JPS58193997A - Oil throwing apparatus for fluid machine - Google Patents

Abstract

PURPOSE:To prevent the leakage of lubricating oil into a working chamber, by employing such an arrangement that lubricating oil is supplied only when a shaft is turned by disposing a screw seal between a bearing and an exhaust port of the working chamber and providing a centrifugal oil feeding means for feeding lubricating oil to the bearing by utilizing the centrifugal force caused by the rotation of the shaft as the oil feeding pressure. CONSTITUTION:A non-contact seal 20, an exhaust port 21 and a retainer ring 22 are provided between a work chamber 1 and a bearing 4, and a screw seal 23 is fitted to a shaft 3 in the manner of facing the retainer ring 22. Further, an oil feed passage 24 is formed in the shaft 3 to extend from a position near an oil feed nozzle 29 toward the inside of the shaft 3, and an oil feed port 25 is branched from the oil feed passage 24 to extend toward the screw seal 23. With such an arrangement, when the shaft 3 begins to turn, lubricating oil ejected from the oil feed nozzle 29 is carried to pockets 26 formed in the screw seal 23 via the oil feed passage 24 and the oil feed port 25 and then supplied to the bearing 4 from a jet oil feed port 27. However, when the shaft 3 is not in rotation, pressure is not produced by the centrifugal force, so that the lubricating oil is not ejected from the jet oil feed port 27.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an oil draining device for a fluid machine, and is suitable for use in unlubricated old screw pressure machines and turbo compressors where the rotor is not lubricated. This invention relates to an oil draining device for a fluid machine in which the pressure of +34 is sometimes lower than atmospheric pressure.

FIG. 1 shows an example of an oil-free screw pressure machine as a fluid machine and a conventional oil cutter device 1.

The screw pressure #i shown in FIG. I will do it. The shaft 3 of the screw rotor 2 is
It is rotatably supported by a bearing device 4). A shaft sealing device 5 is provided between the bearing device 4 and the working chamber 1 to prevent compressed air from leaking from the working chamber 1. The t mountain flows into the working chamber 1 without eaves or 7 points.
is a high-speed rotating shaft sealing VIT5, which is usually
A non-contact type seal 6.8 is used in the working chamber IN.
In order to let a small amount of air escape from the 7-rule 6, an exhaust hole 7 is provided. In this exhaust hole 7 and the bearing device It4 cabinet,
Fixed δn shank plate 9 on the seal 8 side of the shaft seal device 5. Aburadameshima 11. An oil drain 12 is provided. The baffle plate 9 is provided with an oil drain hole 10.
By discharging the oil flowing in from the baffle plate 9,
Bearing device! This prevents the drain oil from leaking from 4.

In FIG. 1, reference numeral 13 indicates a jet nozzle for refueling.

In the screw compressor, when the pressure in the working chamber 1 is higher than the atmospheric pressure, a small portion of the one wave of air flowing from the seal 6 is discharged from the exhaust hole 7, as shown by the solid line arrow in FIG. Most of the leaked air flows from the seal 8 toward the oil drain 12 through the oil reservoir 11 and the oil drain hole 10t. With this method, the oil mist floating in the oil sump chamber 11 is discharged from the oil drain chamber 12 along with the flow of leakage air, so no oil mist will flow into the working chamber 1. .

However, when the pressure inside the working chamber l becomes below atmospheric pressure,
For example, in the case of atmospheric pressure suction, the suction side of the initial pressure stage is always below atmospheric pressure due to the resistance of the suction filter and piping, and when reducing the air volume by reducing the suction pressure, the initial pressure stage It is possible for the discharge side of the pump and the suction side of the pressure stage to be below atmospheric pressure. In this case, air flows into the working chamber 1 through the seals 8 and 6 of the shaft sealing device 5, as shown by the arrow W in FIG. Therefore, the oil mist floating in the oil reservoir ml flows into the working chamber IK along with the air flow.

In order to prevent oil mist from flowing into the working chamber 1, the conventional oil drain 9 device introduces seal air from the exhaust hole 7 to increase the pressure between the seals 6 and 8 of the shaft seal device 5. Tamesumill
Furthermore, the air from the seal 8 is moved θL in the direction indicated by the arrow on the real axis in FIG. 1 to prevent oil mist from flowing into the 19.7-ru 6 side.

However, this conventional technique has the following drawbacks.

■ It is necessary to have a separate seal air source available.

■ If the total pressure of the seal is too low, the amount of air flowing through the seal 8i and into the oil drain chamber 12 will be increased.
The internal pressure of the oil tank (not shown) leading to 2 is high.9
This is extremely disadvantageous in preventing smoke emissions.

■ As mentioned above, the pressure inside the working chamber is higher than atmospheric pressure in a lifting platform operating at full load, but when adjusting the air source by suction, the pressure may be lower than atmospheric pressure, such as initial pressure measurement. In this case, there is a fee to control the airflow by opening the exhaust hole 7 to the atmosphere during full load operation and introducing 7 liters of air at the time of 14!1.

In order to solve the drawbacks of the conventional technology for draining air, an oil draining device shown in 1.42 has been proposed.

What is shown in FIG.
1-order, non-contact type seal 14 towards 41141;
The threaded seal 15 and the lip-type seal 16 are integrally formed with each other, and the lip-type seal 16 is provided with an oil drain hole 17.

In the oil cutter shown in FIG. 2, the shaft 3
When the screw seal 15 is not engaged with the viscous cylinder, a small amount of oil passes through the seal gap 18 between the outer periphery of the shaft 3 and the inner periphery of the lip seal 16. Furthermore, since a small amount of oil is discharged through the oil drain hole 17 due to its own weight, there is no fear of oil leaking into the working chamber l.

By the way, jet lubrication is usually used for lubrication of roller head supports used in oil-free screws, turbo compressors, and other cylinder-speed rotation systems because the circumferential speed of the rotor is variable. In addition, since the motor rotates at high speed, a gear device that increases the speed of the motor rotation is always required, and it is common to use the same lubrication system for this lubrication system and the lubrication system for the compressor bearing. And before the compressor stops, take care of the fluid pressure loss! ! Since the rotor is adiabatic, the rotor part is exposed to high temperatures, so the gaps between the screw rotors and the gap between the shaft 3 and the shaft sealing device are small. Temperatures between the casing and gears are also high due to mechanical loss, and bank crashes are becoming smaller. - Immediately after starting the compressor, the shaft may be raised due to a sudden change in load or a shock from starting the Mt motor.
lIb is unstable. Furthermore, thermal expansion due to mechanical loss of the gear causes a sudden change in the negative surface portion. Therefore, even after the compressor is stopped, it is safe to keep the lubricating oil circulating for the purpose of cooling all parts except the bearing device. Note that since the bearing device is expected to increase in mlt during operation, there is no problem even if it is not particularly cooled. Rather, it is better to start the engine without cooling and with a small bearing clearance. It is well known that before starting up the fcf;& to perform an overhaul, check the @ slip system, check the protection circuit, etc., so only the lubricating oil is circulated with the pressurizer stopped. ing.

During such lubrication, in the case of jet lubrication, the jet of lubricating oil ejected from the jet nozzle 13 is the bearing! ! i:fi
When it hit 4, the rotation of the bearing device 4 was covered with oil mist and became deaf.

In connection with this, the rice delivery technique shown in FIG. 2 has the following problems.

■ Wait, the inflow direction of the gI oil jet is the bearing device 40.
When it is between the rolling elements, l! The lip type seal 16 is not enough to prevent oil from entering, so the oil must pass through the threaded seal 15.
= Oil may come up to the excitation chamber l side, and the sealing effect cannot be said to be sufficient.

■ Furthermore, set! Thread seal 15 due to r'i unrestricted restrictions
and the outer diameter of the shaft 3 where the lip seal 1 is provided.
6 (il-) If there is almost no step difference between the provided portion and the outer diameter of the shaft 3, the above-mentioned oil leakage cannot be prevented.

In addition, in Figure 2, the same members as those shown in Figure 1 are designated with reference symbols.

The purpose of the present invention is to reliably prevent r from being excavated into the formed lIb storm mass, regardless of whether the fluid machine is in operation or stopped, without requiring a seal nitrogen source for each machine. @
(a) To provide an oil draining device (m) for a fluid machine which can automatically lubricate a gear device when the fluid machine is stopped and not oil the bearing device without having to separate thread systems.

The Q# imitation of the present invention is to provide a threaded seal between the exhaust hole of the operating chamber of the fluid machine and the bearing device, and convert the centrifugal force accompanying the rotation of the shaft into hydraulic pressure in the bearing device of the threaded seal. In addition, a centrifugal lubrication means for forcibly supplying lubrication toward the bearing device is provided, and this configuration achieves the above objective f.
i- [I was able to achieve this in the past.

Hereinafter, the present invention will be celebrated based on the drawings.

Stripe 3 figure and #! FIG. 4 shows an embodiment of the present invention applied to a screw compressor, in which the working load 1 and the bearing device 11 are
A non-contact type seal 20, an exhaust hole 21. A holding ring 22 is provided.

On the other hand, a screw 7-rule 23 is fitted onto the shaft 3 at a position corresponding to the presser ring 22, and '! A refueling passage 24 is formed inward from the shoulder on the refueling nozzle side, and a refueling hole 25 is provided midway through the refueling 21i circuit 24 toward the threaded seal 23. In the illustrated embodiment, the oil supply holes 25 are provided at intervals of 180° in the circumferential direction.

On the other hand, a pocket 26 for lubricating oil that communicates with the oil supply hole 25 is formed inside the threaded seal 23.
From 6 onwards, a jet oil supply hole 27 is provided in the bearing device 4.

In this embodiment, the oil supply passage 24 and the oil supply hole 25
, the pocket 26 and the jet oil supply hole 27 constitute a centrifugal oil supply means.

Further, the end cover 28 is provided with a refueling nozzle 29 facing the refueling passage 24.
9 is connected to a lubrication system (not shown) for bearings, gears, etc.

In addition, in Fig. 3, 1 indicates the operation, 2 indicates the screw rotor, and 3
0 indicates an oil drain chamber, and 31 indicates an oil drain section.

The shredding device of the above embodiment operates as follows.

That is, when the screw compressor is in operation, the oil is injected from the oil supply nozzle 29. The l oil hits the end of the shaft 39, the - part flows into the drained oil m31, and the other part flows into the shaft 3 because the shaft 3 is rotating at high speed.
The oil flows into the oil supply passage 24 inside.

The lubricating oil 32 that has entered the oil supply passage 24 is transferred to the shaft 3.
Since the shaft 3 is rotating at high speed, the oil is sent from the oil supply hole 25 to the pocket 26 formed in the threaded seal 23 due to the centrifugal force. Adjustment 111I oil 32 adjusts the light.

The rt'fc lubricating oil 32 is provided in the threaded seal 23 through the 'rLfc jet oil supply hole 2.
A jet of lf1m11# oil is sprayed toward the bearing device 114 through the jet, and the bearing device 4 is forcibly refueled.

In the refueling machine, if the device including the refueling nozzle 29 is more than the device consisting of the jet refueling hole 27, the refueling hole 2
5 and the pocket 26 are filled with lubricating oil, and the pressure P acting on the jet oil supply hole 27 at that time is obtained by the following equation.

Here, r... Specific amount of lubricating oil ω... Angular velocity of the shaft g... Acceleration of gravity hIeJ... As shown in Figure 4, the center of the shaft filled with lubricating oil The distance from

In a high-speed rotating machine such as a screw compressor, the angular velocity ω of the shaft is large and the pressure P is sufficiently high at 1 to 3 kg/m. Therefore, during operation of the screw compressor, the viscous pumping action of the screw seal 23 is always maintained, so even when the pressure in operation 1 is high, the pressure 22 and the screw seal 23 are maintained. It is possible to prevent oil mist from leaking from the gaps between the two.

Next, when the screw FEIim machine is in a stopped state, the lubricating oil injected from the oil supply nozzle 29 gets wet from the end of the oil supply passage 24 and flows into the oil drain part 31, so that the lubricant oil is injected into the oil supply hole 25 and the pocket 26. There is no such thing as 32 being full. Therefore, the inside of the pocket 26 has the same atmospheric pressure as the oil drain section 31,
There is no need to lubricate the bearing device 4, so there is no need to worry about oil leakage.

In addition, even if the shaft 3 stops in a severe condition as shown in FIG. Only the pressure of the oil head that is the difference between the distance sli ht from the center of the shaft 3 shown in FIG. 4 acts on the oil supply hole 27, and the jet oil supply hole 27 has a diameter of
Since it is formed to have a small diameter of 2wx phase, extremely dense lubricating oil simply falls vertically downward, and there is no possibility of oil rising.

Therefore, in this embodiment, regardless of the pressure state of the operating peak 1, and regardless of whether the screw compressor is running or stopped, there is no need for a separate seal air source, etc. It is possible to reliably prevent oil leakage 9 due to operational failure.

In addition, when the screw press machine is stopped, that is, when the shaft 30
Even if lubricating oil is not supplied from the lubricating oil system while rotation is stopped, the bearing f! Bearings and gears are not supplied with oil in position 4! ! It is possible to supply oil to the gear device but not to supply oil to the bearing device 4 while the screw compressor is stopped, without having to separate the direct lubrication system.

Note that in the embodiment shown in FIG. Instead, it's a simple ring-shaped thing.

Next, the fifth example shows another implementation ability of the present invention, in which the crawling ring 33 is #I4hM with the fixed ring 34 and the float ring 35, and the float ring 35 is compressed by the compression spring 3.
6 Knotted flange 34 attached to VC rainbow fixing ring 34
' is pressed against. As in this example, suppress/
By adopting a float ring system that moves in the radial direction for the holding ring 330, even if the holding ring 330 float ring 35 comes into contact with the screw seal 23, shaft 3, etc., the float ring 35 moves in the radial direction. Since the ring 33 escapes and is stored in an appropriate position, the gap between the presser ring 33 and other members can be reduced.

Furthermore, FIG. 6 shows another embodiment of the present invention, in which the bearing device 37 is installed at t41. The case where the second bearing is 38°39 is shown. In this example, all, ! An oil supply slot 40 is installed between the bearings 38 and 39 of s2. This oil supply ring 4o is formed with a pocket 41 that communicates with the oil supply hole 25 formed in the shaft 3, and extends from the pocket 41 toward the first and second bearings 38 and 39. A second jet refueling hole 42,43 is provided. And, this implementation power includes the oil supply hole 25, the bulge 41, and the first. Second jet oil supply hole 42°43
t-through 1st. The second bearings 38, 39 can be sprayed with a jet of lubricating oil and refueled.

Note that the other configurations 9 and operations of the embodiment shown in FIGS. 5 and 6 are the same as those of the embodiment shown in FIGS. 3 and 4.

Further, the present invention is applicable not only to the illustrated screw compressor but also to any fluid machine that rotates at high speed.

The present invention has nine functions as explained above, and includes a spring screw seal, a centrifugal oiling means for converting the centrifugal force of the shaft into hydraulic pressure, and forcibly lubricating the bearing device at the same time. Regardless of whether the fluid machine is running or stopped, and without the need for a separate sealing air source,
This has the effect of reliably preventing oil leakage to the working side.

Furthermore, according to the present invention, the sliding system a of the bearing and gear device is
There is also the advantage that the gear system is lubricated and the bearing system is not lubricated automatically when the shaft is stopped.

[Brief explanation of the drawing]

1 and 2 are longitudinal sectional side views showing the conventional n-crt technology, and 3rd figure is a longitudinal sectional side view showing an embodiment of the present invention.
4 is a sectional view taken along the line A--A in FIG. 3, and FIGS. 5 and 6 are longitudinal sectional side views showing different embodiments of the present invention.

Claims (1)

[Claims] A threaded seal is provided between the exhaust hole of the working chamber of the fluid + S copper and the bearing device, and the centrifugal force accompanying the rotation of 7 yaft is supplied to the bearing device @ of the threaded seal to supply hydraulic pressure. An oil draining device for fluid machinery that is equipped with a centrifugal lubrication means that electrically lubricates the fluid machine.