CN114810338B - Timing system driven supercharging system and adjustable supercharging method - Google Patents
Timing system driven supercharging system and adjustable supercharging method Download PDFInfo
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- CN114810338B CN114810338B CN202210720724.8A CN202210720724A CN114810338B CN 114810338 B CN114810338 B CN 114810338B CN 202210720724 A CN202210720724 A CN 202210720724A CN 114810338 B CN114810338 B CN 114810338B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/04—Mechanical drives; Variable-gear-ratio drives
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
The application discloses timing system driven turbocharging system and can regulate and control pressure boost method, turbocharging system include timing system power take off mechanism and super booster, booster fixed mounting in the top of timing system, turbocharging system still includes: the transmission mechanism comprises 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, and the driven wheel assembly is connected with the input end of the supercharger; wherein the transmission ratio of the transmission mechanism is greater than 1. This application has compact structure, the efficient advantage of pressure boost.
Description
Technical Field
The application relates to the technical field of engines, in particular to a timing system driven supercharging system and an adjustable supercharging method.
Background
Compared with an exhaust gas turbocharger, the super-supercharger is driven by mechanical power of an engine, so that the super-supercharger has the characteristics of good power responsiveness, small size and the like, and is particularly suitable for improving the power performance of a motorcycle engine. However, the power input source, the driving mode and the supporting arrangement of the super supercharger all restrict the overall performance and use effect of the supercharged engine.
Due to the limitations of the particular vehicle and vehicle, the limited installation space provided by the vehicle and engine, and the inconvenience of conventional super-booster installations and power supplies. The scheme that the power source is taken from the crankshaft of the engine and is directly connected with the supercharger often causes large size of a driving chain and more transitional links of chain transmission or belt transmission, and ideal arrangement cannot be realized.
In addition, the supercharging characteristic of the super supercharger is closely related to the mechanical power driving rotating speed of the super supercharger and is restricted, so that the air inlet matching optimization of the engine in the whole working condition range is difficult to realize. In engineering, a high power driving transmission ratio is selected for considering the supercharging air inlet requirement of a low-rotation-speed working condition section, so that the rotation speed of the supercharger is too high and the supercharging is excessive under the high-rotation-speed working condition, and the driving energy waste of the supercharger is caused.
In view of the above two problems, there is a need to develop a super-supercharger system with compact driving structure and adjustable supercharging performance.
Disclosure of Invention
In order to solve the technical problems that the driving power source of the super-supercharging system is unsatisfactory and the transmission structure is complex and not compact, and in order to solve the problem that the super-supercharging system is matched and optimized with the air inlet within the full working condition range of the engine, the application provides the supercharging system which is driven by a timing system and can regulate and control the driving transmission ratio.
The application provides a timing system driven can regulate and control turbocharging system adopts following technical scheme: a timing system driven supercharging system comprises a timing system power output mechanism and a supercharger, wherein the supercharger is fixedly arranged above the timing system, and the supercharging system further comprises: the transmission mechanism comprises 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, and the driven wheel assembly is connected with the input end of the supercharger; the transmission mechanism transmits power output by the output end of the timing system to the input end of the supercharger, and the transmission ratio of the transmission mechanism is greater than 1.
By adopting the technical scheme, the supercharger is fixedly arranged above the timing system, the power transmission path length and the complexity are obviously reduced, so that the overall structure of the power transmission part and the super supercharging part is more compact, the transmission efficiency is higher, and the energy consumption is more saved.
In a further scheme, the system further comprises an intercooler and an engine, the output end of the supercharger is connected with the inlet of the intercooler, and the outlet of the intercooler is connected with an air inlet component of the engine.
By adopting the technical scheme, the whole system is more compact in structure and more reasonable in mutual structural connection.
In a further scheme, the transmission ratio of the transmission mechanism changes according to the different output rotating speeds of the power output mechanism of the timing system, and the change range of the transmission ratio of the transmission mechanism is 1.3-2.6.
By adopting the technical scheme, the matching effect of the supercharger and the working condition of the engine is more ideal by utilizing a variable transmission ratio and variable speed driving mode, so that the power output characteristic of the supercharged engine can better meet the power performance requirement of the vehicle. The transmission ratio of the transmission is about 2.6 when the low speed is 2500rpm, and about 1.3 when the driving end rotates 7000 rpm.
In a further scheme, the driving wheel assembly and the driven wheel assembly are in mesh transmission through a transmission belt or a gear or are in chain or magnetic coupling transmission.
By adopting the technical scheme, the transmission connection structure between the driving wheel assembly and the driven wheel assembly is simpler, the transmission efficiency is higher, and the system failure rate is lower.
In a further scheme, the driving wheel assembly comprises a positioning driving wheel, a variable driving wheel and a rotating speed sensor, and when the rotating speed of the output end of the timing system is increased, the rotating speed sensor drives the variable driving wheel to move towards the direction far away from the positioning driving wheel.
By adopting the technical scheme, when the rotating speed of the output end of the timing system is increased, the distance between the positioning driving wheel and the variable driving wheel is automatically adjusted through the rotating speed sensor, so that the effective transmission diameter of the driving wheel assembly is reduced.
In a further scheme, the driving wheel assembly further comprises a shifting piece and a driving pressing mechanism, the shifting piece is fixedly connected with the variable driving wheel, the rotating speed sensor comprises a ball and an inclined plane track, and the ball is arranged between the inclined plane track and the shifting piece; when the rotating speed of the output end of the timing system is reduced, the ball slides towards the direction close to the positioning driving wheel along the inclined plane track, and the variable driving wheel moves towards the direction close to the positioning driving wheel under the action of the driving pressing mechanism.
Through adopting above-mentioned technical scheme, the change that realizes ball centrifugal force size through the output rotational speed change of timing system, the output rotational speed of timing system is higher, and ball centrifugal force is bigger, and the distance that the ball removed along the inclined plane track is more far away, therefore the ball promotes the distance that displacement piece and variable action wheel kept away from the location action wheel and is bigger, and the equivalent transmission diameter of initiative wheel subassembly diminishes, and drive mechanism's drive ratio diminishes.
In a further scheme, the driven wheel assembly comprises a positioning driven wheel, a variable driven wheel and a driven reset pressing piece, the variable driven wheel can be close to or far away from the positioning driven wheel, and the driven reset pressing piece is used for driving the variable driven wheel to be close to the positioning driven wheel.
Through adopting above-mentioned technical scheme, can follow the action wheel subassembly change from the equivalent transmission diameter of driving wheel subassembly, can cooperate from the action wheel subassembly when realizing that the drive ratio changes, the drive belt that is located between action wheel subassembly and the driven wheel subassembly remains the tensioning throughout and can effectively transmit torque.
In a further scheme, when the rotating speed of the output end of the timing system is increased and the variable driving wheel moves in the direction away from the positioning driving wheel, the driven reset pressing piece pushes the variable driven wheel to approach the positioning driven wheel, and the transmission ratio of the transmission mechanism is reduced at the moment; when the rotating speed of the output end of the timing system is reduced and the variable driving wheel moves towards the direction close to the positioning driving wheel under the action of the driving pressing mechanism, the variable driven wheel moves towards the direction far away from the positioning driven wheel, and the transmission ratio of the transmission mechanism is increased at the moment.
By adopting the technical scheme, when the equivalent transmission diameter of the driving wheel component is smaller, the equivalent transmission diameter of the driven wheel component is larger, and the transmission ratio of the transmission mechanism is smaller; when the equivalent transmission diameter of the driving wheel assembly becomes larger, the equivalent transmission diameter of the driven wheel assembly becomes smaller, and at the moment, the transmission ratio of the transmission mechanism becomes larger. The drive belt is always kept tensioned and can transmit torque efficiently while a change in transmission ratio is achieved.
In order to enable the super-supercharger and a supercharging system formed by the super-supercharger to better meet the requirement of the air inlet characteristic of an engine and solve the technical problems of insufficient supercharging under the working condition of low rotating speed of the engine and excessive supercharging under the working condition of high rotating speed of the engine, the application also provides an adjustable and controllable supercharging method driven by a timing system, which is suitable for the supercharging system, wherein the supercharging method comprises the steps of obtaining the rotating speed value of a power output mechanism of the timing system; when the rotating speed of the power output mechanism of the timing system is increased, the ball slides along the inclined track in the direction away from the positioning driving wheel, meanwhile, the displacement piece and the variable driving wheel are pushed to move in the direction away from the positioning driving wheel, the driven reset pressing piece pushes the variable driven wheel to approach in the direction towards the positioning driven wheel, and at the moment, the transmission ratio of the transmission mechanism is reduced; when the rotating speed of the timing system power output mechanism is reduced, the ball slides towards the direction close to the positioning driving wheel along the inclined plane track, the variable driving wheel moves towards the direction close to the positioning driving wheel under the action of the pressing mechanism, the variable driven wheel moves towards the direction far away from the positioning driven wheel, and the transmission ratio of the transmission mechanism is increased at the moment.
By adopting the technical scheme, the transmission mechanism can automatically adjust the transmission ratio along with the change of the rotating speed of the output end of the timing system, and the transmission belt is always tensioned and can effectively transmit driving power while the change of the transmission ratio is realized.
In a further scheme, the transmission ratio change rule of the transmission mechanism is adapted to the requirement of the air inlet characteristic of the engine, a larger acceleration transmission ratio is adopted in a lower rotating speed working condition state, a relatively smaller acceleration transmission ratio is adopted in a higher rotating speed working condition state, and the transmission ratio change range is 1.3-2.6.
By adopting the technical scheme, the transmission ratio of the transmission mechanism is about 2.6 when the low rotating speed is 2500rpm, and the transmission ratio of the transmission mechanism is about 1.3 when the driving end rotates 7000 rpm. The matching effect of the supercharger and the working condition of the engine is more ideal, so that the power output characteristic of the supercharged engine can better meet the driving requirement of the vehicle.
In order to solve the technical problem of the structural arrangement of the supercharging system of the motor vehicle, the application also provides the motor vehicle comprising the supercharging system.
By adopting the technical scheme, the motor vehicle has the advantages of more compact structure, smaller size and larger design space and practical convenience.
In summary, the present application has at least one of the following beneficial technical effects:
1. the supercharging system driven by the timing system obviously reduces the length and complexity of a power transmission path, so that the overall structures of the power driving part and the super supercharging part are more compact, the transmission efficiency is higher, and the energy consumption is more saved.
2. The utility model provides a supercharging system can be regulated and control utilizes variable drive ratio, variable speed drive mode for the booster is more ideal with the characteristic matching optimization effect that admits air of the engine full operating mode scope, makes the power take off characteristic of supercharged engine satisfy the drive power requirement of vehicle better.
3. The pressurization method driven by the timing system can realize that the transmission ratio of the transmission mechanism is automatically adjusted along with the change of the rotating speed of the output end of the timing system, and the transmission belt is always tensioned and can effectively transmit the rotating speed while the change of the transmission ratio is realized.
Drawings
FIG. 1 is a schematic view of an embodiment of a timing system driven supercharging system according to the present application;
FIG. 2 is a schematic view of another embodiment of a boost system driven by the timing system according to the present application;
FIG. 3 is a schematic cross-sectional view of a first embodiment of a boost system driven by the timing system of the present application;
FIG. 4 is a schematic view of a driven wheel assembly of an embodiment of a boost system driven by the timing system of the present application in cooperation with a supercharger;
FIG. 5 is a schematic diagram of a timing system, a supercharger, and a transmission mechanism of an embodiment of a supercharging system driven by the timing system of the present application;
FIG. 6 is a schematic cross-sectional view of a second transmission mechanism of an embodiment of a boost system driven by the timing system of the present application;
FIG. 7 is a schematic perspective view of a second transmission mechanism of an embodiment of a boost system driven by the timing system of the present application;
FIG. 8 is a schematic structural diagram of a third embodiment of a boost system driven by the timing system of the present application;
FIG. 9 is an enlarged schematic view of FIG. 8 at A;
fig. 10 is a schematic view of a sectional structure B-B of fig. 9.
Reference numerals:
1. a transmission mechanism; 11. a drive wheel assembly; 111. positioning a driving wheel; 112. a variable driving wheel; 113. a rotational speed sensor; 114. an inclined plane track; 115. an active hold-down mechanism; 116. a displacement member; 12. a driven wheel assembly; 121. positioning the driven wheel; 122. a variable driven wheel; 123. a driven reset compression member; 13. a transmission belt; 2. a cylinder; 21. a cylinder housing; 22. a cylinder head; 3. a supercharger; 31. a machine base; 32. an input shaft; 33. a turbine; 34. a tubular body; 4. an intercooler; 5. a timing system; 51. a power take-off mechanism; 61. an oil supply pipe; 62. a control valve; 63. a clamping member; 64. a rotating gear; 65. opening and closing the piece; 66. mounting a plate; 67. a first mounting block; 68. a second mounting block; 69. a rotating shaft; 70. installing a shaft; 71. an engagement port; 72. an outer ring gear ring; 73. installing a sleeve; 74. a centrifugal lever; 75. a return spring; 76. avoiding the mouth; 77. a shielding cover; 78. avoiding the groove.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the present invention will be further described in detail with reference to the accompanying drawings. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined or explained in subsequent figures.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in a specific case to those of ordinary skill in the art.
In the description of the present application, it is to be understood that the terms "upper", "lower", "left", "right", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are only for convenience in describing the present application and simplifying the description, and do not indicate or imply that the referred devices or elements must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present application.
Some embodiments of the invention are described in detail below with reference to the accompanying drawings. Features in the embodiments described below may be combined with each other without conflict.
The first embodiment is as follows:
referring to fig. 1 and 2, a schematic view of a timing system 5 driven boost system is disclosed. The supercharging system comprises a cylinder 2 and a supercharger 3, wherein the cylinder 2 is provided with a cylinder housing 21, the supercharger 3 is provided with a base 31, and the supercharger 3 is fixedly arranged on the cylinder housing 21 through the base 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. Drive mechanism 1 includes action wheel subassembly 11 and follows wheel subassembly 12, is connected with drive belt 13 between action wheel subassembly 11 and follow wheel subassembly 12, and action wheel subassembly 11 is connected with the power take off end of cylinder 2, is connected with the power input end of booster 3 from wheel subassembly 12, and drive mechanism 1's drive ratio is greater than 1. The driving wheel assembly 11 and the driven wheel assembly 12 can also be in gear engagement or in chain or magnetic coupling transmission.
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 air inlet pipe of the air inlet component cylinder head 22 of the engine.
Referring to fig. 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 a synchronous pulley and transmits via 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 power output by the timing system 5 to the driven wheel assembly 12 through a transmission belt, and the driven wheel assembly 12 transmits power to the supercharger 3 through the input shaft 32 of the supercharger 3 which is fixedly connected. The input shaft 32 and the output shaft of the power output mechanism 51 have their axes parallel.
Example two:
referring to fig. 6 and 7, a difference from the first embodiment is that the driving wheel assembly 11 and the driven wheel assembly 12 are V-shaped friction wheels, the positioning driven wheel 121 of the driving wheel assembly 11 is fixedly connected with the power output mechanism 51, the variable driving wheel 112 is connected with an output shaft of the power output mechanism 51 by a spline, the output shaft is designed as a spline, the driving wheel assembly 11 is designed as a spline groove matched with the output shaft, the driving wheel assembly 11 can transmit the power of the power output mechanism 51, and the variable driving wheel 112 can move along the axial direction of the power output 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 is also in spline connection with the input shaft 32, the input shaft 32 is designed to be a spline, the variable driven wheel 122 is designed to be a spline groove matched with the input shaft 32, 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 comprises a positioning driving wheel 111, a variable driving wheel 112 and a rotation speed sensor 113, wherein when the rotation speed of the output end of the timing system 5 is increased, the rotation speed sensor 113 drives the variable driving wheel 112 to move in a direction away from the positioning driving wheel 111.
The driving wheel assembly 11 further includes a shifting member 116 and a driving pressing mechanism 115, the shifting member 116 is fixedly connected to the variable driving wheel 112, the rotation speed sensor 113 includes a ball and a slope rail 114, and the ball is disposed between the slope rail 114 and the shifting member 116. When the output end of the power output mechanism 51 of the timing system 5 increases in rotation speed, the balls slide along the inclined tracks 114 in a direction away from the positioning capstan 111 while pushing the shifting member 116 and the variable capstan 112 to move in a direction away from the positioning capstan 111. When the rotation speed of the output end of the power output mechanism 51 of the timing system 5 is reduced, the balls slide along the inclined track 114 in the direction approaching the positioning driving wheel 111, and the variable driving wheel 112 moves in the direction approaching the positioning driving wheel 111 under the action of the active pressing mechanism 115. Therefore, the transmission ratio of the transmission mechanism 1 is increased or decreased due to the change of the transmission equivalent diameter of the driving wheel and the transmission equivalent diameter of the driven wheel. The driving pressing mechanism 115 is implemented by a compression spring, an acting end of the driving pressing mechanism axially presses the variable driving wheel 112, and the other end of the driving pressing mechanism is fixedly connected with the shaft end of the power output mechanism 51 and is used for keeping the positioning driving wheel 111 and the variable driving wheel 112 to axially press the V-shaped transmission belt 13.
The driven wheel assembly 12 includes a positioning driven wheel 121, a variable driven wheel 122 movable closer to or away from the positioning driven wheel 121, and a driven return pressing member 123 for urging the variable driven wheel 122 closer to the positioning driven wheel 121.
When the rotation speed of the output end of the timing system 5 is increased and the variable driving wheel 112 moves away from the positioning driving wheel 111, the driven reset pressing piece 123 pushes the variable driven wheel 122 to approach towards the positioning driven wheel 121, and at this time, the transmission ratio of the transmission mechanism 1 is reduced; when the rotation speed of the output end of the timing system 5 is reduced and the variable driving wheel 112 moves towards the direction close to the positioning driving wheel 111 under the action of the driving pressing mechanism 115, the variable driven wheel 122 moves towards the direction far away from the positioning driven wheel 121, and the transmission ratio of the transmission mechanism 1 is increased.
The transmission ratio of the transmission mechanism 1 changes according to different rotating speeds output by the power output mechanism 51 of the timing system 5, the transmission ratio change rule of the transmission mechanism 1 adapts to the requirement of the air inlet characteristic of the engine, a larger speed-increasing transmission ratio is adopted in a lower rotating speed working condition, and a relatively smaller speed-increasing transmission ratio is adopted in a higher rotating speed working condition.
In this embodiment, the transmission ratio of the transmission mechanism 1 is about 2.6 when the power output mechanism 51 of the timing system 5 rotates at 2500rpm, and the transmission ratio of the transmission mechanism 1 is about 1.3 when the power output mechanism 51 of the timing system 5 rotates at 7000rpm, and the transmission ratio is varied in a range of 1.3 to 2.6.
Example three:
referring to fig. 8 to 10, different from the above embodiments, the supercharging system further includes an auxiliary oil supply unit, an auxiliary oil supply chamber of the auxiliary oil supply unit is used for storing gasoline, and the gasoline can enter the air inlet through the oil filling pipe, so that the ratio of gasoline in the air is increased while the air intake amount is increased, the utilization of oxygen in the air is increased, and the power of the engine is ensured.
An outer ring gear 72 is fixedly connected to the periphery of the peripheral side wall of the turbine 33, and the auxiliary oil supply chamber is located on one side of the pressurizing cover and is fixedly connected with the engine cover through bolts. The auxiliary fuel supply chamber is filled with gasoline. The auxiliary oil supply chamber is provided with an oil supplementing hole (not shown in the figure) and a plug cover (not shown in the figure) which is detachably connected with the auxiliary oil supply chamber and is used for plugging the oil supplementing hole.
The control valve 62 includes a clamping member 63 clamping the oil supply pipe 61, a rotating gear 64 connected between the worm wheel 33 and the clamping member 63, and an opening member 65 connected to the rotating gear 64.
The holding member 63 includes a mounting plate 66 spaced apart from one side of the tube body 34, a first mounting block 67 fixedly connected to one side of the mounting plate 66 close to the tube body 34, a rotating shaft 69 passing through the mounting block, a second mounting block 68 mounted on the rotating shaft 69, a holding plate 46 mounted on one side of the second mounting block 68 away from the mounting plate 66, and a torsion spring (not shown) sleeved on the rotating shaft 69 and used for driving the holding plate 46 to rotate around the rotating shaft 69.
Two first mounting blocks 67 are distributed at intervals, and two ends of the rotating shaft 69 are respectively arranged between the two first mounting blocks 67 in a penetrating manner.
The second mounting blocks 68 are two and are all 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 abuts against the side of the holding plate 46 close to the mounting plate 66. The holding plate 46 has one end against which the torsion spring is abutted as a driving end, and the other end forms a holding space with the mounting plate 66. The two ends of the oil filling pipe are arranged highly, the higher end of the oil filling pipe is connected with the auxiliary oil supply chamber, and the lower other end of the oil filling pipe penetrates through an intake valve of the engine.
The rotating gear 64 is rotatably connected to the outer side wall of the ring tube body 23 through a mounting shaft 70, a meshing port 71 for the rotating gear 64 to extend into is further formed in the tube body 34, and the meshing port 71 penetrates through the tube body 34 along the wall thickness direction of the tube body 34.
The rotary gear 64 is meshed with an outer ring gear 72 of the turbine 33 through a meshing port 71.
The opening and closing member 65 includes a mounting sleeve 73 fixedly connected to the lower surface of the rotating gear 64, an eccentric rod 74 inserted into the mounting sleeve 73, and a return spring 75 connected between the mounting sleeve 73 and the eccentric rod 74.
A plurality of installation sleeves 73 are arranged at intervals around the axis of the rotating gear 64, telescopic grooves are formed in the installation sleeves 73 along the radial direction of the rotating gear 64, and one ends of the telescopic grooves, which are away from the axis of the rotating gear 64, penetrate through the installation sleeves 73.
The worm gear 33 drives the rotation gear 64 to rotate through the outer ring gear 72, and when the rotation gear 64 rotates, the centrifugal rod 74 is subjected to centrifugal action and moves away from the axis of the rotation gear 64 along the length direction of the telescopic slot, and at the moment, the return spring 75 is pulled and generates corresponding reaction force.
When the engine camshaft 56 rotates, the turbine 33 and the rotary gear 64 rotate, so that the centrifugal lever 74 is subjected to centrifugal force, and the centrifugal lever 74 extends out of the telescopic slot. The part of the centrifugal rod 74 extending out of the telescopic groove is abutted to the driving section of the clamping plate 46, and drives the driving section of the clamping plate 46 to rotate towards the mounting plate 66, at the moment, the clamping space between the other end of the clamping plate 46 and the mounting plate 66 is enlarged, so that the clamping effect on the oil filling pipe is weakened, and therefore gasoline in the auxiliary oil supply chamber enters the air inlet door through the oil filling pipe, the content of gasoline in oil-gas concrete is increased while air inlet is improved, oxygen pressed into the air through the pressurizing component is fully utilized, and the generation of useless power is reduced.
When the rotation speed of the camshaft 56 of the engine is further increased, the centrifugal rod 74 drives the clamping plate 46 to rotate, the evaluation rate is increased, the length of the centrifugal rod 74 extending out of the telescopic groove is increased, the rotating amplitude of the clamping plate 46 is increased, the clamping effect on the oil filling pipe is weakened, and the amount of gasoline entering the air inlet through the oil filling pipe is increased.
When the rotating speed of the camshaft 56 of the engine is gradually reduced, the rotating speed of the rotating gear 64 is reduced, the centrifugal force sensed by centrifugation is reduced, the centrifugal rod 74 is gradually retracted to the telescopic groove under the action of the return spring 75 until the rotating path of one end, extending out of the telescopic groove, of the centrifugal rod 74 is positioned on one side of the clamping plate 46, at the moment, because the oil filling pipe is clamped by the clamping piece 63, gasoline cannot enter the air inlet door through the oil filling pipe, and therefore the phenomena that when the power of the engine is low, the concentration of the gasoline filled into an oil-gas mixture of the engine is too high, and accordingly insufficient combustion and waste occur are reduced.
In order to reduce the leakage of the air compressed in the housing 6 from the avoiding opening 76, a shielding cover 77 is fixedly connected to the inner wall of the bobbin body 34, the shielding cover 77 is disposed corresponding to the avoiding opening 76, and an avoiding groove 78 for the centrifugal rod 74 to rotate and pass through is disposed in the middle of the shielding cover 77.
The avoiding cover divides the interior of the housing 6 and the centrifugal rod 74, and the quality of air compression is guaranteed.
Example four:
based on a timing system driven supercharging system, the embodiment provides an adjustable supercharging method driven by a timing system 5, and the supercharging method specifically includes, but is not limited to, the following steps:
acquiring a rotation 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 is increased, the balls slide along the inclined tracks 114 in the direction away from the positioning driving wheel 111 while pushing the shifting element 116 and the variable driving wheel 112 to move in the direction away from the positioning driving wheel 111, the driven reset pressing element 123 pushes the variable driven wheel 122 to approach in the direction of the positioning driven wheel 121, and at this time, the transmission ratio of the transmission mechanism 1 is reduced;
when the rotation speed of the power output mechanism 51 of the timing system 5 is reduced, the balls slide along the inclined tracks 114 in the direction of approaching the positioning driving wheel 111, the variable driving wheel 112 moves in the direction of approaching the positioning driving wheel 111 under the action of the pressing mechanism, the variable driven wheel 122 moves in the direction of separating from the positioning driven wheel 121, and the transmission ratio of the transmission mechanism 1 is increased.
The transmission ratio change rule of the transmission mechanism 1 is adapted to the requirement of the air inlet characteristic of the engine, a larger speed-raising transmission ratio is adopted in a lower rotating speed working condition state, a relatively smaller speed-raising transmission ratio is adopted in a higher rotating speed working condition state, and the transmission ratio change range is 1.3-2.6.
Example five:
the embodiment discloses a motor vehicle which is provided with a supercharging system driven by a timing system in the first embodiment to the third embodiment and adopts the adjustable supercharging method in the fourth embodiment to supercharge.
It should be noted that, in the above embodiments, the supercharger 3, the cylinder 2, the intercooler 4 and the timing system 5 are all in the prior art, and those skilled in the art can understand that, therefore, the working structure and the working principle are not specifically described.
The foregoing shows and describes the general principles, essential features, and advantages of the invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only for the purpose of illustrating the principles of the invention, but that there are many variations, modifications, substitutions and alterations without departing from the spirit and scope of the invention, which fall within the scope of the invention as claimed.
Claims (7)
1. A timing system driven supercharging system comprising a power take-off (51) of a timing system (5) and a supercharger (3), characterized in that the supercharger (3) is fixedly mounted above the timing system (5), the supercharging system further comprising:
the transmission mechanism (1) comprises a driving wheel assembly (11) and a driven wheel assembly (12), the driving wheel assembly (11) is connected with the output end of a power output mechanism (51) of the timing system (5), and the driven wheel assembly (12) is connected with the input end of the supercharger (3);
the transmission mechanism (1) transmits power output by an output end of a timing system (5) to an input end of the supercharger (3), and the transmission ratio of the transmission mechanism (1) is greater than 1;
the transmission ratio of the transmission mechanism (1) changes according to different rotating speeds output by a power output mechanism (51) of a timing system (5), the change rule of the transmission ratio of the transmission mechanism (1) adapts to the requirement of the air inlet characteristic of an engine, a large acceleration transmission ratio is adopted in a low rotating speed working condition state, and a relatively small acceleration transmission ratio is adopted in a high rotating speed working condition state;
the driving wheel assembly (11) comprises a positioning driving wheel (111), a variable driving wheel (112) and a rotating speed sensor (113), and when the rotating speed of the output end of the timing system (5) is increased, the rotating speed sensor (113) drives the variable driving wheel (112) to move towards the direction far away from the positioning driving wheel (111);
the driving wheel assembly (11) further comprises a shifting piece (116) and a driving pressing mechanism (115), the shifting piece (116) is fixedly connected with the variable driving wheel (112), the rotating speed sensor (113) comprises a ball and an inclined plane track (114), and the ball is arranged between the inclined plane track (114) and the shifting piece (116);
the driven wheel assembly (12) comprises a positioning driven wheel (121), a variable driven wheel (122) and a driven reset pressing piece (123), wherein the variable driven wheel (122) can move close to or away from the positioning driven wheel (121), and the driven reset pressing piece (123) is used for driving the variable driven wheel (122) to be close to the positioning driven wheel (121);
the driving wheel assembly (11) and the driven wheel assembly (12) are V-shaped friction wheels, and the driving wheel assembly (11) and the driven wheel assembly (12) are driven by a driving belt (13).
2. Supercharging system according to claim 1, characterized in that it further comprises an intercooler (4) and an engine, the output of the supercharger (3) being connected to the inlet of the intercooler (4), the outlet of the intercooler (4) being connected to the intake part of the engine.
3. The supercharging system of claim 1, wherein the gear ratio variation ranges from 1.3 to 2.6.
4. The supercharging system according to claim 1, characterized in that, when the rotational speed of the output of the timing system (5) increases, the balls slide along the ramp tracks (114) in a direction away from the positioning drive (111) while pushing the shifting element (116) and the variable drive (112) in a direction away from the positioning drive (111), and when the rotational speed of the output of the timing system (5) decreases, the balls slide along the ramp tracks (114) in a direction towards the positioning drive (111), and the variable drive (112) moves in a direction towards the positioning drive (111) under the action of the active pressing mechanism (115).
5. The supercharging system according to claim 4, characterized in that when the output rotation speed of the timing system (5) increases and the variable driving wheel (112) moves away from the positioning driving wheel (111), the driven return 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) is reduced; when the rotating speed of the output end of the timing system (5) is reduced and the variable driving wheel (112) moves towards the direction close to the positioning driving wheel (111) under the action of the driving pressing mechanism (115), the variable driven wheel (122) moves towards the direction far away from the positioning driven wheel (121), and the transmission ratio of the transmission mechanism (1) is increased at the moment.
6. A method of controlled boosting driven by a timing system, adapted to the boosting system of claim 5, said method comprising:
acquiring a rotating speed value of a power output mechanism (51) of a timing system (5);
when the rotating speed of a power output mechanism (51) of the timing system (5) is increased, the balls slide along the inclined track (114) to the direction far away from the positioning driving wheel (111) and push the displacement piece (116) and the variable driving wheel (112) to move to the direction far away from the positioning driving wheel (111), the driven reset pressing piece (123) pushes the variable driven wheel (122) to approach to the direction of the positioning driven wheel (121), and the transmission ratio of the transmission mechanism (1) is reduced;
when the rotating speed of the power output mechanism (51) of the timing system (5) is reduced, the balls slide along the inclined track (114) towards the direction close to the positioning driving wheel (111), the variable driving wheel (112) moves towards the direction close to the positioning driving wheel (111) under the action of the pressing mechanism, the variable driven wheel (122) moves towards the direction far away from the positioning driven wheel (121), and the transmission ratio of the transmission mechanism (1) is increased at the moment.
7. Supercharging method according to claim 6, characterized in that the transmission ratio variation law of the transmission mechanism (1) is adapted to the requirements of the engine intake characteristics, a large upshift transmission ratio is adopted in a low speed operating state, and a relatively small upshift transmission ratio is adopted in a high speed operating state, and the transmission ratio variation range is 1.3-2.6.
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| CA2743271A1 (en) * | 2010-06-14 | 2011-12-14 | Thomson Superchargers | Belted gear assembly for driving a supercharger |
| US20170211467A1 (en) * | 2016-01-25 | 2017-07-27 | Accessible Technologies, Inc. | Freewheel clutch for supercharger resonance reduction |
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|---|---|---|---|---|
| CN1585866A (en) * | 2002-09-30 | 2005-02-23 | 乌尔里克·罗斯 | Epicyclic gear |
| CN1499056A (en) * | 2002-10-29 | 2004-05-26 | Avl��˹������˾ | I.C. engine with one crankshaft |
| WO2011145222A1 (en) * | 2010-05-21 | 2011-11-24 | トヨタ自動車株式会社 | Vehicle gear shifting control device |
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Effective date of registration: 20221215 Address after: 311100 Room 501-6, Building 2, No. 10, Lingang Road, Renhe Street, Yuhang District, Hangzhou City, Zhejiang Province Patentee after: Zhejiang Saturn Power Intelligent Manufacturing Co.,Ltd. Address before: No. 282, Renliang Road, Renhe street, Yuhang District, Hangzhou, Zhejiang 311100 Patentee before: Hangzhou Saturn Power Technology Co.,Ltd. |
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