CN211737223U - Shifting fork transmission unit and variable-section turbocharger VGT assembly - Google Patents

Abstract

The utility model provides a shift fork drive unit and variable cross section turbo charger VGT subassembly, the utility model discloses a shift fork drive unit is used for accepting outside rotary driving power and drives the dial in the VGT subassembly and rotate, shift fork drive unit includes that one end is constructed the shift fork in shift fork groove, and links firmly and stretches into with the dial regulating pin in the shift fork groove, and for the shift fork groove is connected in the rocking arm axle of the shift fork other end, and the regulating pin has the regulating pin main part, regulating pin main part one end with the shift fork links firmly, the other end stretches into in the shift fork groove to the wearing layer has been constructed on stretching into the outer peripheral face of the regulating pin main part in the shift fork groove. The utility model discloses a construct integrated into one piece's wearing layer on stretching into the outer peripheral face of the adjusting pin main part in the declutch shift groove, not only can improve the wearability of adjusting pin, and also can reduce the manufacturing cost of adjusting pin.

Description

Shifting fork transmission unit and variable-section turbocharger VGT assembly

Technical Field

The utility model relates to an engine turbocharging technical field, in particular to shift fork drive unit, the utility model discloses also relate to variable cross section turbo charger VGT subassembly that has above-mentioned shift fork drive unit simultaneously.

Background

With the development of technology, the requirements of people on the performance of automobile engines are more and more demanding, and the automobile engines are required to have strong power, higher efficiency and clean emission. People's requirements for engine performance require that the engine can achieve a relatively efficient working state under various working conditions, and in order to achieve an efficient working state under various working conditions, the air intake requirements of the engine under various working states must be met.

In order to meet the air intake requirement of the engine, it is desired to make the air intake amount of the engine variable through related designs so as to meet the air intake requirement under different working conditions, for example, the well-known variable valve timing/lift technology, variable intake manifold technology and the like are developed based on the air intake requirement, and in addition, the VGT variable section turbocharging technology which is more common on diesel engines also belongs to the design.

VGT (variable Geometry turbocharger) variable cross-section turbocharging technology can solve the turbo lag of a supercharger, can ensure that a turbocharged engine can ensure good supercharging effect at high and low rotating speeds, and has been widely applied to the field of diesel engines. Because the exhaust temperature of the gasoline engine can reach about 1000 ℃, which is far higher than the exhaust temperature of the diesel engine about 600 ℃, the hardware material used by the current VGT is difficult to bear the high-temperature environment, so the technology can not be applied to the gasoline engine in time.

In recent years, it has been reported that a boggewarina and time saver strapdown have developed a gasoline engine equipped with a variable cross-section turbocharger by using a high-temperature resistant aircraft material, and this technology is called vtg (variable turbine geometry) variable turbine blade technology in time saver, but is still a VGT variable cross-section turbocharger technology in essence.

With the advent of the above VTG variable turbine vane technology, various vehicle companies have started developing their own VGT variable-section turbochargers, and vehicle models to which VGT variable-section turbochargers are applied have come out. In the prior VGT variable cross section turbocharger, a VGT component in the VGT variable cross section turbocharger, namely, a component structure for adjusting the exhaust gas inlet cross section of the turbocharger, an adjusting pin is fixedly connected to a toggle plate and used for bearing the driving of the toggle plate so as to enable the toggle plate to rotate.

The currently applied adjusting pin is generally formed by a bar machining mode, the hardness of an external material is high, a cutter is seriously abraded in the machining process, so that the manufacturing cost is higher, in order to reduce the cutter abrasion, some manufacturers choose to machine the adjusting pin by using heat-resistant steel with low hardness, and then carry out nitriding treatment to improve the surface hardness and the wear resistance, but the nitriding process cannot keep normal wear resistance at the high temperature of 600 ℃.

SUMMERY OF THE UTILITY MODEL

In view of this, the present invention is directed to a shift fork transmission unit, which can improve the wear resistance of the adjusting pin and reduce the manufacturing cost thereof.

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

the utility model provides a shift fork drive unit for in variable cross section turbo charger's VGT subassembly, in order to accept outside rotary driving power and drive dial in the VGT subassembly rotates, shift fork drive unit includes that one end is constructed the shift fork in shift fork groove, with the shift fork is solid and stretch into the regulating pin in the shift fork groove, and for the shift fork groove, connect in the shift fork other end in order to accept the rocking arm axle of outside rotary driving power, just the regulating pin has the regulating pin main part, regulating pin main part one end with the shift fork links firmly, the other end stretches into in the shift fork groove, and in stretching into in the shift fork groove construct on the outer peripheral face of regulating pin main part with regulating pin main part integrated into one piece's wearing layer.

Further, the thickness of the wear-resistant layer is not less than 0.15 mm.

Furthermore, a convex ring which is radially convex and is connected with the wear-resistant layer is formed on the outer peripheral side of the adjusting pin main body.

Further, the adjusting pin is formed by metal powder injection molding.

Furthermore, the adjusting pin main body is made of heat-resistant steel, and the wear-resistant layer is made of wear-resistant alloy.

Furthermore, relative to the shifting fork groove, a through hole is formed at the other end of the shifting fork, and the rocker shaft is inserted and fixedly connected in the through hole.

Furthermore, step parts which are oppositely arranged are formed on the shifting forks on two opposite sides of the shifting fork groove, and the part of the adjusting pin which extends into the shifting fork groove is not higher than the step parts.

Furthermore, two opposite outer side end faces of the shifting fork, which are provided with one end of the shifting fork groove, are arranged in a protruding mode, and each protruding outer side end face is composed of a middle plane located in the middle and arc faces connected to two sides of the middle plane respectively.

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

the utility model discloses a shift fork drive unit constructs integrated into one piece's wearing layer through on the outer peripheral face of the adjusting pin main part that stretches into in the declutch shift groove, not only utilizes the setting of wearing layer to improve the wearability of adjusting pin from this, and except the wearing layer, the adjusting pin main part in the adjusting pin then still can adopt the lower material of hardness simultaneously to with this manufacturing cost that also can reduce the adjusting pin.

Furthermore, the utility model discloses the thickness setting of well wearing layer can guarantee that the adjusting pin has stable wear resistance, and the setting of bulge loop then can do benefit to the fixing of adjusting pin on the dial, and the adjusting pin adopts metal powder injection moulding, then can do benefit to its preparation. Meanwhile, the rocker shaft is fixedly connected with the shifting fork through the through hole, the structure is simple, the design and the connection are easy, the step parts are arranged on the two sides of the shifting fork groove, the abrasion between the adjusting pin and the inner wall of the shifting fork groove can be reduced, and the two sides of the shifting fork are respectively composed of a plane and arc surfaces on the two sides, so that the material consumption of the shifting fork can be reduced, and the cost can be reduced.

Another object of the utility model is to provide a variable cross section turbo charger VGT subassembly for among the variable cross section turbo charger, just:

the VGT component comprises a mounting disc and a rear cover which are oppositely arranged, a poking disc which is rotatably arranged on the mounting disc, a roller which is fixedly connected to the mounting disc and partially arranged on one side of the poking disc in a blocking manner, and a distance sleeve which is fixedly connected to the mounting disc and/or the rear cover, wherein the distance sleeve is supported between the mounting disc and the rear cover, and the distance sleeve and the roller are a plurality of rollers which are arranged along the circumferential direction of the poking disc at intervals;

the VGT subassembly still includes as before the shift fork transmission unit, and follows a plurality of blade units of dial dish circumference interval arrangement, blade unit has and is located the mounting disc with the blade between the back lid, and through the blade axle with the driving lever that the blade links to each other, just the driving lever with the dial dish transmission links to each other, and accepts the rotation of dial dish is ordered about.

Furthermore, the shifting rod is in transmission connection with the shifting disc through a bulge formed at one end of the shifting rod.

The VGT subassembly of this embodiment can improve the wearability of adjusting pin in the subassembly through adopting aforementioned shift fork drive unit to it also is favorable to reducing the manufacturing cost of adjusting pin, and has fine practicality.

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 partial schematic view of a VGT assembly according to an embodiment of the present invention;

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;

fig. 3 is another partial schematic view of a VGT assembly according to an embodiment of the invention;

FIG. 4 is a cross-sectional view taken along line B-B of FIG. 3;

fig. 5 is a schematic structural diagram of a shift lever according to an embodiment of the present invention;

fig. 6 is a schematic structural diagram (with a relief groove) of the shift lever according to the embodiment of the present invention;

FIG. 7 is a front view of the toggle lever shown in FIG. 5;

fig. 8 is a schematic structural diagram of a blade according to an embodiment of the present invention (using a blade shaft);

fig. 9 is a schematic structural diagram (with a material reducing hole) of the shift lever according to the embodiment of the present invention;

FIG. 10 is a schematic view of the shifter lever shown in FIG. 9 at another angle;

fig. 11 is a schematic structural diagram of a blade according to an embodiment of the present invention (using a connecting shaft);

fig. 12 is a partial enlarged view of portion C of fig. 11;

FIG. 13 is a schematic view of the lever (using a fork shaft) adapted to the blade of FIG. 11;

FIG. 14 is a partial schematic view of a VGT assembly employing the vanes of FIG. 11 and the lever of FIG. 12;

FIG. 15 is a cross-sectional view taken in the direction D-D of FIG. 14;

fig. 16 is a schematic structural view of an adjusting pin according to an embodiment of the present invention;

fig. 17 is a schematic structural view of a shifting fork according to an embodiment of the present invention;

fig. 18 is a schematic view illustrating an arrangement of rollers according to an embodiment of the present invention;

fig. 19 is a schematic structural view of a mounting hole on a mounting plate according to an embodiment of the present invention;

fig. 20 is a schematic structural view of a roller according to an embodiment of the present invention;

fig. 21 is a schematic diagram of the arrangement of the VGT assembly in the supercharger according to the embodiment of the present invention;

fig. 22 is a partial enlarged view of portion E of fig. 21;

description of reference numerals:

1-mounting plate, 2-poking plate, 3-poking rod, 4-adjusting pin, 5-shifting fork, 6-distance sleeve, 7-rocker shaft, 8-blade, 9-roller, 10-rear cover, 11-volute, 12-elastic pad, 13-turbine, 14-heat shield, 15-positioning pin, 16-bolt, 17-middle shell, 18-sealing ring, 19-sealing ring;

101-mounting hole, 102-mounting ring, 103-external convex part, 1011-small diameter hole section and 1012-large diameter hole section;

300-deflector rod main body, 301-bulge, 302-through hole, 303-material reduction groove, 304-top plane, 305-end plane, 306-material reduction hole, 307-deflector rod shaft body, 308-connecting hole, 3011-boss, 3012-curved surface and 3013-arc surface;

401-adjusting pin body, 402-wear layer, 4011-convex ring;

501-through hole, 502-shifting fork groove, 503-step part, 504-middle plane and 505-arc surface;

800-vane body, 801-vane shaft, 802-connecting shaft body, 803-bump;

901-head, 902-bulge, 903-press-in end, 9031-large diameter shaft section, 9032-small diameter shaft section.

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 fork transmission unit used in a VGT assembly of a variable-section turbocharger, and meanwhile, the present embodiment also further relates to a VGT assembly of a variable-section turbocharger having the fork transmission unit, in order to describe the structure of the fork transmission unit of the present embodiment and the arrangement of the fork transmission unit in the VGT assembly and even the variable-section turbocharger, the fork transmission unit of the present embodiment will be specifically described in the following description in the process of describing the structure of the integral VGT assembly and the arrangement form of the assembly in the turbocharger.

Before describing the structure of the integral VGT assembly and the arrangement form thereof in the supercharger, it is to be stated that, for the shift transmission unit of the present embodiment, it is undeniably applicable to a VGT assembly as described below, but of course, the shift transmission unit can also be applied to a VGT assembly of a variable cross-section turbocharger having other structure forms, and the present embodiment is not limited thereto, as long as the shift transmission unit of the present embodiment can be provided in the VGT assembly, and the intended use effect can also be obtained.

In the embodiment, regarding the variable cross section turbocharger with VGT assembly, the turbocharger can be like other superchargers of the same type which are applied at present, when the engine runs at low speed, the adjusting vanes reduce the sectional area of the nozzle ring formed by each vane, the turbine speed rises, the boost pressure increases, the boost pressure and the air intake amount at low speed are ensured, when the engine runs at high speed, the adjusting vanes increase the sectional area of the nozzle ring, the turbine speed drops, the supercharger is prevented from overspeed, when the engine accelerates, the adjusting vanes reduce the sectional area of the nozzle ring, the supercharger speed is increased, the boost pressure and the air intake amount are increased, the response speed of the supercharger is increased, and the air intake requirement at transient operation is met.

The variable-section turbocharger of the present embodiment includes a housing, a turbine 13 rotatably disposed in the housing, and a VGT assembly and the like disposed in the housing, wherein the VGT assembly is used to adjust a flow section of exhaust gas flowing to the turbine 13, that is, a sectional area of the nozzle ring, thereby realizing a variable section of the turbocharger.

Since the main inventive point of the supercharger of the present embodiment is the VGT assembly, and the corresponding arrangement of the VGT assembly in the supercharger, only the VGT assembly and its arrangement in the supercharger will be described herein. Except for the VGT assembly and the related content of the arrangement thereof described below, for other structures in the variable-section turbocharger, reference may be directly made to the conventional variable-section turbocharger similar to the present embodiment, and the details thereof will not be described herein.

The VGT assembly of the present embodiment, which is disposed in the housing of the supercharger and shown in fig. 1 to 4, integrally comprises a mounting plate 1, a toggle plate 2, a toggle lever 3, an adjusting pin 4, a shift fork 5, a distance sleeve 6, a rocker shaft 7, a vane 8, a roller 9 and a rear cover 10.

Wherein, mounting disc 1 and back lid 10 constitute the structure basis of VGT subassembly, dial driving disk 2 and rotate and locate on mounting disc 1, and dial 2 and back lid 10 lie in the double-phase offside of mounting disc 1 respectively, and driving lever 3 has constituteed with blade 8 and has accepted dial driving disk 2 and has rotated and orders about to finally realize the changeable blade unit in cross-section, adjusting pin 4, shift fork 5 and rocking arm shaft 7 then have constituteed and have been used for accepting outside rotary drive power, and drive dial driving disk 2 pivoted shift fork drive unit.

Distance cover 6 is for setting up on mounting disc 1 and/or back lid 10 to the butt is between mounting disc 1 and back lid 10, and as an exemplary configuration in this embodiment, distance cover 6 specifically is that one end links firmly on mounting disc 1, and the other end and back lid 10 butt to be used for injecing the space of carrying out the blade 8 and arranging between mounting disc 1 and the back lid 10. And the roller 9 is fixedly connected to the mounting disc 1 and is used for axially limiting the mounting disc 2 after being mounted on the mounting disc 1.

In this embodiment, the above vane units, the distance sleeve 6 and the roller 9 are all multiple groups or multiple groups arranged at intervals along the circumferential direction of the mounting disc 1 or the toggle disc 2, and as for the specific arrangement number of each component, the specific arrangement number can be selected according to the overall design requirement of the supercharger in actual implementation, as long as the specific arrangement number is consistent with the structure and the arrangement principle described herein. Further, as for the external rotational driving force to be transmitted to the shift fork 5 via the rocker shaft 7, the rotational driving force is generally provided by an actuator fixed to the engine corresponding to the supercharger, and the actuator may employ, for example, a stepping motor having a high rotational control accuracy.

This embodiment is based on engine controller's control signal, actuator output rotary driving power, and this outside rotary driving power is accepted to shift fork drive unit and is made 2 rotations of dial plate, and the transmission of 3 is passed through again to the rotation of dial plate 2, finally drives blade 8 and rotates to through the rotation angle of adjusting each blade 8, just can realize the change of nozzle ring sectional area, and then adjustment turbo charger working property.

The following detailed description will be made with reference to the accompanying drawings for the relevant parts of the VGT assembly, and it should be noted that, for each component in the present embodiment, the following description is a preferred embodiment of the structure and specific arrangement thereof, and besides the structure and arrangement given below, it can, of course, adopt other ways to achieve the same function and effect, and the embodiment is not limited to these, and for example, a conventional alternative structure of a certain component or a conventional alternative arrangement thereof can be adopted.

Furthermore, it is first explained that the rotational arrangement of the dial plate 2 on the mounting plate 1, and the arrangement of the mounting plate 1 and the rear cover 10, etc. in the supercharger housing, will be described later with reference to the corresponding drawings. Therefore, the blade unit including the lever 3 and the blade 8, and the fork transmission unit including the adjustment pin 4 and the fork 5, etc. will be described in advance.

In the embodiment, as for the shift lever 3 in the above-mentioned blade unit, specifically, it is used to receive the rotation driving of the shift disc 2 in the VGT assembly to drive the corresponding blade 8 to rotate, as shown in fig. 5, in a specific structure, the shift lever 3 of the embodiment includes a bar-shaped shift lever main body 300, a connection portion is provided at one end of the shift lever main body 300 to form a connection with the blade 8, and a protrusion 301 is also formed at the other end of the shift lever main body 300 opposite to the connection portion. Protruding 301 is evagination to driving lever main part 300 one side along the thickness direction of driving lever main part 300, and in the concrete implementation, this protruding 301 is through imbedding in the breach that 2 borders of driving lever correspond and form promptly, constitutes the transmission between driving lever 3 and the driving lever 2 from this and is connected to can accept the rotation of driving lever 2 and drive.

In the present embodiment, as a preferable embodiment, a material reducing portion recessed or penetrating the shift lever 3 is formed on the other side of the shift lever main body 300 with respect to the protrusion 301, in view of reducing weight and facilitating weight reduction. In this case, as shown in fig. 6, the material reducing portion may be, for example, a material reducing groove 303 concavely formed on the lever main body 300. It should be noted that, with respect to the shift lever 3 of the present embodiment, as a preferred embodiment, a boss 3011 protruding outward toward the shift lever main body 300 along the thickness direction of the shift lever main body 300 may be configured at one end of the shift lever main body 300, and the protrusion 301 is located on the boss 3011.

As also shown in fig. 5, it should be noted that, when the boss 3011 is disposed, the extension of the boss 3011 along the length direction of the shifter lever main body 300 toward the other end of the shifter lever main body 300 should be greater than that of the protrusion 301. From this, utilize boss 3011 to have that surpasss that portion protruding 3011, alright after driving lever 3 and blade 8 assemble, with the spacing of realizing the axial motion of driving disk 2 equally through the contact of this part and driving disk 2, and then the stability that can further guarantee driving disk 2 and set up on mounting disc 1.

In addition, as an optimized design for the boss 3011, the other side of the boss 3011 is configured to have a curved surface 3012 contacting with the end surface of the lever main body 300, relative to the side of the boss 3011 configuring the end of the lever 3. Through the arrangement of the curved surface 3012, when the boss 3011 and the toggle plate 2 touch, the abrasion between the boss 3011 and the toggle plate 2 can be reduced.

In this embodiment, the end of the lever 3 having the boss 3011 and the protrusion 301 is also specifically configured as an end plane 305 formed by the lever main body 300, the boss 3011 and the protrusion 301, so that the end of the lever 3 is planar. Meanwhile, in the present embodiment, the other end surface of the lever 3 can be disposed to be a flat surface with respect to the side having the protrusion 301 and the lever shaft 307, so that the lever body 300 has a top flat surface 304. Through being planar top plane 304 and tip plane 305, can make driving lever 3 overall structure more succinct to do benefit to its shaping, compare in the driving lever structure that uses among the present variable cross section turbo charger in addition, the planar design of this embodiment also can reduce driving lever 3's size, reduces its space and occupies, plays certain material reduction and weight reduction effect. Simultaneously because driving lever 3 is whole to be straight form, also can make the axis body structure of being connected with blade 8 do shorter to can reduce cost.

Based on in the foregoing set up the breach at the border of dial 2 to with protruding 301 cooperation and realize dial 2 to the drive of driving lever 3, protruding 301 this moment also through its two opposite sides can with the inner wall butt of breach, and can constitute driving lever 3 and the drive of dial 2 and link to each other. In this embodiment, as shown in fig. 7, the two opposite sides of the protrusion 301 are both provided with a convex arc shape, so that arc-shaped surfaces 3013 on both sides of the protrusion 301 are formed.

The arrangement of the arc-shaped face 3013 not only enables the protrusion 301 to be in better contact with the toggle plate 2, but also can play a certain role in reducing material and weight under the condition of ensuring the structural strength of the protrusion 301.

In contrast to the projection 301, the present exemplary embodiment is directed to a connection at the other end of the driver 3, which may be, for example, a through hole 302 provided in the driver 3, as an exemplary configuration. When the through hole 302 is adopted, the structure of the blade 8 matched with the through hole 302 is as shown in fig. 8, a blade shaft 801 is fixedly connected to the blade 8, the blade shaft 801 is fixedly connected to the through hole 302 on the shift lever 3 through the mounting disc 1, and the blade shaft 801 can be generally integrally formed with the blade 8, for example, metal powder injection molding can be adopted, and for example, a conventional manner such as interference insertion or welding can be adopted between the blade shaft 801 and the through hole 302.

In this embodiment, except that the blade 8 and the blade shaft 801 may be integrally formed by a metal powder injection molding process, the blade 8 and the blade shaft 801 may be prefabricated separately and then fixed together. However, it is preferable to integrally form the metal powder by injection molding. In this case, for other exemplary embodiments of the driver 3 and the blade 8, which will be mentioned later, as well as the adjusting pin 4, the fork 5, etc., they can also be produced preferably by means of a metal powder injection molding process. Of course, in addition to the metal powder injection molding process, the present embodiment can also be obtained by other existing processes for each component, as long as the process can ensure the structural performance of the component to meet the requirements of the use of the component in the variable-section supercharger.

Still referring to fig. 6, as an example of a preferred arrangement of the material reducing groove 303 of the present embodiment, in this case, compared with the boss 3011 on the other side of the shift lever 3, the extension length of the material reducing groove 303 along the length direction of the shift lever 3 may be greater than that of the boss 3011, so that the weight reduction of the shift lever 3 may be facilitated while the structural strength of the shift lever 3 is ensured. As shown in fig. 9 and 10, in addition to the material reducing groove 303, the material reducing portion of the present embodiment may also employ a material reducing hole 306, in which case the material reducing hole 306 is disposed through both the boss 3011 and the protrusion 301, and thus the protrusion 301 is formed in two halves oppositely disposed.

In addition, in the embodiment, for the vane unit in the VGT assembly, it should be further noted that, in addition to the above structure, the lever 3 and the vane 8 are fixedly connected by the vane shaft 801, as another exemplary embodiment of the vane unit in the embodiment, as shown in fig. 11 to 13, a connection portion on the lever 3 may be a lever shaft 307 integrally formed on the lever main body 300, and accordingly, the vane 8 has the vane main body 801 and a connection shaft 802 fixedly connected to the vane main body 801, the lever shaft 307 has a connection hole 303, and is partially or completely fixedly connected to the connection hole 303 by the connection shaft 802, thereby forming a connection between the vane 8 and the lever 3.

Specifically, the connection shaft body 802 may be press-fitted into the connection hole 303 with interference, and a radially outwardly protruding bulge 803 may be formed on the outer circumferential surface of the connection shaft body 802 to ensure the reliability of the press-fitting connection. The protrusions 803 are preferably provided so as to extend in the axial direction of the connection shaft body 802, and the protrusions 803 are preferably provided so as to be spaced apart from each other in the circumferential direction of the connection shaft body 802, thereby achieving a better connection effect.

The cross section of the bump 803 in the embodiment may be, for example, a semicircular shape as shown in fig. 12, but besides a semicircular shape, the cross section of the bump 803 may also be other shapes such as a square shape, a triangular shape, or a semi-elliptical shape, and besides a long strip shape extending along the axial direction of the connection shaft body 802, of course, the bump 803 in the embodiment may also be a plurality of convex semispherical shapes, or a plurality of long strip structures extending along the axial direction or the circumferential direction of the connection shaft body 802, and the embodiment is not limited thereto as long as it can improve the interference press-fitting reliability of the connection shaft body 802 in the connection hole 303.

Since the connecting shaft 802 on the blade 8 is pressed into the lever shaft 307, after the blade 8 and the lever 3 are assembled, the lever shaft 307 penetrates the mounting plate 1 and contacts the mounting plate 1, and therefore, in order to reduce the wear between the lever shaft 307 and the mounting plate 1, in this embodiment, it is preferable to form a groove circumferentially arranged around the lever shaft 307 on the outer circumferential surface of the lever shaft 307, and the number of the grooves, and the depth and width thereof, are selected according to design experience on the basis of satisfying the structural strength of the lever shaft 307. Further, similarly to the arrangement of the concave groove in the lever shaft body 307, it is needless to say that, in the blade shaft 801 described above, a concave groove structure may be provided on the outer peripheral surface of the blade shaft 801 in view of the same.

In the present embodiment, when the vane shaft 801 is used, the structure of the VGT assembly can be as shown in fig. 1 and 2, and when the matching structure of the connecting shaft body 802 and the lever shaft body 307 is used, the structure of the VGT assembly can be as shown in fig. 14 and 15. No matter the matching structure of the blade shaft 801 or the connecting shaft body 802 and the driving lever shaft body 307 is adopted, the reliable arrangement of the blades 8 can be ensured, and the driving lever 2 can be well driven.

In addition, in this embodiment, it should be noted that, no matter the vane shaft 801 or the matching structure of the connecting shaft body 802 and the shift lever shaft body 307 is adopted, since the VGT assembly needs to adapt to the high-temperature gas flow erosion environment of the exhaust gas when being used in the supercharger, the hardness of the material for manufacturing the vane 8 is generally higher than that of the shift lever 3, so as to meet the strength and corrosion resistance of the vane 8 under the gas erosion. In this case, compared with the case of using the vane shaft 801, on the one hand, the installation of the connecting shaft body 802 on the vane 8 obviously reduces the material consumption of the entire vane 8, and since the material of the vane 8 is expensive, the cost of the vane 8 can be reduced. On the other hand, the driving lever 3 is made of a material with lower hardness, so that not only can the cost be reduced, but also the abrasion between the driving lever shaft body 307 and the mounting disc 1 can be reduced.

In the present embodiment, for the fork transmission unit formed by the adjustment pin 4, the shift fork 5 and the rocker shaft 7, as shown in fig. 16 and 17, one end of the shift fork 5 is configured with a fork groove 502, the adjustment pin 4 fixedly connected to the dial 2 is inserted into the fork groove 502, and the rocker shaft 7 is connected to the other end of the shift fork 5 opposite to the fork groove 502.

The adjusting pin 4 is provided with an adjusting pin main body 401, one end of the adjusting pin main body 401 is preferably fixedly connected with the toggle plate 2 in an interference press-fitting mode, the other end of the adjusting pin main body 401 extends into the shift fork groove 502, and a wear-resistant layer 402 integrally formed with the adjusting pin main body 401 is also constructed on the outer peripheral surface of the adjusting pin main body 401 extending into the shift fork groove 502. The thickness k of the wear-resistant layer 402 should generally be not less than 0.15mm in design, and may be 0.15mm, 0.18mm, 0.2mm, etc., and at the same time, matching with the connection manner of the above interference press-fitting, in this embodiment, a radially outward convex ring 4011 may be preferably configured on the outer peripheral side of the adjusting pin body 401, one side of the convex ring 4011 is connected with the wear-resistant layer 402, so that the press-fitting of the adjusting pin 4 on the toggle plate 2 as a whole can be facilitated by the design of the convex ring 4011.

Of course, instead of a press-fit connection, the adjusting pin body 401 of the adjusting pin 4 can also be connected to the toggle disk 2 by welding. In addition, as mentioned above, the adjustment pin 4 is also preferably formed by a metal powder injection process, and as a wear-resistant structure, the wear-resistant layer 402 should be made of a wear-resistant alloy, and the inner adjustment pin body 401 should be made of a general heat-resistant steel. In this case, for example, the wear-resistant alloy may be a cobalt-based alloy, a molybdenum-based alloy, or a nickel-tungsten alloy that can withstand a high temperature of 600 ℃ or higher, while the heat-resistant steel may be a steel of an appropriate type, and since the wear-resistant layer 402 and the adjustment pin body 401 form the integral adjustment pin 4, care should be taken to select materials such that the adjustment pin body 401 and the wear-resistant layer 402 have the same or similar thermal expansion coefficient, thereby ensuring a stable structure of the adjustment pin 4 when heated.

By arranging the high-temperature-resistant wear-resistant layer 402 on the adjusting pin 4, the adjusting pin 4 can show good surface wear resistance and toughness of the core part, and the effects of less wear-resistant alloy consumption and part cost reduction can be achieved.

For the shift fork groove 502, a through hole 501 is formed at the other end of the shift fork 5, the rocker shaft 7 is inserted and fixedly connected in the through hole 501, and the fixed connection between the rocker shaft and the rocker shaft can be realized in the directions of interference press fitting or welding. In addition, in order to increase the thickness of the contact portion with the adjusting pin 4 and improve the wear resistance between the shift fork 5 and the adjusting pin 4, the embodiment is a preferable embodiment, wherein the shift fork 5 on two opposite sides of the shift fork groove 502 is further configured with oppositely arranged step portions 503, and the portion of the adjusting pin 4 extending into the shift fork groove 502 is not higher than the top surface of the step portion 503.

In this embodiment, the thickness of the end of the shift fork 5 having the through hole 501 is not increased relative to the increased step 503, so that the weight of the shift fork 5 can be prevented from being increased, and the weight reduction is facilitated. In addition, in the present embodiment, further, two opposite outer end surfaces of one end of the shift fork 5 having the fork groove 502 are also configured to be convex, and each convex outer end surface is configured to be composed of a middle plane 504 located at the middle part and two arc surfaces 505 respectively connected to two sides of the middle plane 504. Therefore, materials can be reduced by adopting the circular arc section and the straight line section, and the effect of reducing weight is also achieved.

In the present embodiment, as mentioned above, the roller 9 is configured to axially limit the position of the toggle plate 2, so as to form a limit structure in the VGT assembly. As shown in fig. 18 and fig. 19 and 20, the limiting structure of the present embodiment includes, in addition to the roller 9, a mounting hole 101 disposed on the mounting plate 1 and penetrating through the mounting plate 1, the roller 9 is connected to the mounting hole 101, and the limiting structures formed by the mounting hole 101 and the corresponding roller 9 are multiple sets disposed along the circumferential direction of the mounting plate 1.

In detail, the roller 9 is press-fitted into the mounting hole 101 by interference from the dial 2 side through its press-in end 903, and the roller 9 also has a head 901 partially blocking the dial 2 side. In addition, the mounting hole 101 of the present embodiment is designed to be a stepped hole whose inner diameter increases along the press-fitting direction of the roller 9, and the inner diameter of the mounting hole 101 increases due to the stepped hole, so that an annular air chamber Q is formed between the press-in end 903 of the roller 9 and the inner wall of the mounting hole 101, one end of the air chamber Q is open, and the other end is closed due to the interference press-fitting of the roller 9.

In the embodiment, through the formation of the air cavity Q with one closed end, air cannot flow in the mounting hole 101, so that the conduction of heat at the blade 8 to the interference section of the mounting hole 101 and the press-in end 903 can be relieved, and the risk that the roller 9 is heated and loosened can be reduced. In addition, in the specific design, the radial thickness of the air cavity Q, i.e. the distance between the outer wall of the press-in end 903 and the inner wall of the mounting hole 101 in the diameter direction of the press-in end 903 or the mounting hole 101, may be generally between 0.3mm and 0.4mm, and it may be 0.3mm, 0.35mm, 0.38mm or 0.4mm, for example. The inventor tests that when the radial thickness of the air cavity Q is in the interval, the mounting disc 1 and the roller 9 have good structural performance, and the roller 9 can be effectively prevented from being loosened by heating. Too large or too small a radial thickness is disadvantageous to the structural and anti-loosening effect.

As shown in fig. 19 and 20, the installation hole 101 of the stepped hole in the present embodiment is specifically composed of a small-diameter hole section 1011 and a large-diameter hole section 1012, and as a preferred embodiment, similar to the installation hole 101, the outer diameter of the end portion of the press-in end 903 on the roller 9 is also smaller, so that the press-in end 903 is also stepped. At this time, the press-in end 903 is specifically composed of the large-diameter shaft section 9031 and the small-diameter shaft section 9032, and for the outer diameter W of the large-diameter shaft section 9031, the outer diameter X of the small-diameter shaft section 9032, the inner diameter P of the small-diameter hole section 1011, and the inner diameter L of the large-diameter hole section 1012, W should be slightly larger than P and less than L, and X should be smaller than P and L.

It should be noted that, in the press-in end 903 and the mounting hole 101 provided in this embodiment, the large-diameter shaft section 9031 and the small-diameter hole section 1011 are in interference fit, so that the roller 9 can be fixedly mounted in the mounting hole 101, and meanwhile, since the outer diameter of the small-diameter shaft section 9032 is smaller than the outer diameter of the large-diameter hole section 1012, the small-diameter shaft section 9032 of the press-in end 903 does not press the large-diameter hole section 1012 of the mounting hole 101 when the roller 9 is subjected to interference press-fitting, so that the material around the mounting hole 101 on the mounting disc can be prevented from protruding toward the blade side due to pressing, and clamping stagnation caused by interference with the blade 8 can be avoided.

Through the design of the small-diameter shaft section 9032, the press-in end 903 can be conveniently pressed in when being pressed into the mounting hole 101. In order to ensure the stability of the roller 9 fixed in the mounting plate 1 and avoid the cracking of the mounting plate 1 at the position where the roller 9 is installed, the axial length of the press-in end 903 in interference fit with the mounting hole 101, that is, the depth M of the small-diameter hole section 1011, may be 3.8-4.5mm, and may be, for example, 3.8mm, 4.0mm, 4.2mm, or 4.5 mm. Meanwhile, in this embodiment, the axial length S of the press-in end 903 should also be generally smaller than the depth N of the mounting hole 101, and the axial length of the large-diameter shaft section 9031 may be larger than the depth of the small-diameter hole section 1011, that is, S-Y is greater than M.

The present embodiment is directed to the roller 9, and further as a preferred embodiment, a protruding portion 902 having an outer diameter smaller than that of the head portion 901 is also formed on the side of the roller 9 where the head portion 901 is connected to the press-in end 903. The press-in end 903 is attached to the protruding part 902, and as also shown in fig. 18, the outer circumference of the protruding part 902 is spaced from the toggle disk 2 so that the protruding part 902 does not protrude outside the mounting ring 102 as will be described later. In addition, in this embodiment, due to the arrangement of the protruding portion 902, a gap is formed between the head 901 and the blocked dial 2, so that the contact wear between the head 901 of the roller 9 and the blocked dial can be reduced while the axial limit is performed on the head 901. In this embodiment, a circle of undercut is formed at the contact portion between the press-in end 903 and the protrusion 902, so that the bottom surface of the protrusion 902 can be well attached to the mounting plate 1 after the roller 9 is mounted.

For the rotational installation of the dial plate 2, as an exemplary structure, in the present embodiment, a convex installation ring 102 is formed on one side of the installation plate 1 for receiving the dial plate 2, the installation hole 101 penetrates through the installation ring 102, and the dial plate 2 is sleeved outside the installation ring 102. In the present embodiment, the mounting plate 1 on the outer side of the mounting ring 102 is further provided with an outer protrusion 103 disposed around the mounting ring 102, and the dial plate 2 fitted around the mounting ring 102 is axially supported by the outer protrusion 103, so that a gap is formed between the end surfaces of the dial plate 2 and the mounting plate 1, and contact wear between the two is reduced.

In this embodiment, the VGT assembly is installed in the supercharger as shown in fig. 21 and 22, in which the mounting plate 1 is fixed on the housing, the rear cover 10 is sleeved on the housing and can slide axially, and as a preferred embodiment, one end of the distance sleeve 6 is fixedly connected to the mounting plate 1 by interference press-fitting or welding, and the other end of the distance sleeve 6 abuts against one side of the rear cover 10, so as to support between the mounting plate 1 and the rear cover 1.

In the present embodiment, relative to the distance sleeve 6, an elastic portion is further provided on the other side of the back cover 10, and the elastic portion elastically abuts between the back cover 10 and the housing, and is also arranged in a ring shape along the circumferential direction of the back cover 10. In this case, as an exemplary structure of the elastic portion, specifically, the elastic portion is an elastic pad 12 fitted to the housing, and the elastic pad 12 is abutted against the rear cover 10 and the housing by an abutting surface a and an abutting surface b located on two opposite sides of the elastic portion.

Meanwhile, as an exemplary structure of the supercharger housing, the housing of the present embodiment also includes a volute 11, and an intermediate housing 17 fixedly connected to the volute 11. The turbine 13 in the supercharger is rotatably installed relative to the scroll 11 and the middle housing 17, the rear cover 10 and the elastic pad 12 are specifically sleeved on the scroll 11, the rear cover 10 can axially slide relative to the scroll 11, meanwhile, the inner side of the mounting disc 1 is sleeved on the middle housing 17, and the outer side of the mounting disc 1 is directly clamped between the scroll 11 and the middle housing 17, so that the fixing of the mounting disc 1 in the supercharger housing is realized, and the assembly stability of the VGT assembly is guaranteed.

In this embodiment, middle casing 17 and 11 accessible bolts 16 of volute link firmly together to when volute 11 is connected with middle casing 17, the both ends that middle casing 17 and volute 11 are connected can set up to be set up to locate together to this can be fine centering volute 11 and middle casing 17, guarantee the assembly precision of booster, and prevent that turbine 13 and casing from taking place to rub.

For the above elastic cushion 12, it is generally sufficient to use elastic heat-resistant steel, and the abutting surfaces a and b on both sides of the elastic cushion 12 are also preferably both annular arranged along the circumference of the elastic cushion 12, that is, the whole plane part on each side of the elastic cushion 12 is the abutting surface. Meanwhile, the abutting surface a abutting against the rear cover 10 in the present embodiment is also disposed in a circumference formed corresponding to the connecting line between the distance sleeves 6, that is, the portions of the two sides of the rear cover 10 respectively contacting with the abutting surface a and the distance sleeves 6 are within the same radial dimension range, so that the rear cover 10 can maintain the stress balance under the clamping of the distance sleeves 6 and the elastic pads 12 at the two sides, and avoid the occurrence of serious deformation.

By using the distance sleeve 6 and the elastic pad 12 on both sides of the rear cover 10, when the exhaust gas entering the supercharger contains large particles, if the extrusion force formed by the large particles received by the rear cover 10 exceeds the elastic force of the elastic pad 12, the rear cover 10 will compress the elastic pad 12 and separate from the end surface of the distance sleeve 6, thereby increasing the distance between the vane 8 and the rear cover 10 and the distance between the mounting plate 1 and the rear cover 10, and discharging the particulate under the action of the air flow, so as to reduce the probability of the vane 8 being stuck.

In the embodiment, the elastic pad 12 is respectively abutted to the scroll 11 and the rear cover 10 through the annular abutting surfaces on the two sides of the elastic pad 12, and a certain sealing effect can be generated between the two end surfaces of the rear cover 10, which are opposite to the scroll 11, by utilizing the arrangement of the elastic pad 12, so that the exhaust gas is prevented from entering the turbine 13 through the gap between the rear cover 10 and the scroll 11.

Of course, instead of using the annular elastic pad 12, the elastic portion of the present embodiment may also use a plurality of elastic members located between the back cover 10 and the scroll 11, and the elastic members may use springs, for example, and the springs are equally distributed along the circumferential direction of the back cover 10, so that the elastic portion formed by the plurality of springs together is arranged in an annular shape as a whole.

Besides, besides being composed of a plurality of elastic members, it is further of course possible that the above-mentioned elastic portion is composed of only one spring which is also fitted over the scroll 11, and in spite of one spring or a plurality of springs, it should be noted that the abutting portion of the spring with the back cover 10 is provided corresponding to the other side distance sleeve 6 to ensure the force balance of both sides of the back cover 10. In contrast to the elastic pad 12, when the spring structure such as the above example is adopted, the aforementioned sealing effect between the rear cover 10 and the scroll 11 is obviously lost, and thus the elastic pad 12 is preferably adopted in the specific implementation.

In this embodiment, in addition to the seal formed by the elastic cushion 12, a seal ring 19 is provided between the end surfaces of the scroll 11 and the back cover 10 that are in radial contact with each other, in order to further improve the sealing performance between the back cover 10 and the scroll 11. At this time, specifically, an annular mounting groove is provided at a position of the scroll 11 for sleeving the rear cover 10, the sealing rings 19 are embedded in the mounting groove, and preferably, the two sealing rings 19 may be arranged side by side to ensure a sealing effect.

In addition, the arrangement of the seal ring 19 also allows the rear cover 10 to move axially relative to the scroll 11 smoothly without causing the housing, i.e., the scroll 11 and the rear cover 10, to be separated from each other in a radial direction. Furthermore, by the radial support of the sealing ring 19 on the back cover 10, the deformation of the outlet position of the scroll 11 caused by the radial shake of the back cover 10 can be avoided.

In this embodiment, a heat shield 14 is further provided on one side of the intermediate housing 17 to reduce the heat transfer from the exhaust gas to the other side, and the heat shield 14 is specifically fixed between the intermediate housing 17 and the mounting plate 1. In addition, in order to ensure the sealing performance of the entire supercharger housing, the sealing ring 18 is also interposed between the scroll 11 and the intermediate housing 17 in the present embodiment, and the existing V-shaped sealing ring may be used for the sealing ring 18, and of course, other existing sealing structures may be used instead of the V-shaped sealing ring.

In addition, in order to facilitate the installation of the VGT assembly in the housing, in this embodiment, a positioning pin 15 is also arranged between the mounting disk 1 and the middle housing 17, and two ends of the positioning pin 15 are respectively inserted into the mounting disk 1 and the middle housing 17, so as to connect the mounting disk 1 and the middle housing 17 together, and can play a role in limiting in the assembling process. In this case, the hole in the mounting plate 1 for the insertion of the positioning pin 15 can be designed as a blind hole or a stepped through hole, and when a stepped through hole is used, it should be noted that the inner diameter of the small diameter section in the through hole needs to be smaller than the outer diameter of the positioning pin 15.

Of course, instead of using the positioning pin 15, an associated external limiting structure may be used in the present embodiment to perform the same limiting function, and thus eliminate the positioning pin 15.

The VGT subassembly of this embodiment can be based on the rotational speed operating mode of engine through the turned angle of synchronous adjustment each blade 8 through the application in turbo charger for the nozzle ring sectional area that each blade 8 constitutes changes, and adjustable booster operating condition from this adjusts the air input of engine, and can make the air inlet of engine keep with the state that whole car engine operating mode matches, with the working property of improvement engine.

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. The utility model provides a shift fork drive unit for in the VGT subassembly of variable cross section turbo charger to accept outside rotary driving power and drive dial plate (2) in the VGT subassembly rotate, its characterized in that: the shift fork transmission unit includes that one end is constructed shift fork (5) that has shift fork groove (502), with shift disk (2) link firmly and stretch into adjusting pin (4) in shift fork groove (502), and for shift fork groove (502), connect in shift fork (5) other end in order to accept rocking arm axle (7) of outside rotary driving power, just adjusting pin (4) have adjusting pin main part (401), adjusting pin main part (401) one end with shift disk (2) link firmly, the other end stretches into in shift fork groove (502), and in stretching into in shift fork groove (502) be constructed on the outer peripheral face of adjusting pin main part (401) with adjusting pin main part (401) integrated into one piece's wearing layer (402).

2. The fork transmission unit of claim 1, wherein: the thickness of the wear-resistant layer (402) is not less than 0.15 mm.

3. The fork transmission unit of claim 1, wherein: a convex ring (4011) which is radially convex and is connected with the wear-resistant layer (402) is formed on the outer peripheral side of the adjusting pin main body (401).

4. The fork transmission unit of claim 1, wherein: the adjusting pin (4) is formed by metal powder injection molding.

5. The fork transmission unit of claim 4, wherein: the adjusting pin main body (401) is made of heat-resistant steel, and the wear-resistant layer (402) is made of wear-resistant alloy.

6. The fork transmission unit of claim 1, wherein: relative to the shifting fork groove (502), a through hole (501) is formed at the other end of the shifting fork (5), and the rocker arm shaft (7) is inserted and fixedly connected in the through hole (501).

7. The fork transmission unit according to any one of claims 1 to 6, wherein: step parts (503) which are oppositely arranged are constructed on the shifting forks (5) at two opposite sides of the shifting fork groove (502), and the part of the adjusting pin (4) which extends into the shifting fork groove (502) is not higher than the step parts (503).

8. The fork transmission unit of claim 7, wherein: two opposite outer side end faces of the shifting fork (5) with one end of the shifting fork groove (502) are arranged in a protruding mode, and each protruding outer side end face is composed of a middle plane (504) located in the middle and arc faces (505) connected to two sides of the middle plane (504) respectively.

9. A variable geometry turbocharger VGT assembly for use in a variable geometry turbocharger, characterized in that:

the VGT component comprises a mounting disc (1) and a rear cover (10) which are oppositely arranged, a poking disc (2) which is rotatably arranged on the mounting disc (1), a roller (9) which is fixedly connected to the mounting disc (1) and partially arranged on one side of the poking disc (2) in a blocking manner, and a distance sleeve (6) which is fixedly connected to the mounting disc (1) and/or the rear cover (10), wherein the distance sleeve (6) is supported between the mounting disc (1) and the rear cover (10), and the distance sleeve (6) and the roller (9) are a plurality of distance sleeves which are circumferentially arranged along the poking disc (2) at intervals;

the VGT assembly further comprises a shift fork transmission unit according to any one of claims 1 to 8, and a plurality of vane units arranged at intervals along the circumference of the shift disc (2), the vane units having vanes (8) between the mounting disc (1) and the rear cover (10), and a shift lever (3) connected to the vanes (8) via a vane shaft (801), and the shift lever (3) is in transmission connection with the shift disc (2) to receive the rotational actuation of the shift disc (2).

10. The variable geometry turbocharger VGT assembly of claim 9, wherein: the shifting lever (3) is in transmission connection with the shifting disc (2) through a bulge (301) formed at one end of the shifting lever.

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