JPS5810114A - Turbocharger - Google Patents

Abstract

PURPOSE:To enhance the response characteristic of an automotive turbocharger, by a method wherein a plurality of recesses are provided at the surface of a rotary shaft of a turbocharger, and a jet nozzle for a hydraulic oil for auxiliarily driving the charger is provided in proximity to the recesses. CONSTITUTION:An auxiliary turbine 15 is provided on the rotary shaft 6 of the turbocharger at an intermediate part between bearings 7, 8. Blade elements 16 for the turbine 15 are provided on a surface part of the shaft 6 so as to receive the oil jets ejected from the jet nozzle 17. The turbine 15 is driven by a hydraulic oil pump operated in accordance with the setp-in amount of an accelerator pedal. Accordingly, the revolving speed of the turbocharger is rapidly increased, and the time lag of the turbocharger can be improved.

Description

[Detailed description of the invention] The present invention relates to a turbocharger for an automobile.

In general, engines equipped with a turbocharger have the disadvantage of poor responsiveness in the low speed rotation range of the engine. This drawback causes a decrease in drivability in small passenger cars that are frequently driven at low speeds in urban areas and the like.

In the desire to increase the output to the engine, the accelerator pedal placed in the driver's seat increases the amount of fuel supplied to the engine, or increases the M degree of the throttle valve of the VHFi carburetor, but the exhaust gas Until the energy increases the output of the exhaust turbine and the rotational speed of the re-bocharger increases, there is a time lag in K at the ninth moment of inertia of the shaft system including the impeller. In existing turbochargers, impellers are becoming increasingly smaller and lighter, but it is difficult to reduce the moment of inertia.

For this reason, attempts have been made to improve the responsiveness by using auxiliary means to energize the turbocharger.

One method is to provide an auxiliary air source other than the turbocharger and supply high-pressure air to the turbocharger's compressor only when pressurization is required.

However, this method is difficult to put into practical use when targeting small passenger cars due to the high cost of the auxiliary air source.

Another method is known in which an auxiliary turbine is provided on the rotating shaft of the turbocharger and oil is injected from an injection nozzle to energize the turbocharger. However, in recent years, turbochargers for small passenger cars have become faster and more compact, and it is difficult to newly install an auxiliary turbine in terms of space and ease of assembly. Furthermore, since the rotational speed of the shaft is increased, it is necessary to increase the flow rate of oil in the injection nozzle, and there is a drawback that a high-pressure oil pump must be installed.

The present invention was made to solve the above-mentioned drawbacks, and an object of the present invention is to improve the responsiveness of a turbocharger with a device that is small and has a simple structure.

This invention provides K (i number of recesses) on the surface of the rotating shaft of the turbocharger to receive the velocity energy of the oil jet.
The rotary shaft is directly driven by a high-speed jet of hydraulic oil from an injection nozzle provided close to the rotary shaft.

An embodiment of the present invention is shown in FIGS. 1 and 2 below.

This will be explained with reference to FIGS. 3 and 4.

FIG. 1 shows a longitudinal cross-sectional view of the turbocharger of the present invention,
1 is a center housing, and an exhaust turbine section 2 and a compressor section 3 are disposed at both ends of the center housing. The exhaust turbine 2 is composed of a turbine casing 4 and a turbine impeller 5.

The turbine casing 4 has a center housing 10 side wall. The turbine casing 4 is connected to a carrot exhaust pipe (not shown), and inside the turbine casing 4 is provided an XJIIC in which a turbine impeller 5 rotates. The turbine impeller 5 is fixed to one end of a rotating shaft 6, and the rotating shaft 6 is provided inside the center housing 1 and supported by nine bearings 7 and 8. A thrust metal 9 is fixed to the compressor side of the center hatch, and holds the axial position of the rotating shaft 6 via a thrust collar 10 fixed to the rotating shaft 6.

The compressor part 3 is composed of a compressor blade *weight 11 and a compressor casing 12. The compressor casing 12 is fixed to the center housing IK, and the compressor impeller 11 is located inside the compressor casing 2 and fixed to the rotating shaft 6.

Furthermore, a supply port 13 and a discharge port 14 for lubricating oil are provided in the center of the center housing 1.

An auxiliary turbine 15 is provided at an intermediate portion between bearings 7 and 8 of the rotating shaft 6. The auxiliary turbine 16 is composed of an injection nozzle 16 and a blade element 17, and the blade element 17 is connected to the rotating shaft 6.
The spray nozzle 16 is designed to receive the oil jet sprayed onto the zero surface.

The injection nozzle 16 is fixed to the center housing 1 so as to be perpendicular to the rotating shaft 6. Injection nozzle 16
An injection port 17 is provided at the tip of the blade element 17 in close proximity to the rotating shaft 6 so that the jet stream hits the blade element 17.

FIG. 2 is a sectional view perpendicular to the rotation axis direction of the auxiliary turbine 150 of this embodiment. The same parts as in FIG. 1 are given the same numbers. The injection nozzle 17 is fixed to the side wall of the center housing 10, and the jet from the injection port 17 is
The position is precisely determined so as to approximately contact the circumference of the rotating shaft 60. An oil supply port 19 is provided at the other end of the injection nozzle 17 so that high-pressure hydraulic oil is supplied from an oil pump (not shown).

Figures 3 and 4 show blades installed on the plane of the rotating shaft 60! !
FIG. 3 is a sectional view and FIG. 4 is a front view of the element 16. The vane element 16 is a notch portion machined on the surface of the rotating shaft 60, and is formed such that the passive surface 2° faces the jet tItK, and changes the flow direction of the jet.

FIG. 5 shows a cross-sectional view of the auxiliary turbine section of another embodiment from that shown in FIG. A rotary shaft 60 and a blade element 16 are provided, and a circular nozzle ring 19 is provided concentrically with the rotary shaft 6 around nine parts. The nozzle ring 19 is fixed to the injection nozzle casing 2o, and a flow path 21 is provided between the nozzle ring 19 and the injection nozzle casing 20.

The nozzle ring 19 has a plurality of sand injection ports 24 arranged at equal positions on the circumference. The injection port 24 communicates with the flow path 23 and is provided so that a jet stream blows onto the vane element 16 of the auxiliary bottle.

FIG. 6 shows an overall system diagram of an embodiment of the present invention, in which a turbocharger 26 is installed in the engine body 25, and the discharge side of the compressor 3 of the turbocharger 26 is connected to the intake pipe of the engine 25. 27KI! It is continued. An exhaust pipe 28 of the engine 2s is connected to the inlet side of the exhaust turbine 20.

A bypass valve 29 is provided branching off from the exhaust pipe 28, and its downstream side is connected to the discharge part of the exhaust turbine 2. The bypass valve 29 is driven by a diaphragm 30 to which the pressure of the air intake pipe 27 is guided.

The oil pump 31 is driven by a crankshaft 32 of an engine 2s via a belt 33, and is designed to suck hydraulic oil from an oil tank 34 through a suction pipe 35. An oil control valve 37 is connected to the discharge pipe 36 of the oil pump 31, and a conduit 38 to the injection nozzle 17 of the auxiliary turbine 2 is connected to the outlet side of the oil control valve 37. Oil in the turbocharger 26 is connected to an oil tank 34 through an oil drain pipe 39. The oil control valve 37 is provided with a trap pipe 48 and connected to a suction pipe 355. The oil control valve 87 is operated by the safety magnet 40.

The accelerator pedal 41 is provided with a proximity switch 42, the signal of which is transmitted to the control device 1m4B. A rotation speed detector 44 is provided at the inlet 111 of the compressor 30, and transmits a rotation pulse signal to the control device 4s.

A pressure detector 45 is provided in the intake pipe 27 to detect the supercharging pressure and transmit the signal to the control device 48 . Also,
An engine rotational speed detector 47 is provided adjacent to the output shaft 46 of the engine 25.

Next, the operation of this embodiment will be explained.

The oil pump 31 is driven by the engine 28 >1,
When the auxiliary turbine 15 is not operated, the magnet 4
0FiOFP type 11KTojD, hydraulic oil is oil control valve 37
II) The suction pipe 35Klb passes through the pipe 48, and the oil pump 31 becomes unloaded. When the carrot 2s is operated, the exhaust turbine 2 is driven by the exhaust gas JK, and the =7 pret t-S is driven via the rotating shaft 6. :1 The compressor 3 supplies air to the engine 2s through the intake pipe 27.

When the driver depresses the pedal to accelerate the vehicle, the proximity switch 42 senses the movement of the accelerator pedal 41 and sends a signal to the control device 43. At this time, if the boost pressure detected by the pressure detector 45 is below a certain value, the control device 43 turns on the magnet 40 and supplies high-pressure hydraulic oil to the injection nozzle 17 via the conduit 38. The hydraulic oil is blown out as a high-speed jet from the injection port 18 of the injection nozzle 17, and the flow collides with the rotary shaft 60 and the blade element 16, directly driving the rotary shaft 6. Although the turbocharger is rotated at a low speed by the exhaust gases, the auxiliary turbine increases the engine's power output and can significantly improve response. The spouted hydraulic oil flows from the discharge port 14 to the oil tank 34 through the oil drain pipe 39.

The rotational speed detector 44 of the turbocharger detects rotational pulses and sends them to the control device 43. When the rotational speed of the turbocharger exceeds a certain value, the control device 43 sends an OFF signal to the magnet 4. Cuts off the supply of hydraulic oil to the auxiliary turbine to prevent power loss. Instead of detecting the rotational speed of the turbocharger, it is also possible to detect the engine rotational speed by the rotational speed detector 47, calculate the rotational speed of the turbocharger in the control device 43 based on the boost pressure, and control the oil control valve 37. .

FIG. 5 shows a case where the injection nozzle has a plurality of injection ports 24. -1 It has the advantage that the fluid force acts evenly on the rotating shaft 6.

In the embodiment of this invention, the blade element that functions as a turbine is machined directly onto the rotating shaft, so the structure is extremely simple, and nine auxiliary impellers are manufactured separately from the rotating shaft. Since the fixing step is omitted, the turbocharger can be manufactured at a lower cost than a conventional turbocharger with an auxiliary turbine.

Further, in a small turbocharger, the shaft diameter is about 10 mm, and when an auxiliary turbine impeller is attached to it, the impeller diameter becomes about 20 mm. On the other hand, the rotation speed of the small turbocharger engine in the low speed range is 50,000 rpm.
Since the peripheral speed of the auxiliary turbine is about 5 gm
/s. - In the Bell 17 type turbine, the maximum output is obtained at a jet velocity approximately twice the impeller circumferential speed, so the jet velocity reaches approximately IQQ m/l. Approximately IQQm
To achieve a jet velocity of /@, the discharge pressure is 42K.
A high-pressure oil pump of YF/38 is required, and it is difficult to install such a high-pressure pump in a small passenger car.In the present invention, the rotating shaft is structured to operate as a turbine, so the circumferential speed is low, and the hydraulic pump The discharge pressure is approximately 10 K4
f /as'', which has the advantage of being able to keep the jet velocity low.

The working shafts of the auxiliary turbines can share engine lubricating oil. The oil pump is driven by a belt or the like from the engine's crankshaft. Also, since constantly running a pressure oil pump is uneconomical on fuel, an electromagnetic clutch etc. is installed between the crankshaft and the oil pump when a large engine output is not required or when the engine is in a high speed range. power to the oil pump can be cut off.

In the high speed range of the engine, a sufficiently high boost pressure can be obtained without using auxiliary means for the turbocharger, so there is no need to drive the auxiliary turbine. is 100,000 rpm
In addition to the above, l) the circumferential speed of the rotating shaft increases, so injecting hydraulic oil from the injection nozzle in this state is inconvenient because the power loss of the turbocharger increases. For this reason, the pressure on the discharge side of the turbocharger compressor is detected by a pressure sensor, etc., and when the boost pressure reaches a certain value, a control valve is activated to stop the supply of hydraulic oil to the injection nozzle1. Even if the supply pressure is in a low range, there is no need to operate the auxiliary turbine if the driver does not request an increase in engine output. It is detected by the amount of pressure on the accelerator pedal, and when the amount of pressure on the accelerator pedal reaches a certain value, it is controlled to supply hydraulic oil to the injection nozzle.

Since the auxiliary turbine is actuated according to the amount of darkness of the accelerator pedal, the rotational speed of the turbocharger immediately increases, and the time delay of the turbocharger can be changed.

When the turbocharger rotates at high speed, the auxiliary turbine does not need to operate, and if hydraulic oil is injected in this state, the power loss of the turbocharger will be large, so the injection of hydraulic oil will be stopped according to the rotational speed of the turbocharger. let The rotational speed of the turbocharger can be measured by magnetizing a part of the rotating body and extracting the electric current (KjJ>).

If the rotation speed of the turbocharger cannot be detected,
The turbocharger rotation speed is calculated from the engine rotation speed and boost pressure, and the auxiliary turbine is controlled.

By minimizing the use of the auxiliary turbine as described above, the power consumption of the oil pump can be saved.

As described above, according to the present invention, since the blades of the auxiliary turbine are constructed by providing a notch in the rotating shaft of the turbocharger, the auxiliary turbine can also be used in high speed and small turbochargers. It can be applied at a low price and the rotating shaft of the turbocharger can be directly energized by the auxiliary turbine.

Claims (1)

Claims: LIWi - supercharging air to the engine with an exhaust turbine driven by exhaust gases from the engine on a rotating shaft;
1. A turbocharger provided with a compressor, characterized in that a plurality of recesses are provided on the surface of the rotating shaft, and one or more injection ports are provided adjacent to the recesses. 2. It has a means for detecting the output demand of the engine 5 and a means for detecting the supercharging pressure of the compressor, and when the output quality and demand for the engine reaches a certain value, it supplies hydraulic oil to the injection nozzle and 81j11'14. The turbocharger according to claim 81j11'14, wherein k is provided by a control means for not supplying hydraulic oil to the injection nozzle when the supply pressure is above a certain value. - & A patent claim characterized in that the turbocharger has a means for detecting the rotational speed of the turbocharger, and a control means for not supplying hydraulic oil to the injection nozzle when the rotational speed exceeds a certain value. The turbocharger according to range 2. Also, the claim is characterized in that it has a means for detecting the rotational speed of the engine, and is provided with a control means for stopping the supply of high-pressure oil to the injection nozzle based on the engine rotational speed and supercharging pressure. The turbocharger according to item 2.