CN211737290U - Variable compression ratio drive structure - Google Patents

Abstract

The utility model provides a variable compression ratio drive structure, it is used for ordering about the eccentric shaft rotation in the variable compression ratio mechanism to including setting firmly the harmonic reduction gear unit on the engine cylinder body to and set firmly the motor element on the rigid wheel in the harmonic reduction gear unit, the flexbile gear in the harmonic reduction gear unit is connected with the one end transmission of eccentric shaft, the pivot one end of motor element is overhanging and is connected with the wave generator transmission in the harmonic reduction gear, just the one end that eccentric shaft and flexbile gear link to each other has the extension end that extends to pivot one side, one side of wave generator is rotated and is installed on the extension end of eccentric shaft, the opposite side of wave generator is rotated and is installed in the casing of motor element or slide the butt on the casing of motor element. The utility model discloses a variable compression ratio drive structure can realize the reliable support to the wave generator in the harmonic reduction gear unit, and is favorable to guaranteeing the effective work of whole drive structure.

Description

Variable compression ratio drive structure

Technical Field

The utility model relates to the technical field of engines, in particular to variable compression ratio drive structure.

Background

In order to reduce the engine displacement and improve the fuel combustion efficiency and the fuel economy, the variable compression ratio technology is developed at the same time, and the compression ratio adjusting mode is more and more diversified along with the continuous development of the variable compression ratio technology. The multi-connecting-rod type variable compression ratio mechanism which adopts the matching of the eccentric shaft and the multi-connecting-rod mechanism so as to realize the transmission of the multi-connecting-rod mechanism when driving the eccentric shaft to rotate and further realize the change of the top dead center of the engine piston has become the key point of research and development of many vehicle enterprises.

In the existing multi-link variable compression ratio mechanism, a matching structure of a motor and a harmonic reducer is used as a driving source, and a driving mode for driving an eccentric shaft to rotate is adopted. At present, the transmission mode between motor and the harmonic reducer ware is mostly belt drive among the current structure, or arranges the motor in the side of engine cylinder body to be connected with the harmonic reducer ware transmission. The existing structural form causes the whole width of the engine to be larger, is not beneficial to carrying of the whole vehicle, and in a motor side structure, a motor mounting space is required to be reserved or a motor mounting bracket is required to be processed during cylinder body processing, so that the cylinder body structure is more complex, and the processing difficulty is higher.

In addition, because the flexible gear in the harmonic reducer is a thin-wall part, if the axial play amount of the wave generator is too large in the operation process, the meshing length between the flexible gear and the rigid gear can be influenced, and further the stress of meshing teeth of the flexible gear can be influenced, so that the flexible gear is easy to break, and therefore how to effectively limit the axial play of the wave generator in the design of the driving structure of the variable compression ratio mechanism is also a difficult point in the design.

SUMMERY OF THE UTILITY MODEL

In view of this, the present invention is directed to a variable compression ratio driving structure to support a wave generator in a harmonic reducer and effectively limit axial play thereof.

In order to achieve the above purpose, the technical scheme of the utility model is realized like this:

a variable compression ratio driving structure drives an eccentric shaft in a variable compression ratio mechanism to rotate, and comprises a harmonic reducer unit and a motor unit, wherein the harmonic reducer unit is fixedly arranged on an engine cylinder body, the motor unit is fixedly arranged on a rigid wheel in the harmonic reducer unit, a flexible wheel in the harmonic reducer unit is in transmission connection with one end of the eccentric shaft, one end of a rotating shaft of the motor unit extends outwards and is in transmission connection with a wave generator in the harmonic reducer, an extending end extending towards one side of the rotating shaft is arranged at one end, connected with the flexible wheel, of the eccentric shaft, one side of the wave generator is rotatably arranged on the extending end of the eccentric shaft through a first bearing, and the other side of the wave generator is rotatably arranged in a shell of the motor unit or is in sliding and abutting connection with the shell of the motor unit through a second bearing.

Further, the outer ring of the first bearing is press-fitted into the wave generator in an interference manner, and the inner ring of the first bearing is in clearance fit with the extending end.

Furthermore, the wave generator is rotatably installed in the shell through the second bearing, an outer ring of the second bearing is pressed in the shell in an interference fit mode, and an inner ring of the second bearing is in clearance fit with the wave generator.

Furthermore, the wave generator is in sliding abutting connection with the shell, and a wear-resistant layer is arranged at the position, in sliding abutting connection with the wave generator, of the shell.

Furthermore, a thrust gasket is arranged at the part of the shell, which is in sliding butt joint with the wave generator, the thrust gasket protrudes outwards relative to the shell and is in sliding butt joint with the wave generator, and the wear-resistant layer is arranged on the thrust gasket.

Furthermore, the thrust washer is annular, an embedded groove for embedding the thrust washer is arranged on the shell, the thrust washer and the embedded groove are in transition fit, and an anti-rotation part for limiting the rotation of the thrust washer is arranged between the embedded groove and the thrust washer.

Furthermore, the anti-rotation part comprises an anti-rotation groove arranged on the inner wall of the embedded groove and an anti-rotation block arranged on the thrust gasket and capable of being clamped in the anti-rotation groove.

Further, the first bearings are two bearings arranged side by side.

Furthermore, an oil duct communicated with a lubricating oil path in the engine cylinder body is constructed in the eccentric shaft, the oil duct axially penetrates through the end part of the extending end of the eccentric shaft, a lubricating oil filtering assembly is arranged in the oil duct positioned at the end part of the extending end, an upper oil hole penetrating through the engine cylinder body is formed in the engine cylinder body, and the upper oil hole penetrates through the inner part of the rigid wheel connected with the engine cylinder body so as to downwards spray lubricating oil between the rigid wheel and the flexible wheel.

Furthermore, relative to one side of the flexible gear, which is connected with the eccentric shaft, the other side of the flexible gear is provided with a flexible gear gasket arranged in the flexible gear, the flexible gear is fixedly connected with the eccentric shaft through a connecting piece which is provided with the flexible gear gasket in a penetrating way and the flexible gear, and one end of the eccentric shaft, which is connected with the flexible gear, is rotatably arranged in the rigid gear or the engine cylinder body through a third bearing.

Compared with the prior art, the utility model discloses following advantage has:

the utility model discloses a variable compression ratio drive structure, one side through wave generator is rotated and is installed on the extension of eccentric shaft is served, and the opposite side is rotated and is installed in the casing of electrical unit or slide the butt on electrical unit's casing, from this just can carry on spacingly to the axial both sides of wave generator to can effectually support wave generator, and can restrict wave generator's axial float.

Furthermore, the utility model discloses in rotate the installation through the bearing, simple structure, easily assembly, and when wave generator and casing butt, make first bearing adopt two, also can effectively guarantee the stability that supports wave generator, wearing layer and thrust washer's setting can effectively reduce the friction loss because of sliding the butt and causing simultaneously to improve the durability of structure.

And through the setting of oil duct and oil hole, can effectively lubricate drive structure, can avoid lubricating oil to enter into the motor through the setting of oil blanket, and influence the normal work of motor. Can avoid the flexbile gear to be damaged by the conquassation through the flexbile gear gasket, and through the setting of third bearing, then can radially support the eccentric shaft to reduce its radial runout and protect the flexbile gear.

Drawings

The accompanying drawings, which form a part hereof, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention without undue limitation. In the drawings:

fig. 1 is a schematic structural view of a variable compression ratio mechanism according to an embodiment of the present invention;

fig. 2 is a schematic view of a variable compression ratio driving structure according to an embodiment of the present invention;

FIG. 3 is a schematic illustration of the variable compression ratio drive configuration of FIG. 2 assembled in an engine block;

FIG. 4 is a side view of FIG. 3;

fig. 5 is a schematic view of an offset arrangement of a motor unit according to an embodiment of the present invention;

FIG. 6 is a partial enlarged view of portion A of FIG. 3;

FIG. 7 is a schematic view of a thrust washer according to an embodiment of the present invention;

fig. 8 is a schematic structural diagram of a wave generator according to an embodiment of the present invention in another supporting form;

fig. 9 is a schematic sealing diagram of the motor unit and the timing cover according to the embodiment of the present invention;

fig. 10 is a schematic view of the eccentric shaft preassembly according to the embodiment of the present invention;

fig. 11 is a schematic view of the assembly of the eccentric shaft and the rigid wheel according to the embodiment of the present invention;

fig. 12 is an assembly view of a flexspline according to an embodiment of the present invention;

fig. 13 is a schematic view illustrating the assembly of the eccentric shaft, the rigid gear and the flexible gear in the engine cylinder according to the embodiment of the present invention;

fig. 14 is an assembly view of a wave generator according to the present invention;

FIG. 15 is a schematic view of the timing cover assembly according to an embodiment of the present invention;

description of reference numerals:

1-piston, 2-crankshaft, 3-adjusting connecting rod, 4-executing connecting rod, 5-eccentric shaft, 6-driving connecting rod, 7-engine cylinder, 8-rigid wheel, 9-flexible wheel, 10-wave generator, 11-shell, 12-rotating shaft, 13-gear, 14-first bearing, 15-thrust gasket, 16-flexible wheel gasket, 17-third bearing, 18-timing cover cap, 19-oil feeding hole, 20-oil seal, 21-sealing ring, 22-damping belt pulley, 23-plug terminal, 24-filter screen, 25-oil plug, 26-second bearing, 27-reducer small cover, 28-positioning pin and 29-tooling;

501-eccentric wheel, 502-oil channel, 503-flange part, 504-extension end, 505-connecting hole, 701-positioning pin hole, 1001-inner gear ring, 1101-groove, 1102-embedded groove, 1103-anti-rotation groove and 1501-anti-rotation block.

Detailed Description

It should be noted that, in the present invention, the embodiments and features of the embodiments may be combined with each other without conflict.

The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

The present embodiment relates to a variable compression ratio driving structure, which is generally used as a part of a variable compression ratio mechanism to drive an eccentric shaft in the variable compression ratio mechanism to rotate, thereby realizing adjustment of an engine compression ratio.

In the case of the above variable compression ratio mechanism, which is embodied as a multi-link type variable compression ratio mechanism, and an exemplary structure of the mechanism may be as shown in fig. 1, when the variable compression ratio mechanism is embodied as a piston 1 provided in an engine cylinder, a crankshaft assembly and an eccentric shaft assembly rotating on an engine cylinder 7, and an adjusting link 3 rotatably fitted on a crankshaft 2 in the crankshaft assembly, an actuating link 4 hinged between the piston 1 and one end of the adjusting link 3, and a driving link 6 hinged between an eccentric shaft 5 in the eccentric shaft assembly and the other end of the adjusting link 3, and generally, the driving link 6 is embodied as a eccentric 501 hinged on the eccentric shaft 5.

The variable compression ratio drive structure of the present embodiment is also provided in the engine block 7, and it is used to drive the above-described eccentric shaft 5 to rotate. At this time, during the operation of the engine, based on the control of the engine ECU, the eccentric shaft 5 is driven to rotate by the driving structure, and then the eccentric wheel 501 on the eccentric shaft 5 drives the driving connecting rod 6 to swing, the driving connecting rod 6 swings to change the swing supporting position of itself, and therefore the top dead center position of the piston 1 is also made to be higher or lower by the conduction of the adjusting connecting rod 3 and the executing connecting rod 4, so that the adjustment of the compression ratio of the engine can be realized.

Of course, the variable compression ratio drive structure of the present embodiment may be applied to other variable compression ratio mechanisms employing an eccentric shaft structure, other than the variable compression ratio mechanism shown in fig. 1, and the present embodiment is not limited thereto, as long as the variable compression ratio mechanism can apply the drive structure of the present embodiment and can obtain the intended effects.

In the present embodiment, as shown in fig. 2 to 4, the variable compression ratio drive structure described integrally includes a harmonic reducer unit (X portion) fixed to the engine block 7, and a motor unit (D portion) fixed to a rigid wheel 8 in the harmonic reducer unit. The harmonic reducer unit is still composed of a rigid gear 8, a flexible gear 9 and a wave generator 10 like the existing harmonic reducer structure, and the working principle of the harmonic reducer unit is also consistent with the existing harmonic reducer structure.

Through making the motor unit directly be fixed in on the harmonic speed reducer unit, this embodiment can effectively reduce the size of whole drive structure, makes its compact structure, and does benefit to the arrangement in the engine. One of the points of the present embodiment is that, as will be described in detail later, 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, the other side of the wave generator 10 is rotatably mounted in the housing 11 of the motor unit by the second bearing 26, or the other side of the wave generator 10 is slidably abutted against the housing 11 of the motor unit, thereby realizing reliable support of the wave generator 10 and limiting axial play thereof.

In the harmonic reducer unit of the present embodiment, the rigid gear 8 is fixed to the engine block 7, the flexible gear 9 is in transmission connection with one end of the eccentric shaft 5, one end of the rotating shaft 12 of the motor unit is extended and in transmission connection with the wave generator 10, and the rotating axis of the motor unit is also offset to one side of the rotating axis of the harmonic reducer unit in the present embodiment, so that the motor unit is eccentrically arranged with respect to the harmonic reducer unit. In addition, in the embodiment, the end of the eccentric shaft 5 connected to the flexible gear 9 also has an extending end 504 extending to the side of the rotating shaft 12, the extending end 504 can be specifically referred to as fig. 10 described below, and a shoulder structure is configured on the extending end 504 to perform the following installation of the first bearing 14, and the shoulder is used for limiting the position of the first bearing 14. In the present embodiment, an oil passage 502 communicating with the lubricating oil passage in the engine cylinder 7 is also formed in the eccentric shaft 5, and the oil passage 502 axially penetrates to the end of the extending end 504 of the eccentric shaft 5.

As a preferred embodiment, the present embodiment is directed to the above-described offset arrangement of the motor unit with respect to the harmonic reducer unit, which may be in the height direction of the engine block 7 such that the rotation axis of the motor unit is offset below the rotation axis of the harmonic reducer unit, and particularly, preferentially, as shown in fig. 4, such that 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, the rotational axis of the motor has a distance difference h from the rotational axis of the harmonic reducer unit above the rotational axis.

In the integral structure of the engine, the damping pulley 22 is generally arranged above the harmonic reducer unit, and the engine damping pulley 22 is a flexible part, so that the belt of the gear train is allowed to generate certain amplitude of bounce in the running process in the design requirement. Therefore, by offsetting the motor unit below, it can provide an avoidance space for the bounce of the damping belt pulley 22 and the belt thereon during operation, thereby avoiding the influence on the normal operation of the engine gear train, and by disposing the rotation axis of the motor unit directly below the rotation axis of the harmonic reducer unit, the avoidance effect is optimal at this time.

In the present embodiment, the ring gear 8 of the harmonic reducer unit is fixed to the engine block 7 by bolts, and at the same time, the housing 11 of the motor unit is also fixed to the ring gear 8 by bolts. At this time, the rigid wheel 8 and the housing 11 of the motor unit are also provided with mounting holes for bolts to pass through, and as shown in fig. 5, a two-dot chain line circle e is a connecting line between the mounting holes on the housing 11, and a two-dot chain line circle f is a connecting line between the mounting holes on the rigid wheel 8. Due to the eccentric arrangement of the motor unit, the two-dot chain line circle e intersects with the two-dot chain line circle f instead of being nested, and the housing 11 is also provided with notches at positions corresponding to the mounting holes on the rigid wheel 8 to avoid the mounting holes of the rigid wheel 8, and the notches are larger as they are closer to the intersection of the two-dot chain line circles.

As shown in fig. 2 and 3 in combination with fig. 5, the present embodiment is directed to a transmission connection between a rotating shaft 12 of a motor unit and a wave generator 10, and specifically, an internal gear 1001 is configured in the wave generator 10, a gear 13 is connected to one end of the rotating shaft 12 in transmission connection with the wave generator 10, the gear 13 is located in the wave generator 10, and the gear 13 is also engaged with a part of teeth of the internal gear 1001 to form a meshing connection therebetween. At this time, the teeth of the ring gear 1001 that mesh with the gear 13 are the bottommost portion thereof, matching the eccentric arrangement of the motor unit.

In the present embodiment, through the arrangement of the oil passage 502 in the eccentric shaft 5, lubricating oil can be supplied between the gear 13 and the ring gear 1001, and between the wave generator 10, the flexible gear 9 and other components in the harmonic reducer unit, so as to achieve effective lubrication of each component. At this time, since the extending end 504 of the eccentric shaft 5 is disposed right opposite to the motor unit, and the lubricant oil inevitably contains fine metal impurities, in order to prevent the lubricant oil ejected from the oil passage 502 from entering the motor unit, so that the metal impurities are connected to the solder points on the motor circuit board, and the motor is short-circuited, the embodiment also particularly makes the opening of the oil passage 502 at the end of the extending end 504 and the gear 13 disposed opposite to each other, and the projection of the opening on the gear 13 is also located inside the root circle of the gear 13.

Through 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 root circle of the gear 13, as seen from fig. 2 or 3, that is, the gear 13 is arranged higher than the opening of the oil passage 502, so that the lubricating oil ejected from the opening of the oil passage 502 is blocked by the gear 13 and flows down along the gear 13, and the motor can be protected, and at this time, because the gear 13 is meshed with the teeth at the bottom in the ring gear 1001, the meshing surface between the two is also exactly located on the flow path of the lubricating oil, so that sufficient lubrication can be obtained, and the problems of dry grinding or high-temperature damage and the like caused by insufficient lubrication can be avoided. Of course, in order to further ensure that the lubricating oil does not enter the interior of the motor, the present embodiment may also be provided with an oil seal 20 between the rotating shaft 12 and the housing 11 of the motor unit, as shown in fig. 2 or 3, and the oil seal 20 may be directly made of a commercially available component.

In the actual manufacturing process of the engine, it is sometimes difficult to avoid that the lubricating oil is doped with large metal impurities, in order to avoid the impurities from entering the joint of the gear 13 and the ring gear 1001 from the oil passage 502 and other parts in the harmonic reducer unit, as a preferred embodiment, a lubricating oil filtering assembly for filtering the lubricating oil is also arranged in the oil passage 502 at the end of the extending end 504.

At this time, as an exemplary structure provided for the above-mentioned lubricating oil filtering assembly, as shown in fig. 6, a notch penetrating the oil passage 502 is formed at the end of the extending end 504 on the eccentric shaft 5, and the lubricating oil filtering assembly specifically includes a strainer 24 disposed in the notch, the strainer 24 is pressed in the notch by an oil plug 25 fixedly disposed in the notch, and an oil hole k penetrating itself and having one end communicating with the oil passage 502 is also disposed in the oil plug 25.

It should be noted that, in this embodiment, since the amount of lubricating oil required between the gear 13 and the ring gear 1001, and the flexspline 9, the wave generator 10 and other related components in the harmonic reducer unit is small in use, the diameter of the oil hole k in the oil plug 25 can be designed to be small, so that the lubricating oil can be restricted to ensure the oil pressure in the eccentric shaft 5. In addition, the oil plug 25 can be press-fitted or screwed into a notch at the end of the eccentric shaft 5, and the oil plug 25 can be made of a simpler cylindrical steel block. In the present embodiment, the oil plug 25 is formed by modifying a socket head cap screw, which flattens the tapered end of the screw and drills an oil hole k therein.

It should be noted that the oil plug 25 used in the present embodiment is configured such that the hexagonal socket hole in the oil plug 25 and the oil hole k in the oil plug 25 are communicated with each other to substantially form a part of the oil hole k, but since the hexagonal socket hole has a larger inner diameter than the oil hole k, the lubricating oil discharged from the oil hole k in actual use flows only through the hexagonal socket hole.

By arranging the oil passage 502 in the eccentric shaft 5 and the gear 13 opposite to the opening of the oil passage 502, the lubricating oil from the eccentric shaft 5 of the present embodiment firstly enters the joint of the gear 13 and the inner gear ring 1001, then enters the meshing position of the flexible gear 9 and the rigid gear 8 through the wave generator 10, and finally flows into the oil pan of the engine through the third bearing 17 at the rear end, which will be mentioned later. The lubrication path can meet the lubrication requirements of the gear 13, the inner gear ring 1001, the wave generator 10, the flexible gear 9, the rigid gear 7 and the third bearing 17.

However, as can be seen from fig. 2 or fig. 3, the above-mentioned lubrication path is mainly located below the horizontal plane of the oil passage 502, and since the flexible gear 9 drives the eccentric shaft 5 to rotate only in a certain angle range, and not in a complete rotation, the lubrication range is always fixed in the rotation range of the flexible gear 9, so that poor lubrication is likely to occur in some of the meshing teeth of the flexible gear 9 and the rigid gear 8. In order to avoid such poor lubrication, in a preferred embodiment, in addition to the oil supply of the oil passage 502, the engine block 7 is also provided with an oil applying hole 19 penetrating through the engine block 7, and the oil applying hole 19 penetrates into the inside of the rigid wheel 8 connected to the engine block 7, so that the circulating lubricating oil at the cylinder head, the tensioner or other mechanisms inside the timing cover 18 can be poured down between the rigid wheel and the flexspline 8 9, thereby ensuring the lubricating effect between the flexspline 9 and the rigid spline 8.

In order to prevent larger metal impurities in the lubricating oil, which are difficult to avoid, from entering the meshing portion between the flexible gear 9 and the rigid gear 8, a lubricating oil filtering structure may be provided in the upper oil hole 19, and the structure may be, for example, a strainer fitted into the upper oil hole 19. Furthermore, the upper oil port 19 is preferably arranged with its axial direction perpendicular to the horizontal direction of the engine, although it may be arranged at an angle to the horizontal plane of the engine other than perpendicular.

In the embodiment, the wave generator 10 is of an elliptical structure, radial force cannot be borne in the movement process, the flexible gear 9 is a thin-wall part, when the wave generator 10 is installed in the flexible gear 9, the shape of the flexible gear 9 changes along with the rotation of the wave generator 10, and the shape of the flexible gear 9 is directly determined by the wave generator 10 when meshing teeth on the flexible gear 9 are meshed with the rigid gear 8. If the axial play of the wave generator 10 is too large, the meshing length between the flexible gear 9 and the rigid gear 8 is affected, the force applied to the teeth is directly affected, and even the teeth breaking phenomenon is caused in severe cases, so that the axial play of the wave generator 10 needs to be limited within an allowable range.

Based on the above, the present embodiment is thus provided on the installation of the wave generator 10, as an alternative, as shown in fig. 2 and 3, one side of the wave generator 10 is rotatably installed on the extension end 504 of the eccentric shaft 5 by the first bearing 14, and the first bearings 14 are also two arranged side by side, and are in clearance fit with the extension end 504 and in interference fit with the wave generator 10. At the same time, the other side of the wave generator 10 is in sliding contact with the housing 11 of the motor unit, and in order to reduce friction loss, a wear-resistant layer is also provided at a portion of the housing 11 in sliding contact with the wave generator 10.

The two rows of the first bearings 14 are adopted in the embodiment, so that one-point support can be changed into two-point support in the axial direction, the support is firmer, and the running stability of the wave generator 10 after installation can be ensured. As for the sliding abutment between the wave generator 10 and the housing 11, it may be such that the wave generator 10 is in direct abutment with the housing 11 and the wear-resistant layer is provided directly on the housing 11 in the relevant place. However, since the housing 11 of the motor unit is made of an aluminum material for the end cover portion, the housing is poor in high temperature resistance and wear resistance, and is likely to be ablated at high temperature, and the friction loss is also large.

As a preferable arrangement when the housing 11 and the wave generator 10 are in sliding contact, this embodiment is combined with that shown in fig. 7, specifically, a thrust washer 15 is provided at a position of the housing 11 in sliding contact with the wave generator 10, the thrust washer 15 protrudes outward relative to the housing 11 so as to be in sliding contact with the wave generator 10, and the wear-resistant layer is also provided on the thrust washer 15.

In this embodiment, as an exemplary structure of the thrust washer 15, the thrust washer 15 is annular, and the housing 11 is provided with an insertion groove 1102 for inserting the thrust washer 15. The thrust washer 15 is mounted on the housing 11 by transition fit with the fit-in groove 1102, and a rotation prevention portion for restricting rotation of the thrust washer 15 is also provided between the fit-in groove 1102 and the thrust washer 15. The anti-rotation part specifically includes an anti-rotation groove 1103 disposed on the inner wall of the embedded groove 1102, and an anti-rotation block 1501 disposed on the thrust washer 15 and capable of being clamped in the anti-rotation groove 1103.

Of course, the thrust washer 15 of the present embodiment may have other conventional configurations in addition to the annular thrust washer 15 and its corresponding arrangement described above. Furthermore, it is also possible for the wear-resistant layer provided to be, for example, a wear-resistant alloy layer and the corresponding thrust washer 15 to be made of a steel material as a backing material, or for the thrust washer 15 to be made of another base material and the wear-resistant layer to be provided as a wear-resistant coating.

In addition to the above-described arrangement of the wave generator 10 with one side rotatably mounted by the first bearing 14 and the other side slidably abutting, it should be noted that, as another possible arrangement of the wave generator 10, it is also possible to have one side of the wave generator 10 rotatably mounted on the extension end 504 of the eccentric shaft 5 by means of the first bearing 14 and the other side of the wave generator 10 rotatably mounted in the housing 11 of the motor unit by means of the second bearing 26, as shown in fig. 8.

At this time, only one first bearing 14 is used, and the first bearing 14 is still in interference fit with the wave generator 10, and is still in clearance fit with the extending end 504 of the eccentric shaft 5, and the second bearing 26 on the other side is in clearance fit with the wave generator 10, and is in interference fit with the housing 11 of the motor unit. The present embodiment, by the above-described manner in which both sides are rotatably mounted via bearings, of course, also enables reliable arrangement of the wave generator 10 to limit the amount of axial play of the wave generator 10.

In addition, in the present embodiment, the arrangement of the two wave generators 10 is adopted, the extending end 504 is only arranged at the end of the eccentric shaft 5, and the extending end 504 forms a supporting end for supporting the wave generator 10, compared with the direct supporting mode in which a supporting structure is assembled on the eccentric shaft 5, and then the indirect supporting mode in which the wave generator 10 is assembled is performed, so that the first-stage assembly error can be reduced, and the coaxiality of the extending end 504 and the excircle of the main journal of the eccentric shaft 5 in the assembling process can be effectively ensured, and the transmission precision and reliability of the wave generator 10 are further improved.

In the present embodiment, as also shown in fig. 10, which will be described later, for the connection between the flexspline 9 and the eccentric shaft 5, a radially outwardly protruding flange portion 503 is also formed at the end of the eccentric shaft 5 having the extension end 504, as in the case of the flange attached to the eccentric shaft 5, so that the flange portion 503 is called, and the extension end 504 is also attached to the flange portion 503 and is integrated with the rest of the eccentric shaft 5.

A plurality of connecting holes 505 are provided in the flange 503, wherein the connecting holes 505 are arranged in a ring shape, the connecting holes 505 can be threaded holes, for example, in general, and the flexible wheel 9 can be fastened to the flange 503 by bolts. At this time, since the flexible gear 9 is a thin-walled member, in order to avoid the flexible gear 9 from being damaged by screwing a bolt, in this embodiment, as a preferred implementation form, a flexible gear pad 16 located in the flexible gear 9 may be disposed on the other side of the flexible gear 9 relative to the side of the flexible gear 9 connected to the eccentric shaft 5, the flexible gear 9 is fixedly connected to the eccentric shaft 5 through a connecting member penetrating through the flexible gear pad 16 and the flexible gear 9, and the connecting member here is generally also the bolt.

Meanwhile, regarding the flexible gear pad 16, as an exemplary structure adopted in the present embodiment, the end faces of the two opposite ends are also different in size, so that the outer peripheral surface of the flexible gear pad 16 is similar to a cone, and when in use, the end face with the smaller cross section of the flexible gear pad 16 is attached to the flexible gear 9, thereby facilitating the installation of the flexible gear pad 16 in the flexible gear 9. It should be noted that, instead of using bolts, it is also possible to replace the bolts with rivets or directly weld the flexspline 9 to the flange portion 503 in this embodiment, and when using the welding method, the flexspline 16 may be omitted.

In this embodiment, from the viewpoint of preventing the flexible gear 9 from being deformed too much in the radial direction to protect the flexible gear, a third bearing 17 is also provided at the end of the eccentric shaft 5 connected to the flexible gear 9, so that the eccentric shaft 5 is rotatably mounted in the rigid gear 8 through the third bearing 17. At this time, the radial support of the eccentric shaft 5 by the third bearing 17 can limit the radial runout generated during the cylinder explosion transmitted by the multi-link mechanism borne by the eccentric shaft 5, thereby preventing the flexspline 9 from generating large radial runout due to the driving of the eccentric shaft 5.

It should be noted that, in addition to the third bearing 17 being attached to the ring gear 8, the third bearing 17 may be attached to the engine block 7 in the present embodiment, as a matter of course, in accordance with the dimensional design of the ring gear 8 of the harmonic reducer unit.

In addition, as shown in fig. 2 and fig. 9, the timing cover 18 covering the harmonic reducer unit is attached to the engine block 7, and the motor unit is attached to the rigid wheel 8 across the timing cover 18, and a seal ring 21 is interposed between the housing 11 of the motor unit and the timing cover 18. As shown in fig. 7, a groove 1101 is provided on the outer peripheral wall of the housing 11 of the motor unit, the sealing rings 21 are installed in the groove 1101, and to improve the sealing effect, the sealing rings 21 may be preferably two side by side.

The present embodiment is configured such that the motor unit is connected to the ring gear 8 through the timing cover 18, and a seal structure that seals the fastening bolt of the ring gear 8, the joint surface of the ring gear 8 and the case 11 within the timing cover 18 is provided between the case 11 and the timing cover 18. Therefore, the timing cover 18, the engine cylinder body 7 and the oil pan therein can form a closed space, and the joint surface and the bolt hole which are contacted with lubricating oil are all subjected to oil leakage risk, so that the joint surface of the motor unit and the harmonic reducer unit and the fastening bolt of the harmonic reducer unit can be sealed in the engine cylinder body 7 by arranging the end cover part of the shell 11 in the motor unit and the whole harmonic reducer unit in the closed space, so that the sealing requirements can be reduced or even eliminated, the number of sealing belts can be effectively reduced, the assembly is simplified, and the cost is reduced.

Lubricating oil directly flows into the oil pan after passing through the mounting hole in the rigid wheel 8 in the lubricating process, and the lubricating oil in the harmonic reducer unit cavity also leaks into the oil pan through the joint surface of the shell 11 and the rigid wheel 8, so that the lubricating oil circulation is completed without leakage.

In the present embodiment, the method for assembling the driving structure includes the following steps based on the above-described configuration.

First, the strainer 24 is fixed in the eccentric shaft 5 by the oil plug 25 as shown in fig. 10, but this step can be omitted if the oil strainer assembly is not provided. Then, as shown in fig. 11, the third bearing 17 is press-fitted into the stepped hole of the rigid wheel 8, and the end of the eccentric shaft 5 having the extended end 504 is rotatably mounted in the rigid wheel 8 by passing through the inner ring of the third bearing 17. Next, as shown in fig. 12, the flexible gear 9 is installed in the rigid gear 8, so that the flexible gear 9 is in transmission fit with the rigid gear 8, and the flexible gear 9 is sleeved on the extension end 504 to be attached to the end face of the flange part 503 on the eccentric shaft 5, and then is fixedly connected to the flange part 503 on the eccentric shaft 5 through the flexible gear spacer 16 by bolts.

Then, the engine block 7 is turned 180 ° so that the bottom surface faces upward, the connected rigid ring 8, eccentric shaft 5, and flexspline 9 are fitted into the engine block 7 as shown in fig. 13, and the rigid ring 8 is preliminarily fixed to the engine block 7 by tightening the connecting bolts of the rigid ring 8. Next, the reduction gear small cover 27 is attached to the engine block 7 so as to sandwich the rigid wheel 8 between the reduction gear small cover 27 and the engine block 7, and the rigid wheel 8 and the connection between the reduction gear small cover 27 and the engine block 7 are fastened so that the rigid wheel 8 is fixed in the engine block 7.

Then, the first bearing 14 is press-fitted into the wave generator 10 with interference, and the extending end 504 of the eccentric shaft 5 is inserted from the inner ring of the first bearing 14, whereby the wave generator 10 is rotatably mounted on the extending end 504 of the eccentric shaft 5 via the first bearing 14, and the wave generator 10 is pressed into the flexible gear 9 to be in driving engagement with the flexible gear 9. At this time, when the wave generator 10 is pressed into the flexible spline 9, the wave generator 10 may be rotated into the flexible spline 9 at a constant rotational speed by using a tool 29 having one end fitted into the wave generator 10 as shown in fig. 14, so as to facilitate the pressing of the wave generator 10.

Next, as shown in fig. 15, the timing cover 18 is mounted on the engine block 7, the timing cover 18 is pre-tightened to cover the harmonic reducer unit in the engine block 7, the motor unit is inserted through the timing cover 18 to connect the housing 11 to the rigid wheel 8, and the housing 11 and the timing cover 18 are tightened again, and at this time, the seal ring 21 is sealed between the housing 11 and the timing cover 18 with the insertion of the housing 11, and the connection terminal 23 in the motor unit is located outside the timing cover 18.

The support of the wave generator 10 by the housing 1 is carried out before the installation of the motor unit, depending on the design choice, by means of the thrust washer 15 or the second bearing 26, and the wave generator 10 is brought into contact with the thrust washer 15 as the motor unit is inserted, or the wave generator 10 is inserted into the second bearing 26, it being noted that, if the thrust washer 15 is chosen, the first bearings 14 on the other side are arranged in two side by side arrangement, as described above.

In addition, after the motor unit is inserted into the timing cover 18, the motor unit is also rotated to adjust the angle thereof, so that the axis of the motor unit is positioned right below the axis of the harmonic reducer unit, and the opening of the upper plug-in terminal 23 of the motor unit is horizontally directed to the air intake side relative to the engine block. Therefore, the part of the gear 13 on the motor unit, which is engaged with the internal gear 1001 in the wave generator 10, is located at the lowest position vertically below and on the flow path of the lubricating oil, and the opening of the plug terminal 23 faces the air inlet side, so that the plugging and unplugging of the interface can be facilitated.

In addition, in order to facilitate the installation of the retarder small cover 27 in the engine block 7, the present embodiment may preferably also provide a positioning portion between the engine block 7 and the retarder small cover 27 to preposition the installation of the retarder small cover 27. The positioning portion may be, for example, a positioning pin hole 701 provided in each of the engine block 7 and the reducer small cover 27, and a positioning pin 28 having two ends inserted into the two positioning pin holes 701, or the positioning portion may also adopt other existing conventional positioning structures.

The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. A variable compression ratio drive structure to drive rotation of an eccentric shaft (5) in a variable compression ratio mechanism, characterized in that: the variable compression ratio driving structure comprises a harmonic reducer unit fixedly arranged on an engine cylinder body (7), and a motor unit fixedly arranged on a rigid wheel (8) in the harmonic reducer unit, wherein a flexible wheel (9) in the harmonic reducer unit is in transmission connection with one end of the eccentric shaft (5), one end of a rotating shaft (12) of the motor unit extends outwards and is in transmission connection with a wave generator (10) in the harmonic reducer, and one end of the eccentric shaft (5) connected with the flexible gear (9) is provided with an extension end (504) extending towards one side of the rotating shaft (12), one side of the wave generator (10) is rotatably mounted on the extension end (504) of the eccentric shaft (5) by a first bearing (14), the other side of the wave generator (10) is rotatably arranged in the shell (11) of the motor unit or is in sliding contact with the shell (11) of the motor unit through a second bearing (26).

2. The variable compression ratio drive structure according to claim 1, characterized in that: the outer ring of the first bearing (14) is press-mounted in the wave generator (10) in an interference mode, and the inner ring of the first bearing (14) is in clearance fit with the extending end (504).

3. The variable compression ratio drive structure according to claim 2, characterized in that: the wave generator (10) is rotatably installed in the shell (11) through the second bearing (26), the second bearing (26) is pressed in the shell (11) in an interference fit mode, and an inner ring of the second bearing (26) is in clearance fit with the wave generator (10).

4. The variable compression ratio drive structure according to claim 2, characterized in that: the wave generator (10) is in sliding abutting joint with the shell (11), and a wear-resistant layer is arranged on the part, in sliding abutting joint with the wave generator (10), of the shell (11).

5. The variable compression ratio drive structure according to claim 4, characterized in that: and a thrust washer (15) is arranged at the part of the shell (11) which is in sliding contact with the wave generator (10), the thrust washer (15) protrudes outwards relative to the shell (11) and is in sliding contact with the wave generator (10), and the wear-resistant layer is positioned on the thrust washer (15).

6. The variable compression ratio drive structure according to claim 5, characterized in that: the thrust washer (15) is annular, an embedded groove (1102) for embedding the thrust washer (15) is formed in the shell (11), the thrust washer (15) and the embedded groove (1102) are in transition fit, and an anti-rotation part for limiting the rotation of the thrust washer (15) is arranged between the embedded groove (1102) and the thrust washer (15).

7. The variable compression ratio drive structure according to claim 6, characterized in that: the anti-rotation part comprises an anti-rotation groove (1103) arranged on the inner wall of the embedded groove (1102) and an anti-rotation block (1501) arranged on the thrust washer (15) and capable of being clamped in the anti-rotation groove (1103).

8. The variable compression ratio drive structure according to claim 4, characterized in that: the first bearings (14) are two arranged side by side.

9. The variable compression ratio drive structure according to claim 1, characterized in that: an oil duct (502) communicated with a lubricating oil path in the engine cylinder body (7) is constructed in the eccentric shaft (5), the oil duct (502) axially penetrates through the end part of an extending end (504) of the eccentric shaft (5), a lubricating oil filtering assembly is arranged in the oil duct (502) positioned at the end part of the extending end (504), an upper oil hole (19) penetrating through the engine cylinder body (7) is formed in the engine cylinder body (7), and the upper oil hole (19) penetrates through the inner part of the rigid gear (8) connected with the engine cylinder body (7) so as to downwards spray lubricating oil between the rigid gear (8) and the flexible gear (9).

10. The variable compression ratio drive structure according to any one of claims 1 to 9, characterized in that: and relative to one side of the flexible gear (9) connected with the eccentric shaft (5), the other side of the flexible gear (9) is provided with a flexible gear gasket (16) arranged in the flexible gear (9), the flexible gear (9) is fixedly connected with the eccentric shaft (5) through a connecting piece penetrating through the flexible gear gasket (16) and the flexible gear (9), and one end of the eccentric shaft (5) connected with the flexible gear (9) is rotatably arranged in the rigid gear (8) or the engine cylinder body (7) through a third bearing (17).

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