool, hydraulic oil tap hole (5011) is arranged in spiral chute (5011a), valve pocket cannelure and spiral chute phase cross surface place, when valve pocket seal section is in the middle of spiral chute, valve pocket seal section (5025) can sealing screw groove (5011a) completely, oil inlet hole (5013 is established at spool two ends, 5014) oil inlet hole (5013, 5014) one-way valve (503 is installed, 504), one-way valve flow direction is to outflow by spool, the outlet of upper one-way valve (503) communicates with upper oil hydraulic cylinder, lower one-way valve (504) communicates with lower oil hydraulic cylinder, one-way valve is installed at the driveshaft top of spool, (505), spool (501b) is slidably mounted in valve pocket (502b), valve pocket (502b) is fixed on inner carrier, spool (501b) setscrew nut (4012a) and positioning step (5018a) rotational slide are arranged in the internal surface center mounting hole (4011) of piston top, one-way valve liquid flow path direction from bottom to top, one-way valve (503, 504, 505) circlip type is adopted to move horizontally one-way valve, piston arranges safety installations, eliminate security risk when hydraulic oil heat is splashed swollen, control spool (501b) arranges longitudinal hole (5017) and is in communication with the outside in the space of mounting hole (4011), longitudinal hole (5017) does not communicate with center hole (5012), eliminate the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.

9. double-crankshaft variable compression ratio engine according to claim 1, it is characterized in that, variable piston safety installations scheme one is: mounting safety valve (506) on valve pocket, safety valve import communicates with lower oil hydraulic cylinder, outlet drain is to piston exterior, and opening pressure of safety valve is greater than the working pressure of engine peak speed oil hydraulic cylinder at present.

10. double-crankshaft variable compression ratio engine according to claim 1, it is characterized in that, variable piston safety installations scheme two is: change the seal ring (4031) between inner piston rod (4026) and oil hydraulic cylinder cover plate (403) into opening ring type, utilizes opening slowly to miss the safety ensureing to pacify oil hydraulic cylinder.

11. double-crankshaft variable compression ratio engines according to claim 1, it is characterized in that, circlip type moves horizontally one-way valve (503,504,505) and is made up of valve seat (5031,5041,5054), spool (5032,5042,5057), Returnning spring (5033,5043,5056), in one-way valve open and close process, spool movement direction is perpendicular to engine piston motion direction, and the Returnning spring (5033,5043,5056) of one-way valve is open ring structure.

12. double-crankshaft variable compression ratio engines according to claim 1, it is characterized in that, the sliding valve style position control valve embodiment 3 that variable-compression-ratio piston is installed is: the outer liquid formula variable-compression-ratio piston control valve of three groove sliding sleeve 3-position 4-ways, main valve structure is equivalent to three groove valve pocket 3-position 4-way guiding valves, valve pocket (502c) there are three annular grooves (5021, 5022, 5023), middle annular groove is that upper cylinder half annular groove (5022) communicates with upper oil hydraulic cylinder, on lower cylinder, under annular groove (5021) and lower cylinder, annular groove (5023) communicates with lower oil hydraulic cylinder, spool is hollow structure, spool top is hydraulic oil inflow entrance (5013), circlip type horizontal single-headed valve (503) is installed, it is to outflow by center spool that one-way valve flows to, be communicated with center spool hole (5012), bottom is hydraulic oil outflow opening (5011), hydraulic oil outflow opening (5011) flows out piston, valve pocket is two seal sections (5024 between three annular grooves, 5025), upper seal section (5024) its to be highly more than or equal on spool hydraulic oil inflow entrance annular groove (5015) highly, lower seal section (5025) is highly more than or equal to hydraulic oil outflow opening diameter (5011) in the middle part of spool, spool (501c) is slidably mounted in valve pocket (502c), valve pocket (502c) is fixed on inner carrier, spool (501c) nut (4012) and screw mandrel (5018) are arranged in the internal surface center mounting hole (4011) of piston top, control spool (501c) arranges decompression longitudinal hole (5017a) and is communicated with center hole (5012) in the space of mounting hole (4011), eliminate the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.

13. double-crankshaft variable compression ratio engines according to claim 1, it is characterized in that, the sliding valve style position control valve embodiment 4 that variable-compression-ratio piston is installed is: the outer liquid formula variable-compression-ratio piston control valve of two groove sliding sleeve 3-position 4-ways, main valve structure is equivalent to two groove valve pocket 3-position 4-way guiding valves, valve pocket (502d) there are two annular grooves (5022, 5023), upper annular groove is that upper cylinder half annular groove (5022) communicates with upper oil hydraulic cylinder, lower annular groove communicates with oil hydraulic cylinder under annular groove (5023) under lower cylinder, spool (501d) is hollow structure, spool (501d) has two groups of hydraulic oil ostiums (5013, 5014) and one group of hydraulic oil tap hole (5011), hydraulic oil ostium (5013, 5014) there is jump ring annular groove (5015 periphery, 5016), circlip type is installed and moves horizontally one-way valve (503, 504), it is to outflow by center spool that one-way valve flows to, be communicated with center-pole mesopore (5012), middle part is hydraulic oil outflow opening (5011), valve pocket is seal section (5025) between two annular grooves, spool is seal spool section (50112 between three groups of holes, 50113), valve pocket seal section (5025) is highly more than or equal to the height of hydraulic oil tap hole (5011), seal spool section (50112, 50113) height is more than or equal to valve pocket annular groove (5022, 5023) highly, spool (501d) nut (4012) and screw mandrel (4018) are arranged in the internal surface center mounting hole (4011) of piston top, control spool (501d) arranges decompression longitudinal hole (5017a) and is communicated with center hole (5012) in the space of mounting hole (4011), reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.

14. double-crankshaft variable compression ratio engines according to claim 1, it is characterized in that, the sliding valve style position control valve embodiment 5 that variable-compression-ratio piston is installed is: 3-position 4-way spiral chute genesis analysis formula variable-compression-ratio piston control valve, main valve structure is equivalent to three groove valve pocket 3-position 4-way guiding valves, valve pocket (502e) there are three groups of cannelure (5021a, 5022a, 5023a), middle cannelure is that upper cylinder half cannelure (5022a) communicates with upper oil hydraulic cylinder, cannelure (5021a) on lower cylinder, under lower cylinder, cannelure (5023a) communicates with lower oil hydraulic cylinder, spool (501e) is the tubulose of band center hole, on spool outer cylinder, lower each distribution one group of spiral chute (5013a, 5011ae), upper spiral chute (5013a) communicates with hydraulic oil inflow entrance (5013), and be communicated with center spool hole (5012), lower spiral chute (5011ae) communicates with hydraulic oil outflow opening (5011e), be communicated with space outerpace by longitudinal hole (50111), valve pocket is two seal sections (5024 between longitudinal annular groove, 5025), valve pocket (502e) cannelure and spiral chute (5013a, 5011ae) phase cross surface place, when valve pocket seal section is in the middle of spiral chute, seal section can sealing screw groove completely, spool (501e) is slidably mounted in valve pocket (502e), (502 e) are fixed on inner carrier valve pocket, spool (501e) setscrew nut (4012a) and positioning step (5018a) rotational slide are contained in the internal surface center mounting hole (4011) of piston top, one-way valve (505) is installed at driveshaft top, circlip type horizontal single-headed valve, control spool (501e) arranges decompression longitudinal hole (5017) and is in communication with the outside in the space of mounting hole (4011), decompression longitudinal hole (5017) does not communicate with center hole (5012), reduce the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.

15. double-crankshaft variable compression ratio engines according to claim 1, it is characterized in that, the sliding valve style position control valve embodiment 6 that variable-compression-ratio piston is installed is: 3-position 4-way spiral chute circle distribution formula variable-compression-ratio piston control valve, valve pocket (502f) has four groups of cannelures, on, lower each distribution two groups of cannelures, upper cannelure is divided into cannelure (5021af) on cannelure (5022af) on the upper cylinder half that communicates with upper fluid cylinder and the lower cylinder that communicates with lower oil hydraulic cylinder, lower cannelure is divided into cannelure (5023af1) under cannelure (5022af1) under the upper cylinder half communicated with upper oil hydraulic cylinder and the lower cylinder that communicates with lower oil hydraulic cylinder, spool (501f) outer cylinder circle distribution two groups of spiral chute (5011af, 5013af), wherein one group of spiral chute is hydraulic oil inflow entrance (5013af), be communicated with center spool hole (5012), another group spiral chute is hydraulic oil outflow opening (5011af), be communicated with space outerpace, valve pocket is two seal section (5024f between longitudinal annular groove, 5025f), valve pocket (502f) cannelure and spiral chute (5011af, 5013af) phase cross surface place, when valve pocket seal section is in the middle of spiral chute, seal section can sealing screw groove completely, spool (501f) is slidably mounted in valve pocket (502f), on lower cylinder, under cannelure (5021af) and upper cylinder half, the direction of cannelure (5022af1) is corresponding with the hydraulic oil inflow entrance (5013f) of spool (501f), and under lower cylinder, on cannelure (5023af1) and upper cylinder half, the direction of cannelure (5022af) is corresponding with the hydraulic oil inflow entrance (5011f) of spool (501f), under lower cylinder, on cannelure (5023af1) and upper cylinder half, the direction of cannelure (5022af) is corresponding with the hydraulic oil inflow entrance (5011f) of spool (501f), valve pocket (502f) cannelure and spiral chute (5011af, 5013af) phase cross surface place, when valve pocket seal section is in the middle of spiral chute, seal section can sealing screw groove completely, spool (501f) is slidably mounted in valve pocket (502f), valve pocket (502f) is fixed on inner carrier, spool (501e) setscrew nut (4012a) and positioning step (5018a) rotational slide are contained in the internal surface center mounting hole (4011) of piston top, one-way valve (505) is installed at driveshaft top, control spool (501f) arranges longitudinal hole (5017) and is in communication with the outside in the space of mounting hole (4011), longitudinal hole (5017) does not communicate with center hole (5012), eliminate the pressure that generation missed on a small quantity by hydraulic oil, alleviate and control spool steering force.

16. double-crankshaft variable compression ratio engines according to claim 1, it is characterized in that, the control valve driveshaft of self-pump type's variable-compression-ratio piston is sliding bush type, the driveshaft (808) on top is uniformly distributed semicircle spline (8082), the driving casing of bottom is ring-shaped sleeve, top is uniformly distributed the corresponding hole (8075) of spline semicircle with the driveshaft on top, drive the diameter of trepanning identical with the diameter of the semicircle spline of the driveshaft on top, in the hole of driving casing, steel ball is installed, steel ball half is exposed in driving casing, the steel ball exposed is arranged in the semicircle spline of the driveshaft on top.

17. double-crankshaft variable compression ratio engines according to claim 4, is characterized in that, the steel ball in the hole of driving casing replace with band circular arc head with the bullet nose rod of screw thread, simplified structure.