JPS5941355Y2 - oil cooled compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in an oil-cooled compressor in which a non-contact seal is provided on the bearing side of the main body of a part of the rotor to completely lubricate the bearing part.

In general, the shaft pipe lubrication method for large oil-cooled rotary compressors is to drive the pump fully and supply all the oil, but in relatively small compressors, a part of the rotor By forming a non-contact seal such as a labyrinth seal on the bearing side of one main body, the oil supplied to a part of the rotor is supplied little by little to the bearing part, while the oil accumulated in the bearing part is returned to the return pipe metal. Advantageous is the return to the suction via the pump.

However, with this type of mechanism, when the compressor is operating under load, a portion of the compressed air enters the bearing part along with the oil through the labyrinth seal metal, and is returned to the suction part through the entire return pipe. According to the results, the compression efficiency decreases by about 3%.

Also, during load operation, a small amount of oil that has passed through the oil separator will accumulate on the outlet side of the separation element built into the oil separator, but in order to completely remove this oil, conventionally the oil was sucked in through piping. He was returned to the club.

However, with this method, the actual amount of intake air is reduced by the volume of the oil and a portion of the compressed air that has entered the suction section, and a reduction in compression efficiency is inevitable.

still,! During no-load operation of a compressor, that is, when the suction section is blocked, the bearing section as well as a portion of the rotor are in a vacuum state, so a so-called vacuum sound is generated. Atmospheric air enters the bearing through all the oil seals, and this air passes through the return pipe and returns to the suction section of the rotor body, causing a slight increase in the discharge pressure inside the oil separator.
It has been pointed out that the disadvantage is that the power increases when there is no load, and the unloader function cannot be fully performed.

Furthermore, as a means for preventing the generation of vacuum noise and the slight rise in pressure during no-load conditions as described above, the applicant has proposed that the amount of air in the oil separator is supplied to the bearing section via an unloader 4 to maintain a constant amount of air within the bearing section. We provided a pressure regulating device that allows the entire pressure to be filled with air [Registered Utility Model No. 1374042 (Utility Model No. 55-31268)].

However, since this device supplies only all the air to the bearing, the amount of air supplied to the bearing tends to become uneven due to pressure fluctuations in the oil separator, and if the no-load operation continues for a long time, the bearing may become damaged due to insufficient oil supply. There is a risk of seizure of parts.

The present invention was developed to solve the above-mentioned problems, and its purpose is to connect a conduit that supplies oil accumulated in the oil separation element to the bearing part of the oil tank and has the first throttling mechanism 4. , a branch pipe interposed between the oil fraction and the outlet of the first throttling mechanism and having a second throttling mechanism 4 is provided to supply a predetermined amount of oil to the bearing part regardless of whether it is loaded or unloaded. To provide an oil-cooled compressor which maintains a proper working force of a bearing part and which is free from the risk of deterioration of compression efficiency.

! In addition, another object of the present invention is to fully provide a return pipe for returning the oil supplied from the oil separator or its separation element and accumulated in the bearing part to the compression chamber of a part of the rotor immediately after the compressed air is completely closed, and the bearing The internal pressure 4 is always kept constant to prevent the generation of vacuum noise and the unloader function 4 is maintained when no load is applied.
Furthermore, the present invention provides an oil-cooled compressor that can increase compression efficiency.

Next, one embodiment of the present invention will be explained along with a diagram.

Reference numeral 1 is a motor, which is capable of driving a part of the rotor through a belt 2, and 4 is a bearing part, which supports the rotor body so as to be rotatable 54 times.

A labyrinth portion 6 is formed in the rotor main body 5 to limit leakage 4 between the bearing portion 4 and the rotor portion 3 to a minute amount.

Reference numeral 7 denotes a suction shutoff valve, which has a suction port 84 and is connected to the oil separator 11 via a pipe 9 and a pressure regulating valve 10 .

This oil separator 11 is fully equipped with a minimum pressure pulp 12 and has a built-in separation element 13.

In addition, 14 is drain pulp.

Further, the oil separator 11 is connected to the rotor part 3 via a pipe 15 through an oil cooler 16 and an oil filter 174, so that oil 4 can be supplied to the rotor part 3.

Further, the rotor portion 3 is connected to the oil separator 11 by a pipe 18 via a check valve 19 metal.

In addition, 20 is oil stop pulp.

Reference numeral 21 denotes a return pipe, which connects the bearing part 4 and the compression chamber 22 of the rotor part 3, and interrupts the communication between the suction port 8 and the compression chamber 22 immediately after closing, that is, while the rotor main body 5 is rotating. Immediately thereafter, the compression chamber 22 and the bearing portion 4 are able to communicate with each other.

The outlet side of the separation element 13 communicates with the bearing part 4 through a conduit 23, so that a part of the oil and compressed air accumulated on this outlet side can be supplied to the bearing part 4.

A throttle nozzle 24 is interposed in the middle of this conduit 23 as a first throttle mechanism, and the diameter of this throttle nozzle 240 is designed so that an appropriate amount of oil can be supplied to the bearing part 4, and it is separated during load operation. It is best to make it so thin that only the oil that collects on the outlet side of the element 13 can flow out, but especially in the case of small compressors, it is not possible to make it too thin for processing and prevention of clogging, so it is necessary to compress the oil along with the oil. A portion of the air is sent to the bearing section 4.

In addition, the piping 15 leading to the oil separator 11, oil cooler 16, oil filter 17, and oil stop pal 7'20 is connected to the conduit 23 on the outlet side of the throttle nozzle 24 through a branch pipe 25, and the oil The structure is such that oil can be completely supplied to the bearing portion 4 from the separator 11 as well.

A throttle nozzle 26 is also interposed in the middle of this branch pipe 25 as a second throttle mechanism, and it is appropriate that the diameter of this throttle nozzle 26 is equal to or smaller than that of the throttle nozzle 24.

I will explain the entire structure of the story.

During load operation, the motor 1 drives the rotor body in the rotor part 3, and suction l is drawn from the suction port 8.
The compressed air is stored in the oil separator 11 via the check valve 194.

Thus, oil is supplied from the oil separator 11 to the rotor main body 5 in the rotor part 3 via the oil cooler 16 and the oil filter 174, and most of the oil passes through the pipe 184 to the oil separator 11. , some of the oil passes through the labyrinth section 64 and is supplied to the bearing section 4, and further passes through the entire return pipe 21 and returns to the compression chamber 22 of the rotor section 3.

Here, a part of the oil and compressed air accumulated on the outlet side of the separation element 13 are supplied to the bearing part 4 through the conduit 23 and the throttle nozzle 244, while a part of the oil accumulated at the bottom of the oil separator 11 is also supplied. Since the oil is supplied to the bearing part 4 through the branch pipe 25, the throttle nozzle 26, and the conduit 23, even if the pressure inside the oil separator 11 fluctuates, the oil supplied through the branch pipe 254 acts as a resistance and the oil is supplied to the bearing part. The amount of oil etc. supplied to 4 is made uniform.

! In addition, the bearing part 4 and the compression chamber 22 of the rotor part 3 are communicated with each other immediately after closing, and at this time, the communication between the return pipe 21 and the suction port 8 is blocked by the rotor body 5. The amount of suction from the suction port 8 does not decrease, and on the contrary, the compression efficiency increases by the amount of oil and compressed air sent from the bearing part 4 into the compression chamber 22 immediately after closing.

Next, during no-load operation, the separation element 130
Although oil cannot be supplied from the separation element 13 because no oil accumulates at the outlet (by principle), oil is supplied from the oil separator 11 to the bearing part 4 via the branch pipe 254. The entire oil can be supplied to the bearing portion 4 without measuring too much or too little.

In addition, as mentioned above, the oil etc. supplied into the bearing part 4 is constantly returned to the compression chamber 22 immediately after closing via the return pipe 2, and the separation element 13 of the oil separator 11 is closed during no-load operation. Since compressed air does not flow, there is no oil on the outlet side of the separation element 13, and the compressed air in the oil separator 11 is introduced into the bearing part 4 through the throttle nozzle 24 and the conduit 234, so that the bearing part does not flow during load operation. The pressure increases at 1 near the pressure generated at 4, thereby relaxing the negative pressure in the bearing section 4, and thus clearing out the high vacuum generated due to the vacuum state inside the bearing section 4.

As detailed above, according to the present invention, the oil accumulated on the outlet side of the separation element in the oil separator is supplied to the bearing part through the entire throttle mechanism, and the oil, etc., accumulated on the outlet side of the separation element in the oil separator is supplied to the bearing part, and Since it is configured to return to By communicating through the branch pipe with the throttling mechanism 4, the supply of oil into the bearing is ensured and the amount of oil supplied is uniform, and there is no risk of seizure of the bearing due to insufficient oil supply even after long periods of no-load operation. do not have.

Overall, the structure is simple, there are few failures, and it can be manufactured at low cost, etc., and it has many advantages, and is particularly suitable for medium and small-sized oil-cooled rotary compressors.

[Brief explanation of drawings]

Fig. 1 is a system explanatory diagram showing one embodiment of the present invention, and Fig.
The figure is an explanatory cross-sectional view of the main part of the same embodiment. 3... Rotor part, 4... Bearing part, 1
DESCRIPTION OF SYMBOLS 1... Oil separator, 13... Separation element, 21... Return pipe, 22... Compression chamber, 23... Conduit, 24, 26... Throttle nozzle, 25... Branch pipe.

Claims (1)

[Scope of utility model registration request] A non-contact type seal part 4 is formed on the bearing side of the rotor main body of a part of the rotor, and oil and metal supplied to the compression chamber of the rotor part are supplied in small quantities to the bearing part through the non-contact type seal part. In the oil-fed compressor in which all of the bearing parts are lubricated, an oil separator having a separation element 4 for collecting oil discharged mixed with the compressed air of the oil-fed compressor; Oil accumulated on the discharge side is supplied to the bearing part by a conduit system equipped with a first throttling mechanism and the pressure of compressed air in the oil separator at the bottom of the oil separator. It consists of a branch pipe system equipped with a second throttling mechanism, and a return pipe for returning the oil and compressed air accumulated in the bearing section to the compression chamber immediately after the rotor is closed. An oil-cooled compressor characterized by four features: the pressure in the bearing section is configured to be close to the pressure during full load operation.