WO2016078444A1 - Variable geometry wastegate turbine meeting the requirements of egr circulation and guide vane assembly - Google Patents

Abstract

Disclosed are a variable geometry wastegate turbine meeting the requirements of EGR circulation and a guide vane assembly, wherein the guide vane assembly comprises a guide vane support disk which is provided on a power turbine wheel intake end surface of the turbine and is of a ring shape; several first fluid guiding channels and second fluid guiding channels are arranged at intervals on the the guide vane support disk in the circumferential direction thereof, there is a pre-set included angle between the first fluid guiding channel and the second fluid guiding channel so that the waste gas flowing from an inner intake flow channel can be guided through the first fluid guiding channels to the power turbine wheel, and the waste gas flowing from an outer intake flow channel can be guided through the second fluid guiding channels to the power turbine wheel. The guide vane assembly can avoid or reduce gas flow disturbance, and avoid gas flow impact loss and turning loss, which not only improves the efficiency of the turbine, but also can broaden the flow rate.

Description

Variable section wastegate turbine and vane assembly for EGR cycle needs

The present application claims priority to the following five Chinese patent applications, the entire contents of which are hereby incorporated by reference.

1. Chinese patent application submitted to the China Patent Office on June 25, 2015, application number 201510358065.8, and the invention name is “a variable-section waste-by-pass turbine that meets the needs of EGR cycle”;

2. Chinese patent application submitted to China Patent Office on February 25, 2015, application number 201510086729.X, titled “a variable-section waste-by-pass turbine that meets the needs of EGR cycle”;

3. Chinese patent application filed on November 20, 2014, with the application number of 201410667139.1, and the invention titled “Exhaust Bypass Turbine with Guide Vane”.

Technical field

The present invention relates to the field of engine technology, and more particularly to a variable section wastegate turbine and vane assembly that meets the requirements of an RGR cycle.

Background technique

With the increasingly strict emission regulations, EGR is increasingly used in engines. EGR is called Exhaust Gas Recirculation. Chinese translation for exhaust gas recirculation is to send a small part of the exhaust gas generated by the engine back to the cylinder for combustion. Reduce NOx emissions.

NOx is a gas that is extremely harmful to the human body. It is mainly produced under conditions of high temperature and oxygen enrichment. The higher the combustion temperature and oxygen concentration, the longer the duration, and the more NOx is produced. During the operation of the engine, if part of the exhaust gas is reintroduced into the cylinder in a timely and appropriate amount, since the main component of the exhaust gas CO2 has a larger specific heat capacity, the exhaust gas can absorb and carry out part of the heat generated by the combustion, and bring out the intake air. A certain dilution, thus reducing the maximum temperature and oxygen content of the engine combustion, thereby reducing the formation of NOx compounds.

On supercharged medium-cooled diesel engines, the main way to achieve exhaust gas recirculation is to exhaust the exhaust gas before the turbine. After the introduction of the intercooler, called high-pressure exhaust gas recirculation, in order to ensure the EGR rate under different working conditions, the best way is to use a variable-section turbocharger to adjust the front PT and the middle of the turbine through the cross-section change of the supercharger. The pressure difference of PK after cooling drives the EGR valve.

At present, the most variable-section turbocharger is to add rotating nozzle vanes inside the turbine. By changing the opening degree of the nozzle vanes, the flow passage of the turbine is changed, and the control is convenient. However, since the exhaust gas emitted by the engine has a high exhaust temperature of about 700 degrees Celsius, and there is a tendency to further increase, the exhaust high temperature has strict requirements on the nozzle vane, the transmission mechanism, the nozzle ring support plate, and the external control system, and the engine discharges. Impurities in high temperature exhaust gases pose a reliability hazard to complex moving parts.

Moreover, this type of product is only used in the field of high-end engine pressurization due to expensive price factors. This type of variable-section turbocharger limits marketing in terms of both cost and reliability. In addition to the above main factors, there are some other technical issues:

Problem 1. When the flow rate is reduced, the nozzle opening degree of the small nozzle needs to be closed, the circumferential speed of the turbine intake is increased, and the turbine becomes an impulsive impeller, which is not conducive to the full utilization of the exhaust gas energy, the turbine efficiency is low, and the engine exhaust is caused. Back pressure is too high.

Problem 2: When the blade is opened, the flow path of the turbine intake increases, and the flow loss increases along the path; the nozzle blades are too far from the turbine, and the airflow mixing loss increases.

Problem 3, there must be a gap at both ends of the blade to facilitate the rotation of the blade, but this gap will cause leakage loss and reduce turbine efficiency.

Another variable-section application that is used more is the two-stage flow-path variable-section turbocharger developed by Kangyue Technology. Through the structural design of the traditional turbine shell, the combination of the inner and outer double-layer intake passages is used to form different The flow cross section, the effective segmentation utilizes the exhaust energy of the engine, can realize all the functions of the variable-section turbine, and does not need to set a complicated rotary vane pneumatic adjustment mechanism, the cost is greatly reduced, the reliability is greatly improved, and it will be the future. A research direction.

The structural principle of this type of product is shown in Figure 1. When the engine is running at low speed and low load, the boost pressure is low, the regulating valve 5 is closed, and the turbine casing 1 only has the intake inner flow passage 3 acting, and the air flow is along the inner flow passage. The flow direction 4 flows in, driving the turbine to do work.

As shown in FIG. 2, when the boost pressure reaches a certain level, the control actuator 7 pushes the valve pin assembly 6, the valve pin assembly 6 drives the regulating valve 5 to open, and the intake inner flow passage 3 and the intake air flow. At the same time, the channel 2 acts, and the airflow flows in the flow direction 4 of the inner flow path and the flow direction 8 of the outer flow path to drive the turbine to perform work. However, this structure has also found many problems in the actual test and application process.

as follows:

1. The distribution of the inner and outer runners will produce multiple vortex tongues, the gas flow will easily affect each other, resulting in reduced turbine efficiency; and the turbine with internal and external dual runners has a complex structure, and the turbine is a casting, so production consistency It is difficult to control, and the casting deviation of the double flow channel is large, which has a great influence on the matching performance of the turbine.

Second, in the medium and medium load sections of the engine, the simple valve structure shown in Figures 1 and 2 cannot accurately control the flow and pressure, and the control deviation of flow and pressure will not only affect the matching performance, but also affect the EGR rate. Control, resulting in excessive engine emissions.

Summary of the invention

In order to solve the above technical problem 1, the present invention provides a variable-section exhaust gas bypass turbine and a vane assembly that meets the requirements of an RGR cycle, which can avoid reducing airflow disturbance, avoiding airflow impact loss and cornering loss, and improving Turbine efficiency also broadens the flow.

The present invention provides a vane assembly for a variable-section exhaust gas bypass turbine, the vane assembly including a vane support disc disposed at an inlet end face of a turbine power turbine;

The vane support discs are arranged along the circumferential direction thereof with a plurality of first flow guiding channels and a second flow guiding channel, the first guiding channels and the second guiding channels having a predetermined angle so that the Exhaust gas flowing out of the intake inner flow passage can be guided to the power turbine through the first flow guiding passage, and exhaust gas flowing out of the intake outer flow passage can be guided to the power turbine through the second guiding passage .

Optionally, the circumferential surface of the vane support disk is provided with a plurality of guide vanes protruding from the annular surface, and the guide vanes are opened with a flow guiding groove extending through the vanes to form the slotted guide vanes;

A passage between adjacent ones of the slotted guide vanes forms the first flow guiding channel, and the flow guiding groove forms the second flow guiding channel.

Optionally, the annular surface of the vane support disk is provided with long guide vanes and short guide vanes protruding from the annular surface and spaced apart, and the long guide vanes to the short guide vanes in a counterclockwise direction The passage between the two forms the second flow guiding channel, and the passage between the short guide vane and the long guide vane forms the first Diversion channel.

Optionally, the arrangement angle B of the long guide vanes is 68°-80°, and the arrangement angle A of the short guide vanes satisfies: B-A=0°～5°;

Wherein, the arrangement angle B is a tangent to the central axis of the long guide vane, the tip of the long guide vane near the center of the vane support disc and the center of the vane support disc, the angle between the two; The arrangement angle A is a tangent to the central axis of the short vane, and the short guide vane is adjacent to the center of the vane support disc and the center of the vane support disc, the angle between the two.

The present invention also provides a variable section wastegate turbine that meets the requirements of an RGR cycle, including a turbine casing and a power turbine, the turbine casing being provided with diversion engine exhaust gas to the power turbine to drive the rotation of the power turbine An inner gas passage and an outer air intake passage, wherein the power turbine intake end surface position is provided with a vane assembly according to any of the above.

Optionally, an adjustment valve with an adjustable opening is provided for adjusting an intake air amount of the intake air flow passage; and the adjustment valve is a rotatable central valve. When rotating, the exhaust gas can pass through the valve body. Enter on both sides.

Optionally, the regulating valve is inserted into the turbine casing to directly adjust the amount of intake air entering the intake outer flow passage.

Optionally, the turbine is provided with two sets of the intake outer flow passage and the intake inner flow passage corresponding to the six-cylinder engine, and the adjustment valve includes two valve bodies connected to each other, and is inserted into the turbine shell. Thereafter, the two valve bodies respectively control the intake air amounts of the two intake air flow passages respectively.

As the engine speed increases, the gas flow rate increases, and the intake air flow path participates in the intake air as the regulating valve opens. In the present scheme, the first diversion channel and the second diversion channel are respectively set according to the intake angles of the intake inner flow passage and the intake outer flow passage, and the exhaust gas of the intake inner flow passage flows to the power turbine through the first diversion passage. The exhaust gas of the external flow passage of the intake air flows to the power turbine through the second flow guiding passage, and the exhaust gas of the two flow passages leading to the power turbine does not interfere with each other, thereby reducing the airflow disturbance, avoiding the collision loss and the cornering loss of the airflow, and not only improving the efficiency of the turbine, but also Can broaden traffic. In addition, the pressure ratio and flow rate of the turbine have a great influence on its performance, and the flow passage determines the flow passage cross section. The prior art relies on the flow path design of the turbine casing to control the flow cross section, but as described in the background art, casting The production consistency of the turbine is difficult to control, and the flow rate is difficult to control accordingly. In the embodiment, the vane assembly is provided, and the flow passage area can be controlled by the vane, and the vane assembly can be precisely formed, and the flow area can be obtained.

+ To the precise control, so as not to be affected by the machining accuracy of the turbine casing itself.

The present invention provides a variable-section exhaust gas bypass turbine that meets the needs of an EGR cycle, including a turbine casing having an intake inner flow passage and an intake outer flow passage, an intake inner flow passage and an intake outer flow passage. The non-peripheral structure is adopted respectively, and the intake inner flow passage is responsible for the intake of the power turbine from 0° to (150 to 230)°, and the intake outer flow passage is responsible for the intake of (150 to 230)° to 360°; the turbine casing There is also a waste gas bypass line which is arranged in parallel with the intake outer flow passage and the intake inner flow passage, but does not pass through the power turbine.

The following is a further optimization of the above solution by the present invention:

The turbine also includes a power turbine, a valve seat, an exhaust pipe, and a control accessory thereof, the turbine casing, the valve seat, and the exhaust pipe being sealingly coupled together.

Further optimization: a valve for adjusting the intake air flow rate of the intake air passage is installed in the valve seat.

Further optimization: the regulating valve is installed in the valve seat by adjusting the valve sleeve, and one end of the regulating valve is connected with the control accessory.

Further optimization: the other end of the regulating valve is provided with an adjusting surface, and the adjusting surface is a spiral structure, and its axial height spirals around its own axis.

advanced optimization:

The waste gas bypass line is provided with a waste gas bypass valve that can cooperate with the regulating valve, and the waste gas bypass valve is installed in the valve seat through the wastegate valve bushing, the waste gas bypass valve and the waste gas bypass valve shaft The sleeve is equipped with a spring, and the side of the waste bypass valve close to the regulating valve is provided with an adjusting rod that cooperates with the adjusting surface.

During operation, the control accessory drives the adjustment valve to rotate, adjusts the intake air volume of the intake air passage, adjusts the adjustment surface of the valve to push the adjustment rod, the waste gas bypass valve opens, and compresses the spring. At this time, the bypass exhaust gas bypasses the exhaust gas. The pipeline is discharged. When the valve is adjusted, the wastegate valve returns to the position under the spring force, and the exhaust gas is no longer bypassed.

Further optimization: a guide vane support disc is arranged in the turbine shell near the power turbine, and the vane support disc is provided with a plurality of slotted vanes, and the plurality of slotted vanes are uniformly arranged in a ring shape.

A guide groove is arranged in the middle of the slotted guide vane, and the arrangement angle of the slotted guide vane is 68°-80°, and the two groove sides of the guide groove are obtained by rotating the cutting line around the center of the guide vane support disc, and the slot width is the most Narrow Press 3mm control.

The slotted guide vane is in the form of a gas-solid composite nozzle. When the engine is under low speed and low load, the inner passage of the turbine intake air acts. At this time, the intake angle of the intake inner passage is determined by the formula tan(α)=2πb/(A /r) Obtained, where b is the turbine inlet width, which is a fixed value, and the intake angle is determined by the A/r of the intake air passage.

The vane angle of the inner flow passage of the intake air is designed according to the intake angle of the inner flow passage of the intake air to ensure that the two angles are basically the same. The gas enters the vane along the inner flow passage of the intake air, and then enters the power turbine along the vane, and there is no turning loss in the middle. , high pneumatic efficiency.

As the engine speed increases gradually, the gas flow rate increases, and the intake air flow path will participate in the intake with the opening of the regulating valve. The outer flow path intake angle is also determined by the A/r of the intake air flow path, and the angle of the guide groove is pressed. The intake angle of the out-of-gas flow passage is designed to ensure that the two angles are basically the same. The gas enters the guide trough along the outer flow passage of the intake air, and then enters the turbine along the guide trough to avoid impact loss when installing the complete guide vane (without the guide trough). And the loss of turning, not only improved efficiency, but also widened the flow. Moreover, as the airflow velocity increases, the radial velocity component rises faster, and the presence of the diversion groove makes the flow rate widening of the high speed section more obvious.

In actual work, when the engine is at low speed and low load, the regulating valve is closed, and the intake air is along the exhaust pipe, the valve seat gas inlet, the valve seat inner flow passage interface, the turbine casing inner flow passage inlet, the intake inner flow passage, and the opening. The trough guide vanes flow into the turbine to drive the turbine to work. At this time, the airflow flows to the turbine along the middle of the two slotted guide vanes to drive the turbine to work. At this time, only the intake inner passage acts, the cross section is small, and the flow through the vane It also flows only along the vane angle, and the airflow is concentrated, which can increase the pre-vortex pressure and increase the EGR rate.

When the engine speed and load gradually increase, the regulating valve starts to open, part of the airflow flows through the regulating valve, and flows into the turbine along the outer flow passage interface of the valve seat, the outer runner inlet of the turbine casing, the outer flow passage of the intake air, and the slotted guide vane to adapt to the gradual adaptation. Increased flow demand, in this process, by adjusting the opening of the regulating valve, the pre-vortex pressure can be adjusted to determine the appropriate EGR rate.

In the process of adjusting the regulating valve, after the regulating valve is turned to a certain angle, the adjusting rod is applied with a thrust through the adjusting surface, the adjusting rod drives the waste bypass valve to compress the spring, the waste gas bypass passage is opened, and the exhaust gas bypasses the exhaust pipe exhaust gas. The outlet, the valve seat waste bypass inlet, the valve seat waste bypass outlet, the turbine casing waste bypass inlet, and the turbine casing waste bypass outlet flow out, and a part of the exhaust gas energy is discharged to ensure the supercharger vortex pressure at high speed and high load of the engine. Not too big. And, with As the intake air volume increases, the intake air flows along the guide grooves on the slotted guide vanes, avoiding airflow blockage in the high speed section.

Another optimization scheme: the slotted guide vane includes a long guide vane and a short guide vane, the length of the long guide vane is larger than the length of the short guide vane, and the long guide vane and the short guide vane are spaced apart.

The trailing edge of the small vane is spaced apart from the leading edge of the long vane by a distance in the circumferential direction. It facilitates the flow of air from this point during high-speed engine operation, which can widen the flow and reduce the blockage. The function is similar to that of the slotted guide vane.

The arrangement angle of the long guide vanes is 68° to 80°, and the angular difference between the arrangement angle B of the long guide vanes and the arrangement angle A of the short guide vanes 33 is: B-A=0° to 5°.

The invention adopts a gas-solid composite nozzle, combined with the advantages of both the variable flow passage and the rotary nozzle vane, solves the above problems and forms an innovative variable section solution. Moreover, the slotted guide vane and the long and short guide vane structure of the present invention can change the intake angle, widen the high-speed flow range, and balance the high and low speed turbine performance with the fixed-length guide vane structure. The guide vane realizes the adjustment of the intake angle which can be realized by rotating the nozzle vane, the turbine efficiency is obviously improved, the presence of the vane reduces the backflow of the airflow, not only improves the efficiency of the turbine, but also makes the airflow flow smoothly, avoiding the airflow at the throat. Disturbance, the fuel consumption rate achieves a substantial reduction in the entire matching line.

The invention also provides the following technical solutions:

A variable-section exhaust gas bypass turbine that meets the needs of an EGR cycle, including a turbine casing having a power turbine and an intake runner mounted therein, the turbine casing being disposed adjacent to a power turbine tail to provide a power turbine The introduced gas is introduced into the leafless nozzle of the intake runner;

A vane assembly that adjusts the flow capacity of the turbine casing by changing the number, size, angle, and arrangement of the vanes is mounted in the turbine casing adjacent to the vaneless nozzle.

The following is a further optimization of the above solution by the present invention:

The vane assembly includes a plurality of vanes arranged in a circular arrangement.

Another optimization: the guide vanes include long guide vanes and short guide vanes, the length of the long guide vanes is larger than the length of the short guide vanes, and the long guide vanes and the short guide vanes are spaced apart.

The size of the long and short vanes is determined by flow analysis, but the advantage of using small vanes is to broaden the flow, similar to the length of the compressor impeller, reducing clogging.

Another optimization: a plurality of vanes are separated by a guide vane, and a guide trough is formed on the vane. The direction of the guide trough is consistent with the vane to increase the flow rate at the high point.

The invention adjusts the flow capacity of the turbine shell by adjusting the number, size, angle and arrangement of the vanes, which not only reduces the cost, accelerates the research and development speed, improves the matching precision, but also obtains a major breakthrough in principle. Not only can a series of superchargers share a turbine shell, which greatly reduces the cost of the mold, but also fine-tunes the flow capacity to optimize the matching performance.

DRAWINGS

1 is a schematic diagram of a closed state of a double-flow runner variable-section turbocharger valve in the background art of the present invention;

Figure 2 is a schematic view showing the open state of the double-flow flow path variable-section turbocharger valve in the background art of the present invention;

Figure 3 is a schematic view of the overall installation of Embodiment 1 of the present invention, which shows the connection of the turbine to the exhaust pipe;

Figure 4 is a schematic structural view of a turbine in Embodiment 1 of the present invention, which mainly shows a turbine end intake end position and an internal power turbine;

Figure 5 is a schematic structural view of a turbine casing in Embodiment 1 of the present invention;

Figure 6 is a schematic structural view of an exhaust pipe in Embodiment 1 of the present invention;

Figure 7 is a schematic view showing the valve adjusting structure in the first embodiment of the present invention, which shows the control actuator and the valve seat mounting fit;

Figure 8 is a schematic structural view of a valve seat in Embodiment 1 of the present invention;

Figure 9 is a schematic sectional view showing the valve seat of the first embodiment of the present invention;

Figure 10 is a schematic view showing the structure of an adjusting valve in Embodiment 1 of the present invention, which shows the cooperation of the regulating valve and the waste gas bypass valve;

Figure 11 is a schematic view showing the arrangement of the regulating valve and the end cover in the second embodiment of the present invention;

Figure 12 is a structural view of an end cap in Embodiment 2 of the present invention;

Figure 13 is a structural view of a regulating valve in Embodiment 2 of the present invention;

Figure 14 is a view showing the cooperation of the regulating valve, the end cover and the waste gas bypass valve in the second embodiment of the present invention; intention;

Figure 15 is a schematic view showing the structure of a wastegate bypass valve assembly and a regulating valve having a cam type regulating surface according to Embodiment 3 of the present invention;

Figure 16 is a schematic view showing the arrangement of a wastegate bypass valve assembly installed in a turbine according to Embodiment 3 of the present invention;

Figure 17 is a schematic view showing a regulating valve of a wastegate valve assembly in accordance with a spiral type adjusting surface and mounted on a turbine in Embodiment 3 of the present invention;

Figure 18 is a schematic view showing the cooperation of the wastegate bypass valve assembly and the regulating valve of Figure 17;

Figure 19 is an axial cross-sectional view of the wastegate valve assembly of Figure 18;

Figure 20 is a cross-sectional view of the wastegate valve assembly of Figure 18 and the regulating valve inserted into the turbine casing;

Figure 21 is a schematic view showing the arrangement of a turbine in Embodiment 4 of the present invention;

Figure 22 is a schematic view showing the structure of a regulating valve and a bypass valve in Embodiment 4 of the present invention;

Figure 23 is a schematic structural view of a slotted guide vane according to Embodiment 1 of the present invention;

Figure 24 is a schematic view of the turbine casing A, r;

Figure 25 is a schematic view showing the flow of unguided gas in Embodiment 1 of the present invention;

Figure 26 is a schematic view showing the flow of a vane gas in the first embodiment of the present invention;

Figure 27 is a graph of efficiency comparison, wherein the A line is the turbine efficiency line of the present invention, and the B line is the turbine efficiency line before the improvement;

Figure 28 is a graph showing a comparison of fuel consumption when the turbine and the engine are operated in combination;

Figure 29 is a schematic view showing the structure of long and short guide vanes in Embodiment 5 of the present invention;

Figure 30 is a graph of efficiency comparison of long and short vane turbines and slotted vane turbines, existing conventional wastegate turbines.

In the figure: 1-turbine shell; 2-intake outer runner; 3-intake inner runner; 4-inner runner flow direction; 5-regulating valve; 6-valve pin assembly; 7-control actuator; - Outer flow direction; 9-turbine shell waste bypass inlet; 10 - Turbine shell outer runner inlet; 11 - Turbine shell inner runner inlet; 12-grooved guide vane; 13-turbine shell waste bypass outlet; Exhaust pipe; 15-valve seat; 16-exhaust pipe waste bypass outlet; 17-exhaust pipe gas outlet; 18-valve seat inner flow channel interface; 19-valve seat outer flow channel connection 20-valve seat waste bypass outlet; 21- wastegate bypass valve bushing; 22-regulating valve bushing; 23-valve seat gas inlet; 24-valve seat waste bypass inlet; 25-adjustment surface; Exhaust gas bypass valve; 27-spring; 28-adjusting rod; 29-diversion trough; 30-vane support disc; 31-power turbine; 32-long vane; 33-short vane; 34-tail edge; - leading edge; 36-cutting line; 37-bypass valve assembly; 38-upper housing; 39-upper and lower housing gasket; 40-bypass valve assembly gasket; 41-lower housing; 41a-total Waste gas bypass outlet; 42-bypass valve support shaft; 43-guide sleeve; 44, bolt; 45-screw; 46, end cap; 47-fit adjustment surface; 47a-axial projection; 48-exhaust bypass Valve control actuator.

detailed description

In order to make those skilled in the art better understand the technical solutions of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

Embodiment 1, as shown in FIGS. 3, 4, and 5, a variable-section exhaust gas bypass turbine that satisfies the requirements of an EGR cycle, including a turbine casing 1, a power turbine 31, a valve seat 15, an exhaust pipe 14, and a control attachment thereof The valve seat 15 is disposed between the exhaust pipe 14 and the turbine casing 1. In order to ensure efficient operation, the turbine casing 1, the valve seat 15, and the exhaust pipe 14 are sealingly connected together.

The turbine casing 1 is provided with an intake inner flow passage 3 and an intake outer flow passage 2, and exhaust gas discharged from the engine exhaust pipe 14 can enter the intake inner flow passage 3 and the intake outer flow passage 2. In the present embodiment, the intake inner flow passage 3 and the intake outer flow passage 2 respectively adopt a non-full circumference structure. As shown in FIG. 5, the intake inner flow passage 3 bears a power turbine of 0° to (150 to 230)°. The air and the intake air flow passage 2 bear the intake air of (150 to 230) ° to 360 °. Simulation analysis and practice show that the distribution of this angle is optimal and the efficiency is optimal under various working conditions.

An end surface portion of the turbine casing 1 connected to the valve seat 15 (ie, an intake end surface of the turbine casing 1) is provided with a turbine casing outer runner inlet 10 and a turbine respectively communicating with the intake outer runner 2 and the intake inner runner 3. In the in-shell flow passage inlet 11, the exhaust gas discharged from the exhaust pipe 14 can flow from the two inlets, and flows into the power turbine 31 from the intake outer flow passage 2 and the intake inner flow passage 3, respectively, to drive the power turbine 31 to rotate, thereby driving the turbine. The compressor end of the supercharger operates to effect intake boost.

The turbine casing 1 is further provided with a waste gas bypass line which is arranged in parallel with the intake outer flow passage 2 and the intake inner flow passage 3, but does not pass through the power turbine 31. That is, part of the exhaust gas may flow to the waste gas bypass line, but will be discharged to the outside without driving the rotation of the power turbine 31.

At this time, the end surface portion of the turbine casing 1 connected to the valve seat 15 is further provided with a turbine casing waste gas inlet inlet 9 communicating with the waste gas bypass pipe, and the exhaust hole end wall of the turbine casing 1 is provided There is a turbine casing waste bypass outlet 13 in communication with the wastegate bypass line.

The valve seat 15 is provided with a valve seat inner flow channel interface 18, a valve seat outer flow channel interface 19, a valve seat waste gas bypass outlet 20, and a turbine casing inner flow passage inlet 11, a turbine outer outer runner inlet 10, and a turbine casing waste bypass. The inlet 9 is in communication; the valve seat 15 is also provided with a valve seat gas inlet 23 and a valve seat waste bypass inlet 24. In Fig. 7 and 8, the valve seat inner flow channel interface 18, the valve seat outer flow channel interface 19, the valve seat waste gas bypass outlet 20 are disposed at the top of the valve seat 15, and the valve seat gas inlet 23 and the valve seat waste gas bypass inlet 24 are provided at bottom.

Correspondingly, as shown in FIG. 6, the exhaust pipe 14 is provided with an exhaust pipe gas outlet 17 communicating with the turbine casing outer runner inlet 10 and the turbine casing inner runner inlet 11 through the valve seat 15, and passing through the valve seat 15 An exhaust pipe exhaust gas outlet 16 that communicates with the turbine casing waste bypass inlet 9.

A part of the exhaust gas discharged from the exhaust pipe 14 flows out through the exhaust pipe gas outlet 17, passes through the valve seat 15 and flows into the turbine casing outer runner inlet 10 and the turbine casing inner runner inlet 11 to be distributed, and then enters the power turbine 31.

Another portion of the bypass exhaust gas flows out from the exhaust pipe exhaust gas outlet 16 through the valve seat 15 into the connected turbine casing waste gas bypass inlet 9 and flows out from the turbine casing waste gas outlet 13 without passing through the power turbine 31. The turbine casing 1 is discharged.

As shown in Figures 7, 8, 9, and 10, the valve seat 15 is provided with a valve seat inner flow channel interface 18, a valve seat outer flow channel interface 19, and a valve seat waste gas bypass outlet 20, and a valve seat inner flow channel interface 18 The two ends of the valve housing are respectively communicated with the inner flow passage inlet 11 and the exhaust gas outlet 17 of the turbine casing, and the two ends of the outer flow passage 19 of the valve seat are respectively communicated with the outer runner inlet 10 and the exhaust gas outlet 17 of the turbine casing;

The valve seat waste bypass outlet 20 and the valve seat waste bypass inlet 24 are in communication with the turbine casing waste bypass inlet 9 and the exhaust pipe waste bypass outlet 16, respectively.

In this embodiment, the valve seat 15 is also installed with an adjustment valve 5 that can adjust the intake air flow of the intake air flow passage 2;

Specifically, the regulating valve 5 is mounted in the valve seat 15 by adjusting the valve sleeve 22, and one end of the regulating valve 5 is connected with the valve pin assembly 6, through the valve pin assembly 6 and the control attached Piece drive connection.

The control attachment comprises a control actuator 7 connected to the valve pin assembly 6; the control actuator 7 and the valve pin assembly 6 are arranged outside the turbine casing 1.

The regulating valve 5 preferably employs a rotatable centering valve, as shown in Figure 10, the regulating valve 5 is rotatable about its central axis. In Fig. 9, the door body of the regulating valve 5 completely blocks the passage between the valve seat outer flow passage interface 19 and the valve seat gas inlet 23, and when the regulating valve 5 is rotated by the valve pin assembly 6, the two sides thereof The inner wall of the above passage forms an opening to allow passage of exhaust gas.

Compared with the deflation valve structure shown in the background art, the center valve structure has a proportional relationship between the opening degree and the rotation angle when the rotation is opened, and the intake air amount and the intake pressure can be accurately controlled. This achieves a good match with the engine and improves the precise control of the EGR rate so that the engine meets the emission standards.

The turbine provided in the above embodiment is provided with a waste gas bypass line that exhausts the exhaust gas without passing through the power turbine 31, and at this time, a waste gas bypass valve 26 that controls the opening and closing of the waste gas bypass line is also provided. And, when the intake air amount of the exhaust gas entering the turbine exceeds a predetermined value, the waste gas bypass valve is opened to allow a part of the exhaust gas to be discharged through the waste gas bypass line. Therefore, when the engine is in a high speed condition, the wastegate valve 26 can be opened to allow part of the exhaust gas to be exhausted through the waste bypass line to avoid overspeeding of the supercharger. Therefore, the intake outer flow passage 2 does not need to be set to a large area in order to avoid overspeed of the supercharger at a high speed, and can be set to a small area to ensure the turbine drive performance and the EGR cycle of the medium and medium load; and, by the low speed and the low speed When the load condition is turned to the medium speed condition and the regulating valve 5 is opened, the small area difference of the inner and outer flow passages causes the expansion loss to be reduced.

Further, the wastegate valve 26 and the regulating valve 25 may be linked and configured to: when the regulating valve 5 is opened to a predetermined angle, the wastegate valve 26 is driven to open, and at this time, the intake air amount reaches the predetermined value.

The specific linkage method can be as follows:

As shown in FIG. 9, one end of the regulating valve 5 is mounted to the valve seat 15 through the adjusting valve bushing 22. The other end of the adjusting valve 5 is provided with an adjusting surface 25, and the adjusting surface 25 is a spiral structure, and its axial height is around its own axis. The heart spirals upwards.

The waste gas bypass line is provided with a waste gas bypass valve 26 that can cooperate with the regulating valve 5, and the waste gas bypass valve 26 is installed in the valve seat 15 through the wastegate valve bushing 21, and wastes A spring 27 is mounted between the gas bypass valve 26 and the wastegate valve bushing 21, and an end of the wastegate valve 26 adjacent to the regulating valve 5 is provided with an adjusting rod 28 that cooperates with the regulating surface 25. As shown in Fig. 9, the wastegate valve 26 and the regulating valve 5 are arranged in parallel with each other, and the adjusting lever 28 faces the adjusting surface 25 and is in contact with it.

In operation, the control actuator 7 pushes the valve pin assembly 6, and the valve pin assembly 6 drives the adjustment valve 5 to rotate, and adjusts the intake air amount of the intake outer flow passage 2, and when the rotation angle reaches a certain value, the adjustment rod 28 It can move along the spiral direction of the adjustment surface 25, and the adjustment surface 25 of the adjustment valve 5 can push the adjustment rod 28 to move axially, the waste gas bypass valve 26 opens, and compresses the spring 27, at which time the bypass exhaust gas is from the valve seat exhaust The inlet 24 flows in, flows from the valve seat waste bypass outlet 20 to the turbine casing waste bypass inlet 9, and flows out from the turbine casing waste bypass outlet 13. When the regulating valve 5 is returned, the wastegate valve 26 is at the spring 27 Returning under the action of elastic force, the exhaust gas is no longer bypassed.

An embodiment 2 is also provided below, which is basically the same as the first embodiment, but adopts different linkage modes, and the structure of the adjustment valve 5 is also slightly modified (to be mentioned later), please refer to FIG. 11-14.

In this embodiment, one end of the regulating valve 5 connected to the valve pin assembly 6 is provided with an adjustment surface 25 of axial height variation. At this time, the end cover 46 is further included with the end cover of the adjusting valve 5, and the end cover 46 can be fixed to the casing of the turbine casing 1. The end cover 46 is provided with a structure matched with the adjusting surface 25 opposite thereto, the valve pin The sheet assembly 6 is located outside the end cap 46 and is capable of driving the adjustment valve 5 to rotate.

Specifically, in this embodiment, the end cover 46 is provided with a matching adjustment surface 47 that cooperates with the adjustment surface 25, and the adjustment adjustment surface 47 has an axial protrusion 47a; the adjustment surface 25 is provided with a recess provided along the rotation direction, and correspondingly A convex portion is formed, and the concave portion transitions relatively gently to the convex portion. As shown in FIGS. 11 and 14, when the valve pin assembly 6 rotationally drives the adjustment valve 5 to rotate, the adjustment surface 25 rotates relative to the adjustment adjustment surface 46, and when the axial projection 47a slides over the concave portion to contact the convex portion, the rotation continues. Then, the axial projection 47a slowly pushes up the adjustment surface 25, and the adjustment valve 5 is correspondingly moved in the axial direction.

Therefore, the regulating valve 5 and the wastegate valve 26 can be axially contacted along the regulating valve, and when the adjusting valve 5 is axially moved by the adjusting surface 46, the waste bypass valve 26 is also axially moved to open. Waste gas bypass valve 26.

The linkage arrangement in the above two embodiments is to form an adjustment surface 25 with an axial height change on one component, and then set a linkage portion (such as the adjustment lever 28, The axial protrusion of the adjustment surface 47 is matched, thereby converting the rotary motion into a linear motion, and the linkage control is realized. It can be seen that, in the above embodiment, the adjusting surface 25 and the matching manner of the matching portion are not limited to the above two types. For example, the adjusting surface 25 may be disposed on the wastegate valve 26, and the adjusting rod 28 is disposed on the regulating valve 5, of course. The adjusting rod 28 is disposed on the wastegate valve 26 to prevent the regulating surface 25 from interfering with the exhaust gas flow; the adjusting surface 25 can be disposed on the end cover, and the adjusting surface 46 is disposed on the regulating valve 5.

The snap-fit matching arrangement of the end cap and the regulating valve 5 also makes the stability of the entire linkage mechanism better. Accordingly, as shown in FIGS. 12 and 13, the axial projections and the recesses are both provided in two, and are symmetrically disposed along the center line of the end surface of the corresponding member, so that the stability is higher after the fitting, and the offset is less likely to occur.

The present invention also provides a third embodiment. As shown in FIG. 15, the embodiment is substantially the same as the first embodiment and the second embodiment, but different linkage cooperation modes are adopted, and the structure of the waste gas bypass valve 26 and the regulating valve 5 is also slightly omitted. Changes will be made below.

One end of the regulating valve 5 is connected to the valve pin assembly 6, and the other end is provided with a cam-type regulating surface 25, and the wastegate valve 26 is provided with an adjusting rod 28 which can be in contact with the cam edge. Then, when the regulating valve 5 is rotated, the adjusting lever 8 is axially moved along the wastegate valve 26 to open the valve. Here, the cam-type adjustment surface 25 should be designed such that when rotated to a predetermined angle, the adjustment lever 28 is brought into contact with the cam edge to be moved upward to satisfy the aforementioned intake air amount to a certain extent before the wastegate valve is opened. 26.

In the above embodiment, the wastegate bypass valve 26 and the regulating valve 5 realize the linkage control, and only the driving portion of the regulating valve 5 can be provided, and the components for controlling the wastegate valve 26 need not be separately provided, and the structure is compact and simple; The wastegate valve 26 is controlled by the change of the opening degree of the regulating valve 5, and the opening and closing control of the wastegate valve 25 can conform to the actual intake air amount change, and the control is obviously more accurate than the individual control.

It should be noted that, in the above embodiment, the valve seat 15 is provided to install the adjusting valve 5, the waste gas bypass valve 26 and the like, thereby facilitating the installation of the components and achieving the controllable communication between the turbine casing 1 and the exhaust pipe 14. The present invention also provides another valve arrangement and is more compact in construction, as shown in Figures 15-20.

In this embodiment, a wastegate valve assembly 37 is provided, which is disposed separately from the regulating valve 5, the wastegate bypass valve 37 assembly is directly mounted to the turbine casing 1, and the regulating valve 5 is directly installed in the turbine casing 1, as shown in FIG. As shown, the door of the regulating valve 5 is directly inserted into the intake outer flow passage 2, outside the door body The circumference can be sealingly fitted with the inner wall of the intake air flow passage 2, and when the door body rotates, an opening is formed to conduct the exhaust gas. In the figure, the regulating valve 5 extends through the intake mounting end of the turbine casing 1, one end is connected to the wastegate valve assembly 37, and the other end is connected to the valve pin assembly 6 that drives its rotation.

At this time, the intake mounting end surface of the turbine casing 1 can be directly communicated with the exhaust pipe 14, and accordingly, the exhaust pipe 14 is correspondingly provided with exhaust corresponding to the intake inner flow passage 3 and the intake outer flow passage 2, respectively. mouth.

Due to the different linkage methods, the installation requirements of the valves are also different. Comparing Figures 16 and 17, it can be understood that the spiral type adjustment surface 25, the axially convex type adjustment surface 25, the waste gas bypass valve 26 and the regulating valve 5 are arranged in parallel in the axial direction, and when the cam type adjustment surface 25 is provided. Then, the wastegate valve 26 and the regulating valve 5 will be disposed at an angle, and Figures 15 and 16 are arranged almost vertically.

As shown in FIGS. 18 and 19, the bypass valve assembly 37 specifically includes a wastegate valve 26, an upper casing 38, and a lower casing 41. The upper casing 38 and the lower casing 41 are connected to form a valve cavity. An assembly waste gas bypass outlet 41a is opened in the side wall of the casing 41. The wastegate valve 26 may be supported by a bypass valve support shaft 42 that is disposed within the valve cavity and is provided with a spring 27 at the end of the upper housing 38 to provide a return force. The end of the lower casing 41 is provided with a valve port, and when the wastegate bypass valve 26 is opened, the exhaust gas enters the assembly waste gas bypass outlet 41a through the valve port.

In Fig. 19, the end surface of the wastegate valve 26 protrudes to form an adjustment rod 28, that is, the adjustment rod 28 is integrally formed in the wastegate valve 26 for easy processing, and the linkage control is also more reliable.

A guide sleeve 43 may be disposed in the valve cavity of the wastegate valve assembly 37. The bypass valve support shaft 42 extends through the guide sleeve 43. When the wastegate valve 26 moves axially, the bypass valve support shaft 42 is along the guide sleeve 43. Sliding to prevent the waste bypass valve 26 from shifting axially, affecting the waste bypass. In Fig. 19, the bypass valve support shaft 42 has a large diameter end to support the spring 27.

The turbine provided in the above embodiment is applicable not only to a four-cylinder engine but also to a six-cylinder engine. The structure of Figure 4-10 corresponds to the four-cylinder, and the six-cylinder needs to be provided with two sets of intake inner flow passage 3, intake outer flow passage 2, and waste gas bypass passage, as shown in Figs. 16 and 17, the turbine casing 1 The intake mounting end faces are correspondingly provided with two turbine casing waste bypass inlets 9, a turbine casing outer runner inlet 10, and a turbine casing inner runner inlet 11. At this time, two sets of the above valves can be provided.

This paper also provides a valve structure that is more compact and smaller in size and simpler and more precise for a six-cylinder engine.

As shown in Figures 13, 18, 20, the regulating valve 5 includes two valve bodies connected to each other, and is inserted into After the turbine casing 1, the two valve bodies respectively control the intake air amounts of the two outer flow passages 2. The regulating valve 5 is still installed in linkage with a wastegate valve 26, that is, a valve door body is added to the original regulating valve 5, which is applicable to a six-cylinder engine, which is equivalent to one valve controlling the intake air amount of the two flow passages. Easy to achieve precise control.

The manner in which the plurality of regulating valves 5 and the wastegate valve 26 are interlocked is provided in the above embodiment. It will be appreciated that it is also possible to separately control the wastegate valve 26, as in the embodiment 4 shown in Figs. Similar to the intake air flow venting valve mentioned in the background art, the waste gas bypass valve 26 can also be equipped with a corresponding waste bypass valve control actuator 48, and the waste gas bypass valve can be controlled according to the corresponding intake signal. 26 opening and closing. The wastegate valve control actuator 48 operates in the same manner as the control actuator 7. As shown in Fig. 22, the rod end of the wastegate valve control actuator 48 is extended under air pressure to drive the pin assembly to rotate and drive The wastegate valve 26 is rotated to close or open the valve port.

It should be noted that, in the above embodiment, when the regulating valve 5 and the wastegate bypass valve 26 are interlocked, when the interlocking power is canceled, the exhaust gas bypass valve 26 can be reset to the initial state by providing the spring 27. The spring 27 is combined with the above-mentioned various adjustment surfaces 25 to cooperate, and the opening of the wastegate valve 26 is realized simply and reliably. It can be understood that when the wastegate valve 26 is controlled by the wastegate control actuator 48 to open and close, there is no need to provide a reset device. In fact, in addition to the exhaust bypass valve 26 linkage scheme already mentioned, there are other solutions that enable the linkage of the wastegate valve 26 and the regulating valve 5 without the need to provide a return structure. For example, the end of the regulating valve 5 is provided with a gear, the waste bypass valve 26 is provided with a rack, or the regulating valve 5 is provided with a nut, and the waste bypass valve 26 is provided with a screw. Of course, the above arrangement is relatively simple and difficult. Interfere with the valve port.

The present invention also improves the manner of driving the power turbine 31.

As shown in FIGS. 4 and 23, a vaneless nozzle is provided in the turbine casing 1 at a position close to the power turbine 31 to introduce the exhaust gas discharged from the intake inner flow passage 3 and the intake outer flow passage 2 to the power turbine 31. In the embodiment, the slotted vane 12 is mounted near the vaneless nozzle, and a vane support disc 30 is mounted in the turbine shell 1 at a position close to the power turbine 31. The vane support disc 30 is provided with a plurality of vanes. The slotted vanes 12, in order to achieve a more uniform intake, a plurality of slotted vanes 12 are evenly arranged in a ring shape.

A guide groove 29 is provided at an intermediate position of the slotted vane 12. That is, the circumference of the torus of the vane support disk 30 Slotted vanes are formed by providing a plurality of vanes protruding from the torus and then opening a guide groove 29 extending through the vanes. The arrangement angle B of the slotted vanes 12 (as shown in Fig. 23, the angle is the tangent to the central axis of the slotted vane 12, the tip of the slotted vane 12 near the center of the vane support disc 30 and the center of the vane support disc 30 The connection may be between 68° and 80°, and the two groove sides of the guide groove 29 may be cut by the cutting line 36 (the slotted guide vane 12 is close to the tip of the guide vane support disc 30 and the vane support disc 30) The center line is connected around the center of the vane support disk 30, and the narrowest groove width is controlled by 3 mm.

The slotted vane 12 is in the form of a gas-solid composite nozzle, which combines the functions of a gas flow and a solid nozzle. When the engine is under low speed and low load, the turbine intake passage 3 acts, as will be known to those skilled in the art. The intake angle of the gas passage 3 is obtained by the formula tan(α)=2πb/(A/r), where b is the turbine inlet width and is a fixed value, and the intake angle is determined by the A/r of the intake passage 3 It is decided that A is the zero-sectional area of the turbine casing 1 and R is the distance from the centroid of the section to the axis of the turbine casing 1, as shown in Fig. 24, and Fig. 24 is a schematic view of the turbine casings A and r.

The vane angle (the angle between the two slotted vanes 12) is designed according to the intake angle of the intake inner flow passage 3 to ensure that the two angles are substantially the same, and the gas enters the slotted vane along the intake inner flow passage 3. 12, and then enter the power turbine 31 along the slotted guide vane 12, there is no turning loss in the middle, and the aerodynamic efficiency is high.

As the engine speed is gradually increased, the gas flow rate is increased, and the intake outer flow passage 2 participates in the intake with the opening of the regulating valve 5, and the intake angle of the intake outer flow passage 2 is also determined by the A/r of the intake outer flow passage 2, The angle of the guide groove 29 is designed according to the intake angle of the intake passage 2 to ensure that the two angles are substantially uniform, the gas enters the guide groove 29 along the intake passage 2, and enters the power turbine 31 along the guide groove 29 to avoid installation. The impact loss and cornering loss of the complete vane (without the guide groove 29) not only improves the efficiency, but also broadens the flow. Moreover, as the airflow speed is increased, the radial velocity component of the airflow rises faster, and the presence of the flow guiding groove 29 makes the flow width expansion of the high speed section more obvious.

Figure 23 is a schematic diagram of gas flow. When the engine is running at low speed and low load, the airflow enters the power turbine 31 only in the N direction (angle α, ie, the intake angle). When the engine speed is gradually increased, the airflow will follow M (the angle is β). The two directions of N, that is, the intake angle) and N, are combined to act on the power turbine 31, and δ is a range in which the direction of the airflow flowing into the power turbine 31 changes.

Here, the exhaust gas flow path will be described by taking an embodiment in which the valve seat 15 is provided as an example.

In actual work, when the engine is at low speed and low load, the regulating valve 5 is closed, and the intake air is along the exhaust pipe 14, the valve seat gas inlet 23, the valve seat inner flow channel interface 18, and the turbine casing inner flow passage. The passage between the inlet 11, the intake inner flow passage 3, and the adjacent grooved guide vanes 12 flows into the power turbine 31 to drive the power turbine 31 to perform work.

At this time, the airflow flows to the power turbine 31 along the middle portion of the two slotted guide vanes 12, and the power turbine 31 is driven to work. Only the intake inner runner 3 acts, the cross section is small, and only when flowing through the slotted vane 12 The vane angle inflow, that is, the N direction in Fig. 20, and the airflow is concentrated, which can increase the pre-vortex pressure and increase the EGR rate.

When the engine speed and load gradually increase, the regulating valve 5 starts to open, part of the airflow flows through the regulating valve 5, along the valve seat outer runner interface 19, the turbine casing outer runner inlet 10, the intake outer runner 2, and the slotted vane 12 The power turbine 31 flows into the power turbine 31 to accommodate the increasing flow demand. In this process, by adjusting the opening degree of the regulating valve 5, the pre-vortex pressure can be adjusted to determine an appropriate EGR rate.

In the process of adjusting the regulating valve 5, after the regulating valve 5 is turned to a certain angle (generally corresponding to the high speed section of the engine), the adjusting rod 28 is applied with a thrust through the adjusting surface 25, and the adjusting rod 28 drives the wastegate valve 26 to compress the spring 27 Opening the waste gas bypass line, the exhaust gas along the exhaust pipe waste gas outlet outlet 16, the valve seat waste gas bypass inlet 24, the valve seat waste gas bypass outlet 20, the turbine casing waste gas bypass inlet 9, the turbine casing waste gas bypass outlet 13 Outflow, exhaust a part of the exhaust gas energy, to ensure that the supercharger vortex front pressure is not too large when the engine is at high speed and high load.

Moreover, as the intake air amount increases, the intake air flows along the guide groove 29 on the slotted guide vane 12, that is, the M direction in FIG. 23, and the M direction and the N direction simultaneously intake air, thereby avoiding the air flow in the high speed section. Blocked.

As shown in Figures 25 and 26, the presence of the vanes reduces the backflow of the airflow, which not only improves the efficiency of the turbine, but also smoothes the flow of the airflow, avoids airflow disturbances at the throat, and ensures turbine efficiency.

In addition, the pressure ratio and flow rate of the turbine have a great influence on the performance thereof, and the flow passage determines the flow passage cross section. The prior art relies on the flow passage design of the turbine casing 1 to control the flow passage cross section, but as described in the background art, The production consistency of the foundry turbine is difficult to control, and the flow rate is difficult to control accordingly. In the embodiment, the vane structure is provided, and the flow passage area can be controlled by the vane, and the vane structure can be precisely processed, and the flow passage area can be precisely controlled, so as not to be affected by the machining accuracy of the turbine shell 1 itself.

After setting the vanes, the turbine and engine have achieved significant performance improvements, as follows:

1. The efficiency of the turbine is obviously improved. The efficiency comparison chart is shown in Fig. 27. The thicker black line A above is the efficiency line of the invention, and the thinner black line B below is the turbine efficiency line before the improvement.

2. The fuel consumption comparison curve with the engine combined operation is shown in Fig. 28. With the turbocharger of the present invention, the fuel consumption rate is greatly reduced on the entire matching line.

Embodiment 5, based on the above embodiment, the present invention further provides another vane arrangement form. As shown in FIG. 29, the guide vane includes a long guide vane 32 and a short guide vane 33, and the length of the long guide vane 32 is longer than short. The length of the vane 33, the long vane 32 and the short vane 33 are spaced apart.

The size of the long vane 32 and the short vane 33 is determined according to the flow analysis, but the trailing edge 34 of the short vane 33 and the leading edge 35 of the long vane 32 are at a distance in the circumferential direction to facilitate air flow at the engine speed. From time to time, the flow can be widened and the blockage can be reduced, and the function achieved is similar to that of the slotted vane 12 of the previous embodiment. That is, the long guide vanes 32 are arranged circumferentially along the guide vane support disk 30 at an angle, and the short guide vanes 33 are arranged at another angle, and the passage between the long guide vanes 32 and the short guide vanes 33 is formed in the counterclockwise direction. The flow path in which the gas flow path 3 is turned on, the passage between the short guide vane 33 and the long guide vane 32 forms a flow guide flow path that is electrically connected to the intake outer flow path 2. The specific working process can be understood by referring to the slotted vane 12 described above.

The arrangement angle B of the long guide vanes 32 can be designed to be 68° to 80°, and the angular difference between the arrangement angle B of the long guide vanes 32 and the arrangement angle A of the short guide vanes 33 is: B-A=0° to 5°.

Wherein, the arrangement angle B is a tangent to the central axis of the long guide vane 32, the tip of the long guide vane 32 near the center of the vane support disk 30 and the center line of the vane support disk 30, the angle between the two; the arrangement angle A is The tangent of the central axis of the short vane 31, the short guide vane 31 is close to the center of the vane support disc 30 and the center line of the vane support disc 30, the angle between the two.

The turbine of this kind of vane setting mode is more efficient, and the efficiency comparison chart is shown in Fig. 30:

The thinnest black line A above is the long and short vane turbine efficiency line, the thickest black C line below is the general waste bypass turbine efficiency line, and the middle black line B is the slotted vane turbine efficiency line. As can be seen from the above table, the turbine efficiency of the long guide vanes 32 and the short guide vanes 33 is even higher than that of the slotted vanes 12.

As can be seen from the above description, both the slotted vane 12 and the mating arrangement of the long vane 32 and the short vane 33 are formed to form two first diversion channels and a second diversion having a predetermined angle. The passages (ie, the two are not arranged in parallel, the angle value is related to the intake angle of the intake inner flow passage 3 and the intake outer flow passage 2), so that the exhaust gas flowing out of the intake inner flow passage 3 can pass through the first flow guiding passage Diverted to the power turbine 31, the exhaust gas flowing out of the intake outer flow passage 2 can be diverted to the second flow guiding passage to the The power turbine 31 is described. As above, the passage between the adjacent slotted vanes 12 forms the first flow guiding passage, and the guiding groove 29 forms a second guiding passage; in the counterclockwise direction, between the long vane 32 and the short vane 33 The passage forms a second flow guiding passage, and the passage between the short guide vane 33 and the long guide vane 32 forms a first flow guiding passage.

As long as the exhaust gas of the intake inner flow passage 3 and the intake outer flow passage 2 can be respectively led to the power turbine 31 to widen the flow range, the technical effects as described above can be produced. Obviously, the formation manner of the two flow passages is not limited. The above-described slotted vane 12 and long guide vane 32 and short guide vane 33, of course, the structure of the above embodiment is easy to process, and does not hinder the air flow, and the flow guiding effect is the best. In addition, the flow guiding support disk 30 is separated from the turbine casing 31, and the flow guiding support disk 30 can be finished with precision, and the accuracy is easily ensured, thereby further ensuring the distribution of the airflow and ensuring the efficiency of the turbine.

In the above embodiment, the flow guiding support plate 30 can be installed with a heat shield at a position close to the guide vane at the rear end of the turbine shaft of the power turbine 31, where the heat shield serves as the above-mentioned guide support plate 30, the vane and the heat shield The cover is integrally provided, for example, directly integrated with the heat shield.

We have now described the invention in detail in accordance with the National Patent Law, and those skilled in the art will recognize improvements or substitutions to the specific embodiments disclosed herein. These modifications are within the spirit and scope of the invention.

Claims (14)

1. A vane assembly for a variable cross-section wastegate turbine, characterized in that

   The vane assembly includes a vane support disc (30) disposed at an inlet end face of the turbine power turbine (31);

   The vane support discs (30) are arranged along the circumferential direction thereof with a plurality of first flow guiding channels and second flow guiding channels, the first guiding channels and the second guiding channels having a predetermined angle to Exhaust gas flowing out of the intake inner flow passage (3) can be guided to the power turbine (31) through the first flow guiding passage, and the exhaust gas flowing out of the intake outer flow passage (2) can be The second flow guiding channel is diverted to the power turbine (31).
2. The vane assembly according to claim 1, wherein a circumferential surface of the vane support disk (30) is provided with a plurality of vanes protruding from the annulus, the vanes being open through the a guide vane (29) of the vane to form a slotted vane (12);

   A passage between adjacent ones of the slotted vanes (12) forms the first flow guiding channel, and the flow guiding groove (29) forms the second flow guiding channel.
3. The vane assembly according to claim 1, wherein the annular surface of the vane support disk (30) is provided with long guide vanes (32) and short guide vanes protruding from the annulus and spaced apart from each other (33), in a counterclockwise direction, a passage between the long guide vane (32) to the short guide vane (33) forms the second flow guiding passage, the short guide vane (33) to the A passage between the long guide vanes (32) forms the first flow guiding channel.
4. The vane assembly according to claim 3, wherein the arrangement angle B of the long guide vanes (32) is 68° to 80°, and the arrangement angle A of the short guide vanes (33) satisfies: BA =0°～5°;

   Wherein, the arrangement angle B is a tangent to the central axis of the long guide vane (32), the tip of the long guide vane (32) near the center of the vane support disc (30), and the vane support disc (30) a central line connecting the two; an arrangement angle A is a tangent to the central axis of the short guide vane (31), and the short guide vane (31) is adjacent to the center of the vane support disk (30) The tip is connected to the center of the vane support disk (30), the angle between the two.
5. A variable-section exhaust gas bypass turbine that meets the needs of an RGR cycle, comprising a turbine casing (1) and a power turbine (31), the turbine casing (1) being provided with a pilot engine exhaust gas to the power The turbine (31) is provided with an intake inner flow passage (3) and an intake outer flow passage (2) for driving the power turbine (31) to rotate, wherein the power turbine (31) intake end position is provided as the right The vane assembly of any of claims 1-4.
6. A variable-section exhaust gas bypass turbine according to claim 5, further comprising an adjustment valve (5) having an adjustable opening for adjusting an intake air amount of said intake outer flow passage (2); The regulating valve (5) is a rotatable central valve. When rotating, the exhaust gas can enter through both sides of the valve body.
7. A variable cross-section wastegate turbine according to claim 6, wherein said regulating valve (5) is inserted into said turbine casing (1) for direct adjustment into said intake outer flow passage (2) The amount of intake air.
8. A variable-section exhaust gas bypass turbine according to claim 7, wherein said turbine is provided with two sets of said intake outer flow passage (2) corresponding to a six-cylinder engine, and an intake inner flow passage (3) The regulating valve (5) includes two valve bodies that are connected to each other. After the turbine casing (1) is inserted into the turbine casing (1), the two valve bodies respectively control two intake air flow passages respectively (2). The amount of intake air.
9. A variable section wastegate turbine that meets the needs of an EGR cycle, including a turbine casing (1) and a power turbine (31), characterized by:

   A vane support disc (30) is mounted in the turbine casing (1) near the power turbine (31), and the vane support disc (30) is provided with a plurality of slotted vanes (12), and a plurality of slots The vanes (12) are evenly arranged in a ring shape.
10. A variable section wastegate turbine for meeting EGR cycle requirements according to claim 9 wherein:

    A guide groove (29) is arranged at an intermediate position of the slotted guide vane (12), and the arrangement angle (B) of the slotted guide vane (12) is 68° to 80°, and the two groove sides of the guide groove (29) are cut by The wire (36) is obtained by rotating around the center of the vane support disk (30), and the narrowest groove width is controlled by 3 mm;

    The slotted vane (12) is in the form of a gas-solid composite nozzle. When the engine is under low speed and low load, the turbine inner flow passage (3) acts, and the intake angle of the intake inner passage (3) is determined by the formula. Tan(α)=2πb/(A/r) is obtained, where b is the turbine inlet width, which is a fixed value, and the intake angle is determined by the A/r of the intake inner flow passage (3).

    The vane angle of the intake inner flow passage (3) is designed according to the intake angle of the intake inner passage (3) to ensure The two angles are basically the same, the gas enters the vane along the inner flow passage (3) of the intake, and then enters the power turbine (31) along the guide vane without a turning loss in the middle.
11. A variable section wastegate turbine for meeting EGR cycle requirements according to claim 9, wherein the slotted vane (12) comprises a long guide vane (32) and a short guide vane (33), long guide The length of the leaf (32) is greater than the length of the short guide vane (33), and the long guide vane (32) and the short guide vane (33) are spaced apart.
12. A variable-section exhaust gas bypass turbine that meets the needs of an EGR cycle, comprising a turbine casing (1) in which a power turbine (31) and an intake runner are mounted, on the turbine casing (1) a position near the tail of the power turbine (31) is provided to introduce exhaust gas flowing out of the intake runner into the vaneless nozzle of the power turbine (31);

    The utility model is characterized in that: a vane assembly capable of adjusting the flow capacity of the turbine shell by changing the number, size, angle and arrangement of the vanes is installed in the turbine shell (1) near the vaneless nozzle;

    The vane assembly includes a plurality of vanes arranged in a circular arrangement.
13. A variable section wastegate turbine for meeting EGR cycle requirements according to claim 12, wherein the vane comprises a long vane (32) and a short vane (33), the length of the long vane (32) being greater than The length of the short vane (33), the long vane (32) and the short vane (33) are spaced apart.
14. The variable cross-section wastegate turbine according to claim 12, wherein each of the plurality of vanes is separated by a guide vane, and a guide groove (29) is opened on the vane. The orientation of the guide trough (29) coincides with the vanes.

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