CN203939575U - Double-crankshaft variable compression ratio engine - Google Patents
Double-crankshaft variable compression ratio engine Download PDFInfo
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- CN203939575U CN203939575U CN201420248875.9U CN201420248875U CN203939575U CN 203939575 U CN203939575 U CN 203939575U CN 201420248875 U CN201420248875 U CN 201420248875U CN 203939575 U CN203939575 U CN 203939575U
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Abstract
A kind of reciprocating-piston engine, comprise the structure that double-crankshaft after optimization and variable compression ratio combine, it is characterized in that, at the bent axle of twin crankshaft engine,, the centre of connecting rod (421) reserves the driveshaft of self-pump type's variable-compression-ratio piston, pass through position (413); Control valve pocket (502) on self-pump type's variable-compression-ratio piston, (502a) and control spool (501), (501a) are arranged in the center mounting hole (4023) and outer piston top center mounting hole (4011) of inner carrier; The outer piston of self-pump type's variable-compression-ratio piston (401), inner carrier (402), hydraulic cylinder (403) all adopt axially symmetric structure; Piston control valve driving mechanism (607) is arranged between two bent axles; Difference Flywheel (204) on each bent axle of twin crankshaft engine; The main shaft of two bent axles is installed gear (304), (306), ring gear (301) and external toothing (302) are fixed together, the mainshaft gear of two bent axles (304), (306) are meshing with ring gear (302) and the external toothing (301) of gear ring respectively, on the pto＝power take-off of output shaft on gear ring (303).
Description
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 causes to adjust air inflow and comes the petrol engine of Modulating Power when low-load, and 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, by hydraulic pressure, changes piston length, and coordinates to change the modes such as piston length by spring and hydraulic pressure.Mobile cover type has formed product, and confirms that variable compression ratio engine can significantly 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 at present large-scale promotion.By hydraulic pressure and spring, coordinate the scheme that changes piston with hydraulic pressure, because piston is the parts of a high-speed motion, the difficulty that hydraulic pipe line is set is reliably very large.
The present inventor has designed a kind of piston of self-pump type's variable compression ratio in early stage, by plunger designs, it is double-acting oil hydraulic cylinder, inner carrier at oil hydraulic cylinder is connected with connecting rod, and inner carrier and cylinder body are installed respectively and controlled valve pocket and control spool, control spool and are divided into axial motion type and rotary.In the inner cylinder of two kinds of control valve pockets, all there is fluid passage respectively with upper, lower oil hydraulic cylinder communicates, controlling valve pocket middle is seal section, revolving control spool outside cylinder has spirality fluid passage, the control spool of the axial motion type outside centre of cylinder has annular fluid passage, control spool band 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 that has spirality fluid passage by rotation outer cylinder, or move axially the control spool that outer cylinder has annular fluid passage, can make to control fluid passage and the upper fluid passage of controlling valve pocket inner cylinder on spool outer cylinder, lower fluid passage communicates, fluid passage on controlling spool outer cylinder is when communicating with fluid passage in inner cylinder on valve pocket, when upper oil hydraulic cylinder pressurized, near the hydraulic oil of (typicalness is expansion stroke and lower dead center) upper oil hydraulic cylinder enters control spool by upper oil hydraulic cylinder and flows into lower oil hydraulic cylinder by one-way valve, promotion inner carrier moves upward, piston length shortens, on inner carrier, move simultaneously, when seal section that control valve puts is relative with 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 the fluid passage on controlling spool outer cylinder communicates with fluid passage under control valve pocket inner cylinder, when lower oil hydraulic cylinder pressurized, the hydraulic oil of (typicalness suction stroke and exhaust stroke latter stage) lower oil hydraulic cylinder is entered and is controlled spool and flow into oil hydraulic cylinder by one-way valve by lower oil hydraulic cylinder, promotion inner carrier moves downward, by moving valve core, just realized the upper of inner carrier like this, lower movement, changed the length of piston, the transfer passage that does not need hydraulic oil, do not increase again the configuration difficulty of other parts, but the conventional connecting rod small end starting is positioned at piston axis place, the controlling rod of spool must be arranged on side, causing piston is 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.
Known motor is generally single shaft type, but the motor of double-crankshaft also has research and experiment, twin crankshaft engine is on motor, to have 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, can eliminate the side pressure of piston, while two crank spindles and connecting rod major axial diameter can reduce, reduce frictional loss, but some data of tool are introduced this motor may be upper, near two connecting rod asynchrony phenomenons lower dead center, cause job insecurity, the problems referred to above can increase a coupling shaft by employing and solve, present inventor finds by research, when two bent axles pass through gear coupling, while exporting by single drive shaft again, during due to engine operation, be outwards to export energy (expansion stroke) and alternately occur from outer absorption energy, can cause coupling gear continually in positive and negative drive condition, coupling working gear state is very severe, can cause gear life extremely short.
Summary of the invention
The technical problems to be solved in the utility model is: the processing of (1) self-pump type's variable-compression-ratio piston and the higher problem of installation difficulty; (2) working state of twin crankshaft engine coupling gear is severe, causes the extremely short problem of gear life.
Concrete technological scheme is: at the bent axle of twin crankshaft engine,, the centre of connecting rod reserves the driveshaft of self-pump type's variable-compression-ratio piston, pass through position; Control valve pocket on self-pump type's variable-compression-ratio piston is arranged in the center mounting hole and outer piston top center mounting hole of inner carrier; The outer piston of self-pump type's variable-compression-ratio piston, inner carrier, hydraulic cylinder all adopt axially symmetric structure; Piston control valve driving mechanism is arranged between two bent axles; The main shaft of two bent axles is installed gear, and ring gear and external toothing are fixed together, and the mainshaft gear of two bent axles is meshing with ring gear and the external toothing of gear ring respectively, on the pto＝power take-off of output shaft on gear ring.
Flywheel respectively on each bent axle in the above-mentioned twin crankshaft engine that changes compression ratio, the crankshaft-flywheel of optimizing adopts distributing, be a crank arm with balancer weight and one to be respectively installed not only with balancer weight but also with the crank arm of flywheel on two corresponding bent axles of each cylinder, on two bent axles, different crank arms are alternately distributed, and the crank arm end of spindle mounting hole band flywheel is telescopic.
The bent axle of optimizing adopts completely separated structure, bent axle is divided into main shaft, crank arm and connecting rod macro-axis, between main shaft and crank arm, adopt the conical interference-fit of fastened by screw to link, between crank arm and connecting rod macro-axis, adopt sliding connection, the crank arm connecting rod macro-axis containing flywheel is not blind-hole type, crank arm flywheel containing flywheel is that edge is thick, intermediate thin, between flywheel and cylinder body dividing plate, leave annular space, connecting rod macro-axis is not installed thrust mechanism at the axle head that does not contain the crank arm of flywheel, rely on blind hole thrust, at the crank arm containing flywheel, thrust mechanism is installed, connecting rod macro-axis mounting hole is set on the cylinder body of the position corresponding with connecting rod macro-axis, for installing connecting rods macro-axis and thrust mechanism.
The piston rod Placement of optimizing is: three axles connect, the inner carrier push rod of piston is slidably matched connecting rod is linked together by three hole connectors, wrist pin, connecting rod small end axle, connnecting rod big end axis hole is slidably installed on connecting rod macro-axis, three hole connectors are two dihedral plates of three axis holes that distribute, by connecting plate, form an integral body, it in the middle of connecting plate, is the hole of passing through of controlling spool driveshaft, larger axis hole is piston pin hole, two less axis holes are connecting rod small end axis hole, and preferred three hole connector middle openings are partly the structure outwards increasing.
The control valve of the self-pump type's variable-compression-ratio piston in the above-mentioned twin crankshaft engine that changes compression ratio is divided into rotary and axis portable, in the inner cylinder of two kinds of control valve pockets, all there is fluid passage respectively with upper, lower oil hydraulic cylinder communicates, controlling valve pocket middle is seal section, revolving control spool outside cylinder has spirality fluid passage, the control spool of the axial motion type outside centre of cylinder has annular fluid passage, control spool band 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 that has spirality fluid passage by rotation outer cylinder, or move axially the control spool that outer cylinder has annular fluid passage, can make to control fluid passage and the upper fluid passage of controlling valve pocket inner cylinder on spool outer cylinder, lower fluid passage communicates, fluid passage on controlling spool outer cylinder is when communicating with fluid passage in inner cylinder on valve pocket, when upper oil hydraulic cylinder pressurized, near the hydraulic oil of (typicalness is expansion stroke and lower dead center) upper oil hydraulic cylinder enters control spool by upper oil hydraulic cylinder and flows into lower oil hydraulic cylinder by one-way valve, promotion inner carrier moves upward, piston length shortens, on inner carrier, move simultaneously, when seal section that control valve puts is relative with 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 the fluid passage on controlling spool outer cylinder communicates with fluid passage under control valve pocket inner cylinder, when lower oil hydraulic cylinder pressurized, the hydraulic oil of (typicalness suction stroke and exhaust stroke latter stage) lower oil hydraulic cylinder is entered and is controlled spool and flow into oil hydraulic cylinder by one-way valve by lower oil hydraulic cylinder, promotion inner carrier moves downward, by moving valve core, just realized the upper of inner carrier like this, lower movement, changed the length of piston.
Because inner carrier stroke is little, the installing space of inner carrier upper part is little, and the downward installing space of inner carrier push rod is more sufficient, the seal section of controlling valve pocket is positioned at the following larger distance of inner carrier, lower oil hydraulic cylinder on the other side may be by hydraulic cylinder shutoff, the fluid passage of lower oil hydraulic cylinder can not directly communicate with the lower fluid passage of controlling valve pocket, control valve nested structure and the mounting type optimized are: near inner carrier lower surface place, establishing radially fluid passage, lower oil hydraulic cylinder is communicated with inner carrier mounting hole, control upper part and the inner carrier sealing of the outer cylinder of valve pocket, stay gap controlling between the bottom of valve pocket and inner carrier mounting hole, realizing lower oil hydraulic cylinder passage shifts downwards, meet the installation of controlling valve pocket.
The one-way valve of the upper oil hydraulic cylinder in the twin crankshaft engine of the variable compression ratio of optimizing comprises one-way valve seat, nonreturn valve core and check valve spring, be arranged in the mounting hole of outer piston top center, with control spool concentric, mounting hole bottom is provided with the fluid passage communicating with upper oil hydraulic cylinder.
Lower oil hydraulic cylinder one-way valve in the twin crankshaft engine of the variable compression ratio of optimizing comprises one-way valve seat, nonreturn valve core and check valve spring, one-way valve seat, nonreturn valve core are loop configuration, one-way valve seat is the loop configuration with longitudinal fluid passage, annular fluid passage is stayed in one-way valve seat bottom, the control spool of one-way valve seat lower annular fluid passage relative position is established radial hole, the entrance of realizing one-way valve communicates with control spool center hole, in one-way valve seat, on the corresponding control spool in top, seal ring is installed, is realized the outlet and entrance separation of lower oil hydraulic cylinder one-way valve.
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 hole corresponding with the semicircle spline of 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, half is exposed at steel ball in driving casing, and the steel ball exposing is arranged in the semicircle spline of driveshaft on top.
Above-mentioned control valve drives the steel ball in sliding sleeving hole to replace with circular arc head and bullet nose rod screw thread, carrys out simplified structure.
The beneficial effects of the utility model are: self-pump type's variable-compression-ratio piston is combined with twin crankshaft engine, have reduced the processing of self-pump type's variable-compression-ratio piston and installation difficulty; By disperseing the structure of flywheel, reduce and even eliminate the conversion of bent axle between energy input and output, by two bent axles, adopt the gear ring coupling with internal tooth and external tooth, the coupling manner of output shaft on gear ring, make the working state of two bent axles identical, eliminate the severe working state of coupling gear.
Embodiment
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 be double-crankshaft variable compression ratio engine along the horizontal sectional drawing of crank spindle,
Fig. 3 is self-pump type's variable-compression-ratio piston connecting rod three-dimensional appearance figure,
Fig. 4 is double-crankshaft coupling gear position graph of a relation
Fig. 5 is triple axle linkage connector stereogram,
Fig. 6 connecting rod stereogram,
Fig. 7 wrist pin stereogram
Fig. 8 is not with flywheel crankshaft arm stereogram
Fig. 9 is the crank arm stereogram with flywheel
Figure 10 is rotary control valve variable-compression-ratio piston sectional drawing,
Figure 11 rotary control valve variable-compression-ratio piston spool,
Figure 12 rotary control valve variable-compression-ratio piston valve pocket,
Figure 13 is axial motion type control valve variable-compression-ratio piston sectional drawing,
Figure 14 axial motion type control valve variable-compression-ratio piston spool,
Figure 15 axial motion type control valve variable-compression-ratio piston valve pocket,
Driveshaft on Figure 16 variable-compression-ratio piston control valve,
Under Figure 17 variable-compression-ratio piston control valve, drive sliding sleeve,
Figure 18 variable-compression-ratio piston control valve drives switching mechanism Local map.
Fig. 1 ~ Fig. 4 has described the structure of double-crankshaft variable compression ratio engine double-crankshaft, in order to make drawing succinct, only drawn a set of piston crank mechanism, cylinder body in figure (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 holes (104), spindle mounting hole (104) is tube-in-tube structure with the crank arm end of flywheel, connecting rod macro-axis mounting hole (102) is set on the cylinder body of the position corresponding with connecting rod macro-axis, for installing connecting rods macro-axis and thrust mechanism, cylinder body can be the manufacture at two positions at main shaft place subdivision, also can be fabricated to integrated type by the present embodiment.
The main shaft (201) of two ends band cone angle with not with flywheel crankshaft arm (203) be with the center hole (2031) of flywheel crankshaft arm (204), (2041) by main shaft fastening screw (205) interference fit together, not with flywheel crankshaft arm (203) and band flywheel crankshaft arm (204) connecting rod axis hole (2032), (2042) by connecting rod macro-axis (202), link together, fit system can be that interference fit can be to be also slidably matched, what in the present embodiment, select is to be slidably matched, containing (203) on the crank arm of flywheel, be not (Fig. 2) blind-hole type, the flywheel (2043) that contains the crank arm (204) of flywheel is that edge is thick, intermediate thin, between flywheel and cylinder body dividing plate (103), leave annular space (105), at the crank arm containing flywheel, thrust screw (205) is installed, form complete bent axle, article two, the contrary crankshaft installed of installing of different crank arms is on the mounting hole (104) of cylinder body.
Gear (304) and gear (306) are fixed on main shaft by fastening screw (305), (307) respectively, 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), the gear ratio of external toothing (301) and gear (306) equals the gear ratio of ring gear (302) and gear (304), establishes pto＝power take-off (303) on inside and outside gear ring.
The inner carrier push rod (406) of piston is slidably matched link arm (421) is linked together by three hole connectors (411), wrist pin (431), connecting rod small end axle (434), and connnecting rod big end axis hole (423) is slidably installed on connecting rod macro-axis (202).
Fig. 5 has described the structure of three hole connectors (411), two dihedral plates for three axis holes that distribute, by connecting plate (412), form an integral body, it in the middle of connecting plate (412), is the hole of passing through of spool driveshaft (608), larger axis hole is piston pin hole (414), two less axis holes are connecting rod small end axis hole (415), and preferred three hole connector middle openings are partly the structure outwards increasing.
Fig. 6 has described bar linkage structure, and its structure is similar to plain connecting rod, is divided into link arm (421), connecting rod small end axis hole (422) connnecting rod big end axis hole (423), and the connnecting rod big end of optimization is integrated type, connecting rod small end is outside attenuate structure.
Fig. 7 has described wrist pin structure, is divided into wrist pin (431) main body, lightening hole (433), spool driveshaft (608) pass through hole (432).
Fig. 8 has described and has not been with flywheel crankshaft arm (203) structure, distribution main shaft attachment hole (2031), the large axis hole of connecting rod (2032), eccentric weight (2033).
Fig. 9 has described crank arm (204) structure with flywheel, distribution main shaft attachment hole (2041), the large axis hole of connecting rod (2042), eccentric weight (2043), and flywheel (2043) is an integral body with crank arm.
Figure 10 ~ Figure 12 has described rotary control valve variable-compression-ratio piston structure, piston cylinder cover (403) is fixed on outer piston (401), inner carrier (402) is slidably matched with the inwall of outer piston (401), be slidably matched with the inner carrier push rod (4026) of inner carrier (402) one and the inner hole wall of piston cylinder cover (403), seal ring (4031) is installed on the inwall of piston cylinder cover (403), on inner carrier (402) outer wall, seal ring (4024) is installed, inner carrier push rod (4026) bottom is provided with piston pin hole (4027), outer piston (401), inner carrier (402) and piston cylinder cover (403) have formed, lower oil hydraulic cylinder (4021) (4022).
The whole tubulose for band central through bore (5013) of rotary control valve core (501), the centre of controlling spool outer cylinder arranges the fluid passage (5011) of symmetrical spiral, in spirality fluid passage radial hole (5012) is set, radial hole (5012) is communicated with central through bore (5013) with the fluid passage (5011) of spiral, the fluid passage of spiral (5011) upper, under outer cylinder seal groove (5017a) is set, (5015a), the bottom of control spool is established radial hole (5014) and is communicated with central through bore (5013), control the bottom of spool and establish seal groove (5016a), control the top of spool and establish locating flange (5018).
The tubular structure that rotary control valve cover is band locating flange dish (5024), the symmetrical longitudinal upper and lower fluid passage of inwall (5021)) (5022), annular seal section (5023) longitudinally distributes between fluid passage.
Controlling spool (501) is slidably mounted in outer piston top center mounting hole (4011) by set screw (5018a) Concentric rotation, control the seal groove (5017a) of spool seal ring (5017) is installed, control valve pocket (502) and be fixed on one heart in inner carrier center mounting hole (4023), control valve pocket (502) top and inner carrier sealing, control spool (501) outer diameter identical with control valve pocket seal section (5023) inner diameter, after controlling valve pocket (502) and controlling spool (501) installation, when inner carrier (402) is positioned at middle of stroke, the seal section (5023) of controlling valve pocket is positioned at the centre of spirality fluid passage (5011), on control valve pocket seal section (5023) highly depends on that the width of the spirality fluid passage of controlling spool is longitudinal with control valve pocket, the width of lower fluid passage, when controlling the seal section (5023) of valve pocket and be positioned in the vertical spirality fluid passage (5011) middle of spool, the seal section (5023) of controlling valve pocket can cover spirality fluid passage (5011) completely, the non-fluid passage part diameter of controlling the longitudinal fluid passage of valve pocket is identical with control valve pocket diameter of sealed section, the total height that control valve pocket total height is greater than spirality fluid passage (5011) adds inner carrier total kilometres, to guarantee that spirality fluid passage (5011) does not directly communicate with the two ends of controlling valve pocket, outer piston top center is established oil hydraulic cylinder one-way valve mounting hole (4012), install oil hydraulic cylinder one-way valve (503), comprise one-way valve seat (5031), nonreturn valve core (5032), check valve spring (5033), one-way valve mounting hole bottom is provided with fluid passage (5034) and upper oil hydraulic cylinder) (4021) communicate, the liquid in control spool (501) central through bore (5013) can unidirectional inflow on oil hydraulic cylinder, control on spool middle and lower part radial hole (5014) and the lower oil hydraulic cylinder one-way valve (504) of annular is installed between inner carrier inner hole wall, comprise one-way valve seat (5041), nonreturn valve core (5042), check valve spring (5043), one-way valve seat (5041) is established fluid passage (5045), annular fluid passage (5044) is stayed in one-way valve seat bottom, on inner carrier push rod, establish radially fluid passage (5046), control between valve pocket bottom outer wall and inner carrier endoporus and stay gap (5047), radially fluid passage (5046) communicates with gap (5047), seal ring (5015) is installed in seal groove (5015a), the liquid of controlling spool central through bore can pass through radial hole (5014), fluid passage (5045), nonreturn valve core (5042), oil hydraulic cylinder under gap (5047) and the unidirectional inflow of fluid passage (5046).
During driveshaft (608) rotation, can make to control the fluid passage on spool (501) outer cylinder) (5011) with control in valve pocket inner cylinder, lower fluid passage (5021), (5022) communicate, when the fluid passage (5011) on controlling spool outer cylinder and control valve put fluid passage in inner cylinder (5021) and communicate, the hydraulic oil of upper oil hydraulic cylinder (4021) when upper oil hydraulic cylinder pressurized (typicalness is near expansion stroke and lower dead center) by upper oil hydraulic cylinder enter control spool through under oil hydraulic cylinder one-way valve flow under oil hydraulic cylinder (4022), promoting inner carrier (402) moves upward, piston length shortens, on inner carrier, move simultaneously, when seal section (5023) that control valve puts with control fluid passage (5011) on spool when relative, fluid passage on control spool and upper, lower oil hydraulic cylinder does not all communicate, inner carrier moves into place, equally, fluid passage on controlling spool outer cylinder and control valve put under inner cylinder when fluid passage communicates, the hydraulic oil of lower oil hydraulic cylinder (typicalness suction stroke and exhaust stroke latter stage) when lower oil hydraulic cylinder pressurized is entered and is controlled spool and flow into upper oil hydraulic cylinder through upper oil hydraulic cylinder one-way valve by lower oil hydraulic cylinder, promotion inner carrier moves downward, by rotary spool, just realized the upper of inner carrier like this, lower movement, changed the length of piston.
Unidirectional make-up valve (505) is installed at upper driveshaft (608) top with central through bore, make-up valve consists of one-way valve seat (5051), nonreturn valve core (5052) and check valve spring (5053), liquid in driveshaft (608) can unidirectional inflow control valve core central through bore (5013) in, liquid in oil hydraulic cylinder occurs after leakage, pressure in central through bore (5013) is less than the pressure of the liquid of driveshaft (608), realizes automatically supplementing of oil hydraulic cylinder liquid.
Figure 13 ~ Figure 15 has described axial motion type control valve variable-compression-ratio piston structure, axial motion type is controlled the whole tubulose for band central through bore (5013) of spool (501a), the centre of spool outer cylinder arranges annular fluid passage (5011a), in annular fluid passage, radial hole (5012) is set, radial hole (5012) is communicated with central through bore (5013) with annular fluid passage (5011a), fluid passage (5011a) upper of annular, under outer cylinder seal groove (5017a) is set, (5015a), the bottom of control spool is established radial hole (5014) and is communicated with central through bore (5013), between radial hole (5014) and seal groove (5015a), stay fluid passage (5019), radial hole (5014) bottom is established and by rotatablely moving, is converted into straight-line screw mandrel (506), control the bottom of spool and establish seal groove (5016a).
Axial motion type is controlled valve pocket (502a) for the tubular structure of band locating flange dish (5024a), the symmetrical longitudinal upper and lower fluid passage of inwall (5021a)) (5022a), seal section (5023) longitudinally distributes between fluid passage.
Axial motion type is controlled spool (501a) concentric, axial and is slidably mounted in outer piston top center mounting hole (4011), controls valve pocket (502a) and is fixed on one heart in inner carrier center mounting hole (4023), control valve cover top and inner carrier sealing; Control valve core inner diameter is identical with control valve pocket diameter of sealed section, after controlling valve pocket and controlling spool installation, when inner carrier (402) is positioned at middle of stroke, the seal section (5023) of controlling valve pocket is positioned at the centre of annular fluid passage (5011a), when the seal section of valve pocket is positioned at annular fluid passage (5011a) middle of spool in the vertical, the seal section of valve pocket (5023) just covers annular fluid passage (5011a) completely; The height of controlling the longitudinal fluid passage of valve pocket can be very little, even cancels; Lower oil hydraulic cylinder one-way valve (504) is installed feed screw nut (5061) below, feed screw nut (5061) and the meshing installation of screw mandrel (506), that controls spool stays stroke gap (507), (5071) up and down, and other does not describe part and rotary to drive valve variable-compression-ratio piston identical.
During driveshaft (608) rotation, can make axial motion type control spool (501a) moves axially, the fluid passage (5011a) of controlling on spool outer cylinder puts on inwall with control valve, lower fluid passage (5021a), (5022a) communicate, when the fluid passage (5011a) on control valve outer core face and control valve put fluid passage in inner cylinder (5021a) and communicate, near the hydraulic oil of upper oil hydraulic cylinder (typicalness is expansion stroke and lower dead center) when upper oil hydraulic cylinder pressurized enters control spool by upper oil hydraulic cylinder and flows into lower oil hydraulic cylinder by one-way valve, promotion inner carrier moves upward, piston length shortens, on inner carrier, move simultaneously, when seal section that control valve puts with control fluid passage on spool when relative, fluid passage on control spool and upper, lower oil hydraulic cylinder does not all communicate, inner carrier moves into place, equally, fluid passage on controlling spool outer cylinder and control valve put under inner cylinder when fluid passage communicates, the hydraulic oil of lower oil hydraulic cylinder (typicalness suction stroke and exhaust stroke latter stage) when lower oil hydraulic cylinder pressurized is entered and is controlled spool and flow into oil hydraulic cylinder by one-way valve by lower oil hydraulic cylinder, promotion inner carrier moves downward, by control valve mandrel, to moving valve core, just realized the upper of inner carrier like this, lower movement, changed the length of piston.
Figure 16 ~ Figure 18 has described the structure of variable-compression-ratio piston spool steering driving mechanism, with coordinating referring to Fig. 1, Fig. 2 of associated components, upper driveshaft (608) in figure, for thering is the tubular structure of central through bore (6081), in upper driveshaft (608) middle and upper part, to bottom, be evenly distributed with arc groove (6082), lower driving sliding sleeve (607) is band driveshaft positioning step (6071), turbine positioning step (6071), with the fastening screw thread of turbine (6073), the tubular structure of band central through bore (6074), at lower driving sliding sleeve (607) top, be distributed with steel ball (or bullet nose rod) mounting hole (6075) corresponding with arc groove (6082) on upper driveshaft (608), arc groove (6082) is identical with the diameter of mounting hole (6075), steel ball in mounting hole (6075) or bullet nose rod and arc groove (6082) are slidably matched, upper driveshaft (608) can endwisely slip in lower driving sliding sleeve (607), on while rotating lower driving sliding sleeve (607), driveshaft (608) also rotates.
Fluid infusion rail (601) is the tubular structure with center hole, level is arranged on cylinder base, the position relative with each piston center arranges branched pipe (6011) upwards, branched pipe (6011) is the installation sleeve of lower driving sliding sleeve (607) simultaneously, lower driving sliding sleeve (607) is arranged in branched pipe (6011), lower driving sliding sleeve (607) coordinates with branched pipe (6011) rotational slide, rely on positioning step (6071) and set screw (604) location, turbine (605) is arranged on lower driving sliding sleeve (607), rely on positioning step (6071) location, fastening screw (606) is arranged on the fastening screw thread of turbine (6073), compress and fixed turbine (605), the upper scroll bar (603) identical with number of pistons that distribute of horizontal driveshaft (602), level is arranged on cylinder body, scroll bar (603) and meshing cooperation of turbine (605), rotating horizontal driveshaft (602) just can be with brake control valve core rotate or move axially, make, lower oil hydraulic cylinder liquid directional flow, change piston length.
Fluid infusion rail (601) communicates with engine lubricating oil, and lubricant oil is by fluid infusion rail (601), lower driving sliding sleeve (607), upper driveshaft (608), fluid infusion one-way valve, central through bore (503), upper and lower oil hydraulic cylinder one-way valve fluid replacement in oil hydraulic cylinder (4021), (4021) up and down.
The variable-compression-ratio piston spool steering driving mechanism of this enforcement has adopted turbine, Worm-drive, according to same principle, turbine and scroll bar is replaced with to gear and ratch, or is replaced by a pair of umbrella tooth, also can realize the effect of the present embodiment, no longer describes in detail.
Claims (9)
1. a reciprocating-piston engine, comprise the structure that double-crankshaft after optimization and variable compression ratio combine, it is characterized in that, at the bent axle of twin crankshaft engine,, the centre of connecting rod (421) reserves the driveshaft of self-pump type's variable-compression-ratio piston, pass through position (413); Control valve pocket (502) on self-pump type's variable-compression-ratio piston, (502a) and control spool (501), (501a) are arranged in the center mounting hole (4023) and outer piston top center mounting hole (4011) of inner carrier; The outer piston of self-pump type's variable-compression-ratio piston (401), inner carrier (402), hydraulic cylinder (403) all adopt axially symmetric structure; Piston control valve driving mechanism (607) is arranged between two bent axles; Difference Flywheel (204) on each bent axle of twin crankshaft engine; The main shaft of two bent axles is installed gear (304), (306), ring gear (301) and external toothing (302) are fixed together, the mainshaft gear of two bent axles (304), (306) are meshing with ring gear (302) and the external toothing (301) of gear ring respectively, on the pto＝power take-off of output shaft on gear ring (303).
2. reciprocating-piston engine according to claim 1, it is characterized in that, difference Flywheel (204) on each bent axle, the crankshaft-flywheel of optimizing adopts distributing, be a crank arm with balancer weight (203) and one to be respectively installed not only with balancer weight but also with the crank arm (204) of flywheel, on two bent axles, different crank arms are alternately distributed on two corresponding bent axles of each cylinder.
3. reciprocating-piston engine according to claim 1, it is characterized in that, bent axle adopts completely separated structure, bent axle is divided into main shaft (201), crank arm (203), and connecting rod macro-axis (202) (204), between main shaft and crank arm, adopt the conical interference-fit of fastened by screw to link, between crank arm and connecting rod macro-axis (202), adopt sliding connection, the large axis hole of crank arm (203) connecting rod containing flywheel is not blind-hole type, crank arm flywheel (2043) containing flywheel is that edge is thick, intermediate thin, between flywheel and cylinder body dividing plate, leave annular space (105), connecting rod macro-axis is not installed thrust mechanism at the axle head that does not contain the crank arm (203) of flywheel, rely on blind hole thrust, at the crank arm containing flywheel, thrust mechanism (206) is installed, connecting rod macro-axis mounting hole (102) is set on the cylinder body of the position corresponding with connecting rod macro-axis, for installing connecting rods macro-axis and thrust mechanism.
4. reciprocating-piston engine according to claim 1, it is characterized in that, piston, connecting rod adopts three axles to connect, the inner carrier push rod (4026) of piston is by three hole connectors (411), wrist pin (431), connecting rod small end axle (434) is slidably matched connecting rod is linked together, connnecting rod big end axis hole is slidably installed on connecting rod macro-axis, three hole connectors are two dihedral plates of three axis holes that distribute, by connecting plate (412), form an integral body, for what control spool driveshaft, pass through hole (413) in the middle of connecting plate, larger axis hole is piston pin hole (414), two less axis holes are connecting rod small end axis hole (415), preferred three hole connector middle openings are partly the structure outwards increasing.
5. reciprocating-piston engine according to claim 1, it is characterized in that, control valve nested structure and mounting type have been optimized, near inner carrier lower surface place, establishing radially fluid passage (5046), lower oil hydraulic cylinder is communicated with inner carrier mounting hole, controls the outer wall top and inner carrier sealing of valve pocket, between the bottom of control valve pocket and inner carrier mounting hole, stay gap (5047), realize lower oil hydraulic cylinder fluid passage and shift downwards, meet the installation requirement of controlling valve pocket.
?
6. reciprocating-piston engine according to claim 1, it is characterized in that, the one-way valve (503) of the upper oil hydraulic cylinder in the twin crankshaft engine of the variable compression ratio of optimizing comprises one-way valve seat (5031), nonreturn valve core (5032) and check valve spring (5033), be arranged in the mounting hole (4012) of outer piston top center, with control spool (501), (501a) concentric, mounting hole bottom is provided with the fluid passage (5034) communicating with upper oil hydraulic cylinder.
7. reciprocating-piston engine according to claim 1, it is characterized in that, lower oil hydraulic cylinder one-way valve (504) in the twin crankshaft engine of the variable compression ratio of optimizing comprises one-way valve seat (5041), nonreturn valve core (5042) and check valve spring (5043), one-way valve seat, nonreturn valve core is loop configuration, one-way valve seat is the loop configuration with longitudinal fluid passage (5045), annular fluid passage (5044) is stayed in one-way valve seat bottom, the control spool of one-way valve seat lower annular fluid passage relative position is established radial hole (5014), the entrance of realizing one-way valve communicates with control spool center hole (5013), in one-way valve seat, on the corresponding control spool in top, seal ring (5015) is installed, realizing outlet and the entrance of lower oil hydraulic cylinder one-way valve separates.
8. reciprocating-piston engine 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 on top (608) is uniformly distributed semicircle spline (6082), the driving casing of bottom is ring-shaped sleeve, top is uniformly distributed the hole (6075) corresponding with the semicircle spline of driveshaft on top, drive the diameter of the semicircle spline of the diameter of trepanning and the driveshaft on top identical, in the hole of driving casing, steel ball is installed, half is exposed at steel ball in driving casing, the steel ball exposing is arranged in the semicircle spline of driveshaft on top.
9. reciprocating-piston engine according to claim 4, is characterized in that, the steel ball in the hole of driving casing replaces with circular arc head and bullet nose rod screw thread, simplified structure.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420248875.9U CN203939575U (en) | 2014-05-15 | 2014-05-15 | Double-crankshaft variable compression ratio engine |
| PCT/CN2015/078641 WO2015172692A1 (en) | 2014-05-15 | 2015-05-11 | Engine with double-crankshaft and variable compression ratio |
| EP15792977.9A EP3147479B1 (en) | 2014-05-15 | 2015-05-11 | Engine with double-crankshaft and variable compression ratio |
| US15/338,190 US10087832B2 (en) | 2014-05-15 | 2016-10-28 | Double-crankshaft variable compression ratio engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420248875.9U CN203939575U (en) | 2014-05-15 | 2014-05-15 | Double-crankshaft variable compression ratio engine |
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| Publication Number | Publication Date |
|---|---|
| CN203939575U true CN203939575U (en) | 2014-11-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201420248875.9U Expired - Fee Related CN203939575U (en) | 2014-05-15 | 2014-05-15 | Double-crankshaft variable compression ratio engine |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015172692A1 (en) * | 2014-05-15 | 2015-11-19 | 天津潜景技术咨询有限公司 | Engine with double-crankshaft and variable compression ratio |
| CN105863836A (en) * | 2016-06-16 | 2016-08-17 | 吉林大学 | Gear ring adjustable internal combustion engine variable compression ratio mechanism |
| WO2017063751A1 (en) * | 2015-10-16 | 2017-04-20 | Peter Pelz | Internal combustion engine with double crank drive and variable compression ratio |
| CN106930844A (en) * | 2017-04-13 | 2017-07-07 | 宁波星豪汽车维修有限公司 | A kind of variable compression ratio device |
| CN108019287A (en) * | 2017-12-15 | 2018-05-11 | 东风汽车集团有限公司 | The cylinder block and head and cap assembly of a kind of variable compression ratio engine |
| CN111622836A (en) * | 2020-06-05 | 2020-09-04 | 张家陶 | Engine crankshaft with adjustable radius |
-
2014
- 2014-05-15 CN CN201420248875.9U patent/CN203939575U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015172692A1 (en) * | 2014-05-15 | 2015-11-19 | 天津潜景技术咨询有限公司 | Engine with double-crankshaft and variable compression ratio |
| WO2017063751A1 (en) * | 2015-10-16 | 2017-04-20 | Peter Pelz | Internal combustion engine with double crank drive and variable compression ratio |
| CN105863836A (en) * | 2016-06-16 | 2016-08-17 | 吉林大学 | Gear ring adjustable internal combustion engine variable compression ratio mechanism |
| CN105863836B (en) * | 2016-06-16 | 2018-05-08 | 吉林大学 | Gear ring adjustable type internal-combustion engine variable compression ratio mechanism |
| CN106930844A (en) * | 2017-04-13 | 2017-07-07 | 宁波星豪汽车维修有限公司 | A kind of variable compression ratio device |
| CN108019287A (en) * | 2017-12-15 | 2018-05-11 | 东风汽车集团有限公司 | The cylinder block and head and cap assembly of a kind of variable compression ratio engine |
| CN108019287B (en) * | 2017-12-15 | 2020-07-03 | 东风汽车集团有限公司 | Cylinder body cylinder cover and top cover assembly of variable compression ratio engine |
| CN111622836A (en) * | 2020-06-05 | 2020-09-04 | 张家陶 | Engine crankshaft with adjustable radius |
| CN111622836B (en) * | 2020-06-05 | 2021-11-19 | 张家陶 | Engine crankshaft with adjustable radius |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141112 Termination date: 20190515 |