WO2021170003A1 - Variable compression ratio driving structure, engine, and vehicle - Google Patents

Abstract

A variable compression ratio driving structure, for use in driving an eccentric shaft (5) in a variable compression ratio mechanism to rotate. The variable compression ratio driving structure comprises a harmonic reducer unit fixedly provided on an engine cylinder, and a motor unit fixedly provided on a rigid circular spline (8) in the harmonic reducer unit; a flexspline (9) in the harmonic reducer unit is drivingly connected to one end of the eccentric shaft (5); one end of a rotating shaft (12) of the motor unit extends out and is drivingly connected to a wave generator (10) in the harmonic reducer; the rotation axis of the motor unit is biased to one side of the rotation axis of the harmonic reducer unit; the end of the eccentric shaft (5) connected to the flexspline (9) is provided with an extension end (504) extending to one side of the rotating shaft; an oil channel axially passes through the eccentric shaft (5) to the end of the extension end (504). The variable compression ratio driving structure can give a space for a damper pulley in an engine, and effective work of the driving structure can be effectively ensured. Also provided are an engine and a vehicle.

Description

Variable compression ratio drive structure, engine and vehicle

Cross-references to related applications

This application claims the rights and interests of the Chinese patent application 202010113479.5 filed on February 24, 2020, the content of which is incorporated herein by reference.

Technical field

The application relates to the field of engine technology, and in particular to a variable compression ratio drive structure.

Background technique

In order to reduce engine displacement, improve fuel combustion efficiency and fuel economy, variable compression ratio technology came into being. With the continuous development of variable compression ratio technology, compression ratio adjustment forms are becoming more and more diversified. Among them, 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.

In the current multi-link variable compression ratio mechanism, 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. At present, 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. In addition, in the motor side structure, 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.

In addition, in the current variable compression ratio mechanism, 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. .

Summary of the invention

In view of this, 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.

In order to achieve the above-mentioned purpose, the technical solution of this application is realized as follows:

A 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.

Further, along the height direction of the engine block, the rotation axis of the motor unit is offset below the rotation axis of the harmonic reducer unit.

Further, the rotation axis of the motor unit is located directly below the rotation axis of the harmonic reducer unit.

Further, 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.

Further, 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.

Further, 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.

Further, 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.

Further, 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.

Further, 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.

Further, with respect to the side of the flexspline that is connected to the eccentric shaft, 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.

Further, 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.

Further, 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.

Further, 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.

Further, 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.

Further, 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.

Compared with the prior art, this application has the following advantages:

The 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.

At the same time, in the present application, 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.

In addition, in the present application, 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. And by making one side of the wave generator rotated by the first bearing and mounted on the extension end of the eccentric shaft, and 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.

In addition, 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.

Description of the drawings

The drawings constituting a part of the application are used to provide a further understanding of the application, and the exemplary embodiments and descriptions of the application are used to explain the application, and do not constitute an improper limitation of the application. In the attached picture:

FIG. 1 is a schematic structural diagram of a variable compression ratio mechanism according to Embodiment 1 of the application;

2 is a schematic diagram of the variable compression ratio driving structure according to the first embodiment of the application;

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;

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;

8 is a schematic diagram of the structure of the wave generator according to the first embodiment of the application in another supporting form;

9 is a schematic diagram of the sealing of the motor unit and the timing cover according to the first embodiment of the application;

10 is a schematic diagram of the pre-assembly of the eccentric shaft according to the first embodiment of the application;

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;

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;

FIG. 14 is a schematic diagram of assembling the wave generator 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;

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;

18 is a schematic diagram of the structure of the plug according to the second embodiment of the application;

19 is a schematic diagram of the assembly of the plug according to the second embodiment of the application;

Description of reference signs:

1-piston, 2-crankshaft, 3-adjusting connecting rod, 4-actuating connecting rod, 5-eccentric shaft, 6-driving connecting rod, 7-engine cylinder, 8-rigid wheel, 9-flexible wheel, 10-wave Generator, 11-housing, 12-rotating shaft, 13-gear, 14-first bearing, 15-thrust washer, 16-flexible gasket, 17-third bearing, 18-timing cover, 19 -Oil hole, 20-oil seal, 21-seal, 22-damping pulley, 23-plug terminal, 24-filter, 25-oil plug, 26-second bearing, 27-reducer cover, 28 -Locating pin, 29-tooling, 30-plug;

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.

Detailed ways

It should be noted that the embodiments in the application and the features in the embodiments can be combined with each other if there is no conflict.

Hereinafter, the present application will be described in detail with reference to the drawings and in conjunction with the embodiments.

Example one

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.

Among them, for the above 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.

The 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. At this time, during engine operation, based on the control of the engine ECU, 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.

Of course, in addition to being applied to the variable compression ratio mechanism shown in FIG. 1, the 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.

In this embodiment, as shown in Figures 2 to 4, 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. Among them, 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. However, the motor unit of this embodiment can generally adopt a stepping motor to have better rotation control accuracy. At the same time, 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.

In the harmonic reducer unit of this embodiment, 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 And in this embodiment, 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. In addition, 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 There is a shoulder structure for installing the first bearing 14 in the following, and the shoulder is used for limiting the position on one side of the first bearing 14. In this embodiment, 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.

As a preferred implementation form, 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. At this time, referring to FIG. 5, there is a distance difference h between the rotation axis of the motor and the rotation axis of the harmonic reducer unit above it.

Since in the overall structure of the engine, 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.

In this embodiment, the rigid wheel 8 in the harmonic reducer unit is specifically fixed to the engine cylinder block 7 by bolts. At the same time, the housing 11 in the motor unit is also fixed to the rigid wheel 8 by bolts. At this time, 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. In addition, 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.

As shown in FIGS. 2 and 3 in combination with FIG. 5, 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. At this time, matching the eccentric arrangement of the motor unit, the teeth in the ring gear 1001 meshing with the gear 13 are also the bottom part thereof.

In this embodiment, 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. At this time, 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. In this embodiment, 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.

Via the relative position arrangement between the opening of the oil passage 502 and the gear 13, and the projection of the opening of the oil passage 502 is located in the tooth root circle of the gear 13, from Fig. 2 or 3, the gear 13 becomes higher than the oil passage 502 As a result, the lubricating oil sprayed from the opening of the oil passage 502 will be blocked by the gear 13 and flow down the gear 13, thereby protecting the motor, and at this time, because the gear 13 is in contact with the ring gear The teeth on the inner bottom of the 1001 mesh, and the meshing surface between the two is also on the flow path of the lubricating oil, so that sufficient lubrication can be obtained, and problems such as dry grinding or high temperature damage caused by insufficient lubrication can be avoided. Of course, in order to further ensure that the lubricating oil does not enter the inside of the motor, in this embodiment, as shown in FIG. 2 or FIG. 3, an oil seal 20 may be provided between the shaft 12 and the housing 11 of the motor unit. Parts can be.

In the actual manufacturing process of the engine, it is sometimes unavoidable that the lubricating oil is doped with large metal impurities. This embodiment is to prevent these impurities from entering the junction of the gear 13 and the ring gear 1001 from the oil passage 502, and In other parts of the harmonic reducer unit, as a preferred embodiment, 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.

At this time, as an exemplary structure of the above-mentioned lubricating oil filter assembly, as shown in FIG. 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.

It should be noted in this embodiment that 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. In addition, for 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. In this embodiment, 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.

Regarding the oil plug 25 used in this embodiment, it should also be noted that 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.

Through the oil passage 502 in the eccentric shaft 5 and the arrangement of the gear 13 facing the opening of the oil passage 502, 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.

However, it can be seen from Fig. 2 or Fig. 3 that 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. In order to avoid this poor lubrication situation, as a preferred embodiment, in addition to the oil supply of the oil passage 502, 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.

In order to prevent the inevitable large metal impurities in the lubricating oil from entering the meshing area of 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. In addition, when the oil hole 19 is installed, its axial direction is preferentially perpendicular to the horizontal direction of the engine. Of course, in addition to being vertical, it is also possible to form a certain angle with the horizontal plane of the engine.

In this embodiment, since 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. When the wave generator 10 is installed in the flexspline 9, 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.

Based on the above, in the installation of the wave generator 10 in this embodiment, as an alternative form, as shown in FIGS. 2 and 3, one side of the wave generator 10 is rotatably mounted on the eccentric by the first bearing 14. On the extension end 504 of the shaft 5, 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. At the same time, 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 use of the two rows of first bearings 14 in this embodiment can change the one-point support into the two-point support in the axial direction, making the support more reliable, so as to ensure the smooth operation of the wave generator 10 after installation. For the sliding abutment between the wave generator 10 and the housing 11, it can be such that the wave generator 10 directly abuts the housing 11, and the wear-resistant layer is directly provided on the relevant part of the housing 11. . However, since the shell 11 of the motor unit is mostly made of aluminum material, the material of the end cover is poor, and the high temperature resistance and wear resistance are poor, and high temperature ablation is prone to occur. At the same time, the friction loss is also relatively large.

Therefore, as a preferred arrangement when the housing 11 and the wave generator 10 are in sliding contact, this embodiment is combined with that shown in FIG. The thrust washer 15 protrudes relative to the housing 11 so as to be slidably abutted with the wave generator 10, and the aforementioned anti-friction layer is also located on the thrust washer 15.

This embodiment is used as an exemplary structure of the thrust washer 15. The thrust washer 15 has a ring shape, and the housing 11 is provided with an embedding groove 1102 into which the thrust washer 15 is embedded. The thrust washer 15 is formed on the device housing 11 through a transitional fit with the embedding groove 1102, and a device for restricting the rotation of the thrust washer 15 is also provided between the embedding groove 1102 and the thrust washer 15 Anti-rotation department. The anti-rotation part specifically includes an anti-rotation groove 1103 provided on the inner wall of the embedding groove 1102, and an anti-rotation block 1501 provided on the thrust washer 15 that can be clamped into the anti-rotation groove 1103.

Of course, in addition to the aforementioned annular thrust washer 15 and its corresponding arrangement, the thrust washer 15 of this embodiment can also adopt other conventional structural forms. In addition, for the wear-resistant layer provided, 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.

In this embodiment, in addition to the above-mentioned arrangement that 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, it should be noted that 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.

At this time, 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. In this embodiment, through the above-mentioned way of rotating and mounting on both sides via bearings, of course, the reliable arrangement of the wave generator 10 can also be realized to limit the axial movement of the wave generator 10.

In addition, in this embodiment, 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. Compared with the indirect support form in which the support structure is assembled on the eccentric shaft 5 and then the wave generator 10 is assembled, 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.

For the connection between the flexspline 9 and the eccentric shaft 5 in this embodiment, refer to FIG. 10 which will be described below. The end of the eccentric shaft 5 with the extended end 504 is also formed with a radially convex method. The flange portion 503, which is like the flange plate fixed on the eccentric shaft 5, is named the flange portion 503, and the extension end 504 is also fixedly connected to the flange portion 503 and is connected to the other eccentric shaft 5. Partially integrated structure.

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. At this time, since the flexspline 9 is a thin-walled piece, in order to avoid damage to the flexspline 9 due to the tightening of the bolts, this embodiment is a preferred implementation form. Relative to the side of the flexspline 9 that is connected to the eccentric shaft 5, On the other side of the flexspline 9, 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.

At the same time, for the aforementioned flexspline washer 16, as an exemplary structure adopted in this embodiment, the dimensions of the two opposite ends of the flexspline shim are also different, so that the outer peripheral surface of the flexspline shim 16 is similar to a cone, and When in use, the end surface of the flexspline washer 16 with a smaller cross-section is attached to the flexspline 9, so as to facilitate the arrangement of the flexspline washer 16 in the flexspline 9. It should be noted that in addition to the use of bolts, of course, in this embodiment, the bolts are replaced with rivets, or the flexspline 9 can be directly welded to the flange portion 503, and the flexspline can be omitted when the welding method is adopted. Gasket 16.

In this embodiment, further from the perspective of preventing excessive radial deformation of the flexspline 9 to protect the flexspline, 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. At this time, 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.

It should be noted that, in addition to installing the third bearing 17 in the rigid wheel 8, of course, it is adapted to the size design of the rigid wheel 8 of the harmonic reducer unit. In this embodiment, the third bearing 17 can also be installed in the engine block 7 middle.

In addition, as shown in FIG. 2 and combined with FIG. 9, in this embodiment, 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. Referring again to FIG. 7, 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. In order to improve the sealing effect, the sealing ring 21 is preferably Can be two arranged side by side.

In this embodiment, the motor unit is connected to the rigid wheel 8 through the timing cover 18, and a sealing ring is arranged between the casing 11 and the timing cover 18 to form a sealing structure. The sealing structure can tighten the rigid wheel 8 The joint surface of the fixing bolt, the rigid wheel 8 and the housing 11 is sealed in the timing cover 18. As a result, the timing cover 18, the engine block 7 and the oil pan inside can form a closed space. Since the joint surfaces and bolt holes in contact with the lubricating oil will have the risk of oil leakage, the motor unit middle shell The end cover part of the body 11 and the entire harmonic reducer unit are arranged in a closed space, so that the joint surface of the motor unit and the harmonic reducer unit and the fastening bolts of the harmonic reducer unit can be sealed in the engine block 7 Internally, these parts can reduce or even no sealing requirements, and can effectively reduce the number of sealing tapes, simplify assembly, and reduce costs.

Among them, the lubricating oil flows directly into the oil pan after passing through the mounting holes on the rigid wheel 8 during the lubrication process, and the lubricant in the unit cavity of the harmonic reducer will also leak into the oil through the joint surface of the housing 11 and the rigid wheel 8 There is no leakage in the bottom shell to complete the lubricating oil circulation.

In this embodiment, based on the configuration of the driving structure described above, the assembly method specifically includes the following steps.

First, as shown in Fig. 10, the filter screen 24 is fixed in the eccentric shaft 5 through the oil plug 25. Of course, if the lubricating oil filter assembly is not provided, this step can be omitted. Then, as shown in FIG. 11, 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. Then, as shown in Figure 12, install the flexible wheel 9 into the rigid wheel 8, so that the flexible wheel 9 and the rigid wheel 8 are in transmission cooperation, and the flexible wheel 9 is sleeved on the extension end 504 and is connected to the eccentric shaft 5. 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.

Then, turn the engine block 7 by 180° so that the bottom face upwards, as shown in Figure 13, install the connected rigid wheel 8, the eccentric shaft 5 and the flexspline 9 into the engine block 7, and tighten the rigid wheel 8 The rigid wheel 8 is pre-fixed to the engine block 7 by the connecting bolts. Next, install the small reducer cover 27 on the engine block 7 to sandwich the rigid wheel 8 between the small reducer cover 27 and the engine block 7, and then fasten the rigid wheel 8 and the small reducer cover 27 with the engine The connection between the cylinder blocks 7 makes the rigid wheel 8 fixed in the engine block 7.

Then, the first bearing 14 is interference press-fitted in the wave generator 10, and the extended end 504 of the eccentric shaft 5 is penetrated from the inner ring of the first bearing 14, thereby rotating the wave generator 10 through the first bearing 14. On the extension end 504 of the eccentric shaft 5, the wave generator 10 is pressed into the flexspline 9 to be in cooperation with the flexspline 9 in transmission. At this time, it should be noted that when the wave generator 10 is pressed into the flexspline 9, as shown in FIG. 14, a tool 29 with one end embedded in the wave generator 10 can be used to generate waves at a certain rotation speed. The device 10 is screwed into the flexspline 9 to facilitate the pressing of the wave generator 10.

Next, install the timing cover 18 on the engine block 7 as shown in Figure 15, and first pre-tighten the timing cover 18 to cover the harmonic reducer unit in the engine block 7, and then the motor unit Pass through the timing cover 18 to connect the housing 11 to the rigid wheel 8, and then tighten the housing 11 and the timing cover 18, and at this time, the sealing ring 21 is sealed in the housing with the penetration of the housing 11 Between the body 11 and the timing cover 18, the connection terminals 23 in the motor unit are outside the timing cover 18.

Among them, before the motor unit is installed, 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. At the same time, it should be noted that when the thrust washer 15 is selected, the first bearing 14 on the other side should be the same as before. The described arrangement is two arranged side by side.

In addition, after 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. As a result, 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.

In addition, in order to facilitate the installation of the small reducer cover 27 in the engine block 7, 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. Positioning part of the bit. 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.

Example two

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 In this embodiment, 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.

Specifically, 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.

Wherein, 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.

It should be noted that the outer diameter of the radially outward end of the plug 30 is generally equal to or slightly larger, and slightly smaller than the outer diameter of the inner ring of the first bearing 14, and of course it must be smaller than the outer ring of the first bearing 14. the inside diameter of. In addition to screwing the plug 30 into the recess at the end of the extension end 504, of course, the plug 30 can also be assembled in the recess by means of interference press fitting. And for the end of the plug 30 where the inner ring of the first bearing 14 is blocked, it is disc-shaped due to the radial extension of the entire circumference as shown in FIG. 18, and the end of the plug 30 is currently It is also feasible to have only one or a few radially outwardly extending stopper structures arranged at intervals in the circumferential direction to block the inner ring of the first bearing 14 through the stopper structure.

The same in this embodiment, because the amount of lubricating oil required between the gear 13 and the ring gear 1001 in use, and the flexspline 9, the wave generator 10 and other related components in the harmonic reducer unit is small, Therefore, the diameter of the oil hole k on the plug 30 can also be designed to be smaller, so as to limit the flow of lubricating oil and ensure the oil pressure in the eccentric shaft 5. In addition, for the plug 30 in this embodiment, it can be made of a relatively simple cylindrical steel block, and similar to the oil plug 25 in the first embodiment, an inner plug 30 is also provided in the middle of one end of the plug 30. The hexagonal hole facilitates the screwing operation. At the same time, the same as in the first embodiment, 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.

In this embodiment, in order to ensure the cleanliness of the lubricating oil flowing from the oil hole k, 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.

In this embodiment, the first bearing 14 is rotatably mounted on the extension end 504 of the eccentric shaft 5 through one side of the wave generator 10, and the first bearing 14 and the extension end 504 adopt a clearance fit, and are in contact with the wave generator. Between 10, an interference fit is used. At the same time, the stopper formed by the oil plug 24 provided at the end of the extension end 504 matched with the interference fit of the outer ring of the first bearing 14 and the wave generator 10, and the end of the extension end 504 The shaft shoulder structure corresponds to that of the inner ring of the first bearing 14 at the extension end 504, that is, the eccentric shaft 5. At this time, through the stable connection between the inner and outer rings of the first bearing 14 and the eccentric shaft 5 and the wave generator 10, the reliable arrangement of the wave generator 10 can be realized to limit the axial movement of the wave generator 10.

In this embodiment, 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. Of course, it should also be noted that in this embodiment, in addition to making the plug 30 a dual purpose, the inner ring of the first bearing 14 and the filter screen 15 are limited at the same time. As other feasible implementation forms, 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.

In this embodiment, based on the above-mentioned structure of the driving structure, the assembly method is slightly different from that in the first embodiment, and it specifically includes the following steps.

Firstly, 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.

Then, 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. When the wave generator 10 is pressed into the flexspline 9, 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.

Next, as shown in Figure 19, fit the filter screen 15 into the notch at the end of the extension end 504, and then screw the plug 30 into the notch to fix the filter screen 15 and limit the first bearing 14 at the same time. Extending end 504 on. Of course, if you choose not to install the lubricating oil filter assembly, the installation of the filter screen 15 can be omitted. When the aforementioned limiter adopts other forms, the limiter can also be installed at the end of the extension end 504 at this time to perform The inner ring of the first bearing 14 may be restricted and limited.

Then, turn the engine block 7 by 180° so that its bottom face upwards, and then install the connected eccentric shaft 5 and the harmonic reducer unit into the engine block 7, and tighten the connecting bolts of the rigid wheel 8 to reduce the rigidity. The wheel 8 is pre-fixed to the engine block 7. Next, install the small reducer cover 27 on the engine block 7 to sandwich the rigid wheel 8 between the small reducer cover 27 and the engine block 7, and then fasten the rigid wheel 8 and the small reducer cover 27 with the engine The connection between the cylinder blocks 7 makes the rigid wheel 8 fixed in the engine block 7.

Next, install 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. At this time, 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.

The above descriptions are only the preferred embodiments of this application, and are not intended to limit this application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of this application shall be included in this application. Within the scope of protection.

Claims (17)

1. A variable compression ratio drive structure to drive the eccentric shaft (5) in the variable compression ratio mechanism to rotate, characterized in that: the variable compression ratio drive structure includes a resonance fixed on the engine cylinder (7) The wave reducer unit, and the motor unit fixed on the rigid wheel (8) in the harmonic reducer unit, the flexible wheel (9) in the harmonic reducer unit and the eccentric shaft (5) One end of the motor unit is in a transmission connection, one end of the rotating shaft (12) of the motor unit extends out and is in transmission connection with the wave generator (10) in the harmonic reducer, and the rotation axis of the motor unit is offset from the harmonic On one side of the rotation axis of the wave reducer unit, the end of the eccentric shaft (5) connected with the flexspline (9) has an extension end (504) extending to the side of the rotation shaft (12), and is connected to the An oil passage (502) communicating with the lubricating oil passage in the engine cylinder (7) is constructed in the eccentric shaft (5), and the oil passage (502) axially penetrates to the extension of the eccentric shaft (5) The end of the end (504).
2. The variable compression ratio drive structure according to claim 1, characterized in that: along the height direction of the engine block (7), the rotation axis of the motor unit is offset from the rotation axis of the harmonic reducer unit Below.
3. The variable compression ratio drive structure according to claim 2, wherein the rotation axis of the motor unit is located directly below the rotation axis of the harmonic reducer unit.
4. The variable compression ratio drive structure according to claim 2, characterized in that: an inner ring gear (1001) is constructed in the wave generator (10), and the shaft (12) is connected to the wave generator (10) One end of the transmission connection is connected with a gear (13), the gear (13) is located in the wave generator (10), and the gear (13) and part of the toothing of the ring gear (1001) They are engaged to form a meshing connection between the two.
5. The variable compression ratio drive structure according to claim 4, characterized in that: the opening of the oil passage (502) at the end of the extension end (504) is arranged opposite to the gear (13), and the The projection of the opening on the gear (13) is located inside the tooth root circle of the gear (13).
6. The variable compression ratio drive structure according to claim 1, characterized in that: a lubricating oil filter assembly is provided in the oil passage (502) at the end of the extension end (504), and is installed in the extension end (504). The end of the end (504) is configured with a recess that penetrates the oil passage (502), and the lubricating oil filter assembly includes a filter screen (24) arranged in the recess, and the filter screen (24) is formed by The oil plug (25) fixed in the recess is pressed into the recess, and the oil plug (25) is provided with an oil hole ( k).
7. The variable compression ratio drive structure according to claim 6, characterized in that: one side of the wave generator (10) is rotatably mounted on the extension end (5) of the eccentric shaft (5) by a first bearing (14) 504), the other side of the wave generator (10) is rotatably installed in the housing (11) of the motor unit by a second bearing (26).
8. The variable compression ratio drive structure according to claim 6, characterized in that: one side of the wave generator (10) is rotatably mounted on the extension end (5) of the eccentric shaft (5) by a first bearing (14) 504), the other side of the wave generator (10) slidably abuts on the housing (11) of the motor unit, and the housing (11) and the wave generator (10) ) Wear-resistant layer is provided at the sliding contact part.
9. The variable compression ratio drive structure according to claim 8, characterized in that: a thrust washer (15) is provided at a portion of the housing (11) that is in sliding contact with the wave generator (10) , The thrust washer (15) protrudes relative to the housing (11) to slidably abut the wave generator (10), and the anti-friction layer is located on the thrust washer (15) superior.
10. The variable compression ratio drive structure according to claim 1, characterized in that: relative to the side of the flexspline (9) that is connected to the eccentric shaft (5), the flexspline (9) The other side of the flexspline is provided with a flexspline washer (16) placed in the flexspline (9), and the flexspline (9) is passed through the flexspline shim (16) and the flexspline (16). 9) The connecting piece is fixedly connected with the eccentric shaft (5).
11. The variable compression ratio drive structure according to claim 1, characterized in that: a timing cover (18) covering the harmonic reducer unit is fixedly connected to the engine cylinder (7) , The motor unit traverses the timing cover (18) and is fixedly connected to the rigid wheel (8), and is sandwiched between the motor unit and the timing cover (18) Sealing ring (21).
12. The variable compression ratio drive structure according to claim 1, characterized in that: one side of the wave generator (10) is rotatably mounted on the extension end ( 504), the outer ring of the first bearing (14) is interference press-fitted in the wave generator, and the end of the extension end is fixedly connected to limit the first bearing (14) Limiting part of the inner ring.
13. The variable compression ratio drive structure according to claim 12, characterized in that: a notch penetrating the oil passage (502) is constructed at the end of the extension end (504), and the limiting member is One end is fixedly connected to the plug (30) in the recess, and the other end of the plug (30) is blocked on one side of the first bearing (14) due to its radial extension, and An oil hole (k) penetrating through the plug (30) and communicating with the oil passage (502) is provided in the plug (30).
14. The variable compression ratio drive structure according to claim 13, characterized in that: a lubricating oil filter assembly is provided in the oil passage (502) at the end of the extension end (504), and the lubricating oil filter The component includes a filter screen (24) arranged in the recess, and the filter screen (24) is pressed in the recess by the plug (30).
15. The variable compression ratio drive structure according to any one of claims 1 to 14, wherein the engine block (7) is provided with an oil hole (7) penetrating the engine block (7). 19), and the oiling hole (19) penetrates to the inside of the rigid wheel (8) connected to the engine block (7), so as to direct the rigid wheel and (8) the flexible wheel ( 9) Sprinkle lubricating oil between them.
16. An engine, characterized in that the engine comprises the variable compression ratio drive structure according to any one of claims 1-15.
17. A vehicle, characterized in that the vehicle includes the engine of claim 16.

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