CN114810338A - Timing system driven supercharging system and adjustable supercharging method - Google Patents

Abstract

The present application discloses a booster system driven by a timing system and a regulated booster method. The booster system includes a timing system power output mechanism and a supercharger, and the booster is fixedly installed on the timing system. Above, the supercharging system further includes: a transmission mechanism, the transmission mechanism includes a driving wheel assembly and a driven wheel assembly, the driving wheel assembly is connected with the output end of the timing system power output mechanism, the driven wheel The assembly is connected with the input end of the supercharger; wherein the transmission ratio of the transmission mechanism is greater than 1. The present application has the advantages of compact structure and high boosting efficiency.

Description

A booster system driven by a timing system and a regulated booster method

technical field

The present application relates to the technical field of engines, and in particular, to a supercharging system driven by a timing system and a regulated supercharging method.

Background technique

Compared with the exhaust gas turbocharger, the supercharger is driven by the mechanical power of the engine, so it has the characteristics of good power response and small size, and is especially suitable for improving the power performance of motorcycle engines. However, the power input source, driving mode and support arrangement of the supercharger all restrict the overall performance and use effect of the supercharged engine.

Restricted by specific vehicles and vehicles, the installation space provided by vehicles and engines is limited, and conventional supercharger installation and power supply are relatively inconvenient. The solution that the power source is taken from the engine crankshaft and directly connected to the supercharger often results in a large drive chain size and many transition links of chain drive or belt drive, which cannot achieve the ideal arrangement.

In addition, the supercharger's supercharger characteristics are closely related to and restricted by its mechanical power driving speed, so it is difficult to achieve the optimization of intake air matching in the full range of engine operating conditions. In engineering, a higher power drive transmission ratio is selected in order to take care of the supercharged intake air demand in the low-speed operating condition, which will lead to excessively high supercharger speed and excessive supercharging under high-speed operating conditions, resulting in supercharging. drive energy waste.

Based on the above two problems, it is necessary to develop a supercharger system with a compact driving structure and adjustable supercharger performance.

SUMMARY OF THE INVENTION

In order to solve the technical problems that the driving power source of the supercharger system is not ideal and the transmission structure is complex and not compact, and in order to solve the optimization of the intake air matching between the supercharger and the engine in the full operating range, the present application provides a timing system driven , The supercharging system with adjustable drive transmission ratio.

The regulated supercharging system driven by the timing system provided by the present application adopts the following technical solution: a supercharging system driven by the timing system, including a timing system power output mechanism and a supercharger, and the supercharger is fixed Installed above the timing system, the supercharging system further includes: a transmission mechanism, the transmission mechanism includes a driving wheel assembly and a driven wheel assembly, and the output of the driving wheel assembly and the timing system power output mechanism The driven wheel assembly is connected with the input end of the supercharger; wherein, the transmission mechanism transmits the power output from the output end of the timing system to the input end of the supercharger, and the transmission mechanism The gear ratio is greater than 1.

By adopting the above technical solution, the supercharger is fixedly installed above the timing system, which significantly reduces the length and complexity of the power transmission path, making the overall structure of the power transmission components and the supercharger components more compact and the transmission efficiency higher. Higher and more energy saving.

In a further solution, the system also includes an intercooler and an engine, the output end of the supercharger is connected to the inlet of the intercooler, and the outlet of the intercooler is connected to the intake part of the engine.

By adopting the above technical solutions, the entire system has a more compact structure and more reasonable structural connections between them.

In a further solution, the transmission ratio of the transmission mechanism varies according to the different rotational speeds output by the power output mechanism of the timing system, and the transmission ratio of the transmission mechanism varies in a range of 1.3-2.6.

By adopting the above technical solution, the variable transmission ratio and variable speed drive mode are used to make the matching effect of the supercharger and the engine operating conditions more ideal, so that the power output characteristics of the supercharged engine can better meet the power performance requirements of the vehicle. Specific implementation When the low speed is 2500rpm, the transmission ratio of the transmission mechanism is about 2.6, and when the driving end speed is 7000rpm, the transmission ratio of the transmission mechanism is about 1.3.

In a further solution, the driving wheel assembly and the driven wheel assembly are driven by a conveyor belt or gear meshing or chain or magnetic coupling.

By adopting the above technical solution, the transmission connection structure between the driving wheel assembly and the driven wheel assembly can be made simpler, the transmission efficiency is higher, and the system failure rate is lower.

In a further solution, the driving wheel assembly includes a positioning driving wheel, a variable driving wheel and a rotational speed sensor. When the rotational speed of the output end of the timing system increases, the rotational speed sensor drives the variable driving wheel to move away from the positioning driving wheel. move in the direction.

By adopting the above technical solution, when the rotation speed of the output end of the timing system increases, the distance between the positioning driving wheel and the variable driving wheel can be automatically adjusted by the rotation speed sensor, so that the effective transmission diameter of the driving wheel assembly can be reduced.

In a further solution, the driving wheel assembly further includes a displacement member and an active pressing mechanism, the displacement member is fixedly connected with the variable driving wheel, the rotational speed sensor includes a ball and an inclined track, and the ball is arranged on the inclined track. and the displacement member; when the rotation speed of the output end of the timing system increases, the ball slides along the inclined track to the direction away from the positioning driving wheel and simultaneously pushes the displacement member and the variable driving wheel to move away from the positioning driving wheel. , when the speed of the output end of the timing system decreases, the ball slides along the inclined track in the direction of approaching the positioning driving wheel, and the variable driving wheel moves in the direction of approaching the positioning driving wheel under the action of the active pressing mechanism.

By adopting the above technical solution, the change of the centrifugal force of the ball is realized by the change of the rotational speed of the output end of the timing system. The larger the distance that the displacement member and the variable driving wheel are pushed away from the positioning driving wheel, the smaller the equivalent transmission diameter of the driving wheel assembly and the smaller the transmission ratio of the transmission mechanism.

In a further solution, the driven wheel assembly includes a positioning driven wheel, a variable driven wheel and a driven reset pressing member, the variable driven wheel can move close to or away from the positioning driven wheel, and the driven reset pressing member is To drive the variable driven wheel close to the positioning driven wheel.

By adopting the above technical solution, the equivalent transmission diameter of the driven wheel assembly can follow the change of the driving wheel assembly, and the driven wheel assembly can cooperate with the driving wheel assembly to realize the change of the transmission ratio, while the transmission belt between the driving wheel assembly and the driven wheel assembly is always The tension is maintained and the torque can be transmitted efficiently.

In a further solution, when the rotational speed of the output end of the timing system increases and the variable driving wheel moves in a direction away from the positioning driving wheel, the driven reset pressing member pushes the variable driven wheel to approach the positioning driven wheel, At this time, the transmission ratio of the transmission mechanism becomes smaller; when the output speed of the timing system decreases and the variable driving wheel moves toward the positioning driving wheel under the action of the active pressing mechanism, the variable driven wheel moves away from the positioning When the driven wheel moves in the direction, the transmission ratio of the transmission mechanism becomes larger.

By adopting the above technical solution, when the equivalent transmission diameter of the driving wheel assembly becomes smaller, the equivalent transmission diameter of the driven wheel assembly becomes larger, and the transmission ratio of the transmission mechanism becomes smaller at this time; when the equivalent transmission diameter of the driving wheel assembly becomes larger , the equivalent transmission diameter of the driven wheel assembly becomes smaller, and the transmission ratio of the transmission mechanism becomes larger at this time. While the transmission ratio is changed, the drive belt is always tensioned and can transmit torque efficiently.

In order to make the supercharger and its supercharging system better meet the requirements of the engine's air intake characteristics, the technology of solving the problem of insufficient supercharging under low engine speed conditions and excessive engine pressure under high engine speed conditions Problem, the present application also provides a regulated supercharging method driven by a timing system, which is applicable to the above-mentioned supercharging system, and the supercharging method includes: obtaining the rotational speed value of the power output mechanism of the timing system; When the rotational speed of the power output mechanism of the system increases, the ball slides along the inclined track in the direction away from the positioning driving wheel and simultaneously pushes the displacement member and the variable driving wheel to move away from the positioning driving wheel, and the driven reset is pressed. The component pushes the variable driven wheel to approach the positioning driven wheel, and the transmission ratio of the transmission mechanism becomes smaller at this time; when the rotation speed of the timing system power output mechanism decreases, the ball moves closer to the positioning driven wheel along the inclined track. The wheel slides in the direction, the variable driving wheel moves towards the positioning driving wheel under the action of the pressing mechanism, and the variable driven wheel moves away from the positioning driven wheel, and the transmission ratio of the transmission mechanism becomes larger at this time.

By adopting the above technical solution, the transmission mechanism can automatically adjust the transmission ratio with the change of the output end speed of the timing system. While the transmission ratio is changed, the transmission belt is always kept in tension and the driving power can be effectively transmitted.

In a further scheme, the transmission ratio variation law of the transmission mechanism is adapted to the requirements of the engine air intake characteristics, and a larger speed-up transmission ratio is used in the lower speed working condition, and a relatively smaller speed is adopted in the higher speed working condition. The speed-up transmission ratio varies from 1.3 to 2.6.

By adopting the above technical solution, the transmission ratio of the transmission mechanism is about 2.6 when the low rotation speed is 2500rpm, and the transmission ratio of the transmission mechanism is about 1.3 when the driving end rotation speed is 7000rpm. The matching effect of the supercharger and the engine operating conditions is more ideal, so that the power output characteristics of the supercharged engine can better meet the driving requirements of the vehicle.

In order to solve the technical problem of the structural arrangement of the supercharging system of a motor vehicle, the present application also provides a motor vehicle, including the supercharging system described above.

By adopting the above technical solutions, the structure of the motor vehicle is more compact, the size can be designed smaller, and the design space and practical convenience are larger.

To sum up, the present application has at least one of the following beneficial technical effects:

1. The booster system driven by the timing system of the present application significantly reduces the length and complexity of the power transmission path, making the overall structure of the power drive components and super booster components more compact, with higher transmission efficiency and more energy saving .

2. The application can regulate the supercharging system, and use the variable transmission ratio and variable speed drive mode to make the matching and optimization effect of the intake characteristics of the supercharger and the engine in the full range of operating conditions more ideal, so that the power output characteristics of the supercharged engine are better. meet the driving power requirements of the vehicle.

3. The pressurization method driven by the timing system of the present application can realize the automatic adjustment of the transmission ratio of the transmission mechanism with the change of the rotation speed of the output end of the timing system. While realizing the change of the transmission ratio, the transmission belt is always kept in tension and can effectively transmit the rotation speed.

Description of drawings

1 is a schematic structural diagram of an angle of Embodiment 1 of a booster system driven by a timing system of the present application;

2 is a schematic structural diagram of another angle of Embodiment 1 of the booster system driven by the timing system of the present application;

3 is a schematic cross-sectional structure diagram of Embodiment 1 of the booster system driven by the timing system of the present application;

4 is a schematic structural diagram of the cooperation between a driven wheel assembly and a supercharger in Embodiment 1 of the supercharging system driven by the timing system of the present application;

5 is a schematic structural diagram of a timing system, a supercharger and a transmission mechanism in Embodiment 1 of the supercharging system driven by the timing system of the present application;

6 is a schematic cross-sectional structure diagram of the transmission mechanism of the second embodiment of the booster system driven by the timing system of the present application;

7 is a schematic three-dimensional structural diagram of the transmission mechanism of the second embodiment of the booster system driven by the timing system of the present application;

FIG. 8 is a schematic structural diagram of Embodiment 3 of the booster system driven by the timing system of the present application;

Fig. 9 is the enlarged structure schematic diagram of A place of Fig. 8;

FIG. 10 is a schematic diagram of the cross-sectional structure along the line B-B of FIG. 9 .

Reference number:

1. Transmission mechanism; 11. Driving wheel assembly; 111. Positioning driving wheel; 112. Variable driving wheel; 113. Speed sensor; 114. Inclined track; 115. Active pressing mechanism; Drive wheel assembly; 121, positioning driven wheel; 122, variable driven wheel; 123, driven reset pressing part; 13, transmission belt; 2, cylinder; 21, cylinder cover; 22, cylinder head; 3, supercharger; 31. Machine base; 32. Input shaft; 33. Turbine; 34. Tube body; 4. Intercooler; 5. Timing system; 51. Power take-off mechanism; 61. Oil supply pipe; 62. Control valve; 63 64, rotating gear; 65, opening and closing parts; 66, mounting plate; 67, first mounting block; 68, second mounting block; 69, rotating shaft; 70, mounting shaft; 71, meshing port; 72 73, installation sleeve; 74, centrifugal rod; 75, return spring; 76, avoidance port; 77, shield cover; 78, avoidance groove.

Detailed ways

In order to make the objectives, technical solutions and advantages of the embodiments of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings. The components of the embodiments of the invention generally described and illustrated in the drawings herein may be arranged and designed in a variety of different configurations. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

It should be noted that like numerals and letters refer to like items in the following figures, so once an item is defined in one figure, it does not require further definition and explanation in subsequent figures.

In the description of the present invention, it should be noted that the terms "installed", "connected" and "connected" should be understood in a broad sense, unless otherwise expressly specified and limited, for example, it may be a fixed connection or a detachable connection Connection, or integral connection; may be mechanical connection or electrical connection; may be direct connection or indirect connection through an intermediate medium, and may be internal communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood in specific situations.

In the description of the present application, it should be understood that the orientations or positional relationships indicated by the terms "upper", "lower", "left", "right", etc. are based on the orientations or positional relationships shown in the accompanying drawings, only for the purpose of It is convenient to describe the application and to simplify the description, rather than indicating or implying that the device or element referred to must have a particular orientation, be constructed and operate in a particular orientation, and therefore should not be construed as limiting the application.

Some embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The features of the embodiments described below may be combined with each other without conflict.

Example 1:

Referring to FIG. 1 and FIG. 2 , a schematic diagram of a supercharging system driven by a timing system 5 is disclosed. The supercharging system includes a cylinder 2 and a supercharger 3 , the cylinder 2 is provided with a cylinder cover 21 , the supercharger 3 is provided with a frame 31 , and the supercharger 3 is fixedly installed on the cylinder case 21 through the frame 31 . A transmission mechanism 1 is connected between the power output end of the cylinder 2 and the power input end of the supercharger 3 , and the transmission mechanism 1 transmits the torque of the power output end of the cylinder 2 to the power input end of the supercharger 3 . The transmission mechanism 1 includes a driving wheel assembly 11 and a driven wheel assembly 12, a transmission belt 13 is connected between the driving wheel assembly 11 and the driven wheel assembly 12, the driving wheel assembly 11 is connected with the power output end of the cylinder 2, and the driven wheel assembly 12 is connected with the increaser. The power input end of the compressor 3 is connected, and the transmission ratio of the transmission mechanism 1 is greater than 1. Gear meshing or chain or magnetic coupling transmission may also be used between the driving wheel assembly 11 and the driven wheel assembly 12 .

The output end of the supercharger 3 is connected with the gas inlet of the intercooler 4, and the outlet of the intercooler 4 is connected with the throttle valve and the intake pipe of the cylinder head 22 of the intake part of the engine.

3 and 4 , the driving wheel assembly 11 is fixedly connected to the power output mechanism 51 of the timing system 5 , and the driven wheel assembly 12 is fixedly connected to the input shaft 32 of the supercharger 3 .

Referring to FIG. 5 , the transmission mechanism 1 is driven by a synchronous pulley through a synchronous belt. In the figure, the driving pulley assembly 11 and the driven pulley assembly 12 are both synchronous pulleys, and the transmission belt 13 is a synchronous belt. The driving wheel assembly 11 is fixedly connected with the power output mechanism 51 to transmit the power output from the timing system 5 to the driven wheel assembly 12 through the conveyor belt, and the driven wheel assembly 12 transmits the power to the supercharger through the input shaft 32 of the supercharger 3 that is fixedly connected. device 3. The axes of the input shaft 32 and the output shaft of the power take-off mechanism 51 are parallel.

Embodiment 2:

Please refer to FIGS. 6 and 7. The difference from the first embodiment is that the driving wheel assembly 11 and the driven wheel assembly 12 are V-shaped friction wheels, and the positioning driven wheel 121 of the driving wheel assembly 11 is fixedly connected to the power output mechanism 51. The variable driving wheel 112 is connected with the output shaft of the power output mechanism 51 by splines, the output shaft is designed as a spline, and the driving wheel assembly 11 is designed as a spline groove matched with the output shaft, and the driving wheel assembly 11 can transmit the power output mechanism 51. The power and variable driving wheel 112 can move along the axial direction of the power take-off mechanism 51 . The positioning driven wheel 121 of the driven wheel assembly 12 is fixedly connected with the input shaft 32 , the variable driven wheel 122 and the input shaft 32 are also connected by splines, the input shaft 32 is designed as a spline, and the variable driven wheel 122 is designed to be connected with the input shaft 32 With the matched spline grooves, the driven wheel assembly 12 can transmit the power transmitted by the transmission belt 13 to the input shaft 32 and the variable driven wheel 122 can move along the axial direction of the input shaft 32 . The driving wheel assembly 11 includes a positioning driving wheel 111, a variable driving wheel 112 and a rotational speed sensor 113. When the rotational speed of the output end of the timing system 5 increases, the rotational speed sensor 113 drives the variable driving wheel 112 to move away from the positioning driving wheel. The direction of the wheel 111 moves.

The driving wheel assembly 11 further includes a displacement member 116 and an active pressing mechanism 115. The displacement member 116 is fixedly connected with the variable driving wheel 112, and the rotational speed sensor 113 includes a ball and an inclined surface track 114. The ball is arranged on the inclined surface track 114 and the displacement member. between 116. When the rotational speed of the output end of the power output mechanism 51 of the timing system 5 increases, the ball slides along the inclined track 114 to the direction away from the positioning driving wheel 111 and pushes the displacement member 116 and the variable driving wheel 112 to the direction away from the positioning driving wheel 111 move. When the rotation speed of the output end of the power output mechanism 51 of the timing system 5 decreases, the ball slides along the inclined track 114 toward the positioning driving wheel 111 , and the variable driving wheel 112 moves closer to the positioning under the action of the active pressing mechanism 115 . The driving wheel 111 moves in the direction. Therefore, the change of the equivalent diameter of the transmission of the driving wheel and the equivalent diameter of the transmission of the driven wheel causes the transmission ratio of the transmission mechanism 1 to become larger or smaller. The active pressing mechanism 115 is realized by a compression spring, its working end presses the variable driving wheel 112 axially, and the other end is fixedly connected with the shaft end of the power output mechanism 51, and its function is to keep the positioning driving wheel 111 and the variable driving wheel 112. Press the V-belt 13 axially.

The driven wheel assembly 12 includes a positioning driven wheel 121 , a variable driven wheel 122 and a driven reset pressing member 123 , the variable driven wheel 122 can move close to or away from the positioning driven wheel 121 , and the driven reset pressing member 123 Used to drive the variable driven wheel 122 to approach the positioning driven wheel 121 .

When the rotational speed of the output end of the timing system 5 increases and the variable driving wheel 112 moves away from the positioning driving wheel 111 , the driven reset pressing member 123 pushes the variable driving wheel 122 toward the positioning driving wheel 121 At this time, the transmission ratio of the transmission mechanism 1 becomes smaller; when the speed of the output end of the timing system 5 decreases and the variable driving wheel 112 moves to the direction of approaching the positioning driving wheel 111 under the action of the active pressing mechanism 115, the said The variable driven wheel 122 moves away from the positioning driven wheel 121, and at this time, the transmission ratio of the transmission mechanism 1 increases.

The transmission ratio of the transmission mechanism 1 changes according to the rotation speed output by the power output mechanism 51 of the timing system 5. The transmission ratio of the transmission mechanism 1 is changed in accordance with the requirements of the engine air intake characteristics. In the lower speed condition, a larger increase in speed is used. At higher speeds, a relatively small up-speed transmission ratio is used.

In this embodiment, when the power output mechanism 51 of the timing system 5 rotates at a low speed of 2500 rpm, the transmission ratio of the transmission mechanism 1 is about 2.6, and when the power output mechanism 51 of the timing system 5 is at a high speed of 7000 rpm, the transmission ratio of the transmission mechanism 1 is about 2.6. is 1.3, and the transmission ratio varies from 1.3 to 2.6.

Embodiment three:

Please refer to FIG. 8 to FIG. 10. The difference from the above embodiments is that the supercharging system further includes an auxiliary fuel supply component. The auxiliary fuel supply chamber of the auxiliary fuel supply component is used to store gasoline, and the gasoline can enter the air inlet through the fuel injection pipe. , thereby increasing the ratio of gasoline in the air while increasing the intake air volume, so as to increase the utilization of oxygen in the air and ensure the power of the engine.

An outer ring gear 72 is fixedly connected to the peripheral side wall of the turbine 33, the auxiliary oil supply chamber is located on one side of the supercharging cover, and is fixedly connected to the engine cover through bolts. The auxiliary fuel supply chamber is filled with gasoline. The auxiliary oil supply chamber is provided with an oil filling hole (not shown in the figure) and a plug cover (not shown in the figure) that is detachably connected to the auxiliary oil supply room and used to block the oil filling hole.

The control valve 62 includes a holding member 63 for holding the oil supply pipe 61 , a rotating gear 64 connected between the turbine 33 and the holding member 63 , and an opening and closing member 65 connected on the rotating gear 64 .

The clamping member 63 includes a mounting plate 66 arranged at intervals on one side of the bobbin body 34 , a first mounting block 67 fixedly connected to the side of the mounting plate 66 close to the bobbin body 34 , a rotating shaft 69 pierced through the mounting block, and a mounting block 69 . The second mounting block 68 on the rotating shaft 69 , the clamping plate 46 mounted on the side of the second mounting block 68 away from the mounting plate 66 , and the torsion sleeve sleeved on the rotating shaft 69 and used to drive the clamping plate 46 to rotate around the rotating shaft 69 spring (not shown).

Two first installation blocks 67 are spaced apart, and two ends of the rotating shaft 69 are respectively penetrated between the two first installation blocks 67 .

There are two second mounting blocks 68 and both are sleeved on the outer side wall of the rotating shaft 69 . The clamping plate 46 is fixedly connected to the two second mounting blocks 68 .

One end of the torsion spring is fixed to the mounting plate 66 , and the opposite end is abutted against the side of the clamping plate 46 close to the mounting plate 66 . One end of the clamping plate 46 abutting the torsion spring is the driving end, and the other end forms a clamping space with the mounting plate 66 . Both ends of the oil injection pipe are arranged at a height, the higher end of the oil injection pipe is connected with the auxiliary oil supply chamber, and the lower end is penetrated through the engine intake valve.

The rotating gear 64 is rotatably connected to the outer side wall of the ring tube body 23 through the installation shaft 70, and the bobbin body 34 is also provided with a meshing port 71 for the rotating gear 64 to extend into. Body 34 is set.

The rotating gear 64 passes through the meshing opening 71 and meshes with the outer ring gear 72 of the turbine 33 .

The opening and closing member 65 includes an installation sleeve 73 fixedly connected to the lower surface of the rotating gear 64 , a centrifugal rod 74 inserted through the installation sleeve 73 , and a return spring 75 connected between the installation sleeve 73 and the centrifugal rod 74 .

Several mounting sleeves 73 are arranged at intervals around the axis of the rotating gear 64 . The mounting sleeve 73 is provided with a telescopic groove along the radial direction of the rotating gear 64 , and one end of the telescopic groove away from the axis of the rotating gear 64 penetrates the mounting sleeve 73 .

The centrifugal rod 74 is slidably connected in the telescopic groove, and the centrifugal rod 74 is adapted to the telescopic groove. In order to reduce the collision and interference between the centrifugal rod 74 and the bobbin body 34 after the centrifugal rod 74 extends out of the telescopic groove, a through escape port 76 is opened on the side wall of the bobbin body 34. side.

The turbine 33 drives the rotating gear 64 to rotate through the outer ring gear 72. When the rotating gear 64 rotates, the centrifugal rod 74 will be subjected to centrifugal action, thereby moving away from the axis of the rotating gear 64 along the length of the expansion groove. pull and produce a corresponding reaction force.

When the engine camshaft 56 rotates, the turbine 33 and the rotating gear 64 rotate, so that the centrifugal force received by the centrifugal rod 74 will cause the centrifugal rod 74 to extend out of the telescopic groove. The part of the centrifugal rod 74 extending out of the telescopic slot will abut with the driving section of the clamping plate 46 and drive the driving section of the clamping plate 46 to rotate towards the mounting plate 66 . The holding space will become larger, thereby weakening the clamping effect on the fuel injection pipe, so that the gasoline in the auxiliary fuel supply chamber can enter the intake valve through the fuel injection pipe. content, so as to make full use of the oxygen pressed into the air through the pressurized components, and reduce the generation of useless power.

When the rotational speed of the engine camshaft 56 is further increased, the rate of rotation of the clamping plate 46 driven by the centrifugal rod 74 becomes higher, and the length of the centrifugal rod 74 extending out of the telescopic slot becomes longer, so that the rotation of the clamping plate 46 becomes larger. , the clamping effect on the fuel injection pipe is weakened, and the amount of gasoline entering the air inlet through the fuel injection pipe is increased.

When the rotational speed of the engine camshaft 56 decreases gradually, the rotational speed of the rotating gear 64 decreases, the centrifugal force felt by the centrifugal force becomes smaller, and the centrifugal rod 74 will gradually retract to the telescopic groove under the action of the return spring 75 until the centrifugal rod 74 protrudes from one end of the telescopic groove The rotation path is on the side of the clamping plate 46. At this time, since the fuel injection pipe is clamped by the clamping member 63, the gasoline cannot enter the intake valve through the fuel injection pipe, so as to reduce the amount of fuel charged into the engine when the engine power is low. The gasoline concentration of the oil-gas mixture is too high, resulting in insufficient combustion and waste.

In order to reduce the leakage of the compressed air in the casing 6 from the escape opening 76, a shielding cover 77 is fixedly connected to the inner wall of the bobbin body 34. The escape groove 78 through which the rod 74 rotates.

The avoidance cover will divide the interior of the housing 6 and the centrifugal rod 74 to ensure the quality of air compression.

Embodiment four:

Based on the booster system driven by the timing system, the present embodiment provides a regulated booster method driven by the timing system 5, and the booster method specifically includes but is not limited to the following steps:

Obtain the rotational speed value of the power output mechanism 51 of the timing system 5;

When the rotation speed of the power output mechanism 51 of the timing system 5 increases, the ball slides along the inclined track 114 to the direction away from the positioning driving wheel 111 and pushes the displacement member 116 and the variable driving wheel 112 to move away from the positioning driving wheel 111. The driven reset pressing member 123 pushes the variable driven wheel 122 to approach the positioning driven wheel 121, and the transmission ratio of the transmission mechanism 1 becomes smaller at this time;

When the rotation speed of the power output mechanism 51 of the timing system 5 is reduced, the balls slide along the inclined track 114 to the direction of approaching the positioning driving wheel 111 , and the variable driving wheel 112 will approach the positioning driving wheel 111 under the action of the pressing mechanism. When moving, the variable driven wheel 122 moves away from the positioning driven wheel 121 , and at this time, the transmission ratio of the transmission mechanism 1 increases.

The change law of the transmission ratio of the transmission mechanism 1 is adapted to the requirements of the intake characteristics of the engine, a larger speed-up transmission ratio is used in the lower speed condition, and a relatively small speed-up transmission ratio is used in the higher speed state. , the transmission ratio changes in the range of 1.3 to 2.6.

Embodiment 5:

The present embodiment discloses a motor vehicle, which has the pressure boosting system driven by the timing system described in the first to third embodiments, and adopts the adjustable pressure boosting method of the fourth embodiment to boost pressure.

It should be noted that, in the above embodiment, the supercharger 3, the cylinder 2, the intercooler 4 and the timing system 5 are all existing technologies, which can be understood by those skilled in the art, so the working structure and working principle are not specific. elaborate.

The foregoing has shown and described the basic principles, main features and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited by the above-mentioned embodiments, and the descriptions in the above-mentioned embodiments and the description are only to illustrate the principle of the present invention. Without departing from the spirit and scope of the present invention, the present invention will have Numerous changes, modifications, substitutions, and alterations fall within the scope of the claimed invention.

Claims (10)

1. A supercharging system driven by a timing system, comprising a power output mechanism (51) and a supercharger (3) of the timing system (5), wherein the supercharger (3) is fixedly installed in Above the timing system (5), the supercharging system further includes: A transmission mechanism (1), the transmission mechanism (1) includes a driving wheel assembly (11) and a driven wheel assembly (12), the driving wheel assembly (11) and the power output mechanism ( 51) is connected to the output end, and the driven wheel assembly (12) is connected to the input end of the supercharger (3); Wherein, the transmission mechanism (1) transmits the power output from the output end of the timing system (5) to the input end of the supercharger (3), and the transmission ratio of the transmission mechanism (1) is greater than 1. 2. The supercharging system according to claim 1, characterized in that, further comprising an intercooler (4) and an engine, and the output end of the supercharger (3) is connected to the inlet of the intercooler (4), The outlet of the intercooler (4) is connected with the intake part of the engine. 3. The supercharging system according to claim 1, characterized in that the transmission ratio of the transmission mechanism (1) varies according to the rotational speed output by the power output mechanism (51) of the timing system (5), and the transmission The change law of the transmission ratio of the mechanism (1) is adapted to the requirements of the intake characteristics of the engine, and a large speed-up transmission ratio is adopted in the low-speed working condition, while a relatively small speed-up transmission ratio is adopted in the high-speed working condition. The variation range is 1.3 to 2.6. 4. The supercharging system according to claim 1, characterized in that, the driving wheel assembly (11) and the driven wheel assembly (12) are driven by a transmission belt (13) or gear meshing or chain or magnetic coupling. 5. The supercharging system according to claim 3, wherein the driving wheel assembly (11) comprises a positioning driving wheel (111), a variable driving wheel (112) and a rotational speed sensor (113), when the timing When the rotational speed of the output end of the system (5) increases, the rotational speed sensor (113) drives the variable driving wheel (112) to move away from the positioning driving wheel (111). 6. The supercharging system according to claim 5, wherein the driving wheel assembly (11) further comprises a displacement member (116) and an active pressing mechanism (115), the displacement member (116) Fixedly connected with the variable driving wheel (112), the rotational speed sensor (113) includes a ball and an inclined track (114), the ball is arranged between the inclined track (114) and the displacement member (116); when the timing When the rotational speed of the output end of the system (5) increases, the balls slide along the inclined track (114) in a direction away from the positioning driving wheel (111) and simultaneously push the displacement member (116) and the variable driving wheel (112) away from the positioning driving wheel (111). The positioning driving wheel (111) moves in the direction, and when the rotation speed of the output end of the timing system (5) decreases, the ball slides along the inclined track (114) in the direction of approaching the positioning driving wheel (111), and the variable driving wheel (112) Move in the direction of approaching the positioning driving wheel (111) under the action of the active pressing mechanism (115). 7. The supercharging system according to claim 6, wherein the driven wheel assembly (12) comprises a positioning driven wheel (121), a variable driven wheel (122) and a driven reset pressing member (123) , the variable driven wheel (122) can move close to or away from the positioning driven wheel (121), and the driven reset pressing member (123) is used to drive the variable driven wheel (122) to approach the positioning driven wheel (121) . 8. The supercharging system according to claim 7, characterized in that, when the rotational speed of the output end of the timing system (5) increases and the variable driving wheel (112) moves away from the positioning driving wheel (111), The driven reset pressing member (123) pushes the variable driven wheel (122) to approach the positioning driven wheel (121), and at this time the transmission ratio of the transmission mechanism (1) becomes smaller; when the timing system (5) When the rotational speed of the output end of ) decreases and the variable driving wheel (112) moves in the direction of approaching the positioning driving wheel (111) under the action of the active pressing mechanism (115), the variable driven wheel (122) moves away from the positioning driving wheel (122). The moving wheel (121) moves in the direction, and at this time, the transmission ratio of the transmission mechanism (1) becomes larger. 9. A regulated supercharging method driven by a timing system, characterized in that, applicable to the supercharging system according to claim 8, the supercharging method comprising: Obtain the rotational speed value of the power take-off mechanism (51) of the timing system (5); When the rotation speed of the power output mechanism (51) of the timing system (5) increases, the balls slide along the inclined track (114) to the direction away from the positioning driving wheel (111) while pushing the displacement member (116) and the variable The driving wheel (112) moves away from the positioning driving wheel (111), and the driven reset pressing member (123) pushes the variable driven wheel (122) to approach the positioning driven wheel (121). The transmission ratio of the mechanism (1) becomes smaller; When the rotational speed of the power output mechanism (51) of the timing system (5) decreases, the ball slides along the inclined track (114) in the direction of approaching the positioning driving wheel (111), and the variable driving wheel (112) is under pressure. Under the action of the tightening mechanism, the variable driven wheel (122) moves in the direction of approaching the positioning driving wheel (111), and the variable driven wheel (122) moves away from the positioning driven wheel (121). 10. The supercharging method according to claim 9, wherein the transmission ratio variation law of the transmission mechanism (1) is adapted to the requirements of the engine air intake characteristics, and a large speed-up transmission ratio is adopted in a low-speed operating condition. , and in the high-speed working condition, a relatively small speed-up transmission ratio is used, and the transmission ratio changes in the range of 1.3 to 2.6.

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