Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
  • F01D17/00—Regulating or controlling by varying flow
  • F01D17/10—Final actuators
  • F01D17/12—Final actuators arranged in stator parts
  • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
  • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
  • F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
• • 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
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/12—Control of the pumps
  • F02B37/16—Control of the pumps by bypassing charging air
• • 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
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/12—Control of the pumps
  • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the invention relates to a turbine casing, in particular to a phase adjustable flow turbine casing comprising a staged adjustable flow cross section, which can effectively meet the supercharging requirements under different working conditions of the engine, and belongs to the field of engine supercharging.
• Turbocharging technology is gaining more and more attention as society's requirements for engine performance and emissions increase.
• the supercharging technology increases the intake pressure of the engine by increasing the intake pressure of the engine, so that the engine enters more gas in the same working volume, so the working cycle fuel supply can be increased accordingly, so that the engine can do more work.
• the engine's output power and torque are greatly increased, and the engine structure is relatively enhanced, so that the engine of the same power can adopt a smaller outer shape structure.
• the turbocharging technology uses the turbine to recycle the exhaust gas energy and substantially pressurizes the engine intake air through the compressor without substantially consuming the effective work of the engine; and the turbine has a muffling effect and further causes harmful components in the exhaust gas to further Reacted. So turbochargers increase the engine's power, economy and environmental friendliness. Turbocharging technology is one of the effective technologies for addressing energy shortages and high emissions regulations.
• the high-temperature exhaust gas flowing through the wastegate valve is reduced in distance due to the flow of the exhaust gas, so that the exhaust gas stays in the high temperature environment for a short time, and the harmful components in the exhaust gas which should be reacted in the high-temperature pipeline flow downstream or
• the high-temperature exhaust gas that is discharged into the atmosphere and is lost from the wastegate valve continues to expand in the downstream exhaust pipe, and a large part of the energy is converted into the vibration energy of the sound wave, which increases the engine emission noise. This causes the engine's emission performance to also decrease.
• variable-section turbochargers are a development direction.
• Various variable-section turbochargers have been developed, mainly with variable nozzle ring boosters and variable throat boosters. , tongue-shaped baffle booster, etc.
• the variable nozzle ring supercharger is one of the most advanced new turbochargers.
• Variable Nozzle The ring supercharger achieves a change in the flow cross-sectional area by adjusting the opening of the movable nozzle ring vane to adapt to the intake requirements of the engine under different operating conditions, achieving a good match between the supercharger and the engine.
• variable nozzle ring of the variable nozzle ring supercharger and its transmission and control mechanism are complex, with many parts, high material and processing requirements, making the cost too high, and it is difficult to form a strong market competitiveness.
• the nozzle ring blade system, including its transmission mechanism operates under engine vibration and high temperature conditions of six or seven hundred degrees Celsius or higher, which requires that the nozzle ring blades are movable, and that the nozzle ring blades and the nozzle ring are sealed well.
• the contradiction is formed because of the loss of the parts; the parts working under such conditions are easily deformed and damaged, and it is difficult to accurately adjust the nozzle ring blades, making the reliability and sealing of the variable nozzle ring supercharger difficult to ensure and the operating life is short. .
• the dual-flow turbine shell supercharger has also been greatly developed.
• the main principle is to divide the flow path into two according to the intake state of the turbine casing.
• the single-flow intake is adopted, and the high-speed working condition is adopted.
• the double-channel intake is used.
• the double-flow turbine casing has a relatively simple structure, low component processing requirements, easier implementation, longer working life and more reliability.
• many of the dual flow passages of the current dual-flow turbine casing are arranged side by side, that is, the arc lengths of the two flow passages are equal, as in the patent 201010279953. 8, so that the contact area of the exhaust gas in the flow passage is large, and the flow loss is large.
• the problem to be solved by the present invention is to provide an exhaust gas bypass valve type turbine casing, a variable nozzle ring type turbine casing, and the above-described known double-flow turbine casing (DLP) to provide an engine exhaust gas energy.
• DLP double-flow turbine casing
• the present invention adopts the following technical solutions:
• a staged adjustable flow turbine casing including a turbine casing
• a turbine assembly and an exhaust gas intake passage are installed in the turbine casing; and an intake port communicating with the exhaust gas intake passage is disposed on the turbine casing;
• An intermediate wall is disposed in the exhaust gas inlet flow passage, and the intermediate wall partitions the exhaust gas intake flow passage into an inner flow passage and an outer flow passage;
• the outer flow passage is provided with a first valve device capable of closing the outer flow passage;
• the intermediate wall A second valve device is provided that can connect or disconnect the inner flow passage from the outer flow passage.
• the inner flow passage is located at an inner side of the turbine casing, and the outer flow passage is located at an outer side of the turbine casing, the arcuate flow passage length of the outer flow passage is greater than the arcuate flow passage length of the inner flow passage, and the inner diameters of the inner flow passage and the outer flow passage are both Vertical to the turbine shell axis.
• the first valve device comprises a first valve installed in the outer flow passage
• the first valve is connected to the first valve shaft adjacent to the intake port, and the first valve shaft is located on the outer wall surface of the outer flow passage; the end of the first valve away from the first valve shaft can be driven by the first valve shaft.
• the rotation in the outer flow path downstream of the direction, that is, the angle formed by the first valve when rotating with the intermediate wall is always an acute angle.
• the axis of the first valve shaft is perpendicular to the center line of the outer flow passage.
• the outer side wall surface of the outer flow channel starts from a position where the first valve shaft is placed, and is provided with a A groove having a structural shape corresponding to the first valve to position the first valve adjacent to the outer side wall surface of the outer flow passage, that is, the groove serves as an extreme position of the first valve.
• the first valve shaft is connected with a first actuator control device.
• the first actuator control device comprises a first actuator mounted on the outside of the turbine housing by an actuator bracket, the first actuator being provided with a first actuator push rod, and the first actuator is provided a first piston, the first piston is sealingly connected to the housing of the first actuator, one end of the first actuator push rod is located in the first actuator and is fixedly connected with the first piston, and the other end is connected through the first The rod is drivingly coupled to the first valve shaft.
• the first actuator pusher is provided with a first actuator spring on the outside of the portion of the first actuator housing.
• the first actuator is provided with a first air hole, and the first air hole is connected with a first connecting pipe, and when installed, the first connecting pipe is in communication with the corresponding compressor outlet.
• the intermediate wall is provided with a bypass port at a position close to the air inlet
• the second valve device comprises a second valve installed at the bypass port, the second valve can be rotated in the outer flow channel, and the second valve is connected
• the axis of the second valve shaft is perpendicular to the center line of the outer flow channel.
• the second valve shaft is connected with a second actuator control device.
• the second actuator control device comprises a second actuator mounted on the outside of the turbine housing; the second actuator is provided with a second actuator push rod, and the second actuator is provided with a second piston, second The piston is sealingly connected to the housing of the second actuator, one end of the second actuator push rod is located in the second actuator and fixedly connected with the second piston, and the other end is connected to the second valve shaft through the second linkage rod Drive connection.
• the second actuator pusher is provided with a second actuator spring on the outside of the portion of the second actuator.
• the second actuator is provided with a second air hole, the second air hole is connected with a third communication tube, and the other end of the third communication tube is connected with a two-position three-way gas solenoid valve, and the working state of the second actuator By two three Control through a gas solenoid valve;
• the two-way three-way gas solenoid valve is provided with an outlet air hole, an inlet air hole and a air leakage hole.
• the outlet air hole is in communication with the third communication tube;
• the inlet air hole is connected to the corresponding compressor outlet channel through the second communication tube;
• the two three-way gas solenoid valves are electrically connected to the engine electronic control unit, and the working state of the two-way three-way gas solenoid valves is controlled by the engine electronic control unit.
• the invention realizes a flexible and variable working mode by the above-mentioned structure, and achieves efficient matching of the corresponding supercharger and the engine working conditions.
• the implementation of high, medium and low speed conditions is as follows:
• the staged adjustable flow turbine casing is designed to reduce the flow passage cross section and increase the flow rate of the exhaust gas in the turbine casing.
• the first actuator drives the first wide door to conform to the wall surfaces of the intermediate wall and the outer flow path to form a closed structure, preventing engine exhaust gas from entering the downstream of the outer flow path.
• the second actuator drives the second valve to engage the intermediate wall to close the bypass port, separating the inner flow path from the outer flow path.
• the arrangement of the intermediate wall is such that the turbine intake form is not full circumference, and the outlet nozzle has a small sectional area, so that the exhaust gas can flow into the turbine with high kinetic energy on the outlet nozzle ring of the turbine casing, and more exhaust gas energy is transmitted to
• the turbine makes full use of the exhaust gas energy, increases the speed of the turbine rotor, increases the intake air volume of the engine under low speed conditions, makes the engine do more work, increases the engine low speed torque, achieves a good match with the engine low speed condition, and improves the engine low speed. Dynamic and transient responsiveness of working conditions.
• the staged adjustable flow turbine casing should appropriately increase the flow passage cross section, increase the flow capacity, and ensure the flow rate required for the exhaust gas in the turbine casing.
• the first actuator drives the first valve to be separated from the intermediate wall
• the transmission and control mechanism of the supercharger drives the second valve to be separated from the bypass port on the intermediate wall, the second valve
• the rotating tip is adjacent to the first valve, ie the second valve is in another extreme position.
• the walls of the first valve and the second valve and the outer flow passage form a closed structure facing the outer flow passage, preventing engine exhaust gas from entering the downstream flow passage of the outer flow passage.
• the inner flow path and the outer flow path are connected by an open bypass port.
• the exhaust gas of the engine can enter the turbine casing from the inner flow exhaust gas inlet and the outer flow exhaust gas inlet of the turbine casing, but the closed structure is formed by the walls of the first valve and the second valve and the outer flow passage facing the outer flow passage.
• the exhaust gas merges into the downstream flow path of the inner flow path, and there is no exhaust gas flow downstream of the outer flow path.
• the turbine casing expands the flow cross section by opening the bypass port on the intermediate wall, and additionally increases the outer flow path exhaust gas based on the intake air of the inner flow exhaust gas inlet port.
• Inlet air intake the turbine casing has an additional increased amount of exhaust air, which is also in line with the fact that the engine has a limited amount of exhaust gas in the medium speed condition.
• the turbine casing passes through the inner exhaust air inlet and the outflow.
• the intake air inlet of the exhaust gas reaches the requirement of increasing the intake air amount of the exhaust gas, and the higher flow speed can be ensured.
• the angle formed by the first valve and the second valve respectively with the intermediate wall is always an acute angle, the flow field of the exhaust gas from the upstream of the outer flow passage through the bypass port to the downstream of the inner flow passage is relatively gentle, thereby reducing the flow loss.
• the outlet nozzle ring flow section of the mid-speed turbine casing is the same as the outlet nozzle ring flow section at low speed conditions.
• the turbine is also non-full-cycle intake, but the medium-speed intake is relatively low-speed.
• the booster employing the staged adjustable flow turbine casing is adapted to meet the intake requirements of the engine at medium speed conditions.
• the flow passage cross section of the stage type adjustable flow turbine casing of the present invention is increased to the maximum at high engine operating conditions.
• the first actuator drives the first valve to be close to the groove on the outer side wall surface of the outer flow passage, so that the upper and lower sides of the outer flow passage are connected, so that the exhaust gas entering from the exhaust gas inlet of the outer flow passage can smoothly flow into the outside.
• the downstream flow path of the flow channel is
• the second actuator drives the second valve to fit the intermediate wall to close the bypass port, separating the inner flow path from the outer flow path, so that the exhaust gas flowing downstream of the inner flow path is only from the inner flow path exhaust gas intake. mouth.
• the exhaust gas flows in the upstream and downstream of the entire outer flow passage, and the engine exhaust gas enters the inner and outer flow passages of the turbine casing, the inner flow passage and the outer flow passage, respectively, from the inner flow passage exhaust air inlet and the outer flow passage exhaust air inlet, respectively.
• the flowing exhaust gases do not affect each other.
• both the inner flow path and the outer flow path have exhaust gas flow so that the turbine intake air is in the form of a full circumference, so that the outlet nozzle ring has a larger outlet section for a larger flow of exhaust gas, so that the flow rate of the exhaust gas entering the turbine is not Will be too high to avoid overspeeding the turbine rotor.
• the arrangement of the intermediate wall allows the exhaust gas flow line to be parallel with the intermediate wall when the exhaust gas flows in the turbine casing, thereby avoiding a large lateral flow of the exhaust gas and reducing the flow friction between the large swirl flow and the exhaust gas of different layers. In order to transfer more exhaust gas energy to the turbine.
• the turbine's full-circumference intake distributes the intake air evenly, reducing the imbalance of the supercharger and increasing the efficiency of the turbine's conversion of exhaust energy.
• the turbine's full-circumference intake also allows all the exhaust gases from the engine to fully expand in the turbine casing, avoiding the disadvantage that the wastegate supercharger directly wastes part of the exhaust gas energy, and also creates a further reaction of harmful components in the exhaust gas. Conditions, reduce the harmful components of the exhaust pipe, reduce the emission noise, and improve the engine's emission performance.
• Turbine full-cycle intake avoiding the overspeed of the turbine rotor and fully utilizing the exhaust gas energy, achieving a good match between the supercharger using the stage-adjustable flow turbine shell and the high-speed engine condition, and improving the power of the engine at high speed. Sex and emissions performance.
• the supercharger adopting the stage type adjustable flow turbine shell according to the present invention can satisfy the intake requirements of various working conditions of the engine in high, medium and low conditions, and achieve efficient matching with various working conditions of the engine.
• the staged adjustable flow turbine casing of the present invention has a comparative bypass valve type turbine casing, a variable nozzle ring type turbine casing, and a known dual-flow type turbine casing (DLP) under various operating conditions.
• bypass valve type turbine casing in the low-speed working condition, only the inner flow passage has the exhaust gas flow in the stage-type adjustable flow turbine casing, and the flow characteristic is better than the bypass valve type turbine casing flow through the cooperation of the intermediate wall Road flow Good performance, because the stage adjustable flow turbine shell of the present invention only needs to close the outer flow passage and the bypass opening on the intermediate wall, the mode in which only the inner flow passage works alone is completely designed for low speed conditions, and
• the bypass valve type turbine casing flow passage is arranged in consideration of the flow state when the high-speed working condition bypass valve is opened, so that the low-speed working condition cannot be taken care of excessively.
• the staged variable flow turbine casing of the present invention still has an advantage in low speed conditions, and the second execution of the staged adjustable flow turbine casing
• the drive and control mechanisms of the bypass and the bypass turbocharger are the same.
• the stage-type adjustable flow turbine shell of the present invention has a design entry point in high, medium and low working conditions, while the bypass valve type turbine shell only takes the low speed condition as the entry point, and at high speed, it is taken care of by pure deflation. .
• the staged adjustable flow turbine casing of the present invention has higher exhaust gas energy utilization, especially under high engine operating conditions.
• the stage-type adjustable flow turbine casing of the present invention has only the inner flow passage with exhaust gas flow, so that the exhaust gas is flowing , less sag: transverse flow in the flow direction and mutual interference between different laminar flows, the flow exhaust gas is smaller in contact with the boundary in the cross section, reducing the flow loss, so that the exhaust gas energy is more transmitted to the turbine inlet Moreover, since only the inner flow path has exhaust gas flow, the distance from the gas inlet of the turbine casing to the nozzle ring of the turbine casing is shortened, and the area where the flowing exhaust gas contacts the boundary of the turbine casing is greatly reduced, further reducing the flow.
• the drawbacks of the variable nozzle ring turbine casing to excessively change the flow direction of the exhaust gas are avoided.
• the dual flow passage of the staged adjustable flow turbine casing has exhaust gas flow.
• the presence of the intermediate wall does not affect the flow in the inner and outer flow paths, reduces lateral swirling and flow friction, and reduces flow losses.
• Different nozzle ring types can be set at the outlet nozzle rings of the inner and outer flow passages so that the exhaust gases in both flow passages have an optimum angle to flow into the turbine.
• the turbine equipped with the turbine casing is full-cycle intake, and like the variable nozzle ring-type turbine casing, the turbine runs smoothly and the energy conversion efficiency is high.
• the turbine casing has a more reasonable exhaust gas flow field at low speed conditions, has higher efficiency, and has a slight advantage in high speed conditions. Therefore, with respect to the variable nozzle ring supercharger, the dual flow path structure of the turbine casing makes the exhaust gas flow more reasonable, and the energy loss during the flow is smaller, ensuring more energy entering the turbine. It is simpler in structure, fewer parts, less processing requirements, lower cost, easier mass production, higher reliability and longer operating life.
• the turbine casing of the present invention is relatively related to the background art.
• the dual-flow turbine casing described in the mentioned patent has the following improvements: in the case of low-speed conditions, the present invention is more than the turbine casings in which the two-flow passages are arranged side by side (ie, the arc lengths of the two flow passages are equal)
• the turbine casing adopts an internal flow passage intake mode, and the exhaust gas has a smaller flow distance in the flow passage, a smaller contact area with the wall surface, and less heat transfer with the wall surface, resulting in less energy loss.
• the total contact area of the exhaust gas and the flow channel wall surface in the stage-type adjustable flow turbine casing of the present invention is also smaller than that of the turbine casing in which the dual flow passages are arranged side by side.
• the staged adjustable flow turbine casing of the present invention also specifically increases the medium speed working mode, and improves the exhaust gas energy utilization rate in the medium speed working condition.
• the exhaust gas interferes with each other at the outlet nozzles at high speeds, increasing the energy loss; in the low-speed condition, the discharge angle of the exhaust gas at the outlet nozzles is easily deviated from the optimum angle, so that the turbine enters the turbine.
• the known turbine shells in which the two-channels are arranged side by side have high requirements on the casting process, and the design of the intermediate partition wall between the two flow passages is required to be high, and the intermediate partition walls are difficult to achieve the requirements of low flow loss and easy casting.
• the intermediate wall of the stage adjustable flow turbine shell is directly integrated with the two side wall surfaces of the turbine shell, that is, the casting is convenient, the process requirement is reduced, and the structural strength of the turbine shell is strengthened.
• FIG. 1 is a schematic structural view of a stage-type adjustable flow turbine casing according to an embodiment of the present invention
• FIG. 2 is a schematic structural view of a second actuator of a second control valve according to an embodiment of the present invention
• FIG. 3 is a view showing a relationship between a spring force and a deformation (N-S) of a second actuator according to an embodiment of the present invention
• FIG. 4 is a schematic structural view of a first actuator of a first control valve according to an embodiment of the present invention
• FIG. 5 is a diagram showing a relationship between a spring force and a deformation (N-S) of a first actuator according to an embodiment of the present invention
• FIG. 6 is a schematic view showing a working principle of a low speed condition of a turbine casing according to an embodiment of the present invention
• FIG. 7 is a schematic view showing the working principle of a medium speed condition of a turbine casing according to an embodiment of the present invention.
• Figure 8 is a schematic view showing the working principle of the turbine casing in a high speed working condition according to an embodiment of the present invention.
• a staged adjustable flow turbine casing includes a turbine casing 1 in which a turbine assembly 4 and an exhaust gas intake passage are installed, in an exhaust gas intake flow.
• the middle wall 2 is provided with an intermediate wall 2, which partitions the exhaust gas intake passage into an inner flow passage 3 and an outer flow passage 6, and the turbine casing 1 is provided with an air inlet communicating with the exhaust gas flow passage, the intake air
• the port includes an inner flow path exhaust gas inlet 8 communicating with the inner flow path 3 and an outer flow path exhaust gas inlet port 9 communicating with the outer flow path 6.
• the inner flow exhaust gas inlet 8 and the outer flow exhaust gas inlet 9 are respectively connected to the engine exhaust pipe, and the other end of the turbine assembly 4 passes through the intermediate body and is connected to the compressor.
• An outlet nozzle ring 5 is provided in the turbine housing 1 at a position adjacent to the turbine assembly 4.
• the outer casing structure of the turbine casing 1 can serve as a mounting base for the pneumatic or electronically controlled transmission and control mechanism of the present invention.
• the intermediate face of the intermediate wall 2 is perpendicular to the plane in which the centerlines of the inner runner 3 and the outer runner 6 are located, i.e., parallel to the axis of the turbine casing.
• the intermediate wall 2 has an arcuate configuration with an adjustable curvature, and the arcuate end of the intermediate wall 2 is connected to the outlet nozzle ring 5 and affects the intake angle of the exhaust gas into the turbine.
• the inner flow passage 3 is located inside the turbine casing 1, and the outer flow passage 6 is located outside the turbine casing 1.
• the curved flow passage length of the outer flow passage 6 is larger than the curved flow passage length of the inner flow passage 3, so that the low speed work In other words, only the distance in which the exhaust gas flows when the exhaust gas flows in the inner flow passage 3 is small.
• the centerlines of the inner flow passage 3 and the outer flow passage 6 are both perpendicular to the axis of the turbine casing.
• the intermediate wall 2 is provided with a bypass port 7 at a position close to the intake port, a second valve 21 rotatable in the outer flow channel 6 is installed at the bypass port 7, and a second valve shaft is connected to the second valve 21 22, the second valve shaft 22 is located on a side close to the bypass port 7 away from the air inlet, and the angle formed by the second valve 21 with the intermediate wall 2 is always an acute angle, so that the second wide door 21 is opened.
• the upstream flow path of the outer flow path 6 communicates with the inner flow path 3
• the exhaust gas flow can flow more smoothly from the upstream flow path of the outer flow path 6 to the downstream of the inner flow path 3, reducing the flow resistance.
• the axis of the second wide door shaft 22 is perpendicular to the center line of the outer flow path 6.
• the second valve shaft 22 is connected to a second actuator control device.
• the second actuator control device includes a second actuator 20 mounted externally of the turbine housing 1 via an actuator bracket 14.
• the second actuator 20 is provided with a second actuator push rod 31, and the second actuator 20 is provided with a second piston 24f.
• the second piston 24 and the second actuator 20 are sealed by a casing.
• one end of the second actuator push rod 31 is located in the second actuator 20 and is fixedly connected with the second piston 24, and the other end is drivingly connected to the second valve shaft 22 via the second linkage rod 26.
• a second actuator spring 23 is fitted to the outside of the portion of the second actuator pusher 31 located within the housing of the second actuator 20.
• the second actuator 20 is provided with a second air hole 25, the second air hole 25 is connected with a third communication tube 19, and the other end of the third communication tube 19 is connected with a two-position three-way gas solenoid valve 17, the second actuator The operating state of 20 is controlled by a two-position three-way gas solenoid valve 17.
• the two-way three-way gas solenoid valve 17 is provided with an outlet air hole, an inlet air hole and a air leakage hole 18. When installed, the outlet air hole communicates with the third communication tube 19; the inlet air hole passes through the second communication tube 15 and the corresponding compressor outlet passage
• the two-position three-way gas solenoid valve 17 is electrically connected to the engine electronic control unit ECU, and the operating state of the two-position three-way gas solenoid valve 17 is controlled by the engine electronic control unit ECU.
• the outer wall surface of the outer flow passage 6 is provided with a first valve 11 rotatable in the outer flow passage 6, and when the rotating top end of the first valve 11 is in contact with the intermediate wall 2, the intermediate wall 2 and the outer flow passage
• the wall surface of the 6 and the first valve 11 form a sealing structure to prevent the downstream intake of the outer flow path 6.
• the first valve 11 is connected to the first valve shaft 10 at one end of the air inlet, the first valve shaft 10 is located on the outer wall surface of the outer flow passage 6, and the first valve shaft 10 of the first valve 11 is separated from the first valve shaft 10 at the first end.
• the valve shaft 10 rotates in the outer flow passage 6 downstream of the intake direction, that is, the angle formed by the first valve 11 with the intermediate wall 2 is always an acute angle, so that when the first valve 11 is in contact with the intermediate wall 2, it can be used as the first The extreme position of the second valve 21 when it leaves the intermediate wall 2.
• the axis of the first valve shaft 10 is perpendicular to the centerline of the outer flow passage.
• the outer flow path 6 starts from a position at which the first valve shaft 10 is placed, and has a structural shape and a A corresponding "slot 16" of a wide door 11 is provided to position the first valve 11 when the outer side surface of the outer flow path 6 is adjacent, that is, the groove 16 serves as an extreme position of the first valve 11.
• the first valve shaft 10 is coupled to a first actuator control device.
• the first actuator control device includes a first actuator 13 mounted on the actuator bracket 14, and a first actuator pusher 32 is disposed outside the first actuator 13, the first actuator A first piston 28 is disposed in the first piston 28, and the first piston 28 is sealingly and slidably connected to the housing of the first actuator 13. One end of the first actuator push rod 32 is located in the first actuator 13 and is coupled to the first piston 28. The fixed connection is connected to the first valve shaft 10 via the first linkage rod 30.
• a first actuator spring 27 is fitted to the outside of the portion of the first actuator pusher 32 that is located within the housing of the first actuator 13.
• the first actuator 13 is provided with a first air hole 29, and the first air hole 29 is connected with a first communication tube 12, and when installed, the first communication tube 12 is in communication with a corresponding compressor outlet.
• the rotation ranges of the first valve 11 and the second valve 21 do not overlap each other and do not interfere with each other.
• the first valve 11 can take any angle between the two extreme positions as the working position, and the working position of the second valve 21 can only be in two extreme positions, that is, the second valve 21 is at the two limits. There is no working position between the locations.
• Figure 5 is a diagram showing the relationship between the spring force and deformation (N-S) of the first actuator, wherein ⁇ is the force magnitude and S is the deformation magnitude.
• the force and deformation of the first actuator spring 27 of the first actuator 13 are linear or approximately linear, and the force range is wide, so that the first valve 11 can be stopped between the extreme positions. One position.
• Figure 3 is a diagram showing the relationship between the spring force and deformation (N-S) of the second actuator, wherein ⁇ is the force magnitude and S is the deformation magnitude.
• the force and deformation of the second actuator spring 23 of the second actuator 20 are nonlinear, and the force range is small.
• the second actuator 20 is The second actuator pusher 31 and the second linkage lever 26 are actuated to cause the second valve 20 to quickly shift between extreme positions.
• the second valve 21 is controlled by a two-position three-way gas solenoid valve 17, and the control program is issued by the engine electronic control unit (ECU) according to the working conditions.
• ECU engine electronic control unit
• the ECU When the engine is in a low speed condition, the ECU sends a signal to cause the two-way three-way gas solenoid valve 17 to cut off the connection of the inlet and outlet air holes, and to connect the inlet air hole and the air leakage hole 18, the second actuator push rod 31 and the second.
• the linkage rod 26 drives the second valve 21 to close the bypass port 7 to isolate the inner and outer flow passages:
• the first actuator 13 drives the first linkage rod 30 to the first actuator push rod 32 to drive the first valve 11 and The intermediate wall 2 is fitted.
• the ECU When the engine is in the medium speed condition, the ECU sends a signal to connect the inlet air hole of the two-way three-way gas solenoid valve 17 with the outlet air hole, and disconnects the inlet air hole and the air release hole 18, and the second linkage rod 26 drives the second.
• the valve 21 leaves the bypass port 7 to communicate the inner and outer flow passages; at the same time, the first actuator 13 drives the second linkage rod 30 to drive the first valve 11 away from the intermediate wall 2 at a certain position between the extreme positions.
• the ECU When the engine is in high-speed working condition, the ECU sends a signal to make the two-way three-way gas solenoid valve 17 cut off the connection between the inlet air hole and the outlet hole, and connects the inlet air hole and the air leakage hole 18, and the second linkage rod 26 drives the second valve.
• the bypass port 7 is closed to isolate the inner and outer flow paths; at the same time, the first actuator 13 drives the first linkage rod 30 to bring the first valve 11 closer to the groove 16 on the outer flow path 6.
• the staged adjustable flow turbine casing is required to reduce the flow passage cross section and increase the flow rate of the exhaust gas in the turbine casing 1.
• the first actuator 13 drives the first valve 11, which is brought into contact with the wall faces of the intermediate wall 2 and the outer flow path 6, to form a closed structure, which prevents the engine exhaust gas from entering the downstream of the outer flow path 6.
• the second actuator 20 drives the second valve 21 to engage the intermediate wall 2 to close the bypass port 7 to separate the inner flow path 3 from the outer flow path 6.
• the staged adjustable flow turbine casing should appropriately increase the flow passage cross section, increase the flow capacity, and at the same time ensure the flow rate necessary for the exhaust gas in the turbine casing 1.
• the first actuator 13 drives the first valve 11 to be separated from the intermediate wall 2, and at the same time, the transmission and control mechanism of the supercharger drives the second valve 21 to be connected to the bypass port 7 on the intermediate wall 2. Separate, the rotating tip 13 of the second valve 21 is adjacent to the first valve 11, i.e., the second valve 21 is in the other extreme position.
• the walls of the first valve 11 and the second valve 21 and the outer flow path 6 form a closed structure facing the outer flow path 6, preventing engine exhaust gas from entering the downstream flow path of the outer flow path 6.
• the inner flow path 3 and the outer flow path 6 are connected by the open bypass port 7.
• the exhaust gas of the engine can enter the turbine casing 1 from the inner flow exhaust gas inlet 8 and the outer flow exhaust gas inlet 9 of the turbine casing 1, but due to the wall surfaces of the first valve 11 and the second valve 21 and the outer flow path 6.
• the outer flow passage 6 forms a closed structure, preventing the exhaust gas entering the outer flow passage 6 from the outer flow passage exhaust gas inlet 9 from flowing further downstream of the outer flow passage 6, and the snoring of the bypass opening 7 on the intermediate wall 2, so as to enter the outer flow passage 6
• the upstream exhaust gas can merge with the exhaust gas of the inner flow passage 3 through the bypass port 7 to flow into the downstream flow passage of the inner flow passage 3, and no exhaust gas flows downstream of the outer flow passage 6.
• the turbine casing 1 expands the flow cross section by opening the bypass port 7 on the intermediate wall 2, and additionally increases the intake air of the exhaust gas inlet 8 of the inner flow passage.
• the external flow path exhaust air inlet 9 intake air the turbine casing 1 additionally has a limited amount of exhaust gas intake, which is also in line with the fact that the engine has a limited amount of exhaust gas in the medium speed condition, and at this time, the turbine casing 1 passes through the inflow.
• the intake air inlet 8 and the outer flow exhaust air inlet 9 simultaneously increase the intake air amount and ensure a high flow speed.
• the angle formed by the first valve 11 and the second valve 21 with the intermediate wall 2 is always an acute angle, the flow field of the exhaust gas from the upstream of the outer flow passage 6 through the bypass port 7 into the downstream of the inner flow passage is relatively gentle. Thereby reducing flow losses.
• the flow cross section of the outlet nozzle ring 5 of the turbine casing 1 in the medium speed condition is the same as that of the outlet nozzle ring in the low speed condition.
• the turbine is also a non-full-cycle intake, but the medium speed condition is relatively low speed.
• the intake air volume is larger, the flow rate of the exhaust gas at the outlet nozzle ring 5 is larger, the energy that is introduced into the turbine is more, and the work that can be converted is more, so that the turbine rotor rotates at a higher speed, and the pressurization capability of the compressor is enhanced.
• the supercharger using the staged adjustable flow turbine casing is made to meet the intake requirements of the engine at medium speed.
• the staged adjustable flow turbine casing of the present invention increases the flow passage cross section to a maximum at high engine operating conditions.
• the first actuator 13 drives the first valve 11 so as to be close to the groove 16 on the outer side wall surface of the outer flow path 6, so that the upper and lower sides of the outer flow path 6 communicate with each other so as to enter the exhaust gas from the outer flow path exhaust gas inlet 9. It can smoothly flow into the downstream flow path of the outer flow path 6.
• the second actuator 20 drives the second valve 21 to be engaged with the intermediate wall 2 to close the bypass port 7, separating the inner flow passage 3 from the outer flow passage 6, so that the exhaust gas flowing downstream of the inner flow passage 3 is only From the inner flow exhaust gas inlet 8 .
• the exhaust gas flows in the upstream and downstream of the entire outer flow path 6, and the engine exhaust gas enters the inner flow path 3 and the outer flow path 6 of the turbine casing from the inner flow path exhaust gas inlet 8 and the outer flow path exhaust gas inlet 9, respectively.
• the exhaust gases flowing in the flow path 3 and the outer flow path 6 do not affect each other.
• both the inner flow passage 3 and the outer flow passage 6 have exhaust gas flow so that the turbine intake air is in the form of a full circumference, so that the outlet nozzle ring 5 has a larger outlet section for a larger flow of exhaust gas, so that the turbine can be entered.
• the exhaust gas flow rate is not too high to avoid overspeeding the turbine rotor.
• the exhaust gas flow line is parallel with the intermediate wall 2 as much as possible, to avoid large lateral flow of the exhaust gas, and to reduce the large swirl flow and the exhaust between the different layers of exhaust gas. Flow friction to transfer more exhaust gas energy to the turbine.
• the turbine's full-cycle intake makes the intake air evenly distributed, reducing the imbalance of the supercharger and improving the turbine conversion.
• the turbine's full-circumference intake also allows all the exhaust gases from the engine to fully expand in the turbine casing, avoiding the disadvantage that the wastegate type supercharger directly wastes part of the exhaust gas energy, and also creates a further reaction of harmful components in the exhaust gas. Conditions, reduce the harmful components of the exhaust pipe, reduce the emission noise, and improve the engine's emission performance.
• Turbine full-cycle intake avoiding the overspeed of the turbine rotor and fully utilizing the exhaust gas energy, achieving a good match between the supercharger using the stage-adjustable flow turbine shell and the high-speed engine condition, and improving the power of the engine at high speed. Sex and emissions performance.
• the stage-type adjustable flow turbine casing has a simple structure, flexible control and reliable operation. It meets the air intake requirements of various high and medium operating conditions of the engine to achieve efficient matching with various engine operating conditions.
• the efficiency of the supercharger with the staged adjustable flow turbine casing is superior to that of the variable nozzle ring pressure regulator, and the exhaust gas flow is more reasonable, the structure is simpler, the number of parts is smaller, and the reliability is higher.
• the bypass valve type supercharger the exhaust gas energy utilization efficiency is higher.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Supercharger (AREA)

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• 2012
  • 2012-01-11 CN CN201210006736.0A patent/CN102536433B/zh not_active Expired - Fee Related
  • 2012-03-31 WO PCT/CN2012/000428 patent/WO2013104090A1/fr not_active Ceased

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