JP2005238114A - Bearing structure of slag crusher - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing structure of a slag crusher which minimizes variation in the gap between a seal housing and a roll shaft, lessens the number of components, facilitates checking, and improves the sealing performances by integrating a seal and a bearing into a unit structure. <P>SOLUTION: The bearing structure of the slag crusher which possesses an upper-part pressure vessel and a small-diameter lower-part pressure vessel fixed to a slag discharge opening of a coal gasifying furnace, a roll type crusher crushing slag disposed in the lower-part pressure vessel, and a roll shaft of the roll type crusher penetrating the lower-part pressure vessel is provided with a bearing installed at a penetrating part, of the roll shaft, in the lower-part pressure vessel, an inner side bearing cover installed, to the bearing, at the inner side of lower-part pressure vessel an outer-side bearing cover installed at the outside of the bearing, a vessel-side high-pressure seal installed between the inner-side bearing cover and the roll shaft, and a non-high-pressure seal installed between the outer side bearing cover and the roll shaft. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a high differential pressure shaft seal structure of a slag crusher of a coal gasifier that crushes slag of a coal gasifier.

  Conventionally, what is shown in FIG. 9 is proposed as a slag discharge device. (For example, patent document 1). In the conventional slag discharge device 1, the bottomed cylindrical pressure vessel 2 which is disposed at the bottom of the coal gasification furnace (not shown) and is the casing has a diameter of the upper pressure vessel 3 and the lower pressure vessel 4. Is different. An upper slag hopper 5 having an open bottom is disposed in the upper pressure vessel 3 having a large diameter, and the bottom opening 6 is disposed at an upper end portion of the lower pressure vessel 4 having a small diameter.

  A roll crusher 8 is disposed below the upper slag hopper 5, and the roll crusher 8 has a cylindrical rotating tooth 9 disposed below the bottom opening 6 of the upper slag hopper 5. The rotating teeth 9 are fixed to a roll shaft 66 that passes through the wall of the lower pressure vessel 4 and is disposed in the horizontal direction. A fixed tooth 10 is arranged from the side to the bottom of the rotating tooth 9 so as to face it. A seal portion 65 is provided at a portion where the roll shaft 66 penetrates the wall portion of the lower pressure vessel 4.

  A bearing mounting base 68 and an electric motor mounting base 69 are fixed to the outer wall portion of the lower pressure vessel 4, and a bearing 67 that supports the roll shaft 66 is provided on the base. Furthermore, an electric motor 14 for rotating the roll shaft 66 is disposed at one end of the roll shaft 66. A lower slag hopper 7 is disposed inside the lower pressure vessel 4, and a pipe connection port 17 is provided at the bottom opening 16.

  In the conventional slag discharging apparatus, in order to adjust the seal portion 65, it is necessary to secure a certain space for seal replacement between the seal portion 65 and the bearing 67. On the other hand, a very large radial bending stress is applied to the roll shaft 66 when the lump of slag is crushed, causing the roll shaft 66 to bend. Therefore, the structure of the seal portion 65 has a problem that it is necessary to endure this deflection and seal the leakage of the fluid in the pressure vessel.

  As a seal structure that can withstand this deflection, the structure shown in FIG. 10 has also been proposed. (For example, patent document 2). The high differential pressure shaft seal structure of the conventional slag crusher shown in FIG. 10 is composed of gland packings 74a, 74b, 74c, 74d arranged in multiple stages (four stages) around the rotating shaft 66 and the like, and U-shaped packing. An inner peripheral side seal structure composed of 71C and an outer peripheral side seal structure composed of two U-shaped packings 71a and 71b are provided. The U-shaped packing is disposed in a circumferential groove provided in the lower pressure vessel 4 in order to stabilize its position. A cylindrical concave portion for sealing is provided in a part of the lower pressure vessel 4 through which the roll shaft 66 of the roll crusher passes, and a sealing member is disposed here. The four ground packings 74 a, 74 b, 74 c, and 74 d are in sliding contact with the rotating shaft 66, and two are provided before and after the lantern ring 73.

  A U-packing ring is in close contact with the outermost ground packing 74d. A U-shaped packing 71 c is built in the circumferential groove of the U-shaped packing ring, and the U-shaped packing 71 c is in sliding contact with the roll shaft 66. The U-shaped packing ring is in close contact with the packing press 75 on the outside of the machine, and the packing press 75 is pressed to the inside of the machine by screwing the tip of the packing pressurizing screw 77 into the packing casing 72. The spring 76 is interposed between the packing pressurizing screw 77 and the packing presser 75 by its elastic force, and biases the packing presser 75 toward the inside of the machine to prevent the ground packing 74a and the like from coming off.

  The packing casing 72 is held by the lower pressure vessel 4 with screws through an O-ring and a pressing member. U-shaped packings 71a and 71b are disposed in a circumferential groove further provided in the cylindrical concave portion of the lower pressure vessel 4, and these are in contact with the outer periphery of the cylindrical packing casing 72. Forming a structure. In addition, cleaning grease or water is sent to the U-shaped packing 71c to the 71a to remove dust adhering to the U-shaped packing 71c, 71a, or a differential pressure applied to the packing in one stage (pressure difference between the inner side and the outer side). The reduction is made. In this way, a double seal structure including a seal on the inner peripheral side of a high differential pressure resistance and a seal on the outer peripheral side with good followability is provided, and while the movement of the rotary shaft 66 is suppressed, the U-shaped packing itself follows. The ability to follow the shaft center is satisfied by the nature. However, in the thing of the above-mentioned patent document 2, since the seal structure is complicated and the quantity of packing is large, in order to operate for a long time, periodic inspection and replacement of packing are necessary. There's a problem.

JP-A-11-140465 JP 2000-104835 A

  The present invention has been proposed in view of the above-described conventional circumstances. By integrating the seal and the bearing, the deflection of the roll shaft is minimized, the number of parts is reduced, and the sealing performance is improved. Another object is to provide a bearing structure for a slag crusher.

  The present invention has been made in order to solve the above-described conventional problems, and each of the inventions described in the claims is described as the following (1) to (7) as a bearing structure of a slag crusher. Means.

  (1) The bearing structure of the slag crusher according to the first means includes an upper pressure vessel fixed to the slag discharge port of the coal gasification furnace, and a lower diameter than the upper pressure vessel fixed to the lower portion of the upper pressure vessel. In the bearing structure of the slag crusher, the lower pressure vessel, a roll crusher disposed in the lower pressure vessel and crushing the slag, and a roll shaft of the roll crusher penetrating the lower pressure vessel, A bearing provided in a penetrating portion of the lower pressure vessel of the roll shaft; an inner bearing cover provided inside the lower pressure vessel of the bearing; an outer bearing cover provided outside the bearing; and the inner bearing cover And a container side high pressure seal provided between the roll shaft and a non-high pressure seal provided between the outer bearing cover and the roll shaft.

  (2) The second means is an outer high pressure seal provided on the bearing side from the non-high pressure seal between the outer bearing cover and the roll shaft in the bearing structure of the slag crusher of the first means. And a lubricating oil supply line for supplying high-pressure lubricating oil to the bearing and a lubricating oil pump.

  (3) The third means is an outer high pressure seal provided on the bearing side from the non-high pressure seal between the outer bearing cover and the roll shaft in the bearing structure of the slag crusher of the first means. The bearing includes a lubricating oil supply line for circulating high-pressure lubricating oil, a lubricating oil return line, and a lubricating oil pump.

  (4) The fourth means is a shaft side high pressure provided on the bearing side from the container side high pressure seal between the inner bearing cover and the roll shaft in the bearing structure of the slag crusher of the first means. A clean water supply line for supplying high-pressure clean water and a hydraulic pump are provided between the seal, the container-side high-pressure seal, and the shaft-side high-pressure seal.

  (5) The fifth means is a shaft side high pressure provided on the bearing side from the container side high pressure seal between the inner bearing cover and the roll shaft in the bearing structure of the slag crusher of the first means. A clean water supply line for circulating high-pressure clean water, a clean water return line, and a hydraulic pump are provided between the seal, the container-side high-pressure seal, and the shaft-side high-pressure seal.

  (6) A sixth means is a shaft side high pressure provided on the bearing side from the container side high pressure seal between the inner bearing cover and the roll shaft in the bearing structure of the slag crusher of the third means. A clean water supply line for circulating high-pressure clean water, a clean water return line, and a hydraulic pump are provided between the seal, the container-side high-pressure seal, and the shaft-side high-pressure seal.

  (7) The seventh means is a bearing structure of the slag crusher of the sixth means, wherein the pressure in the seal chamber is made higher than the pressure in the lower pressure vessel or the upper pressure vessel, and the clean water supply pipe Control means for controlling the pressure in the lubricating oil supply pipe to be higher than the pressure in the path is provided.

Since the invention according to each claim described in the claims employs the means described in the above (1) to (7), it has the following effects.
(1) Since the invention according to claim 1 employs the first means, the distance between the bearing and the container-side high-pressure seal can be kept to a minimum, and the shaft deflection of the seal portion is minimized. Can be limited.

  (2) Since the invention according to claim 2 employs the second means, in addition to the effect of (1), the contaminated slag hopper water in the high-pressure vessel is prevented from entering the bearing. can do.

  (3) Since the invention according to claim 3 employs the third means, in addition to the effect of (1), the contaminated slag hopper water in the high-pressure vessel is prevented from entering the bearing. In addition, more deteriorated lubricating oil such as heat can be returned to the tank.

  (4) Since the invention according to claim 4 employs the fourth means, in addition to the effect of (1), high-pressure clean water is supplied between the container-side high-pressure seal and the shaft-side high-pressure seal. As a result, the contaminated slag hopper water in the high-pressure vessel can be prevented from entering the seal sliding surface, and even if high-pressure clean water leaks into the high-pressure vessel, a problem occurs. do not do.

  (5) Since the invention according to claim 5 employs the fifth means, in addition to the effect of (1), high-pressure clean water is provided between the container-side high-pressure seal and the shaft-side high-pressure seal. Since it was made to circulate, the contaminated slag hopper water in the high-pressure vessel can be prevented from entering the bearing, and the bearing and the seal can be cooled. There is no problem even if it leaks into

  (6) Since the invention according to claim 6 employs the sixth means, in addition to the effect of (3) above, between the container side high pressure seal and the shaft side high pressure seal, on the inner side of the bearing. Since the high-pressure clean water is circulated, it is possible to prevent the lubricating oil from leaking into the high-pressure vessel and to cool the bearing, for example, the high-pressure clean water leaks into the high-pressure vessel. However, no problem occurs.

  (7) Since the invention according to claim 7 employs the seventh means, in addition to the effect of the above (6), the inside of the clean water supply line is more than the pressure in the lower pressure vessel or the upper pressure vessel. Therefore, dirty high-temperature and high-pressure water in the pressure vessel does not enter the seal and the bearing. Further, since the pressure in the lubricating oil supply pipe is controlled to be higher than the pressure in the clean water supply pipe, dirt in the pressure vessel does not leak into the bearing or the clean water supply pipe.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view showing the overall structure of a slag crusher according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the bearing structure with a seal of the slag crusher according to the first embodiment of the present invention. FIG. 3 is a cross-sectional view of a bearing structure with a seal for a slag crusher according to a second embodiment of the present invention, and FIG. FIG. 5 is a cross-sectional view of a bearing structure with a seal of a slag crusher according to Embodiment 3 of the present invention, FIG. 6 is a cross-sectional view of a bearing structure with a seal of a slag crusher according to Embodiment 4 of the present invention, and FIG. FIG. 6 is a sectional view of a bearing structure with a seal for a slag crusher according to a fifth embodiment of the present invention. FIG. 8 is a circuit diagram of a control device according to the slag discharge device according to Embodiment 6 of the present invention.

  First, the overall structure of the slag crusher according to the embodiment of the present invention will be described with reference to FIG. In a coal gasifier, coal is burned in a high-temperature, high-pressure atmosphere to generate combustible gas. At that time, the slag in the coal melts and falls to the slag discharge device 1 disposed at the bottom of the coal gasification furnace.

  Since the slag discharge device 1 is connected to the coal gas furnace, the pressure vessel 2 is pressurized with the same pressure of about 3 MPs as in the coal gasification furnace. The pressure vessel 2 is filled with high-temperature and high-pressure slag hopper water 15. The molten slag dropped from the coal gasification furnace into the pressure vessel 2 is cooled by the slag hopper water 15 in the pressure vessel 2 and solidified into large lumps, and the slag hopper water 15 is heated to about 80 ° C.

  The pressure vessel 2 includes a large-diameter cylindrical upper pressure vessel 3 that can withstand the above-described high temperature and high pressure, and a small-diameter cylindrical lower pressure vessel 4 connected to the lower portion of the upper pressure vessel 3. An upper slag hopper 5 having a bottom opening 6 at the bottom is disposed below the large-diameter upper pressure vessel 3 in order to collect the solidified slag at the center lower portion.

  A roll crusher 8 is disposed in the lower pressure vessel 4 below the bottom opening 6 of the upper slag hopper 5. The lower pressure vessel 4 is smaller in diameter than the upper pressure vessel 3 and limited to a width that can accommodate the roll crusher 8 in order to shorten the distance between the bearings of the roll crusher 8 as much as possible.

  The roll crusher 8 includes rotating rotating teeth 9 and fixed teeth 10 fixed to the lower pressure vessel 4.

  The rotating teeth 9 are fixed to a roll shaft 11 that penetrates the wall of the lower pressure vessel 4 and is disposed in the horizontal direction. A bearing 13 with a seal is provided at each site where the roll shaft 11 penetrates the wall of the lower pressure vessel 4. The sealed bearing 13 can withstand the above-described high pressure and high temperature. A cylindrical mounting base 12 is fixed to the outer wall portion of the lower pressure vessel 4, and an electric motor 14 for rotating the roll shaft 11 is disposed at the outer center of the mounting base 12.

  In the above-described configuration, the solidified slag collected by the upper slag hopper 5 is pulverized by the rotating rotating teeth 9 and the fixed teeth 10. At this time, a large bending stress is generated in the rotating tooth 9 in the radial direction. This large bending stress hardly poses a problem because the diameter of the rotating tooth 9 is large. However, the influence on the roll shaft 11 cannot be ignored. The longer the distance from the rotating tooth 9 end of the roll shaft 11 to the bearing 13 with seal, the greater the influence. In the present embodiment, the distance is minimized by integrating the bearing and the seal.

  A lower slag hopper 7 having a bottom opening 16 at the bottom is disposed below the lower pressure vessel 4 in order to collect the crushed slag at the center lower portion. The crushed slag collected by the lower slag hopper 7 passes through the pipe connection port 17 at the lower end of the lower pressure vessel 4 and is discharged to the outside.

  Next, based on FIG. 2, the specific structure of the bearing with a seal in the slag crusher which concerns on Example 1 of this invention is demonstrated. A circular hole is formed in the side wall of the lower pressure vessel 4, and the bearing box 20 is attached to the hole with a number of mounting bolts 28 a with gaskets (not shown) interposed therebetween. In addition, the diameter of the circular hole opened in the side wall is larger than the diameter of the rotating tooth 9 so that the rotating tooth 9 can be inspected and replaced.

  The roll shaft 11 passes through the central opening of the bearing housing 20. The diameter of the roll shaft 11 decreases in three stages: a large diameter, a medium diameter, and a small diameter as it goes outward. Between the bearing housing 20 and the middle diameter portion of the roll shaft 11, there is a self-aligning roller bearing 29 composed of a ring-shaped bearing outer ring 23, a large number of self-aligning rollers 25 and a ring-shaped bearing inner ring 24. Has been inserted.

  An inner bearing cover (seal housing) 21 is provided inside the lower pressure vessel 4 of the self-aligning roller bearing 29. The inner bearing cover 21 is attached to the bearing housing 20 by a number of mounting bolts 28c with a gasket (not shown) interposed therebetween. The large-diameter portion of the roll shaft 11 passes through the center hole of the inner bearing cover 21. A container-side high pressure seal 26a having a pressure resistance of 3.5 MPa or more is disposed between the inner bearing cover 21 and the roll shaft 11, and the high-temperature and high-pressure slag hopper water 15 in the lower pressure container 4 is automatically adjusted. It is sealed so as not to enter the core roller bearing 29.

  On the other hand, an outer bearing cover 22 (seal housing) is provided outside the lower pressure vessel 4 of the self-aligning roller bearing 29. The outer bearing cover 22 is attached to the bearing housing 20 by a number of mounting bolts 28b with a gasket (not shown) interposed therebetween. A small diameter portion of the roll shaft 11 passes through the center hole of the inner bearing cover 21. A ring-shaped non-high pressure seal 27 having a pressure resistance of 1 MPa or less is disposed between the inner bearing cover 21 and the roll shaft 11, and is sealed so that the lubricating oil in the bearing device does not leak to the outside. ing. The non-high pressure seal 27 is sealed by the seal pressing plate 39 and the mounting bolt 40 so as not to drop off.

  The self-aligning roller bearing 29 and the inner and outer cavities A and B are filled with lubricating oil.

  The distance L2 between the center of the self-aligning roller bearing 29 and the rotating tooth 9 is shortened to such an extent that the inner wall of the lower pressure vessel 4 having a circular cross section and the rotating tooth 9 do not contact each other. The distance L1 between the center of the self-aligning roller bearing 29 and the container-side high-pressure seal 26a is also shortened to such an extent that the roll shaft 11 can be shaken by bending in the radial direction.

  The bearing device with a seal according to the first embodiment is configured as described above, and a large bending stress is generated in the radial direction on the roll shaft 11 of the rotating tooth 9 that rotates while pulverizing the slag. The bending stress is supported by a self-aligning roller bearing 29 provided on the side wall of the lower pressure vessel 4. At this time, the distance L2 between the end of the rotating tooth 9 and the center of the self-aligning roller bearing 29 is much shorter than the conventional one. Therefore, the distance L1 between the center of the self-aligning roller bearing 29 and the container side high pressure seal 26a is also shortened, and the radial deflection of the roll shaft 11 at the position of the container side high pressure seal 26a is also very small. The shape of the container-side high-pressure seal 26a can be as simple as providing a tightening rubber on the outer peripheral surface of the seal ring.

  Next, based on FIG. 3, the specific structure of the bearing with a seal in the slag crusher which concerns on Example 2 of this invention is demonstrated. In FIG. 3, the same components as those in FIGS. 1 and 2 are denoted by the same reference numerals. Therefore, points different from FIGS. 1 and 2 will be mainly described. The bearing with a seal according to the second embodiment of the present invention is configured to pressurize and supply lubricating oil to the self-aligning roller bearing 29 in the first embodiment.

  As shown in FIG. 3, a lubricating oil supply passage 33 for supplying lubricating oil to the self-aligning roller bearing 29 is formed in the upper part of the bearing box 20a and the outer bearing cover (seal housing) 22a. Further, an outer high pressure seal 26b having a pressure resistance of 3.5 MPa or more is disposed between the inner side of the outer bearing cover 22a and the roll shaft 11. A cavity C is formed between the non-high pressure seal 27 and the outer high pressure seal 26b, and a lubricant recovery passage 31 connected to the cavity C is formed below the outer bearing cover 22a. A lubricating oil recovery pipe 32 is connected to the lubricating oil recovery passage 31, and the lubricating oil recovery pipe 32 is connected to a lubricating oil tank 38.

  The lubricating oil supply passage 33 is connected to a lubricating oil supply pipe 34 having a lubricating oil filter 35 interposed therebetween. The lubricating oil supply pipe 34 is connected to a discharge port of a lubricating oil pump 36 driven by an electric motor or the like. It is connected. The suction port of the lubricating oil pump 36 is connected to a lubricating oil tank 38. Further, a pressure adjusting valve 37 is connected between the outlet of the lubricating oil pump 36 of the lubricating oil supply pipe 34 and the lubricating oil filter 35, and the supply pressure of the lubricating oil to the self-aligning roller bearing 29 can be adjusted. I am doing so. Note that the lubricating oil pressure in the self-aligning roller bearing 29 is set to a pressure of 3.5 MPa which is the same as or slightly higher than the pressure of the slag hopper water 15 by the pressure adjusting valve 37. The lubricating oil in the self-aligning roller bearing 29 passes through the outer high pressure seal 26b, the cavity C, the lubricating oil recovery passage 31, and the lubricating oil recovery pipe 32, and returns to the lubricating oil tank 38.

  With the above-described configuration, the risk that the slag hopper water 15 enters the self-aligning roller bearing 29 by making the oil pressure in the self-aligning roller bearing 29 equal to or slightly higher than the pressure of the slag hopper water 15. And the reliability is improved.

  As shown in FIG. 4, the supply pressure of the lubricating oil is changed in accordance with the pressure of the slag hopper water 15, thereby minimizing the leakage of the lubricating oil from the container side high pressure seal 26a into the pressure vessel 2. be able to. That is, as shown in FIG. 4, a remote on-off valve 47 is connected between the discharge port of the lubricating oil pump 36 of the lubricating oil supply pipe 34 and the lubricating oil filter 35 instead of the pressure regulating valve 37 of FIG.

  Then, a lubricating oil pressure transmitter 41 for detecting pressure is attached to the lubricating oil supply pipe 34. Furthermore, a pressure vessel pressure transmitter 42 for detecting the pressure in the pressure vessel 2 is attached to the pressure vessel 2. Detection signals from the pressure transmitters 41 and 42 are input to a comparator 44 in the control device 43. The pressure difference calculated by the comparator 44 is compared with a preset reference (allowable) pressure difference by the comparison calculator 45. Then, the valve controller 46 controls the opening degree of the remote on-off valve 47 so that the pressure difference calculated by the comparison calculator 45 becomes zero.

  Next, based on FIG. 5, the specific structure of the bearing with a seal in the slag crusher which concerns on Example 3 of this invention is demonstrated. In Example 3 of the present invention, lubricating oil and clean water are supplied under pressure. In FIG. 5, the same components as those in FIGS. 1 to 3 are denoted by the same reference numerals. Therefore, differences from FIGS. 1 to 3 will be mainly described.

  In the bearing structure with a seal according to the third embodiment, the self-aligning roller bearing 29 is moved by the lubricating oil pump 36 through the lubricating oil supply pipe 34 and the lubricating oil supply passage 33 as in the second embodiment (FIG. 3). Lubricating oil is supplied under pressure. Further, in Example 3, clean water is also pressurized.

As shown in FIG. 5, between the inner bearing cover (seal housing) 21a and the roll shaft 11, two sets of a container side high pressure seal 26a and a bearing side high pressure seal 26c having a pressure resistance of 1 MPa or more are arranged. .
A cavity D is formed between the two sets of the container-side high-pressure seal 26a and the bearing-side high-pressure seal 26c.

  A clean water supply passage 51 is formed in the upper part of the bearing box 20b and the outer bearing cover (seal housing) 22b, and the clean water supply path 51 and the cavity of the bearing box 20b are formed in the upper part of the inner bearing cover 21a. A clean water supply passage 50 communicating with D is formed. The clean water supply passage 51 and the lubricating oil supply passage 33 are formed in the circumferential direction so as not to interfere with each other in the bearing box 20b and the outer bearing cover 22b.

  A clean water supply pipe 52 provided with a supply water filter 53 is connected to the clean water supply passage 51 of the bearing box 20b. The clean water supply pipe 52 is a discharge port of a hydraulic pump 54 driven by an electric motor or the like. It is connected to the. The suction port of the water pressure pump 54 is connected to a clean water tank 56.

  Further, a water pressure adjusting valve 55 is connected between the discharge port of the water pressure pump 54 of the clean water supply pipe 52 and the water supply filter 53, and the container side high pressure seal 26a and the bearing side high pressure seal 26c in the inner bearing cover 21a. The supply pressure of clean water to the cavity D between the two can be adjusted. The water pressure in the cavity D is slightly higher than the pressure of the slag hopper water 15 (about 3 MPa) by the water pressure adjusting valve 55, and the lubricating oil pressure in the self-aligning roller bearing 29 and the cavity A (for example, 4 MPa) or slightly lower pressure (for example, 3.5 MPa). The clean water in the cavity D slightly leaks from the container-side high-pressure seal 26a into the lower pressure vessel 4, but there is no problem because the lower pressure vessel 4 is originally filled with the slag hopper water 15.

  The slag hopper water 15 is contaminated with a large amount of dust generated by the roll crusher 8 and has a high acidity. In the third embodiment, the water pressure (for example, 3.5 MPa) in the cavity D between the container side high pressure seal 26 a and the bearing side high pressure seal 26 c is slightly higher than the water pressure (about 3 MPa) of the slag hopper water 15. By the slightly leaking clean water, the sliding surface of the container side high pressure seal 26a is kept clean, and the reliability of the seal is improved. Furthermore, the water pressure (about 3.5 MPa) in the cavity portion D is made the same as or slightly lower than the pressure (about 4 MPa) in the self-aligning roller bearing 29 and the cavity portion A, so There is no risk of clean water entering and bearing reliability increases.

  Note that the pressure of the water pressure adjusting valve 55 can be controlled by a control device similar to that shown in FIG.

  Next, based on FIG. 6, the specific structure of the bearing with a seal in the slag crusher which concerns on Example 4 of this invention is demonstrated. In FIG. 6, the same components as those in FIGS. 1 to 3 are denoted by the same reference numerals. Therefore, differences from FIGS. 1 to 3 will be mainly described.

  In the bearing structure with a seal according to the fourth embodiment, the lubricating oil is pressurized and circulated to the self-aligning roller bearing 29 with respect to the second embodiment (FIG. 3). As shown in FIG. 6, in the fourth embodiment, as in the second embodiment (FIG. 3), a lubricating oil supply passage 33 is formed in the upper part of the bearing box 20c and the outer bearing cover (seal housing) 22c. Yes. Further, a lubricating oil return passage 57 for returning the lubricating oil from the self-aligning roller bearing 29 is also formed below the bearing box 20c and the outer bearing cover 22c.

  A lubricating oil return pipe 58 is connected to the lubricating oil return passage 57, and the lubricating oil return pipe 58 is connected to the lubricating oil tank 38. Then, the pressure adjustment valve 37 shown in FIG. 3 is stopped, and a pressure adjustment valve 59 is provided in the lubricating oil return pipe 58 instead. The pressure of the lubricating oil in the self-aligning roller bearing 29 is made equal to or slightly higher (3.5 MPa) than the pressure (3 MPa) of the slag hopper water 15 by the pressure adjusting valve 59.

  In the fourth embodiment, the self-aligning roller bearing 29 and the lubricating oil are circulated by circulating the lubricating oil even when water leaks to the self-aligning roller bearing 29 or the lubricating oil deteriorates due to heat. The oil can be kept normal. Therefore, a good bearing function can be maintained.

  As with the pressure adjustment valve 59 shown in FIG. 4, a remote opening / closing valve 47 is provided instead of the pressure adjustment valve 59, and a lubricating oil pressure transmitter 41 for detecting pressure is provided in the lubricating oil supply pipe 34. The pressure vessel 2 may be attached to the pressure vessel 2 to detect the pressure in the pressure vessel 2, and the opening degree of the remote control valve may be controlled by the control device 43 based on the detection signals. .

  Next, based on FIG. 7, the specific structure of the bearing with a seal in the slag crusher which concerns on Example 5 of this invention is demonstrated. In Example 5 of the present invention, lubricating oil is supplied and clean water is circulated. In FIG. 7, the same components as those in FIGS. 1 to 5 are denoted by the same reference numerals. Therefore, differences from FIGS. 1 to 5 will be mainly described. In the fifth embodiment, as in the second embodiment (FIG. 3), the lubricating oil is supplied to the self-aligning roller bearing 29 by the lubricating oil pump 36, the lubricating oil filter 35, the lubricating oil supply pipe 34, and the lubricating oil supply passage 33. Is pressurized.

  Further, in the same manner as in the third embodiment (FIG. 5) of the present invention, a clean water supply passage 50, a clean water is provided at the upper part of the inner bearing cover (seal housing) 21b, the bearing box 20d, and the outer bearing cover (seal housing) 22d. A water supply passage 51 is formed. Further, a clean water return passage 61 is also formed under the bearing housing 20d and the outer bearing cover 22d, and the clean water return passage 61 and the cavity of the bearing housing 20a are also formed under the outer bearing cover 22d and the inner bearing cover 21b. A clean water return passage 60 that communicates with the portion D is formed. The clean water supply passage 51 and the lubricating oil supply passage 33 are formed in the circumferential direction so as not to interfere with each other in the bearing box 20d and the outer bearing cover 22d.

  A clean water return pipe 62 is connected to the clean water return passage 61 of the outer bearing cover 22 d, and the clean water return pipe 62 is connected to the clean water tank 56. A pressure adjusting valve 63 is interposed in the clean water return pipe 62.

  In the fifth embodiment, the water pressure (about 3.5 MPa) in the cavity D between the container side high pressure seal 26 a and the bearing side high pressure seal 26 c is slightly higher than the water pressure (about 3 MPa) of the slag hopper water 15. By the slightly leaking clean water, the sliding surface of the container side high pressure seal 26a is kept clean, and the reliability of the seal is improved. In addition, the water pressure in the cavity D (about 3.5 MPa) is made equal to or slightly lower than the pressure in the self-aligning roller bearing 29 and the cavity A (4 MPa), so that the self-aligning roller bearing 29 is cleaned. There is no risk of water ingress, increasing bearing reliability. Further, by circulating clean water, the container-side high-pressure seal 26a and the bearing-side high-pressure seal 26c are cooled, and wear powder and the like at the seal portion are also collected, so that the reliability of the seal is improved.

  The sixth embodiment is a combination of the mechanism for circulating the lubricating oil of the fourth embodiment shown in FIG. 6 and the mechanism for circulating the clean water of the fifth embodiment shown in FIG. In this case, the lubricating oil supply passage 33 and the clean water supply passage 51 in the upper part in the bearing box 20a, and the lubricating oil return path 57 and the clean water return path 61 in the lower part in the bearing box 20a are arranged so as not to interfere with each other. It is shifted in the direction.

  In the sixth embodiment, the water pressure (about 3.5 MPa) in the cavity D between the container side high pressure seal 26a and the bearing side high pressure seal 26c is slightly higher than the water pressure (about 3 MPa) of the slag hopper water 15; By making the pressure in the self-aligning roller bearing 29 and the cavity A (4 MPa) the same or slightly lower, the sliding surface of the container-side high-pressure seal 26 a is cleaned with clean water that slightly leaks into the lower pressure container 4. In addition, the risk of clean water entering the self-aligning roller bearing 29 is eliminated. Since clean water circulates, the container side high pressure seal 26a and the bearing side high pressure seal 26c are cooled.

  Furthermore, by circulating the clean water, the lubricating oil leaked from the self-aligning roller bearing 29 is discharged from the cavity D together with the clean water. It does not leak into the lower pressure vessel 4 and can maintain a good function as a bearing with a seal.

  Next, pressure control according to the sixth embodiment of the present invention will be described with reference to FIG. As shown in FIG. 8, a lubricating oil pressure transmitter 41 that detects the pressure of the circulating lubricating oil is provided in the lubricating oil supply pipe 34 (or the lubricating oil supply path 33, the lubricating oil return path 57, and the lubricating oil return pipe 58). Is installed. A clean water pressure transmitter 48 for detecting the pressure of circulating clean water is attached to the clean water supply pipe 52 (or the clean water supply path 51, the clean water return path 61, and the clean water return pipe 62). Furthermore, a pressure vessel pressure transmitter 42 for detecting the pressure in the pressure vessel 2 is attached to the upper pressure vessel 3 or the lower pressure vessel 4.

  Then, the detection signal from the clean water pressure transmitter 48 and the detection signal from the pressure vessel pressure transmitter 42 are input to the comparator 44b in the control device 43a. The pressure difference calculated by the comparator 44b is compared with a preset reference (allowable) pressure difference (for example, 0.5 MPa) by the comparison calculator 45b. The opening degree of the pressure regulating valve 63 is controlled by the valve controller 46b so that the pressure difference calculated by the comparator 45b becomes zero (clean water pressure = pressure in the pressure vessel + 0.5 MPa). .

  On the other hand, the detection signal from the lubricating oil pressure transmitter 41 and the detection signal from the pressure vessel internal pressure transmitter 42 are input to the comparator 44a in the control device 43a. The pressure difference calculated by the comparator 44a is compared with a preset reference (allowable) pressure difference (for example, 1 MPa) by the comparison calculator 45a. Then, the valve controller 46a controls the opening degree of the pressure adjustment valve 59 so that the pressure difference calculated by the comparison calculator 45a becomes zero (pressure of clean water = pressure in the pressure vessel + 1 MPa).

  As for the pressure control of the lubricating oil, the detection signal from the lubricating oil pressure transmitter 41 and the detection signal from the clean water pressure transmitter 48 are calculated by the comparator 44c, and the calculated pressure difference is compared with the comparison calculator. In 45a, compared with a preset reference (allowable) pressure difference (for example, 0.5 MPa), the pressure difference calculated by the comparison calculator 45b becomes zero (lubricating oil pressure = clean water pressure + 0. 5 MPa), the opening degree of the pressure regulating valve 59 may be controlled by the valve controller 46a.

In addition, the above-mentioned ones are provided with pressure transmitters and controlled based on the signals, but instead of this, a differential pressure transmitter between the pressure in the pressure vessel and the clean water pressure, the clean water pressure and A pressure difference transmitter with the lubricating oil pressure may be provided, and each pressure control valve may be controlled based on the signal. In short, any control device may be used as long as it is controlled so that the pressure in the pressure vessel ≦ the clean water pressure ≦ the pressure in the pressure vessel + the predetermined value, and the clean water pressure ≦ the lubricating oil pressure ≦ the clean water pressure + the predetermined value. That is, the pressure inside the pressure vessel is not limited to 3 MPa, and even if the pressure is 5 MPa, 10 PMa, etc., the washing water pressure or the like may be increased.

As mentioned above, although embodiment of this invention was described, it cannot be overemphasized that this invention is not limited to said embodiment, A various change may be added to the specific structure within the scope of the present invention. .
For example, the positions of the clean water supply passages 50 and 51 and the clean water return passages 60 and 61, the lubricant supply passage 33 and the lubricant return passage 57 may be upside down or formed in the left-right direction. good.

(A) is a schematic longitudinal cross-sectional view of the slag discharge device main body of the coal gasification furnace which concerns on embodiment of this invention. (B) is a figure which shows arrangement | positioning of a rotation tooth and a fixed tooth. It is a detailed sectional view of the bearing with a seal in the slag discharge device concerning Example 1 of the present invention. It is detail sectional drawing of the bearing with a seal in the slag discharge device concerning Example 2 of the present invention. It is a circuit diagram of the control apparatus which concerns on Example 2 of this invention. It is detail sectional drawing of the bearing with a seal in the slag discharge device concerning Example 3 of the present invention. It is detail sectional drawing of the bearing with a seal in the slag discharge device concerning Example 4 of the present invention. It is detail sectional drawing of the bearing with a seal in the slag discharge device concerning Example 5 of the present invention. It is a circuit diagram of the control apparatus which concerns on the slag discharge apparatus which concerns on Example 6 of this invention. It is a schematic longitudinal cross-sectional view of the slag discharge device main body of the conventional coal gasification furnace. It is sectional drawing of the seal structure in the slag discharge device of the conventional coal gasification furnace.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Slag discharge device 2 Pressure vessel 3 Upper pressure vessel 4 Lower pressure vessel 5 Upper slag hopper 6 Bottom opening 7 Lower slag hopper 8 Roll crusher 9 Rotating tooth 10 Fixed tooth 11 Roll shaft 12 Mounting base 13 Bearing with seal 14 Electric motor 15 Slag hopper water 16 Bottom opening 17 Piping connection port 20, 20a, 20b, 20c, 20d Bearing box 21, 21a, 21b Inner bearing cover 22, 22a, 22b, 22c, 22d Outer bearing cover 23 Bearing outer ring 24 Bearing inner ring 25 Self-aligning roller 26a Container Side high pressure seal 26b Outer high pressure seal 26c Bearing side high pressure seal 27 Non-high pressure seal 28a, 28b, 28c, 28d Mounting bolt 29 Self-aligning roller bearing 31 Lubricating oil recovery passage 32 Lubricating oil recovery tube 33 Lubricating oil supply passage 34 Lubricating oil supply Tube 35 Lubricating oil filter 36 Lubricating oil pump 37, 59, 63 Pressure regulating valve 38 Lubricating oil tank 39 Seal push plate 40 Mounting bolt 41 Lubricating oil pressure transmitter 42 Pressure vessel internal pressure transmitter 43, 43a Controller 44, 44a, 44b, 44c Comparator 45, 45a, 45b Comparison calculator 46, 46a, 46b Valve controller 47 Remote open / close valve 48 Clean water pressure transmitter 50, 51 Clean water supply passage 52 Clean water supply pipe 53 Supply water filter 54 Water pressure pump 55 Water pressure adjustment valve 56 Clean water tank 57 Lubricating oil return passage 58 Lubricating oil return pipe 60, 61 Clean water return passage 62 Clean water return pipe A, B, C, D Cavity portion 65 Seal portion 66 Roll shaft 67 Bearing 68 Bearing mounting base 69 Motor mounting allowance 70 Sealing boxes 71a, 71b, 71c U-shaped packing 72 Packing casing 73 Lantern phosphorus 74a, 74b, 74c, 74d ground packing 75 packing presser 76 spring 77 packing pressure screw

Claims (7)

  An upper pressure vessel fixed to the slag outlet of the coal gasification furnace, a lower pressure vessel fixed to the lower portion of the upper pressure vessel and having a smaller diameter than the upper pressure vessel, and a slag disposed in the lower pressure vessel In a bearing structure of a slag crusher having a roll crusher to be crushed and a roll shaft of the roll crusher penetrating the lower pressure vessel, a bearing provided in a penetrating portion of the lower pressure vessel of the roll shaft; An inner bearing cover provided inside the lower pressure vessel of the bearing, an outer bearing cover provided outside the bearing, a container-side high-pressure seal provided between the inner bearing cover and the roll shaft, A bearing structure for a slag crusher, comprising a non-high pressure seal provided between the outer bearing cover and the roll shaft.   An outer high-pressure seal provided on the bearing side from the non-high-pressure seal between the outer bearing cover and the roll shaft; a lubricating oil supply line for supplying high-pressure lubricating oil to the bearing; and a lubricating oil pump. The bearing structure of the slag crusher according to claim 1, wherein   An outer high-pressure seal provided on the bearing side from the non-high-pressure seal between the outer bearing cover and the roll shaft; a lubricating oil supply line for circulating high-pressure lubricating oil in the bearing; a lubricating oil return line; The slag crusher bearing structure according to claim 1, further comprising a lubricating oil pump.   High-pressure clean water is provided between the shaft-side high-pressure seal provided on the bearing side from the container-side high-pressure seal between the inner bearing cover and the roll shaft, and between the container-side high-pressure seal and the shaft-side high-pressure seal. The bearing structure of the slag crusher according to claim 1, further comprising a clean water supply pipe to be supplied and a hydraulic pump.   High-pressure clean water is provided between the shaft-side high-pressure seal provided on the bearing side from the container-side high-pressure seal between the inner bearing cover and the roll shaft, and between the container-side high-pressure seal and the shaft-side high-pressure seal. The bearing structure of the slag crusher according to claim 1, further comprising a clean water supply pipe to be circulated, a clean water return pipe, and a hydraulic pump.   High-pressure clean water is provided between the shaft-side high-pressure seal provided on the bearing side from the container-side high-pressure seal between the inner bearing cover and the roll shaft, and between the container-side high-pressure seal and the shaft-side high-pressure seal. The bearing structure of the slag crusher according to claim 3, further comprising a clean water supply pipe to be circulated, a clean water return pipe, and a hydraulic pump.   Control to make the pressure in the clean water supply line higher than the pressure in the lower pressure vessel or the upper pressure vessel, and to make the pressure in the lubricating oil supply line higher than the pressure in the clean water supply line The slag crusher bearing structure according to claim 6, further comprising a control unit configured to control the slag crusher.

Images