WO2014103631A1 - 摺動部品 - Google Patents
摺動部品 Download PDFInfo
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- WO2014103631A1 WO2014103631A1 PCT/JP2013/082537 JP2013082537W WO2014103631A1 WO 2014103631 A1 WO2014103631 A1 WO 2014103631A1 JP 2013082537 W JP2013082537 W JP 2013082537W WO 2014103631 A1 WO2014103631 A1 WO 2014103631A1
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- WIPO (PCT)
- Prior art keywords
- pumping groove
- groove
- pumping
- fluid side
- pressure fluid
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- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
- F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
- F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
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- 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
- F16C33/72—Sealings
- F16C33/74—Sealings of sliding-contact bearings
Definitions
- the present invention relates to a sliding part suitable for a sliding part, for example, a mechanical seal, a bearing, and the like.
- the present invention relates to a sliding component such as a seal ring or a bearing that requires a fluid to be interposed in the sliding surface to reduce friction and prevent fluid from leaking from the sliding surface.
- a mechanical seal which is an example of a sliding part
- its performance is evaluated by the amount of leakage, the amount of wear, and torque.
- the performance is improved by optimizing the sliding material and sliding surface roughness of the mechanical seal, and low leakage, long life, and low torque are realized.
- further improvement in the performance of mechanical seals is required, and technical development that exceeds the framework of conventional techniques is required.
- a spiral groove 52 is provided on a sliding surface 51 of a sliding component 50, and an attempt is made to leak to the low-pressure fluid side using the pumping action of the spiral groove 52.
- the sealing function of the sliding surface is improved by pushing back the sealed fluid to the high pressure fluid side (see, for example, Patent Document 1).
- the sliding groove 51 is provided with a spiral groove 52 at an angle for discharging the fluid to the high-pressure fluid side by relative sliding with the counterpart sliding face, and the viscous pump effect of the spiral groove 52 is provided.
- the spiral groove 52 has a low pressure fluid side. It has been confirmed by experiments of the present inventors that steam cavitation occurs at the end 53 (upstream portion of the fluid flow accompanying the relative movement with the mating sliding surface, the inner peripheral side in FIG. 1) 53. ing.
- the present invention relates to vapor cavitation that occurs at the low-pressure fluid side end of the pumping groove (for example, spiral groove) formed on the sliding surface (upstream portion of the fluid flow accompanying relative movement with the mating sliding surface). Accordingly, it is an object of the present invention to provide a sliding component having an improved sealing function on the sliding surface.
- At least one sliding surface of the sliding component communicates with the high-pressure fluid side (sealed fluid side), and the fluid is moved to the high-pressure fluid side by relative sliding with the other-side sliding surface.
- the pumping groove for example, spiral groove
- the low-pressure fluid side for example, the atmosphere side
- An angled pumping groove for example, a spiral groove
- the pumping groove that communicates with the low-pressure fluid side sucks the liquid when liquid exists on the low-pressure fluid side, and generates dynamic pressure near the end of the pumping groove on the high-pressure fluid side.
- a sliding surface on one side of a pair of sliding components that slide relative to each other communicates with the high-pressure fluid side and the low-pressure fluid side.
- a first pumping that is isolated by a sealing surface (refers to the smooth portion of the sliding surface; hereinafter the same) and has an angle for discharging fluid to the high-pressure fluid side by sliding relative to the mating sliding surface.
- a groove is provided, and communicates with the low-pressure fluid side, is isolated from the high-pressure fluid side by a sealing surface, and has an angle for discharging the fluid to the high-pressure fluid side by relative sliding with the mating sliding surface.
- a second pumping groove is provided, and the low-pressure fluid side end of the first pumping groove and the high-pressure fluid side end of the second pumping groove are arranged close to each other. According to this feature, the negative pressure in the vicinity of the end of the first pumping groove on the low-pressure fluid side is relieved and the generation of vapor cavitation is prevented, so that the generation of precipitates is prevented and the foreign matter on the sliding surface is prevented. Adhesion and deposition are prevented, and the sealing performance of the sliding surface can be stably maintained.
- the sliding component of the present invention is secondly characterized in that, in the first feature, the first pumping groove and the second pumping groove are formed in a spiral shape. According to this feature, stable sealing performance can be obtained.
- a plurality of the first pumping grooves and the second pumping grooves are provided in the circumferential direction, and the first pumping groove Each of the second pumping grooves is disposed in a pair. According to this feature, the negative pressure in the vicinity of the low-pressure fluid side end portion of the first pumping groove can be relaxed efficiently and reliably, and the occurrence of vapor cavitation can be prevented.
- the first pumping groove in each of the pumping grooves that form a pair of the first pumping groove and the second pumping groove, is the first pumping groove.
- the second pumping groove is disposed so as to be located upstream in the circumferential direction. According to this feature, the negative pressure generated by the first pumping groove can be efficiently relieved by the dynamic pressure generation effect of the second pumping groove on the downstream side, and the occurrence of vapor cavitation can be prevented.
- the first pumping groove and the The second pumping groove is arranged on substantially the same line in the radial direction. According to this feature, the pressure at the negative pressure starting point of the first pumping groove can be increased by the dynamic pressure generated by the second pumping groove, and the occurrence of vapor cavitation can be suppressed.
- the sliding component according to the fourth or fifth aspect wherein the first pumping groove is formed in each pumping groove forming a pair of the first pumping groove and the second pumping groove.
- the low-pressure fluid side end of the groove and the high-pressure fluid side end of the second pumping groove are arranged so as to be separated from each other in the radial direction.
- the width of the sealing surface required for preventing static leakage can be between the inner peripheral end of the first pumping groove and the outer peripheral end of the second pumping groove, and is stable when stationary. Sealing performance can be obtained.
- a low pressure of the first pumping groove is provided in each pumping groove forming a pair of the first pumping groove and the second pumping groove.
- the fluid-side end portion and the high-pressure fluid-side end portion of the second pumping groove are formed so as to overlap in the radial direction. According to this feature, even when the vaporous cavitation generated in the vicinity of the low-pressure fluid end of the first pumping groove has a radial spread, the high-pressure fluid end of the second pumping groove The dynamic pressure generated in the vicinity can more reliably prevent the occurrence of vapor cavitation.
- a positive pressure generating mechanism is provided on the sliding surface on the high-pressure fluid side from the first pumping groove.
- a pressure release groove is provided so as to be positioned between the first pumping groove and the positive pressure generation mechanism, and the positive pressure generation mechanism and the pressure release groove are in communication with the high-pressure fluid side, The end of the first pumping groove on the high-pressure fluid side communicates with the pressure release groove.
- the present invention has the following excellent effects.
- Negative pressure in the vicinity of the low-pressure fluid side end of the first pumping groove is relieved to prevent the occurrence of vapor cavitation, thus preventing the generation of precipitates and adhesion and accumulation of foreign matter on the sliding surface. Is prevented, and the sealing performance of the sliding surface can be stably maintained.
- first pumping groove and the second pumping groove are formed in a spiral shape, stable sealing performance can be obtained.
- a plurality of first pumping grooves and second pumping grooves are provided in the circumferential direction, and each of the first pumping groove and the second pumping groove is disposed so as to make a pair efficiently. In addition, it is possible to reliably reduce the negative pressure in the vicinity of the low pressure fluid side end portion of the first pumping groove and prevent the occurrence of vapor cavitation.
- the first pumping groove is disposed on the upstream side in the circumferential direction from the second pumping groove.
- the negative pressure generated by the first pumping groove can be efficiently relieved by the dynamic pressure generation effect of the second pumping groove on the downstream side, and the occurrence of vapor cavitation can be prevented.
- the first pumping groove and the second pumping groove are disposed on substantially the same line in the radial direction.
- each pumping groove forming a pair of the first pumping groove and the second pumping groove the low-pressure fluid side end of the first pumping groove and the high-pressure fluid side end of the second pumping groove have a diameter.
- the sealing surface width necessary for preventing stationary leakage is between the inner peripheral side end of the first pumping groove and the outer peripheral side end of the second pumping groove. It is possible to obtain a stable sealing property when stationary.
- each pumping groove that forms a pair of the first pumping groove and the second pumping groove the low-pressure fluid side end of the first pumping groove and the high-pressure fluid side end of the second pumping groove are
- the second pumping groove is formed so as to overlap in the radial direction even when the vaporous cavitation generated in the vicinity of the low pressure fluid side end of the first pumping groove has a radial spread. The generation of vaporous cavitation can be more reliably prevented by the dynamic pressure generated in the vicinity of the end portion on the high-pressure fluid side.
- Example 1 of this invention With reference to FIG.2 and FIG.3, the sliding component which concerns on Example 1 of this invention is demonstrated.
- a mechanical seal which is an example of a sliding part will be described as an example.
- the outer peripheral side of the sliding component which comprises a mechanical seal is demonstrated as a high pressure fluid side (sealed fluid side) and an inner peripheral side is a low pressure fluid side (atmosphere side), this invention is not limited to this.
- the present invention can also be applied to the case where the high-pressure fluid side and the low-pressure fluid side are reversed.
- FIG. 2 is a longitudinal sectional view showing an example of a mechanical seal, which is an inside type that seals the sealed fluid on the high-pressure fluid side that tends to leak from the outer periphery of the sliding surface toward the inner peripheral direction.
- annular ring which is one sliding component provided on the rotary shaft 1 side for driving a pump impeller (not shown) on the high pressure fluid side via a sleeve 2 so as to be rotatable integrally with the rotary shaft 1.
- a ring-shaped stationary ring 5 which is the other sliding part provided in the pump housing 4 in a non-rotating state and movable in the axial direction, and the stationary ring 5 is moved in the axial direction.
- FIG. 3 shows a sliding surface of the sliding component according to the first embodiment of the present invention.
- a pumping groove is formed on the sliding surface of the stationary ring 5 in FIG. 2. To do. The same applies when a pumping groove is formed on the sliding surface of the rotary ring 3.
- the outer peripheral side of the sliding surface S of the stationary ring 5 is the high-pressure fluid side
- the inner peripheral side is the low-pressure fluid side, for example, the atmospheric side
- the counterpart sliding surface rotates counterclockwise.
- the sliding surface S communicates with the high-pressure fluid side and is separated from the low-pressure fluid side by a smooth portion of the sliding surface S (in the present invention, sometimes referred to as “seal surface”) and A first pumping groove 10 having an angle for discharging the fluid to the high-pressure fluid side by sliding relative to the sliding surface is provided.
- the sliding surface S communicates with the low-pressure fluid side and is separated from the high-pressure fluid side by the smooth portion of the sliding surface S, and the fluid is slid relative to the mating sliding surface to cause the fluid to flow.
- a second pumping groove 11 having a discharge angle is provided. Further, the low pressure fluid side end portion 10 ′ of the first pumping groove 10 and the high pressure fluid side end portion 11 ′ of the second pumping groove 11 are disposed close to each other. The “proximity” here will be described later.
- the first pumping groove 10 and the second pumping groove 11 are formed in a linear shape or a curved shape so as to have an angle at which the fluid is discharged to the high pressure fluid side by relative sliding with the mating sliding surface. In this embodiment, in consideration of vibration and noise, it is formed in a spiral shape along the rotation direction of the mating sliding surface. Further, the inclination angle, groove width, and groove depth of the first pumping groove 10 and the second pumping groove 11 depend on, for example, the type (viscosity, etc.), pressure, or relative sliding speed of the fluid to be sealed. The best value is determined. Further, the ratio of the lengths in the radial direction between the first pumping groove 10 and the second pumping groove 11 is also determined according to the same conditions. For example, the length of the first pumping groove 10 ⁇ The second pumping groove 11 is set.
- a plurality of the first pumping grooves 10 and the second pumping grooves 11 are provided in the circumferential direction.
- FIG. 3 an example in which 18 circumferential intervals are provided is shown, but for example, 120 equal intervals or more may be provided.
- each of the first pumping groove 10 and the second pumping groove 11 is disposed in a pair.
- the first pumping groove 10a and the second pumping groove 11a are arranged to make a pair, and the first pumping groove 10a and the second pumping groove 11a are hydrodynamic. It is arranged so as to affect.
- the first pumping groove 10 is located on the upstream side in the circumferential direction from the second pumping groove 11. Also, the low pressure fluid side end portion 10 'of the first pumping groove 10 and the high pressure fluid side end portion 11' of the second pumping groove 11 are arranged so as to be separated from each other in the radial direction. The In this way, the first pumping groove 10 is disposed so as to be positioned upstream of the second pumping groove 11 in the circumferential direction, so that the negative pressure generated by the first pumping groove is reduced on the downstream side. The effect of generating dynamic pressure due to the second pumping groove can effectively relieve the occurrence of steam cavitation.
- the low pressure fluid side end portion 10 'of the first pumping groove 10 and the high pressure fluid side end portion 11' of the second pumping groove 11 are formed so as to be separated in the radial direction, thereby preventing static leakage.
- the required sealing surface width can be between the low pressure fluid side end portion 10 ′ of the first pumping groove 10 and the high pressure fluid side end portion 11 ′ of the second pumping groove 11. Sex can be obtained.
- the sealed fluid which is about to leak to the low pressure fluid side is pushed back to the high pressure fluid side by the pumping action of the first pumping groove 10 communicating with the high pressure fluid side.
- Steam cavitation occurs in the vicinity of the low pressure fluid side end portion 10 '(inner peripheral side in FIG. 1) of the first pumping groove 10 communicating with the first pumping groove 10.
- the second pumping groove 11 communicating with the low-pressure fluid side (for example, the atmosphere side) sucks the liquid when the liquid exists on the low-pressure fluid side, and the second pumping groove 11 has the high-pressure fluid end 11.
- the dynamic pressure reduces the negative pressure in the vicinity of the low pressure fluid side end portion 10 ′ of the first pumping groove 10 communicating with the high pressure fluid side, thereby preventing the occurrence of vapor cavitation.
- the second pumping groove 11 is in the vicinity of the low pressure fluid side end portion 10 ′ of the first pumping groove 10 that introduces atmospheric air and communicates with the high pressure fluid side when no liquid is present on the low pressure fluid side. Reducing the negative pressure of the gas to prevent the occurrence of vapor cavitation.
- proximity in “the low pressure fluid side end portion 10 ′ of the first pumping groove 10 and the high pressure fluid side end portion 11 ′ of the second pumping groove 11 are disposed close to each other”. Means that the first pumping groove 10a and the second pumping groove 11a are arranged at close positions so as to influence hydrodynamically.
- Example 2 of this invention With reference to FIG. 4, the sliding component which concerns on Example 2 of this invention is demonstrated.
- the same reference numerals as those in the first embodiment denote the same members as those in the first embodiment, and duplicate descriptions are omitted.
- the first pumping groove 10 and the second pumping groove 11 are substantially on the same line in the radial direction.
- the low pressure fluid side end portion 10 'of the first pumping groove 10 and the high pressure fluid side end portion 11' of the second pumping groove 11 are close to each other on substantially the same radial line.
- the low pressure fluid side end portion 10 ′ of the first pumping groove 10 and the high pressure fluid side end portion 11 ′ of the second pumping groove 11 are formed so as to be separated from each other in the radial direction.
- the pumping grooves forming a pair of the second pumping grooves 11 are separated from each other, and a sealing surface of the sliding surface S is interposed between the two.
- the first pumping groove 10 and the second pumping groove 11 are disposed on substantially the same line in the radial direction, whereby the pressure at the negative pressure starting point of the first pumping groove is reduced to the second. It can be raised by the dynamic pressure generated by the pumping groove, and the generation of vapor cavitation can be suppressed.
- the low pressure fluid side end portion 10 'of the first pumping groove 10 and the high pressure fluid side end portion 11' of the second pumping groove 11 are formed so as to be separated from each other in the radial direction, thereby preventing static leakage.
- the required sealing surface width can be between the inner peripheral side end of the first pumping groove and the outer peripheral side end of the second pumping groove, and a stable sealing performance can be obtained when stationary.
- Example 3 of this invention With reference to FIG. 5, the sliding component which concerns on Example 3 of this invention is demonstrated.
- the same reference numerals as those in the first embodiment denote the same members as those in the first embodiment, and duplicate descriptions are omitted.
- the first pumping groove 10 is positioned on the upstream side in the circumferential direction from the second pumping groove 11. Further, the low pressure fluid side end portion 10 ′ of the first pumping groove 10 and the high pressure fluid side end portion 11 ′ of the second pumping groove 11 are disposed so as to overlap in the radial direction. Yes. That is, the first pumping groove 10a is disposed on the upstream side in the circumferential direction from the second pumping groove 11a, and the low-pressure fluid side end portion 10 'of the first pumping groove 10a has a radial direction. It extends beyond the intermediate point to near the middle between the intermediate point and the inner periphery, and the high pressure fluid side end portion 11 ′ of the second pumping groove 11 extends to a position slightly exceeding the intermediate point in the radial direction. ing.
- the first pumping groove 10 is disposed so as to be positioned upstream of the second pumping groove 11 in the circumferential direction, so that the negative pressure generated by the first pumping groove is reduced on the downstream side.
- the effect of generating dynamic pressure due to the second pumping groove can effectively relieve the occurrence of steam cavitation.
- the low pressure fluid side end portion 10 'of the first pumping groove 10 and the high pressure fluid side end portion 11' of the second pumping groove 11 are disposed so as to overlap in the radial direction, Even when the vaporous cavitation generated in the vicinity of the low pressure fluid side end 10 ′ of the pumping groove 10 a has a radial spread, it occurs in the vicinity of the high pressure fluid side end 11 ′ of the second pumping groove 11. Due to the dynamic pressure, it is possible to more reliably prevent the occurrence of steam cavitation.
- Example 4 of this invention With reference to FIG. 6, the sliding component which concerns on Example 4 of this invention is demonstrated.
- the same reference numerals as those in the first embodiment denote the same members as those in the first embodiment, and duplicate descriptions are omitted.
- the first pumping groove 10 is located on the upstream side in the circumferential direction from the second pumping groove 11, and the first pumping groove 10
- the low pressure fluid side end portion 10 ′ of the pumping groove 10 and the high pressure fluid side end portion 11 ′ of the second pumping groove 11 are arranged so as to overlap in the radial direction.
- a positive pressure generating mechanism 12 is provided on the sliding surface on the high-pressure fluid side from the first pumping groove 10, and the pressure is set so as to be positioned between the first pumping groove 10 and the positive pressure generating mechanism 12.
- An open groove 13 is provided.
- the positive pressure generating mechanism 12 and the pressure release groove 13 are communicated with the high pressure fluid side via the radial groove 15, and the high pressure fluid side end of the first pumping groove 10 is communicated with the pressure release groove 13. Yes.
- the positive pressure generating mechanism 12 is preferably composed of, for example, a Rayleigh step mechanism 14.
- a plurality of Rayleigh step mechanisms 14 are provided in the circumferential direction, and communicate with the high-pressure fluid side via radial grooves 15. That is, a sealing surface of the sliding surface S is interposed between adjacent Rayleigh step mechanisms 14, the upstream side of the groove 16 of each Rayleigh step mechanism 14 communicates with the radial groove 15, and the downstream side of the groove 16 is a sliding surface.
- a step (step portion) 17 is formed between the moving surface S and the sealing surface.
- the groove 16 and the high pressure fluid side are not in direct communication with each other due to the presence of the sealing surface of the sliding surface S, and are communicated with the high pressure fluid side via the radial groove 15 on the upstream side of the groove 16.
- the pressure release groove 13 is formed of a circumferential groove, is disposed between the first pumping groove 10 and the positive pressure generating mechanism 12 in the radial direction, and communicates with the plurality of radial grooves 15.
- a sealing surface of the sliding surface S is interposed between the pressure release groove 13 and the positive pressure generating mechanism 12.
- the positive pressure generated by the positive pressure generating mechanism 12 widens the interval between the sliding surfaces S, and a liquid film is formed, so that the lubricity is improved. At that time, since the positive pressure generated by the positive pressure generating mechanism 12 is guided to the pressure release groove 13 and is released to the high pressure fluid side, there is little leakage to the low pressure fluid side. Further, the fluid that is going to leak to the low-pressure fluid side beyond the pressure release groove 13 is pushed back to the high-pressure fluid side by the pumping action of the first pumping groove 10 and is guided to the pressure release groove 13 and is released to the high-pressure fluid side. It is.
- the low-pressure fluid in the first pumping groove 10 can be used even in a sliding component having improved lubricity by providing the positive pressure generating mechanism 12 on the sliding surface provided with the first pumping groove 10. Since the negative pressure in the vicinity of the side end portion 10 ′ is relieved to prevent the occurrence of vapor cavitation, the generation of precipitates is prevented, the adhesion and accumulation of foreign matter on the sliding surface is prevented, and the sliding surface is sealed. Sex can be maintained stably.
- Example 5 of this invention With reference to FIG. 7, the sliding component which concerns on Example 5 of this invention is demonstrated.
- the same reference numerals as those in the fourth embodiment denote the same members as those in the fourth embodiment, and duplicate descriptions are omitted.
- the configuration of the positive pressure generating mechanism 12 is slightly different from that of the fourth embodiment shown in FIG. 6, but the other configurations are the same as those of the fourth embodiment.
- the positive pressure generating mechanism 12 of the present embodiment is composed of a Rayleigh step mechanism 14, but each groove 16 communicates directly with the high pressure fluid side on the high pressure fluid side, and the upstream side is connected with the radial groove 15.
- a step (stepped portion) 17 is formed between the downstream side and the sealing surface of the sliding surface S.
- the present invention can also be applied to a case where the inner peripheral side is a high-pressure fluid.
- the case where the first pumping groove 10a and the second pumping groove 11a are arranged to form a 1: 1 pair is not limited to this. Multiple or vice versa may be used. Further, when the first pumping groove 10a and the second pumping groove 11a are densely arranged in the circumferential direction, they do not necessarily need to be arranged in pairs.
- the dynamic pressure generated near the high pressure fluid side end portion 11 'of the second pumping groove 11 relieves the negative pressure near the low pressure fluid side end portion 10' of the first pumping groove 10 to prevent the occurrence of vapor cavitation. What is necessary is just to be arrange
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Abstract
Description
本発明は、少なくとも摺動部品のいずれか一方の摺動面に、高圧流体側(被密封流体側)に連通し、かつ、相手側摺動面との相対摺動により流体を高圧流体側に排出する角度をつけたポンピング溝(例えば、スパイラル溝)に加え、低圧流体側(例えば、大気側)に連通し、かつ、相手側摺動面との相対摺動により流体を高圧流体側に排出する角度をつけたポンピング溝(例えば、スパイラル溝)を設けるものである。低圧流体側(例えば、大気側)に連通するポンピング溝は、低圧流体側に液体が存在する場合は当該液体を吸い込み、また、ポンピング溝の高圧流体側の終端近傍で動圧を発生し、この動圧により高圧流体側に連通する連通するポンピング溝の低圧流体側端部(相手摺動面との相対運動に伴う流体流れの上流側部分。)の負圧を緩和して蒸気性キャビテーションの発生を防止する。また、低圧流体側に液体が存在しない場合は、大気側空気を導入し、高圧流体側に連通するポンピング溝の低圧流体側端部(相手摺動面との相対運動に伴う流体流れの上流側部分。)の負圧を緩和して蒸気性キャビテーションの発生を防止する。
上記目的を達成するため本発明の摺動部品は、第1に、一対の摺動部品の互いに相対摺動する一方側の摺動面には、高圧流体側に連通されると共に低圧流体側とは密封面(摺動面の平滑部を指す。以下、同じ。)により隔離され、かつ、相手側摺動面との相対摺動により流体を高圧流体側に排出する角度を有する第一のポンピング溝が設けられ、さらに、低圧流体側に連通されると共に高圧流体側とは密封面により隔離され、かつ、相手側摺動面との相対摺動により流体を高圧流体側に排出する角度を有する第二のポンピング溝が設けられ、前記第一のポンピング溝の低圧流体側端部と前記第二のポンピング溝の高圧流体側端部とが近接して配設されることを特徴としている。
この特徴によれば、第一のポンピング溝の低圧流体側端部の近傍の負圧が緩和されて蒸気性キャビテーションの発生が防止されるため、析出物の発生が防止され、摺動面に対する異物付着及び堆積が防止され、摺動面の密封性を安定して維持することができる。
この特徴によれば、安定した密封性を得ることができる。
この特徴によれば、効率よく、また、確実に、第一のポンピング溝の低圧流体側端部の近傍の負圧を緩和し蒸気性キャビテーションの発生を防止することができる。
この特徴によれば、第一のポンピング溝により発生する負圧を下流側の第二のポンピング溝による動圧発生効果で効率よく緩和し、蒸気性キャビテーションの発生を防止できる。
この特徴によれば、第一のポンピング溝の負圧起点部の圧力を、第二のポンピング溝により発生する動圧によって上昇させ、蒸気性キャビテーションの発生を抑制することができる。
この特徴によれば、静止漏れ防止に必要となる密封面幅は、第一のポンピング溝の内周側端部と第二ポンピング溝の外周側端部の間とすることができ、静止時に安定した密封性を得ることができる。
この特徴によれば、第一のポンピング溝の低圧流体側端部の近傍で発生する蒸気性のキャビテーションが径方向に広がりを持っている場合でも、第二のポンピング溝の高圧流体側端部の近傍で発生する動圧により、より確実に蒸気性のキャビテーションの発生を防止できる。
この特徴によれば、第一のポンピング溝を備えた摺動面に正圧発生機構を併設することにより潤滑性を高めるようにした摺動部品においても、第一のポンピング溝の低圧流体側端部の近傍の負圧が緩和されて蒸気性キャビテーションの発生が防止されるため、析出物の発生が防止され、摺動面に対する異物付着及び堆積が防止され、摺動面の密封性を安定して維持することができる。
(1)第一のポンピング溝の低圧流体側端部の近傍の負圧が緩和されて蒸気性キャビテーションの発生が防止されるため、析出物の発生が防止され、摺動面に対する異物付着及び堆積が防止され、摺動面の密封性を安定して維持することができる。
(3)第一のポンピング溝及び第二のポンピング溝は周方向に複数設けられ、第一のポンピング溝及び第二のポンピング溝の各々が対をなすように配設されることにより、効率よく、また、確実に、第一のポンピング溝の低圧流体側端部の近傍の負圧を緩和し蒸気性キャビテーションの発生を防止することができる。
(5)第一のポンピング溝及び第二のポンピング溝の対をなす各々のポンピング溝において、第一のポンピング溝と第二のポンピング溝とは半径方向において略同一の線上に配設されることにより、第一のポンピング溝の負圧起点部の圧力を、第二のポンピング溝により発生する動圧によって上昇させ、蒸気性キャビテーションの発生を抑制することができる。
(7)第一のポンピング溝及び第二のポンピング溝の対をなす各々のポンピング溝において、第一のポンピング溝の低圧流体側端部と前記第二のポンピング溝の高圧流体側端部とは径方向において重複するように形成されることにより、第一のポンピング溝の低圧流体側端部の近傍で発生する蒸気性のキャビテーションが径方向に広がりを持っている場合でも、第二のポンピング溝の高圧流体側端部の近傍で発生する動圧より、より確実に蒸気性のキャビテーションの発生を防止できる。
なお、本実施例においては、摺動部品の一例であるメカニカルシールを例にして説明する。また、メカニカルシールを構成する摺動部品の外周側を高圧流体側(被密封流体側)、内周側を低圧流体側(大気側)として説明するが、本発明はこれに限定されることなく、高圧流体側と低圧流体側とが逆の場合も適用可能である。
なお、回転環3の摺動面にポンピング溝が形成される場合も同様である。
摺動面Sには、高圧流体側に連通されると共に低圧流体側とは摺動面Sの平滑部(本発明においては、「シール面」ということがある。)により隔離され、かつ、相手摺動面との相対摺動により流体を高圧流体側に排出する角度を有する第一のポンピング溝10が設けられる。さらに、摺動面Sには、低圧流体側に連通されると共に高圧流体側とは摺動面Sの平滑部により隔離され、かつ、相手摺動面との相対摺動により流体を高圧流体側に排出する角度を有する第二のポンピング溝11が設けられる。また、第一のポンピング溝10の低圧流体側端部10′と第二のポンピング溝11の高圧流体側端部11′とは近接して配設される。
なお、ここでいう「近接」については、後に説明する。
このように、第一のポンピング溝10が第二のポンピング溝11より周方向の上流側に位置するように配設されることにより、第一のポンピング溝により発生する負圧を下流側の第二のポンピング溝による動圧発生効果で効率よく緩和し、蒸気性キャビテーションの発生を防止できる。また、第一のポンピング溝10の低圧流体側端部10′と第二のポンピング溝11の高圧流体側端部11′とは径方向において離間するように形成されることにより、静止漏れ防止に必要となる密封面幅は、第一のポンピング溝10の低圧流体側端部10′と第二ポンピング溝11の高圧流体側端部11′との間とすることができ、静止時に安定した密封性を得ることができる。
なお、上記の「第一のポンピング溝10の低圧流体側端部10′と第二のポンピング溝11の高圧流体側端部11′とは近接して配設される。」における「近接」とは、第一のポンピング溝10aと第二のポンピング溝11aとが流体力学的に影響を及ぼすような近い位置に配設されることを意味する。
なお、図4において、実施例1の符号と同じ符号は実施例1と同じ部材を示しており、重複する説明は省略する。
このように、第一のポンピング溝10と第二のポンピング溝11とは半径方向において略同一の線上に配設されることにより、第一のポンピング溝の負圧起点部の圧力を、第二のポンピング溝により発生する動圧によって上昇させ、蒸気性キャビテーションの発生を抑制することができる。また、第一のポンピング溝10の低圧流体側端部10′と第二のポンピング溝11の高圧流体側端部11′とは、径方向において離間するように形成されることにより、静止漏れ防止に必要となる密封面幅は、第一のポンピング溝の内周側端部と第二ポンピング溝の外周側端部の間とすることができ、静止時に安定した密封性を得ることができる。
なお、図5において、実施例1の符号と同じ符号は実施例1と同じ部材を示しており、重複する説明は省略する。
なお、図6において、実施例1の符号と同じ符号は実施例1と同じ部材を示しており、重複する説明は省略する。
なお、図7において、実施例4の符号と同じ符号は実施例4と同じ部材を示しており、重複する説明は省略する。
本実施例の正圧発生機構12は、レイリーステップ機構14から構成されるが、各グルーブ16は、高圧流体側において、直接、高圧流体側と連通され、また、上流側は半径方向溝15と連通され、下流側は摺動面Sの密封面との間にステップ(段部)17が形成されている。
2 スリーブ
3 回転環
4 ハウジング
5 固定環
6 コイルドウェーブスプリング
7 ベローズ
10 第一のポンピング溝
10′ 低圧流体側端部
11 第二のポンピング溝
11′ 高圧流体側端部
12 正圧発生機構
13 圧力開放溝
14 レイリーステップ機構
15 半径方向溝
16 グルーブ
17 ステップ(段部)
S 摺動面
Claims (8)
- 一対の摺動部品の互いに相対摺動する一方側の摺動面には、高圧流体側に連通されると共に低圧流体側とは密封面により隔離され、かつ、相手側摺動面との相対摺動により流体を高圧流体側に排出する角度を有する第一のポンピング溝が設けられ、さらに、低圧流体側に連通されると共に高圧流体側とは密封面により隔離され、かつ、相手側摺動面との相対摺動により流体を高圧流体側に排出する角度を有する第二のポンピング溝が設けられ、前記第一のポンピング溝の低圧流体側端部と前記第二のポンピング溝の高圧流体側端部とが近接して配設されることを特徴とする摺動部品。
- 前記第一のポンピング溝及び前記第二のポンピング溝は、スパイラル形状に形成されることを特徴とする請求項1記載の摺動部品。
- 前記第一のポンピング溝及び前記第二のポンピング溝は周方向に複数設けられ、前記第一のポンピング溝及び第二のポンピング溝の各々は対をなすように配設されることを特徴とする請求項1または2記載の摺動部品。
- 前記第一のポンピング溝及び第二のポンピング溝の対をなす各々のポンピング溝において、前記第一のポンピング溝が前記第二のポンピング溝より周方向の上流側に位置するように配設されることを特徴とする請求項3記載の摺動部品。
- 前記第一のポンピング溝及び第二のポンピング溝の対をなす各々のポンピング溝において、前記第一のポンピング溝と前記第二のポンピング溝とは半径方向において略同一の線上に配設されることを特徴とする請求項3記載の摺動部品。
- 前記第一のポンピング溝及び第二のポンピング溝の対をなす各々のポンピング溝において、前記第一のポンピング溝の低圧流体側端部と前記第二のポンピング溝の高圧流体側端部とは径方向において離間するように配設されることを特徴とする請求項4または請求項5に記載の摺動部品。
- 前記第一のポンピング溝及び第二のポンピング溝の対をなす各々のポンピング溝において、前記第一のポンピング溝の低圧流体側端部と前記第二のポンピング溝の高圧流体側端部とは径方向において重複するように形成されることを特徴とする請求項4記載の摺動部品。
- 前記第一のポンピング溝より高圧流体側の摺動面には、正圧発生機構が設けられると共に、前記第一のポンピング溝と前記正圧発生機構との間に位置するように圧力開放溝が設けられ、前記正圧発生機構及び前記圧力開放溝は高圧流体側と連通されており、前記第一のポンピング溝の高圧流体側端部は前記圧力開放溝に連通されていることを特徴とする請求項1ないし7のいずれか1項に記載の摺動部品。
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JPWO2021044904A1 (ja) * | 2019-09-02 | 2021-03-11 | ||
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WO2024128135A1 (ja) * | 2022-12-15 | 2024-06-20 | Nok株式会社 | シールリング及び密封構造 |
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US20180223997A1 (en) | 2018-08-09 |
EP2940353B1 (en) | 2020-01-15 |
US20150184752A1 (en) | 2015-07-02 |
JPWO2014103631A1 (ja) | 2017-01-12 |
EP2940353A4 (en) | 2016-07-13 |
AU2013367600A1 (en) | 2015-07-23 |
CN104520617A (zh) | 2015-04-15 |
US20180223998A1 (en) | 2018-08-09 |
US10648569B2 (en) | 2020-05-12 |
AU2013367600B2 (en) | 2016-11-10 |
EP2940353A1 (en) | 2015-11-04 |
JP6161632B2 (ja) | 2017-07-12 |
US9964215B2 (en) | 2018-05-08 |
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