WO2019107292A1 - Dispositif de palier lisse et pompe le comprenant - Google Patents

Dispositif de palier lisse et pompe le comprenant Download PDF

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Publication number
WO2019107292A1
WO2019107292A1 PCT/JP2018/043312 JP2018043312W WO2019107292A1 WO 2019107292 A1 WO2019107292 A1 WO 2019107292A1 JP 2018043312 W JP2018043312 W JP 2018043312W WO 2019107292 A1 WO2019107292 A1 WO 2019107292A1
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Prior art keywords
slide bearing
bearing
sliding
pump
talc
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PCT/JP2018/043312
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English (en)
Japanese (ja)
Inventor
成夏 金
杉山　憲一
和彦 杉山
真 小宮
西谷　要介
Original Assignee
株式会社荏原製作所
学校法人 工学院大学
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Application filed by 株式会社荏原製作所, 学校法人 工学院大学 filed Critical 株式会社荏原製作所
Priority to CN201880076405.XA priority Critical patent/CN111406158B/zh
Publication of WO2019107292A1 publication Critical patent/WO2019107292A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/14—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load specially adapted for operating in water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/20—Sliding surface consisting mainly of plastics

Definitions

  • the present invention relates to a slide bearing device using a resin material and a pump including the same, and more particularly to a slide bearing device suitably used as a radial bearing of a rotary machine such as a pump and a pump including the same.
  • the drainage pump installed at the drainage station to prepare for rapid drainage of a large amount of rainwater caused by such frequent torrential rains should be prepared before rainwater reaches the drainage station to prevent flooding damage caused by delayed start-up. There is a preceding standby operation to start.
  • FIG. 1 is a partial schematic view of a vertical shaft pump performing a leading standby operation.
  • the vertical pump 3 is disposed in the water tank 100 of the drainage station.
  • the vertical pump 3 includes an impeller 22 at the tip of a rotating shaft 10 disposed in the longitudinal direction, and allows the impeller 22 to suck air with water. Thereby, the vertical pump 3 can continue the operation (preceding standby operation) even if the water level of the water tank 100 is equal to or lower than the lowest operation water level LWL.
  • a through hole 5 is provided in a side surface portion of the suction bell 27 on the inlet side of the impeller 22.
  • an air pipe 6 having an opening 6a in contact with the outside air is attached. ing.
  • the vertical pump 3 the amount of supply of air supplied into the vertical pump 3 through the through hole 5 is changed according to the water level, and the displacement of the vertical pump 3 is controlled below the minimum operating water level LWL.
  • FIG. 2 is a diagram for explaining the operating state of the preceding standby operation.
  • the vertical pump is started in advance using rainfall information etc. regardless of the suction water level (A: air operation).
  • A air operation
  • the vertical pump operates from idle operation (air operation) to stir water with the impeller (B: air / water agitation operation)
  • B air / water agitation operation
  • C air-water mixing operation
  • D steady operation
  • the operation shifts to an operation (C: air-water mixing operation) in which the amount of water is gradually reduced while sucking in the air supplied through the through hole from the high water level.
  • C air-water mixing operation
  • E air lock operation
  • FIG. 3 is a cross-sectional view showing the whole of the vertical axis pump 3 performing the leading standby operation shown in FIG. The through hole 5 and the air pipe 6 shown in FIG. 2 are not shown.
  • the vertical shaft pump 3 is connected to the discharge elbow 30 installed and fixed on the pump installation floor, the casing 29 connected to the lower end of the discharge elbow 30, and the lower end of the casing 29, and the impeller 22.
  • a suction bell 27 connected to the lower end of the discharge bowl 28 for sucking in water.
  • a single rotary shaft 10 formed by the upper and lower two shafts being connected to each other by a shaft coupling 26 is substantially in the radial direction substantially central portion of the casing 29 of the vertical pump 3, the discharge bowl 28 and the suction bell 27. It is arranged.
  • the rotating shaft 10 is supported by an upper bearing 32 fixed to the casing 29 via a support member and a lower bearing 33 fixed to the discharge bowl 28 via the support member.
  • An impeller 22 for sucking water into the pump is connected to one end side (the suction bell 27 side) of the rotating shaft 10.
  • the other end side of the rotating shaft 10 extends to the outside of the vertical shaft pump 3 through a hole provided in the discharge elbow 30, and is connected to a driver such as an engine or motor (not shown) that rotates the impeller 22.
  • a shaft seal 34 such as a floating seal, a gland packing, or a mechanical seal is provided between the rotary shaft 10 and a hole provided in the discharge elbow 30, and the shaft seal 34 is a vertical shaft pump with water handled by the vertical pump 3 Prevent outflow to the outside of 3.
  • the driving machine is provided on land so that maintenance and inspection can be easily performed.
  • the rotation of the drive machine is transmitted to the rotating shaft 10 and the impeller 22 can be rotated. Water is sucked from the suction bell 27 by the rotation of the impeller 22, passes through the discharge bowl 28 and the casing 29, and is discharged from the discharge elbow 30.
  • FIG. 4 is an enlarged view of a conventional bearing device applied to the bearings 32 and 33 shown in FIG.
  • FIG. 5 is a perspective view of a slide bearing installed in the bearing device shown in FIG.
  • the conventional bearing device has a sleeve 11 made of stainless steel, ceramics, sintered metal or surface-modified metal on the outer periphery of the rotating shaft 10.
  • the sleeve 11 has a Vickers hardness (Hv) of 800 or more and 2,500 or less.
  • a slide bearing 1 made of a hollow cylindrical resin material is provided on the outer peripheral side of the sleeve 11.
  • the outer peripheral surface of the sleeve 11 faces the inner peripheral surface (sliding surface) 1 a of the slide bearing 1 via a very narrow clearance, and is configured to slide relative to the slide bearing 1.
  • the slide bearing 1 is fixed to a support member 13 connected to a pump casing 29 (see FIG. 3) or the like via a flange portion 12a by a bearing case 12 made of metal or resin.
  • the slide bearing 1 has a hollow cylindrical shape, the inner peripheral surface (sliding surface) 1 a faces the outer peripheral surface 1 b of the sleeve 11, and the outer peripheral surface 1 b fits in the bearing case 12. United.
  • the vertical axis pump 3 shown in FIG. 3 is operated in the atmosphere when the pump is started. That is, the bearings 32, 33 are operated under dry sliding conditions without liquid lubrication.
  • the dry sliding condition refers to a condition in which the atmosphere of the bearings 32 and 33 during pump operation is in the atmosphere without liquid lubrication
  • the dry operation refers to operation under the condition.
  • the bearings 32, 33 shown in FIG. 4 are also operated under drainage conditions in which the bearings flow.
  • the drainage condition means that the atmosphere of the bearings 32, 33 during pump operation is water in which foreign matter (slurry) such as earth and sand is mixed, and the drainage operation is operated under the conditions, for example, air Water mixing operation, whole quantity operation, air lock operation etc.
  • the bearings 32, 33 are used under such conditions.
  • two bearings 32 and 33 are disposed with respect to the rotating shaft 10, but if the length of the rotating shaft 10 becomes longer, more bearings will be provided accordingly. Be placed.
  • a slide bearing device having a slide bearing using a resin material is widely used in rotary machines such as turbomachines and office machines since the resin has good lubricating performance (Patent Documents 1 to 4).
  • a method of evaluating a resin bearing it is performed to evaluate the coefficient of friction and the amount of abrasion of a resin by rotating a disk-shaped resin in a state where the disk surface of the disk-shaped resin is pressed against a flat plate.
  • Some rotary machines such as turbo machines use a resin material for a slide bearing for a radial bearing that receives a load acting in a direction perpendicular to the axial direction of the rotary shaft.
  • a sliding bearing for a radial bearing used in a water pump is used without entering lubricating oil into the gap (sliding portion) between the rotating body and the sliding bearing, with pumping water introduced. For this reason, when the water pump handles contaminated water (contaminated water) such as soil, the contaminated water may intrude into the sliding surface of the sliding bearing (sliding surface of the bearing). In this case, since the centrifugal force works in the radial direction of the slide bearing, it is difficult to axially discharge the foreign matter that has entered the gap between the rotary body and the slide bearing.
  • SiO 2 which is the main component of soil (foreign matter)
  • SiO 2 which is the main component of soil (foreign matter)
  • the resin material is abraded. Therefore, in the operation of the water pump which handles the foreign matter mixed water, there is a problem that the wear amount of the slide bearing is increased and the life of the slide bearing is shortened.
  • the vertical axis pump may be operated not only when the sliding surface of the bearing is in the water but also in a state where the sliding surface of the bearing is exposed to the atmosphere, as in the case of the leading standby operation.
  • the vertical pump is operated under the dry lubrication condition in which the sliding surface of the slide bearing is exposed to the atmosphere as described above, a slide bearing device with low friction under the dry lubrication condition is required.
  • FIGS. 6A and 6B are schematic cross-sectional views showing the state of the rotary shaft 10, the sleeve 11, and the slide bearing 1 during pump operation.
  • the sliding bearing 1 used for the bearings 32 and 33 shown in FIG. 3 and the sleeve 11 attached to the rotating shaft 10 contact each other when sliding The frictional heat generated by the parts increases.
  • the hatched portions shown in FIGS. 6A and 6B are portions of the slide bearing 1, the rotation shaft 10, and the sleeve 11 which become hot.
  • the rotary shaft 10 may locally expand and the rotary shaft 10 may be slightly bent.
  • the vibration due to the interference between the rotating body (the rotating shaft 10 and the sleeve 11) of the vertical pump and the fixed body (slide bearing 1) and the increase in the bearing load are likely to occur. That is, when the rotating body and the fixed body contact each other in the unbalanced direction of the rotating body and heat is generated at the contact portion, a temperature distribution is generated in the axial cross section of the rotating shaft 10 and the rotating shaft 10 is bent .
  • the present invention has been made in view of the above-described circumstances, and in a slide bearing device for a radial bearing used in a water pump, in an operation in water containing foreign matter (slurry) such as earth and sand, wear resistance as in the prior art
  • a slide bearing device comprising a slide bearing stably maintained with a low friction coefficient even in a relatively high PV value range under dry lubrication conditions sliding in the atmosphere while maintaining the To provide a pump having the
  • the carbon fiber can increase the strength of the slide bearing and reduce the linear expansion coefficient, and as a result, the shape change of the slide bearing can be suppressed to a low level, and the positive effect of maintaining long and stable performance is desired.
  • the coefficient of friction may repeatedly rise and fall rapidly during operation, and although it is not always stable, it is effective to contain a large amount of carbon fiber in order to reduce the maximum coefficient of friction at that time.
  • Talc has the effect of lowering the coefficient of friction by containing it in the slide bearing material. However, the effect of talc alone is limited.
  • a suitable range of carbon fiber and talc is found, and their synergetic effect can stabilize the maximum friction coefficient by the effect of talc even if the content of carbon fiber is relatively low, and However, even if the amount of carbon fiber is relatively large, the range in which the wear resistance can be maintained can be defined.
  • the present inventors examined as an important factor affecting low friction and wear resistance, focusing on the area ratio of carbon fiber on the sliding surface of the bearing and the content ratio of talc to the sliding bearing. As a result, when the area ratio of carbon fiber and the content ratio of talc are respectively within predetermined numerical ranges, the sliding bearing has a low friction coefficient, a high critical PV value, and a good abrasion resistance. I found it to be.
  • a sliding bearing device is provided.
  • This slide bearing device is a slide bearing device provided with a slide bearing, and the slide bearing includes aromatic polyether ketone, talc, carbon fiber, and unavoidable impurities, and the content ratio of the talc to the slide bearing is It is 7 mass% or more and 18 mass% or less, and the area ratio of the carbon fiber in the slide surface of the slide bearing is 27% or more and 35% or less.
  • the sliding surface of the sliding bearing is configured to be operable either in contact with the atmosphere or in contact with water mixed with earth and sand.
  • the aromatic polyether ketone is PEK, PEEK, PEKK or PEEKK.
  • the carbon fiber has a diameter of 5 ⁇ m to 10 ⁇ m.
  • the talc is scaly and has a minor axis diameter of 0.1 ⁇ m or more and a major axis diameter of 15 ⁇ m or less, and the major axis diameter is smaller than the minor axis diameter. More than 1 time and 15 times or less.
  • a pump is provided.
  • This pump is provided with the above-mentioned slide bearing device.
  • a bearing for use in a slide bearing device for a radial bearing of a water pump wherein the bearing is used in any of underwater operation including slurry and dry lubrication condition sliding in the atmosphere.
  • a slide bearing device comprising a slide bearing stably maintained with a low friction coefficient without deteriorating wear resistance even in a relatively high PV value range, and a pump comprising the same be able to.
  • FIG. 6 is a partial schematic view of a vertical pump performing a leading standby operation. It is a figure explaining the driving
  • the slide bearing device according to the present embodiment has, for example, the same structure as the slide bearing device shown in FIG. That is, the slide bearing device according to the present embodiment includes the rotary shaft 10 and the sleeve 11 which are rotating bodies, and the slide bearing 1 which is a fixed body. Moreover, the slide bearing 1 used for the slide bearing apparatus which concerns on this embodiment has a structure similar to the slide bearing 1 shown in FIG.
  • the slide bearing 1 is composed of a composite material of aromatic polyether ketone, talc, carbon fiber, and unavoidable impurities.
  • the inner peripheral surface of the cylindrical slide bearing 1 constitutes an inner peripheral surface (sliding surface) 1 a of the bearing in contact with the outer peripheral surface of the sleeve 11. That is, the slide bearing 1 is made of a material having an aromatic polyether ketone, talc, and carbon fiber that provides low friction, high strength, and abrasion resistance.
  • talc reduces the coefficient of friction as a solid lubricant
  • carbon fibers provide abrasion resistance and a low coefficient of friction
  • the friction of the sliding surface after the start of sliding causes deformation of the bearing due to thermal expansion to be large, and the area of the sliding surface in contact with the sleeve as the mating material tends to be small.
  • the surface pressure applied to the contacting sliding surface increases, thereby exceeding the limit PV value of the material. If the limit PV value is exceeded, seizing of the sliding surface of the sliding bearing to the sleeve occurs, resulting in a rapid increase in the coefficient of friction and damage to the bearing.
  • carbon fibers are contained in the sliding surface of the sliding bearing, deformation due to thermal expansion of the sliding surface can be prevented, and the seizure resistance of the sliding bearing is improved.
  • the aromatic polyether ketone preferably contains at least one of PEK (polyether ketone), PEEK (polyether ether ketone), PEKK (polyether ketone ketone), and PEEKK (polyether ether ketone ketone).
  • Talc is a solid lubricant, and the larger the amount, the more effective the friction coefficient is reduced.
  • the content of talc in the slide bearing is 7% by mass to 18% by mass, preferably 10% by mass to 17% by mass, and more preferably 12% by mass to 15% by mass. Lubricity improves that the content rate of the talc with respect to a slide bearing is in the said range, and the friction coefficient of the sliding surface of a slide bearing can be reduced.
  • the area ratio of carbon fibers in the slide surface of the slide bearing is 27% or more and 35% or less, preferably 30% or more and 34% or less, and more preferably 31% or more and 33% or less.
  • the lubricity can be improved and the friction coefficient of the slide surface of the slide bearing can be reduced.
  • the content ratio of talc to the slide bearing is 7% by mass to 18% by mass, and the area ratio of carbon fiber in the slide surface of the slide bearing is 27% to 35% or less It is.
  • the content of talc is preferably 9% to 15% by mass, and the area ratio of carbon fibers is preferably 30% to 33%, and the content of talc is 10%. % Or more and 12% by mass or less, and the area ratio of the carbon fiber is more preferably 31% or more and 32% or less.
  • the content rate of talc can be measured by the following method. That is, 100 g of the molded slide bearing is measured and fired at 800 ° C. to decompose and volatilize components such as carbon fiber and aromatic polyether ketone, recover talc as ash, and measure the weight of ash. And the ratio of the weight of an ash content (talc) with respect to the weight (100 g) of a slide bearing is calculated, and it is set as the content rate of a talc.
  • the shape of talc is preferably scaly, elliptical or the like.
  • the minor axis diameter is preferably 0.1 ⁇ m or more, more preferably 0.5 ⁇ m to 13 ⁇ m, and most preferably 5 ⁇ m to 11 ⁇ m, and the major axis diameter 15 ⁇ m or less is preferable, 1 ⁇ m or more and 14 ⁇ m or less is more preferable, and 6 ⁇ m or more and 12 ⁇ m or less is the most preferable.
  • magnification of the major axis diameter with respect to the minor axis diameter is preferably more than 1 and preferably 15 times or less, more preferably 1 to 10 times, and most preferably 1 to 5 times.
  • magnification of the major axis diameter with respect to the minor axis diameter, major axis diameter and / or minor axis diameter of talc is within the above range, talc functions as a solid lubricant to improve lubricity, and the sliding surface of the slide bearing Coefficient of friction can be reduced.
  • the minor axis diameter and major axis diameter of talc should be secondary electron image taken using SEM (HITACHI, field of view: 95 ⁇ m ⁇ 125 ⁇ m, applied voltage: 15.0 kV, magnification: 1000 ⁇ ).
  • the image analysis of the observation portion can be performed using an image analysis program: AxioVision (manufactured by ZEISS).
  • the area ratio of carbon fiber can be measured by the following method. That is, a smooth surface is provided on a molded slide bearing, and 10 places are randomly selected on the smooth surface, and an optical microscope (50-100 times objective lens made by Keyence) is used for each place to measure 214 ⁇ m long ⁇ horizontally Shoot a 285 ⁇ m flat surface. The photographed plane of 214 ⁇ m long and 285 ⁇ m wide is used as an observation portion, and the carbon fiber portion is identified by image analysis. The ratio of the area of the carbon fiber to the entire area of the observation portion is calculated, and the average of the calculated values at ten locations is determined to be the area ratio of the carbon fiber.
  • the image analysis of the observation portion of the slide bearing surface is the same as the pixel characteristics (brightness, color) of the carbon fiber, using the same image analysis program as described above used in the image analysis of talc. By extracting the part having.
  • the carbon fibers are preferably composed of staple fibers.
  • the diameter of the carbon fiber observed on the sliding surface 1a of the bearing is preferably 5 ⁇ m to 10 ⁇ m, more preferably 5.5 ⁇ m to 9 ⁇ m, and most preferably 6 ⁇ m to 8 ⁇ m.
  • the diameter of the carbon fiber is subjected to an image analysis using the same image analysis program as described above used in the image analysis of talc using an optical microscope (manufactured by Keyence, objective lens 50 to 100 times). It can be measured.
  • the length of the carbon fiber observed on the sliding surface 1a of the bearing is preferably 5 ⁇ m to 1000 ⁇ m, more preferably 6 ⁇ m to 500 ⁇ m, and most preferably 7 ⁇ m to 200 ⁇ m.
  • talc, aromatic polyether ketone and carbon fiber are heated and mixed by a twin screw kneader to prepare a resin composition, and the resin composition is compression-molded and then subjected to surface processing.
  • Slide bearings can be manufactured.
  • a slide bearing device can be manufactured using this slide bearing, and furthermore, a pump can be manufactured using this slide bearing device.
  • Example 1 first, carbon fiber, talc, and aromatic polyether ketone are mixed using a twin-screw kneader so that each of the area ratio of carbon fiber and the content ratio of talc becomes the values shown in Table 1. To produce pellets. The obtained pellet was put in a mold, pressurized and heated, and formed into primary processing, and then a detailed shape was imparted by secondary processing machining to manufacture a slide bearing. Then, with respect to the obtained slide bearing, evaluation of slurry wear resistance, friction coefficient and limit PV value was performed.
  • the area ratio of carbon fiber and the content ratio of talc were measured by the above-mentioned method, and the image analysis conditions at the time of calculating the area ratio of carbon fiber were set as follows. ⁇ In the measurement program wizard, Set the pixel "Brightness -0.66, Contrast 2.65, Gamma 1.00” Click “Set Tolerance 3; Edge Size 1"
  • sand particles containing silica sand (main component: Sio 2 ) having an average particle size of about 5 ⁇ m and silica sand having an average particle size of about 30 ⁇ m in a ratio of 1: 1 have a concentration of 3000 mg / L.
  • the mixture was poured into water to prepare water containing a slurry.
  • the bearing device including the above-mentioned slide bearing is immersed in water containing the obtained slurry, and WC-based cemented carbide under the condition of PV value 0.6 MPa ⁇ m / s in water maintained at 25 ° C.
  • the initial surface roughness (Ra) of WC base cemented carbide is 2 hours at a PV value of 1.0 MPa ⁇ m / s using a device shown in FIG.
  • the friction coefficient was measured continuously at intervals of 0.5 seconds for 2 hours while sliding on the surface of 3.2 without using lubricating oil.
  • the average value of the friction coefficient in 1 hour of the second half in 2 hours of operation was computed, and it was set as the friction coefficient of the slide bearing.
  • the friction coefficient of the slide bearing is 0.1 or less, the friction is small and good, and when it exceeds 0.1, the friction is large and defective.
  • the maximum friction coefficient of the slide bearing When the maximum friction coefficient of the slide bearing is 0.1 or less, the friction coefficient can be maintained low throughout the entire operation period, which is good ( ⁇ ). On the other hand, when it exceeds 0.1, the friction during operation The coefficient may be high, which is considered to be a defect (x).
  • Invention Example No. 1 The sliding bearings 1 to 6 had a wear rate of 30 ⁇ m / h or less and were excellent in the slurry wear resistance.
  • Comparative Example No. Although the sliding bearings of Nos. 3, 4 and 6 to 9 have a wear rate of 30 ⁇ m / h or less and are excellent in the resistance to slurry abrasion, Comparative Examples No. 1 and No. 2 have the following characteristics.
  • the sliding bearings of 1, 2 and 5 had a wear rate exceeding 30 ⁇ m / h and had poor resistance to slurry wear.
  • the slurry abrasion resistance tended to deteriorate as the area ratio of carbon fibers and / or the content of talc increased.
  • the sliding bearings 1 to 6 had good coefficients of friction of 0.1 or less.
  • Comparative Example No. Although the sliding bearings 1 to 7 have a coefficient of friction of 0.1 or less, which is a good result, Comparative Example No. 1 has a good result.
  • the sliding bearings of 8 and 9 had a coefficient of friction exceeding 0.1, which was inferior to the results.
  • the coefficient of friction fluctuates with the area ratio of carbon fibers, the coefficient of friction increases as the area ratio of carbon fibers decreases, and the coefficient of friction decreases as the area ratio of carbon fibers increases. there were.
  • the sliding bearings 1 to 6 had a maximum coefficient of friction of 0.1 or less, which was a good result.
  • Comparative Example No. Although the sliding bearings of No. 1 and No. 2 have a maximum friction coefficient of 0.1 or less, which is a good result, Comparative Example No.
  • the sliding bearings of 3 to 9 had a maximum coefficient of friction exceeding 0.1 and were inferior in results.
  • the maximum friction coefficient varies depending on the area ratio of carbon fibers and the content ratio of talc, and the area ratio of carbon fibers is 27% or more and / or the content ratio of talc is 7% by mass or more In this case, the maximum coefficient of friction was 0.1 or less, and good results were obtained.
  • the invention example no. 1 to 6 and Comparative Example No. 1 In the slide bearings of 1 to 4, the temperature at a position 5 mm deep from the slide surface of the slide bearing was 120 ° C. or less, and the evaluation of the critical PV value was good. On the other hand, Comparative Example No. In all of the slide bearings 5 to 9, the temperature at a position 5 mm deep from the slide surface of the slide bearing exceeded 120 ° C., and the evaluation of the critical PV value became poor. As can be seen from the results in Table 1, the evaluation of the critical PV value fluctuates depending on the area ratio of the carbon fiber, and deteriorates as the area ratio of the carbon fiber decreases, and tends to improve as the area ratio of the carbon fiber increases.
  • the area ratio of carbon fiber is 27% or more and 35% or less
  • the content ratio of talc is 7% by mass or more and 18% by mass or less according to the invention example No.
  • the comparative bearings No. 1 to 6 of Comparative Examples No. 1 to No. 6 have good overall evaluation, while at least one of the area ratio of carbon fiber and the content ratio of talc does not satisfy the above-mentioned numerical range.
  • the slide bearings of 1 to 9 were poor in overall evaluation.
  • Example No. 1 of Example 1 The slide bearings of No. 3 and the slide bearings of the comparative example (sliding bearings composed of PEEK resin and carbon fiber of continuous fiber and containing no talc) are each radial bearings of the vertical mixed flow pump shown in FIG. It used as a certain bearing 32 and 33, and the drainage operation and dry operation of water containing actual foreign matter (earth and sand) were repeated.
  • Invention Example No. 1 of Example 1 was obtained.
  • the wear rate of the slide bearing of No. 3 is 25.3 ⁇ m / h
  • a rapid rise in bearing temperature occurs in a short time during dry operation, and it is necessary to stop the operation of the pump.
  • example No. 1 of Example 1 In the case of No. 3 sliding bearing, no sudden temperature rise occurred and the pump could be operated stably. That is, by using the slide bearing of the present invention for the bearings 32, 33 used under severe conditions where drainage operation and dry operation are repeatedly performed, excellent bearing characteristics both in the atmosphere and in the water containing foreign matter can be obtained. I was able to demonstrate.
  • FIG. 7A compared with FIG. 7B, almost no pulse-like rapid rise / drop was seen in any of the coefficient of friction and temperature, and the range of rise / drop was very small even in the case of rapid rise / drop. From this result, it was found that the operating condition of the slide bearing was very stable.
  • No. 1 of the example of this invention of Table 1 is.
  • No. 5 and No. 5 of the comparative example Each of the seven plain bearings was attached to the device shown in FIG. 4 and operated for 2 hours under the respective operating conditions of PV value: 0.4, 0.5, 0.75, or 1.0 m / s ⁇ MPa.
  • the maximum friction coefficient of the slide bearing is determined as the largest friction coefficient among the friction coefficients measured continuously at intervals of 0.5 seconds, and the largest among the friction coefficients measured during two hours of operation.
  • No. 5 and No. 5 of the comparative example A graph (FIG. 8) was made showing the time variation of the maximum friction coefficient and bearing temperature for No.7.
  • the sliding bearing of No. 5 had a lower maximum coefficient of friction, and its value was stable without any significant change within the PV value range of 0.4 to 1.0 m / s ⁇ MPa. From the results, it was found that the sliding bearing of the present invention was able to maintain a low coefficient of friction for the entire period of operation under various conditions of PV values, and was able to perform stable operation.
  • No. 1 of the comparative example In the slide bearing of No. 7, the maximum friction coefficient exhibited a relatively large value within the PV value range of 0.4 to 1.0 m / s ⁇ MPa, and the value largely fluctuated depending on the PV value. From this result, it was found that the sliding bearing of the comparative example may have a high coefficient of friction during operation, and the maximum coefficient of friction fluctuates depending on the PV value, resulting in unstable operation.
  • the slide bearing device according to the present embodiment can be used for a slide bearing device as a radial bearing operating in atmospheric operation and a slide bearing device as a radial bearing operating in water in which foreign matter is mixed.
  • the slide bearing device according to the present embodiment can also be used for a slide bearing device as a radial bearing in which the operation in water containing foreign matter and the operation in the atmosphere are repeated.

Abstract

L'invention concerne : un dispositif de palier lisse destiné à un palier radial utilisé dans une pompe à eau, le dispositif de palier lisse comprenant un palier lisse dans lequel, tandis que la résistance à l'usure équivalente à celle obtenue dans le passé est maintenue pendant un fonctionnement sous une eau contenant des corps étrangers tels que du sable (suspension), la résistance à l'usure est maintenue de manière stable à un faible coefficient de frottement même dans une plage de valeurs de PV comparativement élevée en condition de lubrification sèche lors d'un glissement dans l'air ; et une pompe comprenant le dispositif de palier lisse. Un dispositif de palier lisse comprend un palier lisse, le palier lisse comprenant une polyéther cétone aromatique, du talc, des fibres de carbone et d'inévitables impuretés, la teneur en talc dans le palier lisse étant de 7 à 18 % en masse, et le rapport surfacique des fibres de carbone à la surface de glissement du palier lisse étant de 27 à 35 %.
PCT/JP2018/043312 2017-11-30 2018-11-26 Dispositif de palier lisse et pompe le comprenant WO2019107292A1 (fr)

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