JPS6038592B2 - Seal structure on the driven equipment side of high-speed rotating equipment - Google Patents

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a seal structure on the driven equipment side of a high-speed rotating equipment,
In particular, the present invention relates to a driven equipment side seal structure for high speed rotating equipment that can achieve a complete seal between the rotating shaft and the driven equipment in high speed rotating equipment such as a turbo weekly payer.

[Conventional technology]

Generally, high-speed rotating equipment such as a turbo weekly payer has a turbine wheel as the main driving equipment, and a blower wheel as the driven equipment, and these are connected at the center by the same rotating shaft supported by a bearing part.

In recent years, for vehicles such as buses, trucks, passenger cars, and tractors,
Turbochargers are commonly used in diesel or gasoline engines used for agricultural or construction machinery to increase output and reduce fuel consumption.

By the way, when this type of supercharger is installed in an internal combustion engine, the turbine side as a driving device of the supercharger is connected to the exhaust system of the internal combustion engine, and the driven device is connected to the intake system of the internal combustion engine as an example of a proa. be.

This blower side constitutes a so-called combrezzar, but since the blower compartment that houses the blower fan wheel is under negative pressure, the lubricating oil supplied to the bearing is likely to leak to the blower side. There's a problem. Therefore, conventionally, in order to prevent lubricating oil from leaking from the bearing part to the blower side as a driven device via the rotating shaft, a seal ring is generally provided on the sliding part between the rotating shaft and the driven device. .

[Problems to be Solved by the Invention] However, this seal ring has a slight gap between it and the super saddle portion, and there is a possibility that leakage may occur from this gap.

Therefore, when seal rings are employed, it is necessary to provide a plurality of seal rings on the sliding saddle in order to improve sealing performance, resulting in a problem that the structure of the seal part becomes complicated and maintenance becomes difficult. It has also been proposed to use a mechanical seal instead of a seal ring.

This mechanical seal maintains airtightness by bringing the seat into sliding contact with a washer attached to a rotating shaft using a resilient member such as a spring, and has high sealing performance. By the way, high-speed rotating equipment such as a turbo weekly feeder has large fluctuations in rotational speed and temperature, which causes pulsations in the lubricating oil.

For this reason, the pulsation causes the sheet to be separated from the washer against the spring force of the spring member, and even this type of mechanical seal cannot be expected to provide a reliable and complete seal. [Object of the Invention] The present invention was devised in view of the problem of the seal portion on the driven equipment side of high-speed rotating equipment such as a turbo weekly payer, and to effectively solve the problem.

The purpose of the present invention is to reliably prevent the effects of lubricating oil pulsation, and to achieve a complete seal between a rotating shaft and a driven device in high-speed rotating equipment such as a turbocharger. Another object of the present invention is to provide a seal structure on the side of a driven device of a high-speed rotating device, which has a simple structure, can achieve miniaturization of the device, and is easy to maintain. [Summary of the Invention] In order to achieve the above object, the present invention provides a high-speed rotating device in which a main device and a driven device are connected by a rotating shaft supported by a bearing section interposed between them. An insertion hole through which the rotating shaft is inserted is formed in a partition wall that partitions the device from the equipment, and the oil chamber is boxed outside the insertion hole to form an open annular oil chamber facing the bearing section. , an annular flange portion covering a part of the entrance of the oil chamber is formed on the rotating shaft, and a seal portion is provided between the flange member and an inner inner wall of the oil chamber to seal the gap therebetween; , a biasing means is provided in the oil chamber to press and bias the seal member against the flange member, and pulsation of lubricating oil is supplied and discharged from the oil chamber to the outside of the flange member at the entrance of the oil chamber. A pulsation prevention section is provided to relax and attenuate the vibration.

〔Example〕

A preferred embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 shows a turbo-compounding machine 1 as a high-speed rotating device, and this turbo weekly feeder 1 has a turbine device 2 as a main device and a blower device 3 as a driven device. 4 are connected via a partitioned bearing chamber 5.

Further, a turbine impeller (not shown) constituting the turbine equipment 2 and a blower fan wheel 6 constituting the blower equipment 3 are connected to each other via the same rotating shaft 7 whose center portion is rotatably supported by the bearing portion 4. connected. On the other hand, the blower device 3 is partitioned from the bearing casing 5 by a partition wall 8 that partitions the bearing casing 5. A housing 9 forming the blower device 3 is attached to the partition wall 8 . This housing 9 is formed with a blower casing 11 having an atmospheric air suction port 10 that opens in the axial direction. Further, the housing 9 is formed with a swirl chamber 12 for guiding the pressurized air ejected in the radial direction to a discharge port (not shown). Lotus has been passed. That is, the other end of the rotating shaft 7, to which the turbine wheel of the turbine equipment 2 is attached at the negative end, penetrates the working wall 8 and is inserted into the shaft.
B of device 3. The fan wheel 6 extends into the casing 11 and is attached to the rotating shaft 7. The seal structure of the present invention is for maintaining airtightness between the rotating shaft 7 and the partition wall 8 in order to seal or shield between the inside of the bearing casing 5 and the product casing 11. As shown in Fig. 2, the rotating shaft 7
The rotation axis 7 at the part where it penetrates the partition wall 8 has a
A thrust collar 15 integrally having an annular flange member 14 extending in the radial direction is fixed to the bearing chamber 5 by a drum.

On the other hand, an insertion hole 16 for inserting the rotating shaft 7 together with the thrust collar 15 is formed in the above-mentioned partition plate 8, and the insertion hole 16 is sewn on the outer circumferential side of the insertion hole 16 to face the inside of the bearing wheel chamber 5. An annular oil chamber 17 is formed which is open.

As shown in FIGS. 2 and 3, this oil chamber 17 has a groove shape with one side wall being the sleeve 18 of the partition wall 8 through which the thrust cover 15 is inserted. A plurality of (three in the illustrated example) mooring protrusions 19 are formed extending radially inward. Further, a part of the oil chamber 17 is covered by the flange member 14. In the oil chamber 17, an annular seal member 20 that is attached to the thrust collar 15 is housed. In particular, in the embodiment, the sealing member 20 is composed of a superlattice body 21 such as a carbon bushing formed into an annular shape with different steps, and a circle ring 22. This seal member 20 brings the small-diameter entrance end 21a of the sliding body 21 into contact with the end face of the flange member 14 on the oil chamber 17 side, and also contacts the inner step 21b of the sliding body 21 and the outer periphery of the sleeve portion 18 of the partition wall 8. ○ between the inner wall of the oil chamber 17 and the
It is housed in the oil chamber 17 with a ring 22 interposed therebetween. As shown in FIG. 3, an engagement groove 23 that engages with the engagement protrusion 19 in the oil chamber 17 is formed on the outer circumference of the sliding body 21. It is constructed so that it does not rotate in all directions. In addition, oil chamber 17
A conical coil spring 24 is housed in the spring 24 as a biasing means for pressing the bush body 21 constituting the seal member 20 against the end face of the flange portion 14, and one end (large diameter end) of this spring 24 is connected to the oil chamber. The other end (small diameter end) is in contact with the large flea entrance end 21c of the sliding body 21 via the annular spring receiver 25.

The spring receiver 25 covers an annular entrance portion 26 defined between the inner step portion 21b of the sliding body 21 and the outer circumferential portion of the sleeve portion 18 of the partition wall 8, and restricts the movement of the O-ring 22. It is also structured as follows. On the other hand, on the outside of the flange portion 14 at the entrance 27 of the oil chamber 17, a pulsation prevention member 28 is provided to prevent pulsation or pulsation of the lubricating oil supplied into the bearing casing 6. .

The pulsation prevention member 28 is located on the flange member 14 at the inlet 27 of the oil chamber 17, and has an annular closed portion formed between the outer circumference of the flange member 14 and the outer inner wall 17b facing in the axial direction of the oil chamber 17. It consists of an annular plate formed to cover. As shown in FIG. 3, a plurality of engagement tongues 28a are formed at appropriate intervals along the circumferential direction on the outer circumferential portion of the pulsation prevention member 28 as attachment means therefor.
An annular groove 29 along the circumferential direction is formed in the outer inner wall 17b, and the engagement tongue 28a engages with the annular groove 29. This annular groove 29 has an inlet 2 for introducing the engaging tongue 28a.
9a is formed, and the pulsation prevention member 28 can be attached by inserting the engaging tongue portion 28a into the annular groove 29 through the introduction port 29a and slightly rotating it in the circumferential direction. Furthermore, a plurality of lubricating oil introduction notches 28b are formed on the outer periphery of the pulsation prevention member 28, and the pulsation prevention member 28 is formed between the outer periphery and the outer inner wall 17b of the oil chamber 17 and on the inner periphery when the pulsation prevention member 28 is installed. It is set so that gaps a and Sb are formed between the flange portion and the outer peripheral portion of the flange portion 14, respectively. In FIGS. 1 and 2, reference numeral 30 denotes a thrust bush which is iron-mounted on the rotating shaft 7 between the bearing portion 4 and the flange member 14, and 31 is iron-mounted on the thrust bush 30, with a radius inside. A thrust metal member 32 having an oil passage 31a along the direction is a seal ring interposed between the thrust collar 15 of the sleeve portion 18 of the partition wall 8.

Next, we will discuss the effect.

The seal member 20 housed in the oil chamber 17 has a sliding saddle body 21, which is a component thereof, pressed in the direction of the saddle by a spring 24, and slides into contact with the end face of the flange member 14 attached to the rotating shaft 7. 22 seals between the sliding body 21 and the sleeve portion 18 of the partition wall 18, thereby completely sealing the space between the rotating shaft 7 and the partition wall 8.

Therefore, it is possible to completely seal the rotating shaft 7 that connects the general bearing part 4 to the bearing casing 5 and the blower device 3 as a driven device, even if the inside of the blower casing 11 becomes negative pressure. The lubricating oil in the bearing casing 5 does not leak into the blower casing 11. In particular, even if the lubricating oil that is circulated around the seal member 20 through the oil passage 31a of the thrust metal 31 pulsates due to rapid fluctuations in the rotational speed of the rotating shaft 7, the pulsation will be suppressed. It is relaxed or attenuated by the pulsation prevention member 28 at the inlet 27 of the oil chamber 17.

This is because the defective portion 28 formed in the pulsation prevention member 28
b and the gap Sa serve as an orifice, and when the pulsation of the circulating oil passes through the gap Sa, it is attenuated or smoothed, and the oil chamber 1
This is because it works in such a way that it does not act directly on 7. Therefore, separation between the flange member 14 and the sliding saddle body 21 due to pulsation can be reliably prevented and a complete seal can be achieved. In addition, the lubricating oil blown away from the outer circumference of the thrust bush 30 by centrifugal force is transferred to the oil chamber 17.
The oil chamber 17 collides with the green portion of the outer periphery of the inlet 27, and the momentum causes the oil chamber 17 to pass through the outer gap Sa and the notch 28b of the pulsation prevention member 28.
The liquid flows into the bottom wall 17a along the outer inner wall 17b of the oil chamber 17, as shown by the arrow in FIG. It turns out. In this way, as the alcohol body 21, which is a component of the seal member 20, is pressed against the flange member 14 by the hydraulic pressure, the lubricating oil in the oil chamber 17 is transferred to the pulsation prevention member 28.
New lubricating oil is discharged from the inner gap Sb and continuously circulated and supplied to the oil chamber 17 to efficiently cool the sealing member 20 that is heated by friction, thereby improving sealing performance as much as possible. can be done. On the other hand, since the seal structure of the present invention is of a so-called cassette type in which the seal member 20 is detachably housed in the oil chamber 17, the seal member 20 can be easily replaced and maintenance is easy.

In the above embodiment, the sealing member 20 is composed of the sliding body 21 and the circle ring 22, but the point is that if it is possible to seal between the flange member 14 formed on the rotating shaft 7 and the partition wall 8, this can be used. It is not limited to.

Further, in the above embodiment, the thrust collar 15 and the partition wall 8
Although the seal ring 32 is interposed between the rotary shaft 7 and the partition wall 8, it is not necessary to provide it because the seal member 20 completely seals between the rotary shaft 7 and the partition wall 8. [Effects of the Invention] In summary, the present invention exhibits the following excellent effects.

■ A seal member that seals between the flange member formed on the rotating shaft and the partition wall is provided in the oil chamber, and a pulsation prevention section is provided at the entrance of this oil chamber, so that the pulsation of the lubricating oil is relaxed and attenuated, and the seal member It is possible to reliably prevent the impact on
Therefore, complete sealing between the rotating shaft and the driven equipment in high-speed rotating equipment such as turbochargers can be achieved.

(2) Furthermore, since the lubricating oil is circulated within the oil chamber to cool the seal member, deterioration of the seal member due to frictional heat can be prevented, and the durability and sealing performance of the seal member are improved.

(2) In particular, a cassette type structure in which the seal member is housed in the oil chamber is adopted, so assembly is easy and maintenance such as replacing the seal member is easy.

(2) The structure is simple, and the seal structure on the driven equipment side of high-speed rotating equipment such as a turbo weekly payer can be simplified, and the entire equipment can be downsized.

[Brief explanation of drawings]

Fig. 1 is a cutaway sectional view showing an embodiment of the seal structure of the present invention, Fig. 2 is an enlarged sectional view of section A in Fig. 1, and Fig. 3 is a section taken along line mm in Fig. 2. FIG. In the figure, 1 is a turbo supercharger illustrated as a high-speed rotating device,
2 is a turbine device which is a main device, 3 is a blower device which is a driven device, 4 is a bearing part, 7 is a rotating shaft, 8 is a partition wall, 1
4 is a flange member, 16 is an insertion hole, 17 is an oil chamber, 27 is a coil spring serving as a biasing means, and 28 is a pulsation prevention member. Figure 2 Figure 1 Figure 3

Claims (1)

[Claims] 1. In a high-speed rotating device in which a main device and a driven device are connected by a rotating shaft supported by a bearing section interposed between them, the rotating shaft is inserted through a partition wall that partitions the bearing section and the driven device. an annular oil chamber is formed outside of the insertion hole, surrounding the insertion hole, and facing the bearing portion and opening, and covering a part of the entrance of the oil chamber on the rotating shaft. An annular flange member is formed, a sealing member is provided between the flange member and an inner inner wall of the oil chamber for sealing therebetween, and the sealing member is biased to press against the flange member within the oil chamber. High-speed rotation characterized in that a biasing means is provided, and a pulsation prevention member is provided on the outside of the flange member at the entrance of the oil chamber for moderating and attenuating the pulsation of lubricating oil supplied and discharged from the oil chamber. Seal structure on the driven device side of the device.