WO2021170003A1 - Structure d'entraînement à taux de compression variable, moteur et véhicule - Google Patents

Structure d'entraînement à taux de compression variable, moteur et véhicule Download PDF

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Publication number
WO2021170003A1
WO2021170003A1 PCT/CN2021/077712 CN2021077712W WO2021170003A1 WO 2021170003 A1 WO2021170003 A1 WO 2021170003A1 CN 2021077712 W CN2021077712 W CN 2021077712W WO 2021170003 A1 WO2021170003 A1 WO 2021170003A1
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WO
WIPO (PCT)
Prior art keywords
compression ratio
variable compression
wave generator
eccentric shaft
flexspline
Prior art date
Application number
PCT/CN2021/077712
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English (en)
Chinese (zh)
Inventor
杨乐
刘涛
苏旭朝
张树旻
尹吉
渠娜
刘君宇
董高峰
钟德华
王文远
孟金
Original Assignee
长城汽车股份有限公司
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Filing date
Publication date
Application filed by 长城汽车股份有限公司 filed Critical 长城汽车股份有限公司
Publication of WO2021170003A1 publication Critical patent/WO2021170003A1/fr

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    • 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
    • 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

Definitions

  • the application relates to the field of engine technology, and in particular to a variable compression ratio drive structure.
  • variable compression ratio technology came into being.
  • compression ratio adjustment forms are becoming more and more diversified.
  • the multi-link variable compression ratio mechanism that uses the eccentric shaft to cooperate with the multi-link mechanism to drive the eccentric shaft to rotate through the multi-link mechanism to realize the change of the top dead center of the engine piston has become a large number of car companies. The focus of research and development.
  • the matching structure of the motor and the harmonic reducer is used as the driving source, and the eccentric shaft is driven to rotate is a more driving form.
  • the transmission mode between the motor and the harmonic reducer in the existing structure is mostly belt transmission, or the motor is arranged on the side of the engine cylinder and connected to the harmonic reducer for transmission.
  • the existing structural form causes the overall width of the engine to be large, which is not conducive to the installation of the entire vehicle.
  • the motor installation space or the motor mounting bracket needs to be processed when the cylinder is processed, which also makes the cylinder structure relatively Complex and difficult to process.
  • the drive structure composed of the motor and the harmonic reducer is also easy to interfere with the damping pulley and damping belt on the engine, which is not conducive to the overall design of the engine. .
  • the present application aims to propose a variable compression ratio drive structure, so as to make the overall drive structure compact and avoid interference with the damping pulley.
  • variable compression ratio drive structure to drive the eccentric shaft in the variable compression ratio mechanism to rotate.
  • the variable compression ratio drive structure includes a harmonic reducer unit fixed on the engine cylinder and fixed on the The motor unit on the rigid wheel in the harmonic reducer unit, the flexible wheel in the harmonic reducer unit is drivingly connected to one end of the eccentric shaft, and one end of the rotating shaft of the motor unit extends out and is in harmony with the
  • the wave generator in the wave reducer is in transmission connection, and the rotation axis of the motor unit is offset to one side of the rotation axis of the harmonic reducer unit.
  • An extension end extending from one side of the rotating shaft, and an oil passage communicating with the lubricating oil passage in the engine cylinder is constructed in the eccentric shaft, and the oil passage axially penetrates to the end of the extension end of the eccentric shaft Department.
  • the rotation axis of the motor unit is offset below the rotation axis of the harmonic reducer unit.
  • rotation axis of the motor unit is located directly below the rotation axis of the harmonic reducer unit.
  • an internal gear ring is constructed in the wave generator, a gear is connected to one end of the rotating shaft that is in transmission connection with the wave generator, the gear is located in the wave generator, and the gear and Part of the teeth of the inner ring gear mesh with each other to form a meshing connection between the two.
  • the opening of the oil passage at the end of the extension end is arranged opposite to the gear, and the projection of the opening on the gear is located inside the dedendum circle of the gear.
  • a lubricating oil filter assembly is provided in the oil passage at the end of the extension end, and a notch penetrating the oil passage is formed at the end of the extension end, and the lubricating oil filter assembly includes The filter screen is arranged in the recess, and the filter screen is pressed into the recess by an oil plug fixed in the recess, and the oil plug is provided with one end penetrating through itself and the oil plug. The oil hole connected by the channel.
  • one side of the wave generator is rotatably mounted on the extension end of the eccentric shaft by a first bearing, and the other side of the wave generator is rotatably mounted on the housing of the motor unit by a second bearing. middle.
  • one side of the wave generator is rotatably mounted on the extension end of the eccentric shaft by a first bearing, and the other side of the wave generator slidably abuts on the housing of the motor unit, and A wear-resistant layer is provided at a portion of the housing that is in sliding contact with the wave generator.
  • a thrust washer is provided at a portion of the housing that is in sliding contact with the wave generator, and the thrust washer is convex with respect to the housing and slidably abuts against the wave generator , And the anti-friction layer is located on the thrust washer.
  • a flexspline pad placed in the flexspline is provided on the other side of the flexspline, and the flexspline is The connecting piece of the flexspline gasket and the flexspline is fixedly connected with the eccentric shaft.
  • a timing cover covering the harmonic reducer unit is fixedly connected to the engine cylinder, and the motor unit crosses the timing cover and is fixedly connected to the rigid wheel And a sealing ring is sandwiched between the motor unit and the timing cover.
  • one side of the wave generator is rotatably mounted on the extension end of the eccentric shaft by a first bearing, and the outer ring of the first bearing is interference press-fitted in the wave generator and mounted on the The end of the extension end is fixedly connected with a limiting member for limiting the inner ring of the first bearing.
  • a notch penetrating the oil passage is constructed at the end of the extension end, the stopper is a plug with one end fixedly connected in the notch, and the other end of the plug is caused by itself The radially extends outwardly and is blocked on one side of the first bearing, and an oil hole that penetrates itself and communicates with the oil passage is provided in the plug.
  • a lubricating oil filter assembly is provided in the oil passage at the end of the extension end, and the lubricating oil filter assembly includes a filter screen arranged in the recess, and the filter screen is formed by the plug Compressed in the recess.
  • the engine block is provided with an oil hole that penetrates the engine block, and the oil hole penetrates to the inside of the rigid wheel connected to the engine block, so as to Lubricating oil is poured down between the rigid wheel and the flexible wheel.
  • the present application also provides an engine including the variable compression ratio drive structure of the present application.
  • the application also provides a vehicle including the engine of the application.
  • variable compression ratio drive structure of the present application can effectively reduce the overall size of the drive structure by directly fixing the motor unit on the harmonic reducer unit, making the structure compact, which is beneficial to the arrangement in the engine, and at the same time by making
  • the rotation axis of the motor unit is offset relative to the rotation axis of the harmonic reducer unit, and the eccentric arrangement of the motor can be used to avoid the damping belt, so as to avoid interference with the damping pulley, which is beneficial to the overall design of the engine.
  • the motor unit is biased directly below to have a better avoidance effect, and the projection of the oil passage opening is within the range of the tooth root circle of the gear, which can block the sprayed lubricating oil to prevent the lubricating oil from entering the motor internal.
  • the setting of the oil seal can further prevent the lubricating oil from entering the motor, and the setting of the oil hole can better ensure the lubrication effect of the reducer.
  • one side of the wave generator is rotatably mounted on the eccentric shaft, and the other side is rotatably mounted on the housing of the motor unit or sliding against the housing, so that the wave generator can be reliably supported to limit The amount of axial movement of the wave generator.
  • the wave generator can be reliably supported to limit The amount of axial movement of the wave generator.
  • the outer ring of the first bearing is interference press-fitted in the wave generator, and setting a limiter can make the first bearing
  • the inner ring is limited on the extension end, so that the wave generator can also be axially limited, and the wave generator can be effectively supported in the same way to limit its axial movement.
  • the present application can reduce the friction loss during sliding contact through the arrangement of the thrust washer and the wear-resistant layer, and the arrangement of the flexspline gasket can prevent the flexspline from being crushed and damaged, and by making the timing cover cover Covering the reducer, arranging the motor unit and setting the sealing ring, can effectively ensure the sealing effect of the driving structure position.
  • FIG. 1 is a schematic structural diagram of a variable compression ratio mechanism according to Embodiment 1 of the application;
  • variable compression ratio driving structure is a schematic diagram of the variable compression ratio driving structure according to the first embodiment of the application.
  • FIG. 3 is a schematic diagram of the variable compression ratio drive structure shown in FIG. 2 after being assembled in an engine block;
  • Figure 4 is a side view of Figure 3;
  • FIG. 5 is a schematic diagram of the offset arrangement of the motor unit according to the first embodiment of the application.
  • Figure 6 is a partial enlarged view of part A in Figure 3;
  • Fig. 7 is a schematic diagram of the arrangement of the thrust washer according to the first embodiment of the application.
  • FIG. 10 is a schematic diagram of the pre-assembly of the eccentric shaft according to the first embodiment of the application.
  • FIG. 11 is a schematic diagram of the assembly of the eccentric shaft and the rigid wheel according to the first embodiment of the application;
  • Figure 12 is a schematic diagram of the assembly of the flexspline according to the first embodiment of the application.
  • FIG. 13 is a schematic diagram of the assembly of the eccentric shaft, the rigid wheel and the flexible wheel in the engine block according to the first embodiment of the application;
  • 15 is a schematic diagram of assembling the timing cover according to the first embodiment of the application.
  • variable compression ratio driving structure 16 is a schematic diagram of the variable compression ratio driving structure according to the second embodiment of the application.
  • Figure 17 is a partial enlarged view of part B in Figure 16;
  • 19 is a schematic diagram of the assembly of the plug according to the second embodiment of the application.
  • 501-Eccentric wheel 502-Oil passage, 503-Flange, 504-Extended end, 505-Connecting hole, 701-Locating pin hole, 1001-Inner gear ring, 1101-groove, 1102-installation groove, 1103 -Anti-rotation slot, 1501-anti-rotation block.
  • This embodiment relates to a variable compression ratio drive structure, which is generally used as a part of the variable compression ratio mechanism to drive the eccentric shaft in the variable compression ratio mechanism to rotate, thereby realizing the adjustment of the engine compression ratio.
  • variable compression ratio mechanism it is specifically a multi-link variable compression ratio mechanism, and an exemplary structure of the mechanism may be as shown in FIG. 1, at this time, the variable compression ratio mechanism is specifically It includes a piston 1 arranged in the engine cylinder, a crankshaft assembly and an eccentric shaft assembly rotating on the engine cylinder 7, and an adjusting connecting rod 3 that is rotated and fitted on the crankshaft 2 in the crankshaft assembly, and is hinged to the piston 1.
  • the executive link 4 between one end of the adjustment link 3 and the drive link 6 between the eccentric shaft 5 hinged in the eccentric shaft assembly and the other end of the adjustment link 3, and generally, the drive link 6 Specifically, it is hinged with the eccentric wheel 501 on the eccentric shaft 5.
  • variable compression ratio drive structure of this embodiment is also arranged in the engine block 7 and is used to drive the above-mentioned eccentric shaft 5 to rotate.
  • the eccentric shaft 5 is driven to rotate by the drive structure, and the eccentric wheel 501 on the eccentric shaft 5 can drive the drive link 6 to swing, and the drive link 6 swings to make itself swing
  • the support position changes, and the transmission of the adjusting connecting rod 3 and the executing connecting rod 4 also makes the top dead center position of the piston 1 higher or lower, so that the engine compression ratio can be adjusted.
  • variable compression ratio drive structure of this embodiment can also be used in other variable compression ratio mechanisms using an eccentric shaft structure. It is restricted as long as the variable compression ratio mechanism can apply the drive structure of this embodiment and can obtain the expected effect.
  • the overall structure of the variable compression ratio drive structure includes a harmonic reducer unit (X part) fixed on the engine cylinder 7, and a solid The motor unit (Part D) provided on the rigid wheel 8 in the harmonic reducer unit.
  • the harmonic reducer unit is the same as the existing harmonic reducer structure, it is still composed of rigid wheel 8, flexible wheel 9 and wave generator 10, and the working principle of the harmonic reducer unit is also similar to that of the existing harmonic reducer.
  • the structure of the harmonic reducer is the same.
  • the motor unit of this embodiment can generally adopt a stepping motor to have better rotation control accuracy.
  • this embodiment enables the motor unit to be directly fixed on the harmonic reducer unit, which can effectively reduce the size of the overall driving structure and make the structure compact to facilitate the arrangement in the engine.
  • the rigid wheel 8 is fixed on the engine cylinder block 7, the flexible wheel 9 is drivingly connected to one end of the eccentric shaft 5, and one end of the rotating shaft 12 of the motor unit extends out and is drivingly connected to the wave generator 10
  • the rotation axis of the motor unit is also offset to one side of the rotation axis of the harmonic reducer unit, so that the motor unit is eccentrically arranged relative to the harmonic reducer unit.
  • the end of the eccentric shaft 5 connected with the flexspline 9 in this embodiment also has an extension end 504 extending to the side of the rotating shaft 12. The extension end 504 can be specifically referred to in FIG. 10 described below.
  • the extension end 504 is configured on the extension end 504
  • an oil passage 502 communicating with the lubricating oil passage in the engine cylinder 7 is also constructed in the eccentric shaft 5, and the oil passage 502 axially penetrates to the end of the extension end 504 of the eccentric shaft 5.
  • this embodiment is aimed at the offset arrangement of the above-mentioned motor unit relative to the harmonic reducer unit, which may be along the height direction of the engine cylinder 7 so that the rotation axis of the motor unit is offset from the harmonic Below the rotation axis of the wave reducer unit, and in particular, preferably, as shown in FIG. 4, the rotation axis n of the motor unit is located directly below the rotation axis m of the harmonic reducer.
  • the rotation axis n of the motor unit is located directly below the rotation axis m of the harmonic reducer.
  • the upper part of the harmonic reducer unit is generally a damping pulley 22, and the engine damping pulley 22 is a flexible part, the design requirements need to allow the wheel train belt to generate a certain amount of beating during operation. Therefore, by biasing the motor unit below, it can provide a space for the vibration of the damping pulley 22 and the belt on it to avoid the impact on the normal operation of the engine train.
  • the rotation axis is set directly below the rotation axis of the harmonic reducer unit, and the avoidance effect is the best at this time.
  • the rigid wheel 8 in the harmonic reducer unit is specifically fixed to the engine cylinder block 7 by bolts.
  • the housing 11 in the motor unit is also fixed to the rigid wheel 8 by bolts.
  • the rigid wheel 8 and the housing 11 of the motor unit are respectively provided with mounting holes for bolt penetration, and as shown in FIG. 5, the double-dot chain circle e is the mounting holes on the housing 11.
  • the double-dot chain circle f is also the connection line between the mounting holes on the rigid wheel 8. Due to the eccentric arrangement of the motor unit, the two-dot chain circle e crosses the two-dot chain circle f instead of nesting.
  • the positions of the housing 11 corresponding to the mounting holes on the rigid wheel 8 are also respectively Notches are formed to avoid the mounting holes of the rigid wheel 8, and the closer these notches are to the intersection of the two dash-dotted circles, the larger the size.
  • the transmission connection between the shaft 12 of the motor unit and the wave generator 10 in this embodiment is specifically that an inner ring gear 1001 is constructed in the wave generator 10, and A gear 13 is connected to one end of the rotating shaft 12 that is in transmission connection with the wave generator 10.
  • the gear 13 is located in the wave generator 10, and the gear 13 also meshes with part of the teeth of the ring gear 1001 to form a gap between the two. Engaged and connected.
  • the teeth in the ring gear 1001 meshing with the gear 13 are also the bottom part thereof.
  • the oil passage 502 of the eccentric shaft 5 through the aforementioned arrangement of the oil passage 502 of the eccentric shaft 5, it can be transmitted between the gear 13 and the ring gear 1001, as well as the wave generator 10, the flexspline 9 and other components in the harmonic reducer unit. Lubricating oil is provided between them to achieve effective lubrication of various components.
  • the extended end 504 of the eccentric shaft 5 since the extended end 504 of the eccentric shaft 5 is arranged directly to the motor unit, fine metal impurities are unavoidable in the lubricating oil. Therefore, in order to prevent the lubricating oil sprayed from the oil passage 502 from entering the motor unit, the metal impurities are connected to the motor circuit The solder joints on the board cause the motor to short circuit.
  • the opening of the oil passage 502 at the end of the extension end 504 is arranged opposite to the gear 13, and the projection of the opening on the gear 13 is also located at the tooth root of the gear 13 Inside the circle.
  • an oil passage 502 located at the end of the extension end 504 is also provided with a lubricating oil filter assembly for filtering lubricating oil.
  • the filter assembly specifically includes a filter screen 24 arranged in the recess, and the filter screen 24 is pressed in the recess by an oil plug 25 fixed in the recess, and the oil plug 25 is also provided with one end and an oil passage that penetrates itself. 502 connected oil hole k.
  • the amount of lubricating oil required between the gear 13 and the ring gear 1001, as well as the flexspline 9, the wave generator 10 and other related components in the harmonic reducer unit during use is relatively large. Therefore, the diameter of the oil hole k on the oil plug 25 can be designed to be small, so that the flow of lubricating oil can be restricted and the oil pressure in the eccentric shaft 5 can be ensured.
  • the oil plug 25 it can be interference press-fitted or screwed into the recess at the end of the eccentric shaft 5, and the oil plug 25 can be made of a relatively simple cylindrical steel block.
  • the oil plug 25 is modified from a hexagon socket screw with a taper end, which flattens the taper end of the screw and drills an oil hole k inside.
  • the inner hexagonal hole and the oil hole k in the oil plug 25 penetrate through, and essentially constitute a part of the oil hole k, but due to the hexagonal inner hole k
  • the inner diameter of the hole is larger than the oil hole k, and the lubricating oil sprayed from the oil hole k in actual use only flows through the inner hexagonal hole.
  • the lubricating oil coming from the eccentric shaft 5 in this embodiment first enters the junction of the gear 13 and the ring gear 1001, and then Then the wave generator 10 enters the meshing place of the flexible wheel 9 and the rigid wheel 8, and finally flows into the oil pan of the engine through the third bearing 17 mentioned below at the rear end.
  • the above lubrication path can meet the lubrication requirements of the gear 13, the ring gear 1001, the wave generator 10, the flexible wheel 9 and the rigid wheel 7, and the third bearing 17.
  • the above-mentioned lubrication path is mainly at a position below the horizontal plane where the oil passage 502 is located, and because the flexspline 9 drives the eccentric shaft 5 generally only rotates within a certain angle range, but not The full rotation will cause the lubrication range to always be fixed within the rotation range of the flexspline 9, so that parts of the meshing teeth of the flexspline 9 and the rigid wheel 8 are prone to poor lubrication.
  • the engine cylinder 7 is also provided with an oil hole 19 that penetrates the engine cylinder 7.
  • the oil hole 19 penetrates to the inside of the rigid wheel 8 connected to the engine block 7 so as to be able to drench between the rigid wheel and the flexible wheel 9 at the cylinder head, tensioner or other mechanism inside the timing cover 18 Circulate lubricating oil to ensure the lubrication effect between the flexible wheel 9 and the rigid wheel 8.
  • a lubricating oil filter structure can also be provided in the above-mentioned oiling hole 19, and the structure may be assembled to the oiling hole, for example.
  • the filter in 19 is fine.
  • its axial direction is preferentially perpendicular to the horizontal direction of the engine.
  • the shape of the wave generator 10 is an elliptical structure, it is not allowed to bear radial force during the movement, and the flexspline 9 is a thin-walled piece.
  • the flexspline 9 The shape changes with the rotation of the wave generator 10.
  • the shape of the flexspline 9 is directly determined by the wave generator 10 during the meshing process of the meshing teeth on the flexspline 9 with the rigid wheel 8. If the axial movement of the wave generator 10 is too large, it will affect the mesh length between the flexible wheel 9 and the rigid wheel 8, and directly affect the force of the teeth. The amount of axial movement must be limited within the allowable range.
  • one side of the wave generator 10 is rotatably mounted on the eccentric by the first bearing 14.
  • the first bearings 14 are also two arranged side by side, with clearance fit between them and the extension end 504, and interference fit between them and the wave generator 10.
  • the other side of the wave generator 10 slidably abuts on the housing 11 of the motor unit, and in order to reduce the friction loss, the part of the housing 11 that slidably abuts the wave generator 10 is also provided with a resistance. Grinding layer.
  • the thrust washer 15 of this embodiment can also adopt other conventional structural forms.
  • the wear-resistant layer it may be, for example, a wear-resistant alloy layer, and the corresponding thrust washer 15 uses a steel material as the backing material, or the thrust washer 15 is made of other base materials, which is resistant to It is also possible that the grinding layer is provided as a wear-resistant coating.
  • the wave generator 10 is arranged to be rotated by the first bearing 14 on one side, and the other side adopts a sliding abutment arrangement
  • the wave generator 10 is another feasible option.
  • the setting method as shown in FIG. 8 at this time, can also make one side of the wave generator 10 still rotatably mounted on the extension end 504 of the eccentric shaft 5 through the first bearing 14, while the other side of the wave generator 10 is
  • the second bearing 26 is rotatably installed in the housing 11 of the motor unit.
  • first bearing 14 only one first bearing 14 can be used, and there is still an interference fit between the first bearing 14 and the wave generator 10, and there is still a clearance fit between the first bearing 14 and the extension end 504 of the eccentric shaft 5. There is a clearance fit between the second bearing 26 and the wave generator 10, and an interference fit with the housing 11 of the motor unit.
  • the reliable arrangement of the wave generator 10 can also be realized to limit the axial movement of the wave generator 10.
  • the above two arrangements of the wave generator 10 are adopted, and only an extension end 504 is provided at the end of the eccentric shaft 5, and the extension end 504 constitutes a support end for supporting the wave generator 10.
  • this direct support form can reduce the first-level assembly error, and the extension end 504 is the same as the outer circle of the main journal of the eccentric shaft 5
  • the process processing can also effectively ensure the coaxiality during the assembling process of the wave generator 10, thereby improving its transmission accuracy and reliability.
  • the flange portion 503 is provided with a number of connecting holes 505 arranged annularly.
  • the connecting holes 505 may generally be threaded holes, and the flexspline 9 can be fastened to the flange portion 503 by bolts.
  • this embodiment is a preferred implementation form.
  • a flexspline washer 16 located in the flexspline 9 can be provided, and the flexspline 9 is fixedly connected to the eccentric shaft 5 by passing through the flexspline washer 16 and the connecting piece of the flexspline 9
  • the connecting piece is generally the above-mentioned bolt.
  • a third bearing 17 is also provided at the end connecting the eccentric shaft 5 and the flexspline 9 to pass the third bearing 17 makes the eccentric shaft 5 rotatably installed in the rigid wheel 8.
  • the radial support of the eccentric shaft 5 via the third bearing 17 can limit the radial beating generated when the cylinder transmitted by the multi-link mechanism borne by the eccentric shaft 5 explodes, so as to prevent the flexspline 9 from being caused by the eccentric shaft 5. Drive and appear big radial runout.
  • a timing cover 18 covering the harmonic reducer unit is fixedly connected to the engine cylinder 7, and at this time, the motor unit is the horizontal
  • the timing cover 18 is penetrated to be fixedly connected to the rigid wheel 8, and a sealing ring 21 is also sandwiched between the housing 11 of the motor unit and the timing cover 18.
  • a groove 1101 is provided on the outer peripheral wall of the housing 11 of the motor unit, and the above-mentioned sealing ring 21 is installed in the groove 1101.
  • the sealing ring 21 is preferably Can be two arranged side by side.
  • the filter screen 24 is fixed in the eccentric shaft 5 through the oil plug 25.
  • this step can be omitted.
  • the third bearing 17 is first interference press fitted in the stepped hole on the rigid wheel 8, and then the end of the eccentric shaft 5 with the extended end 504 is passed through the inner ring of the third bearing 17 to be rotatably mounted on the inner ring of the third bearing 17 Just round 8 in.
  • the end face of the flange part 503 is attached, and then the flange part 503 on the eccentric shaft 5 is fixedly connected with the flange part 503 on the eccentric shaft 5 through the flexspline gasket 16 and bolts.
  • the housing 1 supports the wave generator 10 through the thrust washer 15 or the second bearing 26 according to the design choice, and the wave generator 10 is connected to the wave generator 10 as the motor unit penetrates.
  • the thrust washer 15 can be connected, or the wave generator 10 can be installed in the second bearing 26.
  • the first bearing 14 on the other side should be the same as before.
  • the described arrangement is two arranged side by side.
  • the motor unit is inserted into the timing cover 18, it is also necessary to rotate the motor unit to adjust its angle so that the axis of the motor unit is directly below the axis of the harmonic reducer unit, and the terminal 23 is plugged into the motor unit.
  • the opening of the engine is horizontally directed to the intake side relative to the engine block.
  • the meshing part of the gear 13 on the motor unit and the ring gear 1001 in the wave generator 10 is located at the lowest position vertically below, and is on the flow path of the lubricating oil, while the opening of the plug-in terminal 23 faces the entrance The air side can also be easily plugged and unplugged.
  • this embodiment may also be preferably provided between the engine block 7 and the small reducer cover 27 to predetermine the installation of the small reducer cover 27.
  • the positioning portion may include, for example, positioning pin holes 701 respectively provided on the engine block 7 and the small cover 27 of the reducer, and positioning pins 28 whose two ends are inserted into the two positioning pin holes 701, or the positioning
  • the part can also adopt other existing conventional pre-positioning structures.
  • This embodiment also relates to a variable compression ratio drive structure, which has substantially the same structure as the variable compression ratio drive structure in the first embodiment. The difference is that as shown in FIG. 16 in combination with FIGS. 17 and 18
  • one side of the wave generator 10 is rotatably mounted on the extension end 504 of the eccentric shaft 5 by the first bearing 14, and is assembled by interference between the outer ring of the first bearing 14 and the wave generator 10, And through the arrangement of the limiting member that limits the inner ring of the first bearing 14 at the end of the extension end 504, the wave generator 10 can be reliably supported and the axial movement of the wave generator 10 can be restricted.
  • the end of the extension end 504 of the eccentric shaft 5 is configured with a notch penetrating the oil passage 502, and as an exemplary structure, the limiting member of this embodiment is specifically one end fixedly connected to the The plug 30 in the recess, the other end of the plug 30 is blocked on one side of the inner ring of the first bearing 14 due to its radial extension, and the plug 30 is also provided with a penetrating through itself and The oil hole k through which the oil passage 502 communicates.
  • the plug 30 of this embodiment may preferably have one end screwed into the recess, and the other end of the plug 30 extends radially outward to limit the stop on one side of the inner ring of the first bearing 14, thereby Cooperating with the shoulder structure on the extension end 504 on the other side can also achieve the limit restriction on the inner ring of the first bearing 14.
  • the inner hexagonal hole and the oil hole k in the plug 30 penetrate through, and substantially constitute a part of the oil hole k, but due to the hexagonal inner hole
  • the inner diameter is larger than the oil hole k, and the lubricating oil sprayed from the oil hole k in actual use only flows through the inner hexagonal hole.
  • a lubricating oil filter assembly for filtering lubricating oil is also provided in the oil passage 502 at the end of the extension end 504, and is used as the lubricating oil.
  • the exemplary structure of the oil filter assembly is shown in FIG. 17.
  • the above lubricating oil filter assembly specifically includes a filter mesh 24 arranged in the recess, and the filter mesh is also compressed in the recess by the plug 30.
  • the first bearings 14 are also preferably two arranged side by side, so that through the two rows of the first bearings 14, one-point support can be changed into two-point support in the axial direction, making the support more reliable.
  • the inner ring of the first bearing 14 and the filter screen 15 are limited at the same time.
  • a plugging structure with an oil hole k like the oil plug 25 in the first embodiment can be embedded in the recess at the end of the extension end 504 to compress the filter screen 15.
  • the limiter used for the inner ring limit of the first bearing 14 can be screwed or interference press fitted on the outer circumference of the extension end 504, and is also blocked on the inner ring side of the first bearing 14 structure.
  • the third bearing 17 is interference press fitted into the stepped hole on the rigid wheel 8, and then the end of the eccentric shaft 5 with the extended end 504 is passed through the inner ring of the third bearing 17 to be rotatably installed in the rigid wheel 8. Then install the flexible wheel 9 into the rigid wheel 8, so that the flexible wheel 9 and the rigid wheel 8 are in a transmission fit, and the flexible wheel 9 is sleeved on the extension end 504 to fit the end face of the flange 503 on the eccentric shaft 5. , Then pass through the flexspline gasket 16 and use bolts to be fixedly connected with the flange portion 503 on the eccentric shaft 5.
  • the first bearing 14 is press-fitted in the wave generator 10, and then the wave generator 10 with the first bearing 14 is installed in the flexspline 9 located in the rigid wheel 8, thereby passing the wave generator 10 through the first bearing 14
  • a bearing 14 is rotatably mounted on the extension end 504 of the eccentric shaft 5 to make the wave generator 10 and the flexspline 9 drive and cooperate.
  • the tool 29 can also be used to rotate the wave generator 10 into the flexspline 9 at a certain rotation speed, so that the wave generator 10 can be pressed in.
  • the timing cover 18 installs the timing cover 18 on the engine cylinder block 7, and first pre-tighten the timing cover 18 to cover the harmonic reducer unit in the engine cylinder block 7, and then pass the motor unit through the timing cover
  • the cover 18 connects the housing 11 to the rigid wheel 8 and then tightens the housing 11 and the timing cover 18.
  • the sealing ring 21 is sealed between the housing 11 and the timing cover 18 as the housing 11 penetrates, and the connecting terminal 23 in the motor unit is outside the timing cover 18.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne une structure d'entraînement à taux de compression variable, destinée à être utilisée pour entraîner en rotation un arbre excentrique (5) dans un mécanisme à taux de compression variable. La structure d'entraînement à taux de compression variable comprend une unité de réducteur d'harmoniques disposée de manière fixe sur un cylindre de moteur et une unité de moteur disposée de manière fixe sur une cannelure circulaire rigide (8) dans l'unité de réducteur d'harmoniques ; une cannelure flexible (9) dans l'unité de réducteur d'harmoniques est reliée par entraînement à une extrémité de l'arbre excentrique (5) ; une extrémité d'un arbre rotatif (12) de l'unité de moteur s'étend vers l'extérieur et est reliée par entraînement à un générateur d'ondes (10) dans le réducteur d'harmoniques ; l'axe de rotation de l'unité de moteur est sollicité vers un côté de l'axe de rotation de l'unité de réducteur d'harmoniques ; l'extrémité de l'arbre excentrique (5) reliée à la cannelure flexible (9) est pourvue d'une extrémité d'extension (504) s'étendant vers un côté de l'arbre rotatif ; un canal d'huile traverse axialement l'arbre excentrique (5) jusqu'à l'extrémité de l'extrémité d'extension (504). La structure d'entraînement à taux de compression variable peut donner un espace pour une poulie d'amortisseur dans un moteur et un travail efficace de la structure d'entraînement peut être efficacement assuré. L'invention concerne aussi un moteur et un véhicule.
PCT/CN2021/077712 2020-02-24 2021-02-24 Structure d'entraînement à taux de compression variable, moteur et véhicule WO2021170003A1 (fr)

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