JPH06113503A - Hermetically sealed lubricator for electric rotating machine - Google Patents

Abstract

PURPOSE:To obtain a hermetically sealed lubricator for electric rotating machine in which reliability is enhanced by preventing leakage of cooling gas without increasing the size of emergency power supply facility. CONSTITUTION:Second pressure regulation valves 20, 22 for boosting the delivery pressures of normal and emergency hermetically sealed oil pumps 6, 8, and valves 21, 23 for interrupting the discharge conduits of pressure regulation valves 7, 9 for the oil pumps 6, 8 are arranged in the return loops of the oil pumps 6, 8 on the delivery side thereof. A pressure switch 25 is also provided in order to detect hermetically sealed oil pressure in the downstream of a pressure difference regulation valve 10 thus operating the oil pumps 6, 8 in parallel.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a sealing oil supply device for a rotary electric machine which is used for preventing leakage of hydrogen gas from a shaft penetrating portion of the rotary electric machine which is cooled by hydrogen gas. .

[0002]

2. Description of the Related Art Generally, a sealing oil supply device for a rotating electric machine is designed to prevent hydrogen gas from leaking to the atmosphere from a portion passing through a shaft of a rotating shaft when the rotating electric machine is forcibly cooled by hydrogen gas. The rotary electric machine is provided with a shaft seal portion, supplies pressure oil, and thereby seals hydrogen gas.

FIG. 9 shows a system diagram of this device. In the figure, 1 is a turbine generator that is a rotating electric machine, and 2 is
A shaft seal portion for sealing hydrogen gas in the turbine generator 1,
3 is a supply oil pipe for supplying sealing oil to the shaft seal portion 2, 4
Is a vacuum oil tank for deaerating and dehydrating the sealing oil for sealing the hydrogen gas of the rotary electric machine 1 with the lubricating oil from the bearing oiling device 12, and the reference numeral 5 denotes a constant amount of sealing oil in the vacuum oil tank 4. A float valve for controlling the surface, 6 is a regular sealing oil pump driven by an AC power supply for supplying the sealing oil in the vacuum oil tank 4 to the shaft seal portion 2, and 7 is a discharge pressure of the regular sealing oil pump 6. It is a pressure adjusting valve for adjusting to a desired value and is discharged to the feedback loop when the discharge pressure exceeds a set pressure.

Further, 8 is an emergency sealing oil pump driven by a DC power source for operating as a backup when the regular sealing oil pump 6 fails, and 9 is a discharge pressure of the emergency sealing oil pump 8. It is a pressure adjusting valve for adjusting to a predetermined value and is discharged to the feedback loop when the discharge pressure exceeds a set value. The reference numeral 10 automatically adjusts the valve opening according to conditions such as the rotation speed of the turbine generator 1 and the hydrogen gas pressure in the machine, and the supply oil pressure of the sealing oil supplied to the shaft seal portion 2 is always specified by the pressure of the hydrogen gas in the machine. It is a differential pressure regulating valve that keeps the differential pressure between the supply pressure and the hydrogen gas pressure inside the machine constant so as to increase by the value of.

Further, 12 is an oil tank in which the sealing oil supplied to the shaft seal portion 2 returns through the return pipe 11, and the lubricating oil supplied to each bearing of the steam turbine and the generator returns and is stored together. 13, a bearing oil supply pump 14 for supplying the lubricating oil of the oil tank 13 to each bearing portion, for cooling the oil temperature of the lubricating oil whose temperature has risen due to frictional heat in each bearing portion and shaft seal portion to a predetermined temperature A bearing oil supply device including an oil cooler 15 and the like. Reference numerals 17 and 18 denote check valves of the sealing oil discharged from the regular sealing oil pump 6 and the emergency sealing oil pump 8, respectively. A vacuum pump (not shown) is connected to the vacuum oil tank 4 so that the sealing oil in the vacuum oil tank 4 is deaerated and dehydrated.

In the above structure, during normal operation, part of the lubricating oil having a predetermined temperature in the bearing oil supply device 12 passes through the branch pipe 16 and the float valve 5 in the vacuum oil tank tank 4 to pass through the vacuum oil tank. A fixed amount is stored in 4 as a sealing oil.
The sealing oil in the vacuum oil tank 4 is adjusted to a desired sealing oil pressure by the pressure adjusting valve 7 by the regular sealing oil pump 6, and then passes through the supply oil pipe 3 via the differential pressure adjusting valve 10 to pass through the shaft of the turbine generator 1. The hydrogen film supplied to the seal portion 2 prevents the hydrogen gas inside the machine from leaking to the outside. The sealing oil supplied to the shaft seal portion 2 returns to the oil tank 13 via the return pipe 11, and the lubricating oil cooled to a predetermined temperature in the oil cooler 15 by the bearing oil supply pump 14 circulates again. .

Further, in an emergency such as when the regular sealing oil pump 6 is stopped or the AC power source is lost, the emergency sealing oil pump 8 is automatically activated to seal the shaft seal portion 2 of the turbine generator 1. The system is such that the turbine generator 1 can be continuously operated without being supplied with oil and leaking hydrogen gas inside the machine to the outside.

[0008]

In the conventional sealed oil system configured as described above, when a serious accident occurs in the power transmission system, such as the loss of the on-site power supply to each device in the power station, Since the turbine generator can be stopped safely when the plant is stopped, the emergency sealing oil pump 8 driven by the DC power source is started, and after a few minutes, the emergency diesel power generation system is started and the regular sealing oil pump is important. It supplies power to various devices and supplies necessary sealing oil.

However, in a large-capacity power plant such as a nuclear power plant, since the steam turbine and the steam turbine generator are large-sized, it takes one hour or more before the inertial force of the steam turbine is greatly stopped. Then, during this period, the lubricating oil and the sealing oil must be continuously supplied to the bearings and the shaft seal portion 2 of the steam turbine or the turbine generator.
Since the cooling water in 15 is stopped, the temperature of the lubricating oil rises due to the frictional heat of the bearings, etc., and the temperature of the sealing oil also rises accordingly. The amount of sealing oil required at the seal portion will increase. The required amount of oil at that time reaches 3 to 3.5 times that of normal operation. Further, the amount of seal oil also increases due to the large damage of the seal ring portion. In the case of such a serious accident, there were the following problems.

(1) Generally, pressure adjusting valves 7 and 9 for adjusting the discharge pressure of the regular sealing oil pump 6 and the emergency sealing oil pump 8.
The setting value of is set so that the flow rate is 2 to 2.5 times the normal sealing oil amount so that it can be sufficiently supplied even if the sealing oil amount increases due to small scratches on the shaft seal. Since the setting is made, when the oil amount becomes larger than that, if the pipe resistance increases and becomes equal to the set pressure in the pressure regulating valve, it becomes impossible to supply any more and the hydrogen gas in the machine leaks. (2) When the capacity of the regular sealing oil pump 6 or the emergency sealing oil pump 8 is increased and the discharge pressure is increased, the amount of leak in the pressure adjusting valves 7 and 9 increases during normal operation, which causes noise and vibration. In addition to problems such as oil temperature rise due to heat of stirring, the drive motor becomes large and power consumption increases. (3) When the power supply in the plant is lost, if the power of the cooling water supplied to the oil cooler is incorporated into the emergency diesel power generation system in order to keep the temperature of the lubricating oil and sealing oil constant, the cooling water will be stored in the plant. The cooling water is supplied to all the heat exchangers, and the power is extremely large, so the emergency power supply equipment becomes large. Most of the cooling water is used in the heat exchanger to cool the heat generated by the turbine generator, but when the plant is stopped, the generator will be in a no-load operation state, so heat is generated. However, it is uneconomical to incorporate the cooling water system into the emergency power system only for the oil cooler. On the other hand, the vacuum oil tank is supplied with lubricating oil in an amount substantially the same as the amount of sealing oil supplied from the bearing oil supply device 12 to the shaft seal portion 2, and the inside of the vacuum oil tank 4 is maintained in a vacuum state by a vacuum pump (not shown). By doing so, the sealing oil in the vacuum oil tank 4 is deaerated and dehydrated, and is supplied as high quality sealing oil to the shaft seal portion 2 by the sealing oil pump 6 to remove moisture when the in-machine hydrogen gas of the rotary electric machine 1 comes into contact with the sealing oil. The hydrogen gas purity is prevented from deteriorating due to moisture absorption or the inclusion of air or the like.

In order to sufficiently obtain the effect of deaerating and dehydrating the sealing oil, the bypass oil connected to the outlet pipe of the regular sealing oil pump 6 is used to recirculate and spray the sealing oil into the vacuum oil tank to degas and dehydrate the sealing oil. The recirculating oil amount is usually about 2 to about 2 of the sealing oil amount supplied to the shaft seal portion 2 of the turbine generator.
I need three times. Therefore, the designed discharge amount of the regular sealing oil pump 6 is 3 to 4 times as large as the supplied sealing oil amount in consideration of the degassing / dehydration recirculating oil amount and the sealing oil amount supplied to the turbine generator. Will be needed.

Further, in recent years, with the increase in capacity of turbine generators, the amount of sealing oil has also increased, and the sealing oil pump is becoming larger. In addition to the sealed oil pump, a recirculating oil pump was needed to obtain the amount of recirculating oil required for degassing and dehydration in order to increase the oil capacity. These not only consume too much power, but also the sealing oil supply device becomes excessively large to increase the construction cost, and further, it requires a great deal of money to maintain the operation and reliability of the dynamic equipment. I was trying.

A first object of the present invention is to provide a sealing oil supply device for a rotating electric machine, which prevents leakage of cooling gas in the rotating electric machine without increasing the size of emergency power supply equipment and improves reliability. To provide. A second object of the present invention is to re-install the sealing oil for deaeration and dehydration without installing a recirculation pump or increasing the capacity of a regular sealing oil pump even if the rotating electric machine has a large capacity. It is an object of the present invention to provide a sealing oil supply device for a rotary electric machine that can secure a circulating oil amount.

[0014]

The present invention is based on the above-mentioned first aspect.
In order to achieve the purpose of the above, a vacuum oil tank for supplying degassed and dehydrated sealing oil to a shaft seal portion of a rotating electric machine in which a cooling gas is sealed, a regular sealing oil pump and an emergency sealing oil pump, In a sealed oil supply device for a rotary electric machine equipped with the pressure regulating valve and the differential pressure regulating valve of claim 1, a bypass pipeline is provided in a feedback loop on the discharge side of the first pressure regulating valve, and the first pressure regulation is performed in the bypass pipeline. A shutoff valve is provided on the discharge side of the first pressure adjusting valve according to the sealing oil pressure downstream of the second pressure adjusting valve and the differential pressure adjusting valve whose set pressures are different from each other, and A pressure detector is provided for detecting the pressure of the sealing oil and transmitting a signal for operating the regular sealing oil pump and the emergency sealing oil pump in parallel.

Further, in order to achieve the above-mentioned second object, the present invention provides a vacuum oil tank for supplying degassed and dehydrated sealing oil to a shaft seal portion of a rotating electric machine in which a cooling gas is sealed, which is normally used. In a sealing oil supply device for a rotary electric machine equipped with a sealing oil pump, an emergency sealing oil pump, a pressure adjusting valve, and a differential pressure adjusting valve, an ejector for sucking the sealing oil in a vacuum oil tank into a return loop on the discharge side of the pressure adjusting valve. Is provided.

[0016]

According to the first means, the normal sealing oil pump and the emergency sealing oil pump are operated in parallel according to the sealing oil pressure downstream of the differential pressure regulating valve corresponding to the sealing oil amount, and the first pressure is applied. By switching from the adjusting valve to the second pressure adjusting valve, it becomes possible to increase the amount and pressure of sealing oil to be supplied,
It is possible to prevent the cooling gas from leaking from the rotating electric machine and safely stop the rotating electric machine.

According to the second means, the sealing oil returned to the vacuum tank via the feedback loop on the discharge side of the pressure control valve becomes a high-speed flow by passing through the ejector, and the sealing oil is provided inside the vacuum oil tank on the outer circumference of the ejector. The sealing oil is sucked and mixed, and the amount of oil supplied to the ejector is increased by about 2 to 3 times and sprayed. The sealing oil in the vacuum oil tank can be recirculated, and the capacity of the regular sealing oil pump is increased. It is not necessary to install a recirculation pump or a recirculation pump, and the device can be made compact and the operating cost can be reduced.

[0018]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a system diagram showing an embodiment of the present invention.
Note that the same parts as those in FIG. 9 described above are denoted by the same reference numerals, and redundant description will be omitted. In FIG. 1, 20 is a second pressure regulating valve for increasing the discharge pressure of the regular sealing oil pump 6, 21 is a shutoff for shutting off the discharge pipeline of the pressure regulating valve 7 on the regular sealing oil pump 6 side. The valve 22 is a second pressure adjusting valve for increasing the discharge pressure of the emergency sealing oil pump 8, and 23
Is a shutoff valve for shutting off the discharge pipeline of the pressure control valve 9 on the emergency seal oil pump 8 side, 24 is a pressure guiding pipe for switching the shutoff valves 21 and 23, and 25 is a differential pressure control valve 10. A pressure switch for detecting the downstream pressure, 26 is a relay circuit for transmitting a signal for activating the regular sealing oil pump 6 and the emergency sealing oil pump 8 in response to a signal from the pressure switch 25. Two-way ball valves are used as the shutoff valves 21 and 23, respectively.

FIG. 2 is a diagram showing the relationship between pressure and flow rate in one-pump operation and two-pump operation in parallel. The maximum flow rate in one-pump operation is Q, and in the case of two-pump operation, it is two. Although it is the flow rate for the unit and the total flow rate is Q ', the discharge pressure is actually adjusted to P ₁ by the pressure adjusting valve, and the flow rate is Q ₁ .

Next, the operation of this embodiment will be described. When an accident occurs such that the power source in the station is lost, the AC power source for driving the regular sealing oil pump 6 is cut off, and at the same time, the emergency sealing oil pump 8 driven by the DC power source is started,
Sealing oil is supplied to the shaft seal portion 2 of the turbine generator 1, but since the cooling water of the oil cooler 15 is stopped, the lubricating oil is generated by the friction heat of the bearings of the steam turbine and the turbine generator.
The temperature rises. Along with that, the temperature of the sealing oil supplied to the shaft seal portion 2 also rises, using a part of the lubricating oil.
Since the viscosity changes, the amount of sealing oil required also increases, reaching 2 to 2.5 times the rated value in about 10 minutes. Differential pressure adjustment valve at that time
Although 10 is fully opened, the pressure downstream of the differential pressure adjusting valve 10 becomes equal to the pressure set by the pressure adjusting valves 7 and 9, but the set value of the pressure switch 25 is set slightly lower than the set value of the pressure adjusting valve 10. Then, the pressure switch 25 is actuated before the pressures become equal to each other, the AC power is supplied from the emergency diesel power generation system via the relay circuit 26, and the normal sealed oil pump 6 that is in the startable state is restarted to perform the emergency operation. The seal oil pump 8 is operated in parallel to increase the supplied seal oil amount.

On the other hand, the shut-off valves 21 and 23 arranged in the discharge conduits of the usual pressure adjusting valves 7 and 9 are two-way ball valves, which are normally opened by the spring in the drive cylinder.
The pressure downstream of the differential pressure regulating valve 10 is guided to the drive cylinder through the pressure guiding pipe 24, and when the predetermined pressure is reached, the piston in the driving cylinder is pushed to close the ball valve, and the discharge lines of the normal pressure regulating valves 7 and 9 are closed. Shut off.

Due to this interruption, the discharge pressures of the regular sealing oil pump 6 and the emergency sealing oil pump 8 are adjusted by the second pressure adjusting valves 20 and 22, respectively. By the way, the second pressure regulating valves 20 and 22 are the usual pressure regulating valves 7 and 9
Since it is set to P ₂ higher than the set pressure P _{1 of} 2
Even if the effective amount of sealing oil in parallel operation increases from Q ₁ to Q ₂ and the pipe resistance increases, the shaft seal 2
It becomes possible to supply the sealing oil to.

The present invention is based on the above-mentioned embodiment (hereinafter,
The present invention is not limited to the first embodiment), and various modifications can be made. FIG. 3 is a system diagram showing a main part of another embodiment (hereinafter, referred to as a second embodiment) of the present invention. This second
In the embodiment, a pressure control valve is used instead of the conventional pressure adjusting valves 7 and 9.
28 and 29, the pressure detector 30 detects the pressure downstream of the differential pressure regulating valve 10, and the controller 31 calculates such that the pressure is higher than the pressure by a predetermined value. The discharge pressure of the regular sealing oil pump 6 and the emergency sealing oil pump 8 is controlled by adjusting the opening of the feed control valve to 29. Further, as in the first embodiment described above, the pressure downstream of the differential pressure regulating valve 10 is detected by the pressure switch 25, and when the preset pressure is reached, the regular sealing oil pump 6 and the emergency sealing are provided via the relay circuit 26. A signal for operating the oil pump 8 in parallel is sent.

FIG. 4 is a system diagram showing the essential parts of another embodiment (hereinafter, referred to as a third embodiment) of the present invention. In the third embodiment, pressure adjusting valves 32 and 33 equipped with a DC motor are used in place of the pressure adjusting valves 28 and 29 for manually adjusting in the above-described second embodiment, and the pressure downstream of the differential pressure adjusting valve 10 is adjusted. When the pressure detected by the pressure switch 25 reaches a preset pressure, the regular sealed oil pump 6 and the emergency sealed oil pump 8 are operated in parallel via the relay circuit 26, and at the same time, the pressure regulating valve is operated.
It is configured such that electric power is supplied to the DC motors 32 and 33 for a predetermined time and the set values of the pressure adjusting valves 32 and 33 are adjusted to a predetermined pressure.

FIG. 5 is a system diagram showing still another embodiment of the present invention (hereinafter referred to as the fourth embodiment). Figure 5
In the figure, 19 is a vacuum pump for discharging gas and moisture contained in the oil in the vacuum oil tank 4, and 35 is a vacuum oil tank return pipe. Reference numeral 36 is an ejector provided in the oil of the vacuum oil tank 4, which sucks the oil in the vacuum oil tank 4 by the ejector effect and discharges it from the spray nozzle 37 by the sealing oil flowing in the vacuum oil tank return pipe 35. is there. The emergency sealing oil pump system is not shown.

In such a configuration, during normal operation of the rotating electric machine, the oil in the vacuum oil tank 4 is sent to the sealing oil supply circuit by the regular sealing oil pump 6, and the differential pressure regulating valve 10 is used to supply hydrogen gas in the machine of the rotating electric machine 1. Predetermined value from pressure (usually about 0.5 kg
/ Cm ² ) It is adjusted to a high pressure and is supplied as sealing oil to the shaft seal portion 2 of the rotary electric machine 1 via the oil supply pipe 3. The oil film formed by the seal ring portion of the in-machine penetration portion cuts off hydrogen gas inside the machine of the rotary electric machine 1 from outside air, and prevents hydrogen gas from leaking out of the machine.

The sealing oil supplied to the shaft seal portion 2 is returned to the oil tank of the bearing oil supply device (not shown) via the bearing return pipe 11. In addition, the vacuum oil tank 4 has a float valve 5
By constantly maintaining a predetermined oil level in the bearing oil supply pipe 16 the amount of the bearing lubricating oil supplied to the shaft seal portion 2 is the same.
It is supplied from the bearing oiling device via. At all times, the circulation of the sealing oil supply system as described above is repeated.

On the other hand, in the shaft seal portion 2, since the sealing oil and the in-machine hydrogen gas of the rotary electric machine 1 are in direct contact with each other, the sealing oil supplied to the shaft sealing portion 2 may be affected by moisture or atmospheric gas contained in the sealing oil. The purity of the hydrogen gas in the aircraft is reduced. Therefore, in order to prevent the operation performance of the rotating electric machine from being hindered, the sealing oil is previously deaerated and dehydrated in the vacuum oil tank 4.

That is, a part of the discharge oil amount of the regular sealing oil pump 6 is returned to the vacuum oil tank 4 by the vacuum oil tank return pipe 35 via the hydraulic pressure adjusting valve 10 and sent to the ejector 36 in the vacuum oil tank 4. When the return oil passes through the ejector 36 as a high-speed flow, the oil in the vacuum oil tank 4 on the outer periphery of the ejector 36 is sucked and mixed to increase the amount of oil, and the oil is discharged from the spray nozzle 37 into the vacuum oil tank 4. It Atmospheric gas and water mixed in the oil are separated here and discharged to the outside by the vacuum pump 19. As described above, the oil in the vacuum oil tank 4 is repeatedly recirculated to maintain a sufficient deaerated and dehydrated state.

Therefore, the fifth structure constructed as described above
According to the embodiment, the oil in the vacuum oil tank 4 much larger than the amount of oil returned to the vacuum oil tank 4 from the discharge line of the regular sealed oil pump 6 can be sent to the spray nozzle 37 to be deaerated and dehydrated, The miniaturization of the regular sealing oil pump 6 can be realized.

FIG. 6 is a system diagram showing still another embodiment of the present invention (hereinafter referred to as the fifth embodiment). In the fifth embodiment, a vacuum oil tank return pipe 39 communicating with the vacuum oil tank return pipe 35 from the outlet side of the hydraulic pressure adjusting valve 7 to the vacuum oil tank 4 via the second hydraulic pressure adjusting valve 38 is provided as shown in FIG. The configuration is different from that of the fourth embodiment described above.

The fifth embodiment is constructed so that even if the amount of sealing oil supplied to the shaft seal portion 2 of the rotary electric machine 1 fluctuates, efficient deaeration and dehydration of the sealing oil can be maintained. is there.

During normal operation and stoppage of the rotary electric machine 1, the amount of sealing oil varies due to changes in the behavior of the seal ring that forms an oil film in the shaft seal portion 2 of the rotary electric machine 1. Therefore, the amount of return oil from the discharge side of the regular sealing oil pump 6 in the vacuum oil tank return pipe 35 to the vacuum oil tank 4 varies. Therefore, the secondary pressure of the hydraulic pressure adjustment valve 7 changes. That is, since the inlet pressure of the ejector 36 fluctuates, the vacuum oil tank 4 in the ejector 36 changes.
The suction performance of the oil inside varies. In particular, when the amount of fluctuation in the amount of sealing oil is large, the effect of deaerating and dehydrating the sealing oil in the vacuum oil tank 4 is greatly reduced.

Therefore, in the fifth embodiment, the second hydraulic pressure adjusting valve 38 is used.
The pressure in the vacuum oil tank return pipe 35, that is, the ejector
By constantly maintaining the inlet pressure of 36 at a predetermined value, the performance of the ejector 36 can be maintained in an optimum state.

FIG. 7 is a system diagram showing still another embodiment of the present invention (hereinafter referred to as a sixth embodiment). In the sixth embodiment, as shown in the figure, the ejector 40 is arranged outside the vacuum oil tank 4, and the suction pipe 41 sucks the oil in the vacuum oil tank 4 to the ejector 40.

FIG. 8 is a system diagram of still another embodiment of the present invention (hereinafter referred to as the seventh embodiment). This 7th
In the embodiment, as shown in the figure, a vacuum oil tank return pipe is provided to the ejector 36 from the discharge side of the regular sealed oil pump 6 through the throttle mechanism 42.
It is configured to supply the amount of return oil by 35.
As a result, the recirculation oil amount supplied to the ejector 36 can be arbitrarily adjusted by the throttle mechanism 42.

The inlet pressure of the ejector 36 is the same as the discharge pressure of the regular sealing oil pump 6 and is kept at a predetermined value by the hydraulic pressure adjusting valve 7. Therefore, even if the amount of sealing oil varies depending on the operating conditions of the rotating electric machine, the amount of oil supplied to the ejector 36 can be maintained at a predetermined value, and optimal operation of the ejector 36 can be achieved.

[0038]

As described above, according to the present invention, the discharge pressures of the regular sealing oil pump and the emergency sealing oil pump are changed by changing the set pressure of the pressure adjusting valve, and the differential pressure adjusting valve downstream of the differential pressure adjusting valve is changed. By detecting the sealing oil pressure and operating the regular sealing oil pump and the emergency sealing oil pump in parallel, not only a serious accident such as an extremely rare power transmission system, but also the shaft seal part is significantly damaged and the seal is kept above a predetermined level. Even if the amount of oil is required, it is possible to reliably and stably supply the sealing oil, and to cope with the current pump capacity without upsizing the emergency power supply equipment for a serious accident. Therefore, it is possible to provide a sealing oil supply device for a rotary electric machine that is extremely economical and has improved reliability.

Further, according to the present invention, since the ejector is provided in the return line of the regular sealed oil pump, the recirculated oil for deaeration and dehydration processing for returning from the discharge side of the regular sealed oil pump to the vacuum oil tank. The amount is enough to be 1/2 to 1/3 of the conventional one, and even in a large-capacity rotating electric machine, it is not necessary to install a recirculation pump or increase the capacity of the regular sealing oil pump, and the operating cost is reduced by reducing the amount of electric power. Further, it is possible to make the apparatus compact, and further, it is possible to provide a sealing oil supply device for a rotary electric machine, which improves reliability by reducing dynamic equipment.

[Brief description of drawings]

FIG. 1 is a system diagram showing an embodiment of the present invention.

FIG. 2 is a diagram showing the relationship among the number of operating sealed oil pumps, pressure, and flow rate related to the present invention.

FIG. 3 is a system diagram showing a main part of another embodiment (second embodiment) of the present invention.

FIG. 4 is a system diagram showing a main part of still another embodiment (third embodiment) of the invention.

FIG. 5 is a system diagram showing a main part of still another embodiment (fourth embodiment) of the present invention.

FIG. 6 is a system diagram showing a main part of still another embodiment (fifth embodiment) of the present invention.

FIG. 7 is a system diagram showing a main part of still another embodiment (sixth embodiment) of the present invention.

FIG. 8 is a system diagram showing a main part of still another embodiment (seventh embodiment) of the present invention.

FIG. 9 is a system diagram showing a conventional sealing oil supply device for a rotary electric machine.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Rotating electric machine, 2 ... Shaft seal part, 3 ... Supply oil pipe, 4 ... Vacuum oil tank, 5 ... Float valve, 6 ... Regular sealed oil pump,
9 ... Pressure adjusting valve, 8 ... Emergency sealing oil pump, 10 ... Differential pressure adjusting valve, 11, 35 ... Return pipe, 12 ... Bearing oiling device, 13 ... Oil tank,
16 ... Branch pipe, 19 ... Vacuum pump, 20, 22 ... Second pressure adjusting valve, 21, 23 ... Shutoff valve, 24 ... Pressure guiding pipe, 25 ... Pressure switch,
26 ... Relay circuit, 28,29 ... Pressure control valve, 31 ... Controller, 3
2, 33 ... Electric pressure control valve, 36, 40 ... Ejector, 38 ... Second hydraulic pressure control valve, 42 ... Throttling mechanism.

 ─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor Junji Nomoto 1-1-1, Shibaura, Minato-ku, Tokyo Inside Toshiba Head Office

Claims (2)

[Claims] 1. A vacuum oil tank for supplying degassed and dehydrated sealing oil to a shaft seal portion of a rotary electric machine having a cooling gas sealed therein, a regular sealing oil pump and an emergency sealing oil pump, and a first pressure. In a sealing oil supply device for a rotary electric machine comprising a regulating valve and a differential pressure regulating valve, a bypass pipe line is provided in a feedback loop on the discharge side of the first pressure regulating valve, and the first pressure regulating line is provided in the bypass pipe line. A second pressure adjusting valve having a different set pressure from the valve, and a shutoff valve for shutting off the discharge side of the first pressure adjusting valve according to the sealing oil pressure downstream of the differential pressure adjusting valve, and the differential pressure adjusting A seal oil supply device for a rotary electric machine, comprising a pressure detector for detecting a seal oil pressure downstream of a valve and transmitting a signal for operating the regular seal oil pump and the emergency seal oil pump in parallel. 2. A vacuum oil tank for supplying degassed and dehydrated sealing oil to a shaft seal portion of a rotary electric machine having a cooling gas sealed therein, a regular sealing oil pump and an emergency sealing oil pump, a pressure adjusting valve, In a sealed oil supply device for a rotary electric machine equipped with a differential pressure adjustment valve, an ejector for sucking the sealed oil in the vacuum oil tank is provided in a return loop on the discharge side of the pressure adjustment valve. Oil supply device.