JPS60162002A - Thrust controller for exhaust turbine supercharger - Google Patents

Abstract

PURPOSE:To reduce the pressure-receiving area of a bearing, by connecting the space on the back of the impeller of a compressor to the atmosphere through a control valve, connecting the space on the compressor-facing side of a turbine disk to that on the discharge side of the compressor through a control valve, and connecting the space on the opposite-the-compressor side of the disk to a gas outlet port through a control valve. CONSTITUTION:A rotor shaft 13 is supported halfway by thrust bearings 23, 24. An enclosed chamber C on the back of the impeller 1 of a compressor is connected to the atmosphere through a control valve 43. An enclosed chamber A on the side of a turbine disk 12 in the face of the compressor is connected to the discharge side 37 of the compressor through a control valve 45. An enclosed chamber B on the side of the disk 12 opposite the compressor is connected to a gas outlet port 40 through a control valve 47. The axial position of the rotor shaft 13 is detected by axial position gauges 49, 50 to control the degrees of opening of the control valves 43, 45, 47 depending on the deviation of the axial position of the rotor shaft. The thrust of the shaft 13 is thus minimized, so that the pressure-receiving area of each thrust bearing can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a shaft thrust adjustment device for an exhaust turbine supercharger in which a rotor shaft is supported between an exhaust turbine and a compressor.

A conventional structure of an exhaust turbine supercharger in which a rotor shaft is supported between an exhaust turbine and a compressor is shown in FIG. That is, it is rotated by the compressor impeller 1 which sucks air through the air suction port 36 of the compressor casing 35 and discharges compressed air from the air discharge port 37, and the exhaust gas sent from the gas port 39 of the turbine casing 38. A rotor shaft 13 connects a turbine disk 12 with a protruding turbine blade 11 for discharging exhaust gas that has finished its work from an exhaust gas outlet 40, and the compressor side of the intermediate portion of the rotor shaft is connected to the compressor side. With journal bearing 21,
In addition, the turbine side is supported by a turbine side journal bearing 22, and compressor side thrust bearings 23 are provided on both sides of the thrust receiver 41, which is protruded from the rotor shaft 13 at the intermediate portion of both bearings. A turbine-side thrust bearing 24 is disposed on each side to support the axial thrust, and a compressor-side labyrinth packing 25 and a turbine-side labyrinth packing 26 are installed on both outsides of both journal bearings to prevent leakage of lubricating oil. At the same time, an air leakage prevention labyrinth packing 29 is provided around the outer periphery of the sealed chamber (C) on the back side of the impeller to release the air in the sealed chamber to the atmosphere through the air release path 42. Sealed chambers (A) and (B) are arranged on both sides of the turbine disk, and the sealed chamber (A) is sealed by a high-pressure air leak prevention labyrinth packing 27 arranged on the outer periphery of the disk, and each of the bearings is sealed. The high-pressure air from the air outlet can be freely introduced into the sealed chamber through a high-pressure air path 31 bored in the bearing case 30 or a conduit, and the sealed chamber (B) is provided with the outer periphery of the disk. The exhaust gas intrusion prevention labyrinth packing 28 provided in the chamber prevents gas from entering the chamber, and the chamber is communicated with the atmosphere or connected to the gas outlet passage via a pipe. In addition,
The exhaust gas from the exhaust gas inlet flows into the turbine blade 11 through the nozzle port 32 of the nozzle 33, and one exhaust gas outlet is constituted by a gas outlet casing 34.

Therefore, when considering the axial thrust of the above-mentioned structure of the conventional exhaust turbine supercharger, for convenience of explanation, the axial thrust is divided into the compressor side and the turbine side.
In addition, if we look at the direction of the axial thrust, we will first notice the thrust F on the compressor side.
B is the sum of the force FBI from the air suction port 36 side of the impeller 1 and the force FB2 from the back side, that is, the closed chamber (C) side, but since the force FB2 is large, it is always in the positive (+) direction. Since this value is extremely large in a compressor with a high pressure ratio, the air inside the closed chamber (C) is released to the atmosphere to reduce the thrust force FB. In addition, the thrust force FT on the turbine side is the resultant force of the pressure difference before and after the turbine blades and the momentum FTI (always in the positive (+) direction, but its magnitude depends on the degree of reaction of the turbine), the closed chamber (A ) side FT□ (approximately determined by compressor discharge pressure Pd and acts in the negative (=) direction), and force FT8 from the closed chamber (B) side (the force F
Like Tt, it is influenced by the degree of reaction of the turbine, and is positive (
(acting in the +) direction), and is therefore given by FT = FTI FT2 + FT8. Therefore, the axial thrust F"ro'r is a composite force of the compressor side thrust FB and the turbine side thrust FT, and changes depending on the degree of reaction of the turbine.7->1-1/'
fp 1 1-, kml-4-u--1-h---
- If the change due to the degree of reaction is shown in Figure 2, if the degree of reaction of the turbine is large, the axial thrust FTo'r will be positive (+
It is known that the force becomes a large force in the ) direction, and when the degree of recoil is small, it becomes a force in the negative (-) direction. For this reason, in the conventional exhaust turbine supercharger, the pressure receiving area difference between the compressor-side thrust bearing 23 and the turbine-side thrust bearing 24 is adjusted to correspond to the magnitude of the axial thrust FToT that changes according to changes in the degree of reaction of the turbine. However, these structures are not only unsatisfactory in terms of performance, but also have a negative impact on the manufacturing cost structure. This is also a bad idea.

This invention was made in view of the current situation, and by making it possible to adjust the thrust force acting on the back surface of the compressor impeller and the thrust force acting on both sides of the rotor disk, the rotor shaft can be adjusted. To provide a axial thrust adjusting device for an exhaust turbine supercharger that makes the axial thrust zero or a minimum value and satisfies the pressure receiving area of each thrust bearing at the minimum regardless of the degree of reaction of the turbine. This is the purpose.

Next, an embodiment of the present invention will be described with reference to the drawings.
In FIG. 3, the air inlet 3 of the compressor casing 35
The compressor impeller 1 which increases the pressure of the intake air from 6 and discharges it from the air outlet 37 is rotated by the flow gas from the exhaust gas population 39 of the turbine casing 38, and the gas that has finished its work is transferred to the gas outlet. Exhaust gas outlet 4 of casing 34
A turbine blade 11 for discharging air from 0 is connected to a protruding turbine disk 12 through a rotor shaft 13 having a thrust bearing 41 disposed in the middle, and compressor-side journal bearings 21 are connected to both sides of the intermediate portion of the rotor shaft. and turbine-side journal bearings 22, and the compressor-side thrust bearings 23 and turbine-side thrust bearings 24 support the axial thrust on both sides of the thrust bearings. A labyrinth packing 25 on the 1-machine side and a labyrinth packing 2G on the turbine side are installed to prevent lubricating oil leakage, and an air leakage prevention labyrinth packing 29, which is an outer layer on the back surface of the impeller, is installed to seal the airtight chamber (
C), and the high-pressure air leakage prevention labyrinth packing 27 is formed with the compressor side of the turbine disk as the outer layer, and the sealed chamber (A) is the exhaust gas intrusion prevention labyrinth with the outer layer formed on the opposite side of the compressor. Sealed chambers (B) are formed by gaskets 28, and atmospheric discharge pipes 44 with control valves (VC) 43 interposed are connected to appropriate locations of the sealed chambers (C) of the exhaust turbine supercharger. The sealed chamber (A) and the air discharge port are connected by a high pressure air introduction pipe 46 via a control valve (vA) 45, and the sealed chamber (B) and the gas outlet casing are A compressor-side shaft position meter 49 attached to the compressor-side shaft end of the rotor shaft 13 and a compressor-side shaft position meter 49 attached to the turbine-side shaft end of the rotor shaft 13 are connected to each other by an exhaust gas communication pipe 48 via a control valve (VB) 47. A shaft position transmitter 51 transmits the respective shaft positions detected by the turbine side shaft position meter 50 and transmits the valve opening degrees of the control valves (VA) 45, (VB) 47, and (VC) 43. an opening degree determination device 53 that calculates and instructs the valve opening degree of each control valve according to a preset process so that the respective measured values detected by the dual-axis position meters are equal to each other using the valve opening degree transmitter 52; The valve opening deviation value corrected by the corrector is connected to a deviation corrector 54 which corrects the deviation between the valve opening detection value of each control valve and the valve opening setting value given by the opening determination device. The controller 55 is connected to a valve opening controller 55 that sets an increase or decrease in the valve opening in accordance with the amount, and further to an actuator 56 that transmits the increase or decrease in the valve opening of each control valve to the respective valve according to a signal from the controller. It is made by connecting. In addition, in the above description of the shaft position meter, the case was described in which the shaft position meter was provided at both ends of the rotor shaft 13, but the shaft position meter may be provided only on one side, and in this case, If the opening determination device 53 is made to calculate and give an instruction so that the detected shaft position matches the initial shaft position when the shaft thrust is zero,
It has a similar effect.

Therefore, according to the present invention, the pressure in each sealed chamber can be controlled by adjusting the valve opening degree of each of the control valves, so that the individual thrust and the entire p-axis thrust of the supercharger can be controlled. 4 a, 4 a, 4, 4 engineering, 4 o, 4
To explain this using an example of adjusting the axial thrust shown in the diagrams, the resultant force F of the pressure difference before and after the turbine blade and the momentum
In Fig. 47, ``rt'' is uniquely determined in the range from 'I'll (reaction Keio University) to T21 (low recoil degree) depending on the recoil degree of the turbine, and the force from the closed chamber (A) side. F
In FIG. 4A, T2 can be freely adjusted in the range from T21 (when the control valve is fully open) to T22 (when the control valve is fully closed) by controlling the control valve (VA) 45, so it can be adjusted in the middle. T24 can be set, and the force FT from the sealed chamber (B) side can be set.
8 is uniquely determined in the range of Ta2 (low reaction, before adjustment) to Ta2 (low reaction, before adjustment) when the control valve (VB) is fully closed in FIG. (1) The pressure PB in the sealed chamber (B) is set to the gas outlet pressure PE in the control valve.
A function in which the valve is closed in the following cases (pB≦PE) and opened in the case of PB>PE; (2) a gas flow from the sealed chamber toward the gas outlet is prevented from gas intrusion by labyrinth packing 2;
8, so if an orifice or conduit of an appropriate shape is installed in place of the valve (VB) to provide one of the uncontrolled functions, the force FT
8 to a constant force T88 (control valve (V
Therefore, as shown in the fourth engineering drawing, the thrust force FT on the turbine side can be adjusted to T48 (after adjustment by B) by control adjustment of control valves (vA) and (VB).
Reaction Keidai, adjust FT to minimum possible, T48 ”'rt
t + T21 + T8B) to T44 (low recoil, adjusted to FT-0, T44 = TL2 + T25 +
'raa), and then the force FBI from the air inlet of the compressor impeller can be set in the range of
The force FB2 from the back of the impeller is uniquely determined to be 13tt by the compressor specifications, and the force FB2 from the back of the impeller is expressed by the control valve (v
c) from B2□ (when the valve is fully closed) to 82
Since it can be adjusted within the range of 2 (when the valve is fully open), settings such as B28.824 between that range can be freely set.
In Fig. 4, the thrust force FB on the compressor side is determined by the control valve (V
By adjusting the control in c), it can be set in the range from B41 (when the valve is fully closed, B41 = Btt + B21) to B42 (when the valve is fully open, B42 - B11 + B22), so B4B (B48 '' Bl□ 10 B28), B44 (B44 ” Bit + B24
) etc. can be freely set. As mentioned above, the thrust force FT1 on the turbine side and the thrust force FB on the compressor side can be set by controlling the respective control valves, so the axial thrust force FTOT of the supercharger, which is the resultant force of these, can be set freely. To give an example of a case where the degree of reaction is large, in the fourth diagram, the turbine side thrust FT is positive (+
) is applied, the compressor side thrust FB is the above 'r
The absolute value is equal to aa and in the opposite direction, that is, negative (-
), the axial thrust F”ro'r is selected.
is M FTOT4B (FTOT4B ”” T4B
+B4B) can be set to zero, and unless the degree of reaction is large, the turbine side thrust FT can be set to T4.
Although it can be adjusted to zero value by itself as in 4,
Since the compressor side thrust force FB is naturally adjusted to a zero value like B44, the resultant force becomes the axial thrust force FTOT44, which has a zero value.

As mentioned above, the present invention controls the turbine side L2L with the control valves (VA> and (VB), respectively, and controls the compressor side thrust with the control valve (VC), thereby controlling the side thrust. Since the supercharger shaft thrust, which is the resultant force of the

[Brief explanation of the drawing]

Fig. 1 is a longitudinal cross-sectional side view of the main parts of a conventional exhaust turbine supercharger, Fig. 2 is a curve diagram showing the value of the supercharger axial thrust corresponding to the degree of reaction of the turbine, and Fig. 3 is a diagram of the present invention. An explanatory diagram showing a part of the control system in a longitudinal sectional side view of the main part showing an example of
4A, 4A, 4 and 4 engineering drawings are curve diagrams showing an example of adjusting the thrust on the turbine side; 4th O, 4ka and 4K are curve diagrams showing an example of adjusting the thrust on the compressor side; The fourth diagram is a curve diagram showing an example of adjusting the supercharger axial thrust. 1...Compressor impeller, 11...Turbine blade, 12@-Turbine disk, 13-Rotor shaft, 21...Compressor side journal bearing, 22...Turbine side journal bearing,
23. Compressor side thrust shaft, 24. Turbine side thrust bearing, 25. Compressor side labyrinth packing, 26. Turbine side labyrinth packing, 27. High pressure air leak prevention labyrinth packing, 28. Q exhaust gas. Intrusion prevention labyrinth seal, 29...Air leak prevention labyrinth seal, 30@・Bearing case, 31・-High pressure air path, 32
...Nozzle inlet, 33.. Nozzle, 34.. Gas outlet casing, 35.. Compressor casing, 36.. Air suction port, 37.. Air discharge port, 38.. Turbine casing, 39.. Exhaust gas Inlet, 40...Exhaust gas outlet, 4
1... Thrust receiver, 42... Air discharge path, 43... Control valve (
VC), 44... Atmospheric discharge pipe, 45... Control valve (VA)
, 46... High pressure air introduction pipe, 47... Control valve (VB),
48...Exhaust gas communication pipe, 49...Compressor side shaft position meter,
50...Turbine side shaft position meter, 51...Shaft position transmitter,
52... Valve opening degree transmitter, 53... Valve opening degree judgment J device, 5
4. Deviation corrector, 55. Valve opening controller, 56
...Actuator, (A)...Sealed chamber, (B)...Sealed chamber, (C)...Sealed chamber. Procedural amendment (method) May 21, 1980 Director-General of the Patent Office Kazuo Wakasugi 1, Indication of case: Japanese Patent Application No. 16112 of 1981 2, Title of invention: Shaft thrust adjustment device in exhaust turbine supercharger 3;
Person making the amendment Relationship to the case Applicant Name Mitsubishi Heavy Industries, Ltd. 4, Sub-Agent Address: 8-chome, Yurakucho, Chiyoda-ku, Tokyo 100
No. 1 Hibiya Park Building No. 519 (Telephone 213-
0686) 5, Daily Amendment Order April 24, 1982
Day 6, subject of correction Drawing 7, content of correction #54-7 or 4th drawing are attached as attached.
C Figure B 4-1 Kotoguchi soil extraction pressure pd (mmHg) Figure 4-1 Figure 11 Pressure machine/mouth outlet pressure P Tsuji (mm?19) Figure 4-O Figure 4-Force diagram

Claims (1)

[Scope of Claims] ■ A turbine disk with a compressor impeller and turbine blades protruding from both shaft ends is arranged, and both sides of a thrust bearing protruding from the middle of the rotor shaft are provided with thrust bearings, and Both sides are supported by journal bearings, and one
The sealed chamber on the back side of the impeller is vented to the atmosphere through a control valve, and the sealed chamber on the compressor side of the disk and the compressor air discharge port are connected via the control valve to the air outlet on the compressor side of the disk. A shaft position transmitter that communicates the side sealed chamber and the gas outlet through a control valve, and transmits the shaft position detected by shaft position sensors at both shaft ends of the rotor shaft, and a valve opening of each control valve. A valve opening transmitter that transmits the valve opening is connected to an opening determination device that calculates and instructs the valve opening according to a setting process so that the measured values of the two axis position meters are equal, and then each valve opening is detected. a deviation corrector that corrects the deviation between the value and the valve opening set value of the opening determination device; and a valve opening controller that sets an increase/decrease in the valve opening in response to the deviation value corrected by the corrector. Furthermore, an axial thrust adjustment device for an exhaust turbine supercharger, characterized in that the device is continuously connected to an actuator that transmits an increase/decrease in the opening degree of each valve to each valve according to a signal from the controller. ■A turbine disk with a compressor impeller and turbine blades protruding from both ends of the rotor shaft is installed. Both sides of the thrust receiver protruding from the middle of the rotor shaft are equipped with thrust bearings, and each side of the thrust receiver is equipped with journal bearings. At the same time, the sealed chamber on the back side of the impeller is vented to the atmosphere through a control valve, and the sealed chamber on the compressor side of the disk and the compressor air discharge port are connected via the control valve to the A shaft position transmitter and each control valve that communicate the closed chamber on the opposite side of the disk compressor and the gas outlet via control valves, and transmit the shaft position detected by the shaft position sensor at one shaft end of the rotor shaft. A valve opening degree transmitter that transmits the valve opening degree of the detected shaft position is connected to an opening degree determination device that calculates and instructs the valve opening degree according to a setting process so that the detected shaft position corresponds to the initial shaft position when the shaft thrust is zero value. connection,
Next, a deviation corrector corrects the deviation between each valve opening detection value and the valve opening setting value of the opening determination device, and further increases or decreases the valve opening in accordance with the deviation value corrected by the corrector. Axial thrust in an exhaust turbine supercharger, characterized in that the axial thrust in an exhaust turbine supercharger is connected in series to a valve opening controller that sets the opening, and further to an actuator that transmits an increase/decrease in the opening of each valve to each valve based on a signal from the controller. Adjustment device.