CN111927872A - Crankshaft system of internal combustion engine with variable compression ratio, internal combustion engine and control method thereof - Google Patents

Crankshaft system of internal combustion engine with variable compression ratio, internal combustion engine and control method thereof Download PDF

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Publication number
CN111927872A
CN111927872A CN202010969154.7A CN202010969154A CN111927872A CN 111927872 A CN111927872 A CN 111927872A CN 202010969154 A CN202010969154 A CN 202010969154A CN 111927872 A CN111927872 A CN 111927872A
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China
Prior art keywords
hydraulic oil
combustion engine
internal combustion
oil
compression ratio
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CN202010969154.7A
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CN111927872B (en
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施军
晏慧
黄琪
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Chongqing University of Science and Technology
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Chongqing University of Science and Technology
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
    • F16C3/12—Crankshafts assembled of several parts, e.g. by welding by crimping releasably connected
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/22—Cranks; Eccentrics
    • F16C3/28—Adjustable cranks or eccentrics

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

The invention discloses an internal combustion engine crankshaft system with a variable compression ratio, an internal combustion engine and a control method thereof.A crank throw of the crankshaft system mainly comprises a crank arm with a hollow structure and a connecting rod journal, the connecting rod journal is movably arranged in relative to the crank arm, a rotating wheel is rotatably arranged in the crank arm and can rotate under the driving of an electric, hydraulic or mechanical structure, and the connecting rod journal can move along the radial direction of the crankshaft under the driving of the rotating wheel so as to change the effective working length of the crank throw. The method can meet the requirement of adjusting the compression ratio of the internal combustion engine, has good operability, is stable and reliable, and is beneficial to prolonging the service life of the internal combustion engine.

Description

Crankshaft system of internal combustion engine with variable compression ratio, internal combustion engine and control method thereof
Technical Field
The invention relates to the technical field of internal combustion engines, in particular to an internal combustion engine crankshaft system with a variable compression ratio, an internal combustion engine and a control method thereof.
Background
The compression ratio of an internal combustion engine is the ratio of the cylinder internal volume at the bottom dead center of a piston to the cylinder internal volume at the top dead center of the piston, and plays an important role in the power output and the thermal efficiency of the internal combustion engine. According to the operating principle of an internal combustion engine, the internal combustion engine requires a high compression ratio at a small load to improve the operating efficiency of the internal combustion engine, and a small compression ratio at a large load to avoid so-called "knocking" of the internal combustion engine to improve the power output. In a general spark-ignition internal combustion engine, the position of a crankshaft is fixed, the crank throw length of the crankshaft is unchanged, and the length of a connecting rod is unchanged, so that the position of a piston at a top dead center and a bottom dead center is unchanged, the compression ratio of the internal combustion engine is fixed, and the fixed compression ratio is a compromise choice for considering both a large load condition and a small load condition. Thus, such fixed compression ratio engines suffer from a large thermal efficiency penalty at low loads, while power output is limited by "knock" at high loads.
When the compression ratio of the internal combustion engine can be variably adjusted, the small load region can increase the compression ratio to improve the thermal efficiency of the internal combustion engine, and the large load region can decrease the compression ratio to raise the power output of the internal combustion engine. Many published patents also realize the variable compression ratio of the internal combustion engine, mainly adopt the eccentric wheel to change the crankshaft main bearing position, change the connecting rod bearing position through the eccentric wheel, change the distance between the crankshaft main shaft center and the piston top surface through the eccentric wheel and other modes, but most of these structures can cause the eccentricity of the crankshaft main shaft, the connecting rod shaft or the piston pin, and then lead to the problems of poor working stability, short service life or large abnormal sound of the internal combustion engine.
Disclosure of Invention
To solve the above problems, the present invention provides a crankshaft system of an internal combustion engine with a variable compression ratio, an internal combustion engine and a control method thereof, which can adjust the compression ratio of the internal combustion engine in a more stable manner, improve the working stability and reliability, and prolong the service life, etc
In order to achieve the purpose, the technical scheme of the invention is as follows:
the utility model provides a compress variable internal-combustion engine crankshaft system of ratio, includes the bent axle body and distributes along bent axle body axial for support the main bearing seat of bent axle body, the bent axle body is formed with the crank throw between two adjacent main bearing seats, the crank throw includes the connecting rod journal and connects two crank arms at connecting rod journal both ends respectively, its characterized in that: the connecting rod journal can slide along the radial direction of the crankshaft body relative to the crank arm, a rotating wheel is rotatably arranged in the crank arm, and the rotating wheel can rotate around the axis of the crankshaft body under the driving of an electric, hydraulic or mechanical structure and drives the connecting rod journal to slide to be close to or far away from the crankshaft body.
By adopting the scheme, in the working process of the crankshaft, the rotating wheel is mainly driven to rotate by external force, the rotating motion of the rotating wheel is converted into linear movement of the connecting rod journal, the moving distance of the connecting rod journal is adjusted by depending on the structure of the rotating wheel, the position of the connecting rod journal in the radial direction of the crankshaft is changed, namely the effective length of the crank throw is changed, the purpose of adjusting the compression ratio of the internal combustion engine is achieved, the eccentricity of a crankshaft main shaft, a connecting rod shaft or a piston pin is avoided, the eccentric wear of a piston and a crank-connecting rod mechanism of the internal combustion engine is reduced, the adjustment.
Preferably, the method comprises the following steps: the outer side of the crank arm is provided with a main journal, the rotating wheel and the main journal are coaxially arranged, the front surface of the rotating wheel is provided with an arc-shaped groove A, and an offset distance is formed between the circle center of the arc-shaped groove A and the circle center of the rotating wheel;
the crank arm is provided with a through hole for the insertion part to extend into, and the through hole limits the moving stroke of the connecting rod journal. By adopting the scheme, the sliding of the connecting rod journal is mainly guided and driven by the arc-shaped groove A of the rotating wheel, and the secondary limiting is carried out on the connecting rod journal through the hole, so that the sliding stability of the connecting rod journal is improved.
Preferably, the method comprises the following steps: the crank arm is internally provided with a sinking groove used for mounting the rotating wheel, the sinking groove is step-shaped, and the rotating wheel and the corresponding sinking groove surround to form a sealed chamber;
the runner has and extends the back shaft to both sides, the one end outside that the back shaft is close to the trunnion has two blade A, two blade B have in the heavy inslot, blade A and blade B will sealed cavity separates and forms four hydraulic pressure grease chamber, four hydraulic pressure grease chamber all is connected with the hydraulic pressure oil circuit.
The rotating wheel can rotate under stable pressure by adopting the mode that four hydraulic oil chambers respectively enter and exit oil, so that the rotating stability of the rotating wheel is favorably improved, namely the stability of the effective length adjustment of the crank throw is improved, the connecting rod journal can be stably kept at an adjusting position, and the rotating wheel has good stress bearing capacity.
Preferably, the method comprises the following steps: the outer side of the crank arm is provided with a main journal, the main journal is provided with an annular oil duct A and an annular oil duct B, and the four hydraulic oil chambers are respectively a hydraulic oil chamber A, a hydraulic oil chamber B, a hydraulic oil chamber C and a hydraulic oil chamber D which are sequentially distributed along the circumferential direction;
the hydraulic oil chamber A and the hydraulic oil chamber C are communicated with the annular oil duct A through an oil hole duct A in the main journal, the hydraulic oil chamber B and the hydraulic oil chamber D are communicated with the annular oil duct B through an oil hole duct B in the main journal, and the main bearing seat is provided with an oil hole duct C and an oil hole duct D which are respectively communicated with the annular oil duct A and the annular oil duct B. Scheme more than adopting, the mode that sets up double annular oil duct on utilizing the main journal fills the hydraulic oil room to two relative hydraulic pressure grease chambeies in the sealed chamber and fills the hydraulic oil operation to realize the adjustment of swiveling wheel rotation direction, and can not produce the interference with the high-speed pivoted operating mode of bent axle, satisfy the operating mode demand.
Preferably, the method comprises the following steps: the communication positions of the oil pore passage A and the hydraulic oil chamber C as well as the communication positions of the oil pore passage B and the hydraulic oil chamber D are all positioned at the positions close to the blades B in the corresponding oil chambers. Scheme more than adopting, the positive arc recess of cooperation swiveling wheel carries on spacingly to the rotation of swiveling wheel, guarantees through the rotatable angle of the positive recess of design that blade A's position can not block off the oil pore way, ensures promptly that the swiveling wheel rotates the in-process, corresponds hydraulic pressure grease chamber and must be in the connected state all the time with the oilhole way that corresponds, and hydraulic oil business turn over is smooth and easy, improves the reliability that the swiveling wheel rotated the adjustment.
Preferably, the method comprises the following steps: the swiveling wheel dorsal part has the boss A who suits with heavy groove, boss A imbeds heavy inslot, between boss A's the circumference outside and heavy inslot wall, between blade A outside and the heavy inslot wall and between back shaft and the heavy groove all be equipped with seal structure. By adopting the scheme, the phenomenon of oil channeling among the hydraulic oil chambers is favorably prevented, so that the pressure fluctuation error is larger, and the reliability and the stability of hydraulic drive adjustment are further improved.
Preferably, the method comprises the following steps: the upper and lower both sides of the inherent swiveling wheel of crank arm are equipped with spout A and spout B respectively, connecting portion and spout A sliding fit, have in the spout B with its sliding fit's balanced heavy, have on the swiveling wheel and be the arc recess B that centrosymmetry set up with arc recess A, have on the balanced heavy with arc recess B sliding fit's the protruding B of column. By adopting the scheme, the arc-shaped groove B drives the balance weight to synchronously move with the connecting rod journal, when the connecting rod journal moves along the direction far away from the center of the crankshaft body, the balance weight also moves towards the direction far away from the center of the crankshaft body, otherwise, the balance weight synchronously moves towards the center of the crankshaft body, and the stability of the integral rotation work of the crankshaft body is favorably ensured.
Preferably, the method comprises the following steps: the swiveling wheel openly has boss B, boss B is located arc recess B and arc recess A's inboard, its circumference profile with arc recess B suits with arc recess A, the tip of connecting portion and counter weight with boss B side slip butt. By adopting the scheme, the bearing capacity of the sliding connecting rod journal is increased in the compression and expansion strokes, and the service life is prolonged.
On this basis, the application provides an internal-combustion engine, has the variable function of compression ratio to satisfy more operating mode demands, its technical scheme as follows:
an internal combustion engine comprises the internal combustion engine crankshaft system with the variable compression ratio and is provided with a hydraulic oil tank, wherein the hydraulic oil tank is connected with an oil pumping pipeline and an oil return pipeline, and the oil pumping pipeline and the oil return pipeline are both communicated with an annular oil duct A and an annular oil duct B;
the oil pump is characterized in that a three-way change-over valve A and a three-way change-over valve B are respectively arranged on the pump oil pipeline and the oil return pipeline, an electronic actuator is configured on the three-way change-over valve A and the three-way change-over valve B, a high-pressure oil pump is arranged on the pump oil pipeline, and the high-pressure oil pump is located between the three-way change-over valve A and the hydraulic.
By adopting the scheme, the oil pumping pipeline and the oil return pipeline are respectively communicated with the two annular oil ducts through the two three-way conversion valves, and the connection port communication state of the three-way conversion valves is controlled only through the electronic actuator during control, so that the switching of oil inlet and oil return of each hydraulic oil chamber is realized, the operability of the adjustment of the compression ratio of the internal combustion engine is improved, and the implementation cost is relatively low.
Further, the present application provides a control method for the above internal combustion engine, which is mainly used for controlling the adjustment of the compression ratio, and has good feasibility, and the specific scheme is as follows:
when an internal combustion engine central controller sends a compression ratio increasing instruction to an internal combustion engine, a first interface and a second interface of a three-way conversion valve A are communicated through an electronic actuator, a first interface and a second interface of a three-way conversion valve B are communicated, hydraulic oil enters a hydraulic oil chamber A and a hydraulic oil chamber C through a pump oil pipeline, the hydraulic oil in the hydraulic oil chamber B and the hydraulic oil chamber D flows back to a hydraulic oil tank through an oil return pipeline, the hydraulic oil pushes a rotating wheel on the left side of the same connecting rod journal to rotate clockwise, and a rotating wheel on the right side of the same connecting rod journal rotates anticlockwise, so that the connecting rod journal and a balance;
after internal-combustion engine central controller sent the reduction compression ratio instruction to the internal-combustion engine, make three change-over valve A's first and third interface intercommunication through electronic actuator, three change-over valve B's first and third interface intercommunication, hydraulic oil passes through pump oil pipeline and gets into hydraulic pressure oil chamber B and hydraulic pressure oil chamber D, hydraulic pressure oil chamber A and hydraulic pressure oil chamber C's hydraulic pressure oil tank is flowed back to through returning oil pipeline, and hydraulic oil promotes same connecting rod journal left side swiveling wheel anticlockwise rotation, right side swiveling wheel clockwise to make connecting rod journal and balanced heavy move along the direction that is close to the bent axle center.
By adopting the control method, the stable adjustment of the effective working length of the crank throw can be quickly realized, the operability is good, and the rotation directions of the two rotating wheels on the same crank throw are opposite, so that the sliding stability of the crank throw is further improved, the pressure-bearing capacity is improved, and the reliability and the stability are better.
Compared with the prior art, the invention has the beneficial effects that:
the internal combustion engine crankshaft system with the variable compression ratio, the internal combustion engine and the compression ratio control method thereof provided by the invention mainly adopt a hydraulic driving mode to realize the adjustment of the effective working length of the crank throw of the crankshaft, meet the adjustment requirement of the compression ratio of the internal combustion engine, have good operability and stable and reliable integral structure, and are beneficial to prolonging the service life of the internal combustion engine and the like.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a cross-sectional view of the present invention;
FIG. 3 is a schematic view of a connecting rod journal and counterweight mounting arrangement;
FIG. 4 is a schematic view of the relative positions of blade A and blade B;
FIG. 5 is an exploded view of the bell crank mounting structure;
FIG. 6 is a side view of FIG. 5;
FIG. 7 is a geometric relationship between the arc grooves A and B and the rotation center thereof;
FIG. 8 is a front view of the rotator wheel;
FIG. 9 is a schematic view of the rear structure of the rotator wheel;
FIG. 10 is a schematic view of a rod journal configuration;
FIG. 11 is a schematic view of a crank arm configuration;
FIG. 12 is an exploded view of the crank arm structure;
FIG. 13 is a sectional view of the mounting of the swivel wheel;
FIG. 14 is a schematic view of the main journal internal oil gallery;
FIG. 15 is a schematic view of an oil passage in a main bearing housing;
FIG. 16 is a schematic view of the seal between the rotor and the sink;
fig. 17 is a schematic view of the structure of the balancing weight;
FIG. 18 is a schematic diagram showing the relative positions of the rotary wheel, the connecting rod journal and the counterweight when the rotary wheel is driven to rotate clockwise by hydraulic oil to achieve the maximum effective length of the crank throw;
FIG. 19 is a schematic representation of the piston position at the maximum effective length of the bell crank;
FIG. 20 is a schematic diagram showing the relative positions of the oil path structure and the rotary wheel, the connecting rod journal and the counterweight when the hydraulic oil in the four hydraulic oil chambers are communicated with each other to maintain pressure balance;
FIG. 21 is a schematic view of the effective crank length and piston position of the rotary wheel of FIG. 20;
FIG. 22 is a schematic view of the oil path configuration and the relative positions of the rotor, the connecting rod journal and the counterweight when the rotor is rotated counterclockwise by the hydraulic oil to achieve the minimum effective throw length;
FIG. 23 is a schematic representation of the piston position at which the bell crank reaches its minimum effective length.
Detailed Description
The present invention will be further described with reference to the following examples and the accompanying drawings.
Referring to fig. 1 and 23, a crankshaft system of an internal combustion engine with variable compression ratio, an internal combustion engine and a control method thereof are shown, wherein the crankshaft system of the internal combustion engine with variable compression ratio mainly comprises a crankshaft body 100 and main bearing seats 400 distributed along the axial direction of the crankshaft body 100 and used for supporting the crankshaft body 100, a crank throw 200 is formed on the crankshaft body 100 between two adjacent main bearing seats 400, the crank throw 200 is rotatably supported on the main bearing seats 400 through an outer main journal 300, the crank throw 200 in the present application is an assembly structure and comprises a connecting rod journal 210 and two crank arms 220 respectively connected to two ends of the connecting rod journal 210, the connecting rod journal 210 can slide along the radial direction of the crankshaft body 100 relative to the crank arms 220, a rotating wheel 230 is rotatably mounted inside the crank arms 220 and can drive the connecting rod journal 210 to slide relative to the crank arms 220 when the rotating wheel 230 rotates so as to change, the rotary wheel 230 is capable of rotating about the axis of the crankshaft body 100 under the driving of electric power, hydraulic pressure, or other mechanical driving structure.
In order to fully ensure the sliding stability and the bearing capacity of the connecting rod journal 210, the rotating directions of the two rotating wheels 230 corresponding to the same crank 200 are opposite during the adjustment process.
Referring to fig. 5, 6, 8 to 13, the crank arm 220 of the present embodiment is a hollow structure, the main body of the rotator 230 is a circular disc structure, the middle part of the crank arm 220 has a hollow cavity adapted to the rotator 230, the side of the hollow inner cavity close to the small end of the crank arm 220 is provided with a chute A224 communicated with the hollow inner cavity, the side of the small end of the crank arm 220 far away from the main journal 300 is provided with a through hole 221 communicated with the chute A224, as shown in fig. 10, both ends of the connecting rod journal 210 have insertion portions 211 extending outward in the axial direction thereof, the insertion portions 211 being fitted with the through holes 221, the insertion portions 211 having a cylindrical shape, it can be extended into the sliding groove a224 through the through hole 221, the end of the insertion portion 211 has a connection portion 212 arranged along the radial direction thereof, the connection portion 212 has a plate-shaped structure, the end of the connection portion 212 has a columnar protrusion a213 extending upward along the thickness direction thereof, and the columnar protrusion a213 has a cylindrical shape and is arranged in parallel with the insertion portion 211.
Taking the example of the rotation of the hydraulically driven rotator 230, the rotator 230 has a support shaft 232 penetrating through both sides along the thickness direction thereof, the rotator 230 is coaxially disposed with the main journal 300 through the support shaft 232, one side of the crank arm 220 close to the main journal 300 has a sink 222 adapted to the structure of the back side of the rotator 230 (the side close to the main journal 300, and the side far from the main journal 300 is the front side), the back side of the rotator 230 and the inner wall of the sink 222 surround to form a sealed chamber, and the sealed chamber is connected with a hydraulic oil path to drive the rotator 230 to rotate.
The front surface of the rotating wheel 230 has an arc-shaped groove a231, the size of the arc-shaped groove a231 is adapted to the cylindrical protrusion a213, and the arc-shaped groove a231 is eccentrically disposed relative to the rotation center of the rotating wheel 230, i.e. as shown in fig. 7, an offset distance L exists between the center of the arc-shaped groove a231 and the center of the rotating wheel 230, the arc radius of the arc-shaped groove a231 is R, the journal 210 extends into the sliding slot a224 through the insertion portion 211, the connecting portion 212 is in sliding fit with the sliding slot a224, the cylindrical protrusion a213 at the end portion is inserted into the arc-shaped groove a231 and is in sliding fit therewith, and when the rotating wheel 230 rotates, the arc-shaped groove a231 can drive the.
The sunken groove 222 is step-shaped and comprises three sections with gradually increasing diameters from inside to outside, namely a shaft fixing section 2220, a hydraulic working section 2221 and a rotating matching section 2222, the diameter of the main body of the rotating wheel 230 is matched with that of the rotating matching section 2222, the back side of the rotating wheel 230 is provided with a boss A234 coaxially arranged with the rotating wheel, the diameter of the boss A234 is matched with that of the hydraulic working section 2221, the diameter of a support shaft 232 is matched with that of the shaft fixing section 2220, the outer side of one section of the support shaft 232 extending into the sunken groove 222 is provided with two blades A233, the two blades A233 are symmetrically arranged along the axis of the support shaft 232 and protrude outwards along the axis of the support shaft, the distance from the outer end of each blade A233 to the axis of the support shaft 232 is matched with the diameter of the hydraulic working section 2221, after the rotating wheel 230 is installed, the back side of the rotating matching section 2222 is matched with the bottom surface of the rotating matching section, the boss A, meanwhile, the hydrodynamic working section 2221 is internally provided with two symmetrical and fixedly arranged blades B223, the width of the two blades B223 is consistent with that of the blade a233, the inner side surface of the blade a233 is tightly attached to the bottom surface of the hydrodynamic working section 2221, and the outer side surface boss a234 of the blade B223 is tightly attached.
The two blades a233 and the two blades B223 divide the sealed chamber into four relatively independent hydraulic oil chambers, the hydraulic oil passages are separately communicated with the four hydraulic oil chambers, and when different hydraulic oil chambers are charged and discharged with hydraulic oil, the rotating wheel 230 can be driven to rotate clockwise and counterclockwise (note: in this embodiment, clockwise and counterclockwise are not absolute rotating directions, and the directions shown in fig. 18 and 22 are respectively used as references, and different references, different hydraulic oil passages can cause the rotating direction of the rotating wheel 230 to change, and the implementation manner is within the protection scope of the present application).
As can be seen from fig. 14 and 15, the hydraulic oil path in this embodiment mainly includes an annular oil path a310 and an annular oil path B311 that are disposed on the main journal 300, the four hydraulic oil chambers are respectively a hydraulic oil chamber a312, a hydraulic oil chamber B313, a hydraulic oil chamber C314, and a hydraulic oil chamber D315 that are sequentially distributed along the circumferential direction, and the main bearing seat 400 is provided with an oil passage C410 and an oil passage D420 that are respectively communicated with the annular oil path a310 and the annular oil path B311.
The hydraulic oil chamber a312 and the hydraulic oil chamber C314 are communicated with the annular oil passage a310 through an oil passage a316 in the main journal 300, the hydraulic oil chamber B313 and the hydraulic oil chamber D315 are communicated with the annular oil passage B311 through an oil passage B317 in the main journal 300, the main bearing seat 400 is provided with an oil passage C410 and an oil passage D420 which are respectively communicated with the annular oil passage a310 and the annular oil passage B311, and it should be noted that in order to ensure that each hydraulic oil chamber can be always communicated with the corresponding oil passage during the rotation of the rotary wheel 230, the communication positions of the oil passage a316 and the hydraulic oil chamber a312 and the hydraulic oil chamber C314, and the communication positions of the oil passage B317 and the hydraulic oil chambers B313 and D315 are both located in the corresponding oil chamber at positions close to the vane B223.
As shown in the drawings, the main journal 300 is provided with four oil passages a316 and four oil passages B317 corresponding to the annular oil passage a310 and the annular oil passage B311, respectively, and with this structure, it is also possible to facilitate synchronous control of two adjacent rotating wheels 230, maintain rotation synchronism, improve rotation adjustment reliability, facilitate arrangement, and the overall stability of the main journal 300 is maintained, so that the two oil hole channels a316 are respectively located at two opposite sides of the main journal 300, the same two oil hole channels B317 are also located at two opposite sides of the main journal 300, the overall dynamic balance of the crankshaft can be effectively ensured, meanwhile, the rotary wheel can be better adapted to the position of the blade B223, the length of an oil duct is shortened, the processing difficulty is reduced, and the like, in order to ensure that in the process of adjusting the rotary wheels 230 at two sides of the same crank 210, the rotation directions are opposite, so the angular positions of the blades B223 in the two opposite sunk grooves 222 after the installation are in a symmetrical posture.
In this embodiment, in order to further improve the working reliability of the hydraulic oil circuit, in this embodiment, sealing structures are respectively disposed between the outer side of the circumference of the boss a234 and the inner wall of the hydraulic working section 2221, between the end of the vane a233 and the inner wall of the hydraulic working section 2221, between the vane B223 and the supporting seat 232, and between the end of the supporting shaft 232 and the shaft fixing section 2220, as shown in fig. 16, in specific implementation, the outer end of the vane a233 has a sealing strip a2330 embedded along the thickness direction thereof, the inner end of the vane B223 has a sealing strip B2230 embedded along the thickness direction thereof, the sealing strips a2330 and B2230 can prevent the radial flow-through of hydraulic oil, the inner sealing rings (not shown in the figure) are respectively sleeved on the circumferences of the supporting shaft 232 and the boss a234, the inner sealing rings are used for preventing the axial flow-through of hydraulic oil, and similarly, the outer sealing rings 430 are respectively disposed on the bearing shell, to prevent hydraulic oil from flowing out of the gap between the main journal 300 and the bearing shell.
From the perspective of the rotational stability of the crankshaft, in the present embodiment, each crank arm 220 is further provided with a counterweight 240, as shown in fig. 3 and 17, a sliding slot B225 is disposed inside a large end of the crank arm 220, the sliding slot B225 is communicated with the sinking slot 222 and is located on two opposite sides of the sinking slot 222 with respect to the sliding slot a224, the counterweight 240 is slidably disposed in the sliding slot B225, the front surface of the rotating wheel 230 is provided with an arc-shaped groove B235, the arc-shaped groove B235 and the arc-shaped groove a231 are symmetrically disposed with respect to the center of the rotating wheel 230, and the counterweight 240 is provided with a cylindrical protrusion B241 slidably fitted with the arc-shaped sliding slot B235, so that when the rotating wheel 230 rotates, the counterweight 240 can synchronously slide with the connecting rod journal 210, that is, when the connecting rod journal 210 moves away from the center of the rotating wheel 230, the counterweight 240 also moves.
On the basis, in order to improve the moving smoothness of the connecting rod journal 210 and the balance weight 240 and increase the pressure bearing capacity of the connecting rod journal and the balance weight during the rotation of the rotating wheel 230, a boss B236 is arranged on the front surface of the rotating wheel 230, as shown in the figure, the boss B236 is positioned between the arc-shaped groove B235 and the arc-shaped groove a231, the circumferential profile of the boss B236 is matched with the inner profiles of the arc-shaped groove B235 and the arc-shaped groove a231, namely, the boss B is arranged in parallel to form a cam profile, after the connecting rod journal 210 and the balance weight 240 are completely installed and matched with the rotating wheel 230, the connecting part 212 is in sliding contact with the circumferential side wall of the balance weight 240 with the boss B236 at the end part, and the main function of the balance weight 240 is to enable the weight of the crankshaft to.
In order to facilitate the installation of the connecting rod journal 210 in this embodiment, the crank arm 220 is designed to be an assembly structure and made of high-strength steel, and mainly includes a fixing portion 226 integrally formed with the main journal 300 and a covering portion 227 fastened to the fixing portion 226, wherein the covering portion 227 and the fixing portion 226 can be fixed by screws or welding and the like to form a hollow installation cavity, the covering portion 227 further includes an upper cover 2270 and a lower cover 2271, the upper cover 2270 and the lower cover 2271 can be fixedly connected by welding and form a through hole 221 by surrounding arc notches at opposite ends, the through hole 221 is similar to a strip-shaped hole in structure, the width of the through hole 221 is adapted to the insertion portion 211, the length of the through hole is slightly greater than or equal to the moving distance of the insertion portion 211, and the end of the connecting rod journal 210 has a shielding portion 214 adapted to the through hole 221.
Based on the internal combustion engine crankshaft system with the variable compression ratio, the application provides an internal combustion engine which mainly comprises the internal combustion engine crankshaft system with the variable compression ratio and is specifically provided with four crank throws 200, the crankshaft system is provided with a hydraulic oil tank 500, the hydraulic oil tank 500 is connected with a pump oil pipeline 510 and an oil return pipeline 520, the tail ends of the pump oil pipeline 510 and the oil return pipeline 520 are simultaneously communicated with an annular oil duct A310 and an annular oil duct B311, a three-way change-over valve A530 and a three-way change-over valve B540 are respectively arranged on the pump oil pipeline 510 and the oil return pipeline 520, the three-way change-over valve A530 and the three-way change-over valve B540 are provided with an electronic actuator, the communication state and the internal communication state of each interface and the corresponding oil pipeline can be switched through the electronic actuator, a high-pressure oil pump 550 is arranged on the pump oil pipeline 510, the high-pressure oil pump 550 is positioned between the three-way change, hydraulic oil may also be pressurized and fed into the annular oil passage B311, and when the annular oil passage a310 is in the oil-intake state, the annular oil passage B311 is in the oil-return state, whereas when the annular oil passage B311 is in the oil-intake state, the annular oil passage a310 is in the oil-return state.
When the central controller of the internal combustion engine sends a command of increasing or decreasing the compression ratio to the internal combustion engine, the electronic actuator switches the communication state of the corresponding three-way switching valve interface, the hydraulic oil pushes the rotating wheel 230 to rotate, so that the connecting rod journal 210 and the balance weight 240 move in the direction away from or close to the center of the crankshaft, thereby realizing the adjustment of the compression ratio of the internal combustion engine, and in the adjustment process, the rotating directions of the rotating wheels 230 on both sides of the same crank 200 are opposite.
When the compression ratio of the internal combustion engine needs to be increased, through a central control operation, an internal combustion engine central controller sends a compression ratio increasing instruction to the internal combustion engine, a first port a and a second port B of a three-way switching valve A530 are communicated through an electronic actuator, a first port a and a second port B of a three-way switching valve B540 are communicated, as shown in FIG. 18, hydraulic oil enters an annular oil passage A310 through a pump oil pipeline 510 and then enters a hydraulic oil chamber A312 and a hydraulic oil chamber C314 through corresponding oil pore passages, hydraulic oil in the hydraulic oil chamber B313 and the hydraulic oil chamber D315 returns to the annular oil passage B311 through the corresponding oil pore passages and flows back to a hydraulic oil tank 500 through an oil return pipeline 520, a rotating wheel 230 on the left side of a connecting rod journal 210 rotates clockwise, a rotating wheel 230 on the right side rotates counterclockwise, so that the connecting rod journal 210 and a counterweight 240 move in a direction far away from, the bell crank 200 reaches a maximum effective working length.
When the compression ratio of the internal combustion engine needs to be reduced, after an internal combustion engine central controller sends a compression ratio reduction instruction to the internal combustion engine through a central control operation, a first port a and a third port C of a three-way switching valve A530 are communicated through an electronic actuator, and a first port a and a third port C of a three-way switching valve B540 are communicated, as shown in 21, hydraulic oil enters an annular oil passage B311 through a pump oil pipeline 510 and enters a hydraulic oil chamber B313 and a hydraulic oil chamber D315 through corresponding oil hole passages, hydraulic oil in the hydraulic oil chamber A312 and the hydraulic oil chamber C314 flows back to the annular oil passage A310 through corresponding oil hole passages, and finally flows back to the hydraulic oil tank 500 through an oil return pipeline 520, a rotating wheel 230 on the left side of a connecting rod journal 210 rotates anticlockwise, a rotating wheel 230 on the right side rotates clockwise, and the connecting rod journal 210 and a counterweight 240.
Referring to fig. 20, when the internal combustion engine needs to maintain the current compression ratio and the central controller of the internal combustion engine issues a command to maintain the compression ratio to the internal combustion engine, the electronic actuator makes the second port B and the third port C of the three-way switching valve a530, the second port B and the third port C of the three-way switching valve B540 communicate, the second port B of the three-way switching valve a530 communicates with the third port C of the three-way switching valve B540 and simultaneously communicates with the annular oil passage a310, the third port C of the three-way switching valve a530 communicates with the second port B of the three-way switching valve B540 and simultaneously communicates with the annular oil passage B311, that is, the hydraulic oil chambers a312, C314, B313 and D315 in the same crank arm 220 communicate with each other, thereby maintaining a hydraulically stable state, preventing the rotary wheel 230 from rotating, and thereby maintaining the position of the journal connecting rod 210, i.e. keeping the compression ratio of the internal combustion engine unchanged.
Further, the rotation of the rotation wheel 230 may be achieved by a mechanism such as a stepping motor driving a worm gear, in addition to the hydraulic driving in the above-described embodiment.
Referring to fig. 1 to 23, in the assembly of the crankshaft system of the internal combustion engine, attention is paid to the installation of a sealing structure between a rotating wheel 230 and a sink 222 during the assembly of a crank throw 200, a connecting rod journal 210 and a balance weight 240 are matched with the rotating wheel 230, a covering part 227 is fixedly connected with a fixing part 226, and finally the assembled crankshaft system of the internal combustion engine is installed in the internal combustion engine, and an oil channel C410 and an oil channel D420 on a main bearing seat 400 are simultaneously connected with a pump oil pipeline 510 and an oil return pipeline 520 through pipelines, so that a three-way switching valve a530 and a three-way switching valve B540 can be controlled by a central controller of the internal combustion engine, and the pipeline communication state can be switched through external operation.
On the other hand, referring to fig. 7, after the rotating wheel 230 rotates around the rotation center by an angle, an included angle between a connecting line between the center of the cylindrical protrusion a213 and the center of the rotating wheel and the horizontal center line of the rotating wheel is θ, a distance between the inner edges of the cylindrical protrusion a213 and the cylindrical protrusion B241 and the rotation center of the rotating wheel 230 is X, an offset distance between the arc groove a231 and the center of the rotating wheel 23 is L, and an arc radius of the arc groove a231 is R, then the following relationships exist:
Figure BDA0002683425970000141
according to the formula, when the rotating wheel 230 rotates a certain angle, a uniquely determined X value can be obtained.
As shown in FIGS. 20 and 21, when the internal combustion engine is in the intermediate load condition, the compression ratio is the intermediate value γ2And keep unchangeable, the center of cylindrical protrusion A213 center is 90 degrees with the horizontal central line contained angle of swiveling wheel with the line of swiveling wheel center for theta, that is blade A233 and blade B223 mutually perpendicular, when the swiveling wheel rotated to this angle, make hydraulic oil chamber A312, hydraulic oil chamber C314, hydraulic oil chamber B313 and hydraulic oil chamber D315 in the hydraulic oil chamber communicate with each other through switching over the valve, keep the oil pressure of blade A233 both sides unanimous, thereby control effective crank length Q2X2+ r remains constant and r is the fixed throw length of the connecting rod journal 210, thereby controlling the compression ratio at the desired value and remaining constant.
Figure BDA0002683425970000142
Wherein s is2The stroke at the intermediate compression ratio.
V is the sum of the combustion volume at the intermediate compression ratio and the clearance volume at the top dead center.
And A is the cross-sectional area of the cylinder.
As shown in fig. 18 and 19, when the rotary wheel 230 is rotated clockwise as shown in the figure, the connecting rod journal 210 and the balance weight 240 are moved away from the crankshaft center, and the crank throw 200 reaches the maximum effective working length, the distance from the inner edge of the columnar protrusion a213 to the rotation center of the rotary wheel 230 reaches the maximum value X1The effective crank length Q1 at this time is X1+ r, r is the radial length of the connecting rod journal 210.
At this time, the internal combustion engine reaches the maximum compression ratio of γ1，
Figure BDA0002683425970000151
Wherein s is1The stroke at the maximum compression ratio.
Similarly, as shown in fig. 22 and 23, when the rotating wheel 230 rotates counterclockwise as shown in the figure, the connecting rod journal 210 and the balance weight 240 move toward the crankshaft center, the crank throw 200 reaches the minimum effective working length, and the distance from the inner edge of the columnar protrusion a213 to the rotation center of the rotating wheel 230 reaches the minimum value X3The effective crank length Q3 at this time is X3+r。
At this time, the internal combustion engine reaches the minimum compression ratio of γ3：
Figure BDA0002683425970000152
Wherein s is3The stroke at the minimum compression ratio.
Finally, it should be noted that the above description is only a preferred embodiment of the present invention, and those skilled in the art can make various similar representations or increase or decrease the number of crank throws of the present crankshaft system to be applied to internal combustion engines with other cylinder numbers without departing from the spirit and scope of the present invention.

Claims (10)

1. An internal combustion engine crankshaft system with a variable compression ratio comprises a crankshaft body (100) and main bearing seats (400) axially distributed along the crankshaft body (100) and used for supporting the crankshaft body (100), wherein a crank throw (200) is formed between two adjacent main bearing seats (400) of the crankshaft body (100), the crank throw (200) comprises a connecting rod journal (210) and two crank arms (220) respectively connected to two ends of the connecting rod journal (210), and the internal combustion engine crankshaft system is characterized in that: the connecting rod journal (210) can slide along the radial direction of the crankshaft body (100) relative to the crank arm (220), a rotating wheel (230) is rotatably mounted inside the crank arm (220), and the rotating wheel (230) can rotate around the axis of the crankshaft body (100) under the driving of an electric, hydraulic or mechanical structure and drives the connecting rod journal (210) to slide to be close to or far away from the crankshaft body (100).
2. The crankshaft system for a variable compression ratio internal combustion engine according to claim 1, wherein: a main journal (300) is arranged on the outer side of the crank arm (220), the rotating wheel (230) and the main journal (300) are coaxially arranged, an arc-shaped groove A (231) is formed in the front surface of the rotating wheel (230), and an offset distance is formed between the circle center of the arc-shaped groove A (231) and the circle center of the rotating wheel (230);
the two ends of the connecting rod journal (210) are provided with insertion parts (211) extending outwards, the end part of each insertion part (211) is provided with a connecting part (212) arranged along the radial direction, the end part of each connecting part (212) is provided with a columnar protrusion A (213) matched with the arc-shaped groove A (231) in a sliding mode, the crank arm (220) is provided with a through hole (221) for the insertion part (211) to extend into, and the through hole (221) limits the moving stroke of the connecting rod journal (210).
3. The variable compression ratio internal combustion engine crankshaft system of claim 1, wherein: the crank arm (220) is internally provided with a sunk groove (222) for mounting the rotating wheel (230), the sunk groove (222) is step-shaped, and the rotating wheel (230) and the corresponding sunk groove (222) surround to form a sealed chamber;
swiveling wheel (230) have to both sides extension back shaft (232), the one end outside that back shaft (232) are close to main journal (300) has two blade A (233), two blade B (223) have in heavy groove (222), blade A (233) and blade B (223) will sealed cavity separates and forms four hydraulic pressure grease chambeies, four hydraulic pressure grease chamber all is connected with hydraulic pressure oil circuit.
4. The crankshaft system for a variable compression ratio internal combustion engine according to claim 3, wherein: a main journal (300) is arranged on the outer side of the crank arm (220), an annular oil passage A (310) and an annular oil passage B (311) are arranged on the main journal (300), and the four hydraulic oil chambers are respectively a hydraulic oil chamber A (312), a hydraulic oil chamber B (313), a hydraulic oil chamber C (314) and a hydraulic oil chamber D (315) which are sequentially distributed along the circumferential direction;
the hydraulic oil chamber A (312) and the hydraulic oil chamber C (314) are communicated with the annular oil passage A (310) through an oil passage A (316) in the main journal (300), the hydraulic oil chamber B (313) and the hydraulic oil chamber D (315) are communicated with the annular oil passage B (311) through an oil passage B (317) in the main journal (300), and the main bearing seat (400) is provided with an oil passage C (410) and an oil passage D (420) which are respectively communicated with the annular oil passage A (310) and the annular oil passage B (311).
5. The crankshaft system for a variable compression ratio internal combustion engine according to claim 4, wherein: the communication position of the oil duct A (316) with the hydraulic oil chamber A (312) and the hydraulic oil chamber C (314), and the communication position of the oil duct B (317) with the hydraulic oil chamber B (313) and the hydraulic oil chamber D (315) are both positioned at the position corresponding to the position close to the blade B (223) in the oil chamber.
6. The crankshaft system for an internal combustion engine with a variable compression ratio according to any one of claims 3 to 5, characterized in that: the back side of the rotating wheel (230) is provided with a boss A (234) matched with the sinking groove (222), the boss A (234) is embedded into the sinking groove (222), sealing structures are arranged between the outer side of the circumference of the boss A (234) and the inner wall of the sinking groove (222), between the outer side of the blade A (233) and the inner wall of the sinking groove (222) and between the supporting shaft (232) and the sinking groove (222).
7. The crankshaft system for a variable compression ratio internal combustion engine according to claim 2, wherein: crank arm (220) are equipped with spout A (224) and spout B (225) respectively in the upper and lower both sides of swiveling wheel (230), connecting portion (212) and spout A (224) sliding fit, have in spout B (225) and balance weight (240) rather than sliding fit, have arc recess B (235) that are central symmetry setting with arc recess A (231) on swiveling wheel (230), have on balance weight (240) with arc recess B (235) sliding fit's column protruding B (241).
8. The crankshaft system for a variable compression ratio internal combustion engine as claimed in claim 7, wherein: the front face of the rotating wheel (230) is provided with a boss B (236), the boss B (236) is positioned on the inner sides of an arc-shaped groove B (235) and an arc-shaped groove A (231), the circumferential profiles of the boss B (236) and the arc-shaped groove A (231) are matched, and the end parts of the connecting part (212) and the balance weight (240) are in sliding abutting joint with the side face of the boss B (236).
9. An internal combustion engine, characterized by: comprising the crankshaft system of an internal combustion engine with variable compression ratio as claimed in claims 1 to 8, and equipped with a hydraulic oil tank (500), said hydraulic oil tank (500) being connected with a pump oil line (510) and an oil return line (520), said pump oil line (510) and oil return line (520) being both in communication with an annular oil passage a (310) and an annular oil passage B (311);
the oil pump is characterized in that a three-way change-over valve A (530) and a three-way change-over valve B (540) are respectively arranged on the oil pumping pipeline (510) and the oil return pipeline (520), the three-way change-over valve A (530) and the three-way change-over valve B (540) are provided with electronic actuators, a high-pressure oil pump (550) is arranged on the oil pumping pipeline (510), and the high-pressure oil pump (550) is positioned between the three-way change-over valve A (530) and the hydraulic oil tank (500).
10. A control method of an internal combustion engine according to claim 9, characterized in that: when an internal combustion engine central controller sends a compression ratio increasing instruction to an internal combustion engine, a first interface and a second interface of a three-way switching valve A (530) are communicated through an electronic actuator, a first interface and a second interface of a three-way switching valve B (540) are communicated, hydraulic oil enters a hydraulic oil chamber A (312) and a hydraulic oil chamber C (314) through a pump oil pipeline (510), the hydraulic oil in the hydraulic oil chamber B (313) and the hydraulic oil chamber D (315) flows back to a hydraulic oil tank (500) through an oil return pipeline (520), a rotating wheel (230) on the left side of a connecting rod journal (210) rotates clockwise, a rotating wheel (230) on the right side rotates anticlockwise, and the connecting rod journal (210) and a balance weight (240) move in the direction far away from the center of a;
after an internal combustion engine central controller sends a compression ratio reducing instruction to an internal combustion engine, a first interface and a third interface of a three-way switching valve A (530) are communicated through an electronic actuator, a first interface and a third interface of a three-way switching valve B (540) are communicated, hydraulic oil enters a hydraulic oil chamber B (313) and a hydraulic oil chamber D (315) through a pump oil pipeline (510), the hydraulic oil of the hydraulic oil chamber A (312) and the hydraulic oil chamber C (314) flows back to a hydraulic oil tank (500) through an oil return pipeline (520), a rotating wheel (230) on the left side of a connecting rod journal (210) rotates anticlockwise, a rotating wheel (230) on the right side rotates clockwise, and the connecting rod journal (210) and a balance weight (240) move in the direction close to the center of a crankshaft.
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