sliding parts

Abstract

A sliding component is provided that allows sliding surfaces to slide smoothly against each other in either forward or reverse rotational direction. A sliding part (10) (20) having a pair of sliding surfaces (11) and (21) arranged opposite to a location that rotates relative to the rotating machine when the rotating machine is driven, wherein on one sliding surface (11), a first dynamic pressure generating groove (13) extending in one circumferential direction in communication with the space (S1) on one side of the inner diameter side space (S1) and the outer diameter side space (S2), a second dynamic pressure generating groove (16) extending in the other circumferential direction, and a communication groove (17) communicating with the space (S1) on one side are provided, and the communication groove (17) has an annular groove (19) and a communication groove (18) communicating with the annular groove (19) and the space (S1) on one side, and the second dynamic pressure generating groove (16) is arranged on the side of the space (S1) rather than the annular groove (19) and also communicates with the annular groove (19).

Description

Technology Field

[0001] The present invention relates to a sliding component used in a shaft or bearing. Background Technology

[0002] Mechanical seals are known as sliding components that prevent leakage of a sealed fluid around a rotating shaft in rotating machinery, for example, consisting of a pair of annular sliding rings that rotate relative to each other and slide against each other. In such mechanical seals, there is a recent demand for a reduction in energy lost due to sliding for reasons such as environmental measures, and there are types in which dynamic pressure generating grooves are provided on the sliding surfaces of the sliding rings.

[0003] For example, the mechanical seal shown in Patent Document 1 has a plurality of dynamic pressure generating grooves provided in the circumferential direction, which are in communication with the space on the fluid side to be sealed, which is on the outer diameter side of the sliding surface of one sliding ring, and extend in the inner diameter direction while inclined in one circumferential direction.

[0004] When the sliding ring rotates relative to the seal, the sealing fluid is concentrated from the space on the sealing fluid side toward the closed end of the dynamic pressure generating groove, thereby generating static pressure and causing the sliding surfaces to separate. At the same time, a fluid film of the sealing fluid is formed between the sliding surfaces, thereby improving lubricity and enabling the sliding surfaces to slide smoothly. Prior art literature

[0005] International Publication No. 2020 / 162025 (page 14, Fig. 10) The problem to be solved

[0006] Depending on the type of rotating machine to which a mechanical seal such as that of Patent Document 1 is applied, the rotation direction of the sliding ring may be switched according to the situation, so a mechanical seal capable of responding to the relative rotation direction of both sides of the sliding ring was desired. However, in the mechanical seal of Patent Document 1, while lubrication can be improved by the static pressure generated by the dynamic pressure generating groove during the relative rotation of the sliding ring, the relative rotation in the reverse direction of the sliding ring is not taken into account, and since static pressure cannot be generated in the dynamic pressure generating groove during the relative rotation in the reverse direction of the sliding ring, lubrication between the sliding surfaces cannot be improved.

[0007] The present invention was made by focusing on these problems and aims to provide a sliding component capable of smoothly sliding sliding surfaces together in either forward or reverse rotational direction. means of solving the problem

[0008] To solve the above problem, the sliding part of the present invention is,

[0009] A sliding component having a pair of sliding surfaces arranged opposite to a relative rotating location when the rotating machine is driven,

[0010] On one sliding surface, a first dynamic pressure generating groove extending in one circumferential direction in communication with one side of the inner diameter space and one side of the outer diameter space, a second dynamic pressure generating groove extending in the other circumferential direction, and a conductive groove communicating with the one side space are provided.

[0011] The second dynamic pressure generating groove is positioned on the space side on one side of the conductive groove and is also in communication with the conductive groove.

[0012] According to this, during relative rotation in one circumferential direction while driving a rotating machine, the fluid in one space is supplied from the closed end of the first dynamic pressure generating groove to the sliding surface. Additionally, during relative rotation in the other circumferential direction while driving a rotating machine, the fluid in one space is supplied through a conductive groove from the closed end of the second dynamic pressure generating groove to the sliding surface. Therefore, the lubrication between the sliding surfaces is good regardless of the relative rotation direction.

[0013] Between the first dynamic pressure generating groove and the second dynamic pressure generating groove, a land extending in the circumferential direction may be provided.

[0014] According to this, since the static pressure generated by the first dynamic pressure generating groove and the second dynamic pressure generating groove is generated in the same land, the separation state between the sliding surfaces becomes approximately the same regardless of the relative rotation direction.

[0015] The closed end of the first dynamic pressure generating groove and the closed end of the second dynamic pressure generating groove may face each other in the radial direction.

[0016] According to this, the fluid supplied from one dynamic pressure generating groove to the sliding surface is efficiently recovered in the other dynamic pressure generating groove positioned oppositely.

[0017] The above-mentioned connecting groove may have an annular groove and a connecting groove that connects the annular groove with the space on one side.

[0018] According to this, the annular groove can reliably recover fluid flowing from one side of the space to the other side between the sliding surfaces. In addition, since the annular groove can store a large amount of fluid, fluid is reliably supplied to the second dynamic pressure generating groove.

[0019] The first dynamic pressure generating groove and the second dynamic pressure generating groove may be spiral grooves.

[0020] According to this, the first dynamic pressure generating groove and the second dynamic pressure generating groove can be arranged densely in the circumferential direction.

[0021] The above communication groove may be extended so as not to intersect the above first dynamic pressure generating groove and the above second dynamic pressure generating groove.

[0022] According to this, the connecting groove does not interfere with the generation of dynamic pressure in the first dynamic pressure generating groove and the second dynamic pressure generating groove.

[0023] A third dynamic pressure generating groove may be provided on the space side other than the conductive groove on one of the sliding surfaces above.

[0024] According to this, since a third dynamic pressure generating groove is provided in the space on the other side of the aforementioned conductive groove, the lubricity or sealing performance between the sliding surfaces is further enhanced by the dynamic pressure generated in the third dynamic pressure generating groove.

[0025] The above third dynamic pressure generating groove may be a curved groove connected to the above conductive groove.

[0026] According to this, the state of the dynamic pressure of the third dynamic pressure generating groove changes depending on the relative rotation direction of the sliding surface. Brief explanation of the drawing

[0027] FIG. 1 is a cross-sectional view showing an example of a mechanical seal in Example 1 of the present invention. FIG. 2 is a view of the sliding surface of the static sealing ring in Example 1 from the axial direction. FIG. 3 is an enlarged view of the sliding surface of the stationary sealing ring during forward rotation of the rotary sealing ring in Example 1, viewed from the axial direction. FIG. 4 is an enlarged view of the sliding surface of the stop seal ring during reverse rotation of the rotary seal ring in Example 1, viewed from the axial direction. FIG. 5 is a view of the sliding surface of the stop seal ring in Example 2 of the present invention seen from the axial direction. FIG. 6 is a view of the sliding surface of the stop seal ring in Example 3 of the present invention seen from the axial direction. FIG. 7 is an enlarged view of the sliding surface of the stationary seal ring during forward rotation of the rotary seal ring in Example 3, viewed from the axial direction. FIG. 8 is an enlarged view of the sliding surface of the stop seal ring during reverse rotation of the rotary seal ring in Example 3, viewed from the axial direction. FIG. 9 is a view of the sliding surface of the stop seal ring in Example 4 of the present invention seen from the axial direction. FIG. 10 is a view of the sliding surface of the stop seal ring in Example 5 of the present invention seen from the axial direction. FIG. 11 is an enlarged view of the sliding surface of the stationary sealing ring during forward rotation of the rotary sealing ring in Example 5, viewed from the axial direction. FIG. 12 is an enlarged view of the sliding surface of the stop seal ring during reverse rotation of the rotary seal ring in Example 5, viewed from the axial direction. FIG. 13 is an enlarged view of the sliding surface of the stop seal ring in Example 6 of the present invention, viewed from the axial direction. FIG. 14 is an enlarged view of the sliding surface of the stop seal ring in Example 7 of the present invention, viewed from the axial direction. FIG. 15 is an enlarged view of the sliding surface of the stop seal ring of Example 1, a variation of Example 1, viewed from the axial direction. FIG. 16 is an enlarged view of the sliding surface of the stop seal ring of Example 2, a variation of Example 1, viewed from the axial direction. FIG. 17 is an enlarged view of the sliding surface of the stop seal ring of Example 3, a variation of Example 1, viewed from the axial direction. Specific details for implementing the invention

[0028] A form for implementing a sliding part according to the present invention is described below based on an example.

[0029] Example 1

[0030] A mechanical seal as a sliding part according to Example 1 will be described with reference to FIGS. 1 to 4. In addition, in this embodiment, an atmosphere (A) exists in the inner space (S1) of the mechanical seal and a fluid to be sealed (F) exists in the outer space (S2). The inner diameter side of the sliding ring constituting the mechanical seal is described as the leakage side (low pressure side) as the other space, and the outer diameter side is described as the fluid to be sealed side (high pressure side) as the one space. Additionally, for convenience of explanation, dots may be added to grooves formed on the sliding surface in the drawings.

[0031] The mechanical seal for an automobile shown in FIG. 1 is an inside type that seals the fluid to be sealed (F) in the outer space (S2) that is about to leak from the outer diameter side of the sliding surface toward the inner diameter side, and the inner space (S1) is open to the atmosphere (A). In addition, in this embodiment, the fluid to be sealed (F) is a high-pressure liquid, and the atmosphere (A) is a gas with a lower pressure than the fluid to be sealed (F) is exemplified.

[0032] The mechanical seal is mainly composed of a rotating seal ring (20) as a sliding ring on one side and a stationary seal ring (10) as a sliding ring on the other side. The rotating seal ring (20) is an annular shape and is provided in a state where it can rotate together with the rotation axis (1) through a sleeve (2) on the rotation axis (1). The stationary seal ring (10) is an annular shape and is provided in a state where it can move in the axial direction and also in a non-rotating state on a seal cover (5) fixed to the housing (4) of the device to be mounted. The stationary seal ring (10) is axially supported by an elastic member (7). The sliding surface (11) of the stationary seal ring (10) and the sliding surface (21) of the rotating seal ring (20) are arranged to slide closely together. In addition, the sliding surface (21) of the rotating seal ring (20) is a flat surface, and no concave portions such as grooves are provided on this flat surface.

[0033] The stationary sealing ring (10) and the rotating sealing ring (20) are typically formed from SiC (hard material) or a combination of SiC (hard material) and carbon (soft material), but are not limited thereto; any sliding material used as a sliding material for mechanical seals can be applied. Furthermore, as SiC, materials consisting of two or more phases with different components and compositions, such as sintered bodies made of boron, aluminum, carbon, etc. as sintering aids, are used, for example, SiC with dispersed graphite particles, reaction-sintered SiC consisting of SiC and Si, SiC-TiC, SiC-TiN, etc. As for carbon, materials such as carbon mixed with carbonaceous and graphite materials, resin-molded carbon, and sintered carbon can be used. In addition, other than the above sliding materials, metal materials, resin materials, surface modification materials (coating materials), composite materials, etc. can also be applied.

[0034] As shown in FIGS. 2 to 4, the rotating seal ring (20) is configured to slide relative to the stationary seal ring (10) in a clockwise direction as indicated by the solid arrow, or in a counterclockwise direction as indicated by the dashed arrow. Hereinafter, the direction of the solid arrow is described as the forward rotation direction of the rotating seal ring (20), and the direction of the dashed arrow is described as the reverse rotation direction of the rotating seal ring (20).

[0035] On the sliding surface (11) of the stop seal ring (10), a plurality of first dynamic pressure generating grooves (13), a plurality of second dynamic pressure generating grooves (16), and one conductive groove (17) are provided. The conductive groove (17) is composed of a plurality of connecting grooves (18) and an annular groove (19).

[0036] The first dynamic pressure generating groove (13) is arranged in a plurality (33 in this embodiment) in a circumferential direction on the outer diameter side of the sliding surface (11). The first dynamic pressure generating groove (13) has an end (13A) on the outer diameter side communicating with the outer space (S2), and extends in one direction in the circumferential direction, that is, in the forward rotation direction of the rotation seal ring (20), based on the communication point. Specifically, the first dynamic pressure generating groove (13) is a spiral groove that extends in an arc shape while inclined with a clockwise component from the outer diameter side toward the inner diameter side. In addition, the end (13B) on the inner diameter side of the first dynamic pressure generating groove (13) has a closed shape, that is, a closed end.

[0037] This first dynamic pressure generating groove (13) is formed with a constant depth in the elongation direction.

[0038] The second dynamic pressure generating groove (16) is arranged in a plurality (33 in this embodiment) in a circumferential direction on the outer diameter side of the annular groove (19). The second dynamic pressure generating groove (16) has an end (16A) on its inner diameter side communicating with the annular groove (19), and extends in the reverse rotation direction of the rotation seal ring (20), that is, in the other circumferential direction, based on the point of communication. Specifically, the second dynamic pressure generating groove (16) is a spiral groove that extends in an arc shape while inclined with a counterclockwise component from the inner diameter side toward the outer diameter side. In addition, the end (16B) on the outer diameter side of the second dynamic pressure generating groove (16) has a closed shape, that is, a closed end.

[0039] This second dynamic pressure generating groove (16) is formed with a constant depth in the elongation direction. In addition, in this embodiment, the depth of the second dynamic pressure generating groove (16) is the same depth as the depth of the first dynamic pressure generating groove (13).

[0040] In addition, the inner end (13B) of the first dynamic pressure generating groove (13) and the outer end (16B) of the second dynamic pressure generating groove (16) are positioned opposite each other in the diameter direction with the land (12A) described later sandwiched between them.

[0041] The communication grooves (18) are arranged in a plurality (three in this embodiment) evenly in the circumferential direction on the outer diameter side of the sliding surface (11). The communication grooves (18) communicate with the outer space (S2) and extend in an arc shape while inclined with a clockwise component from the outer diameter side toward the inner diameter side.

[0042] In detail, the communication groove (18) extends approximately parallel to the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) when viewed from the axial direction. In other words, the communication groove (18) extends so as not to intersect the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16).

[0043] Additionally, the communication groove (18) is formed to be longer in the elongation direction than the first dynamic pressure generating groove (13). Between the communication grooves (18) adjacent to each other in the circumferential direction, a predetermined number (11 each) of the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) are arranged.

[0044] This communication groove (18) is formed with a constant depth in the elongation direction. Additionally, the depth of the communication groove (18) is formed deeper than the depth of the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16).

[0045] The annular groove (19) is formed in an annular shape when viewed from the axial direction, and the inner diameter end of each connecting groove (18) is in communication with the annular groove (19). In other words, the annular groove (19) is in communication with the outer space (S2) through each connecting groove (18).

[0046] This annular groove (19) is formed with a constant depth in the circumferential direction. In addition, in this embodiment, the depth of the annular groove (19) is the same as the depth of the connecting groove (18).

[0047] In addition, the portion of the sliding surface (11) other than the first dynamic pressure generating groove (13), the second dynamic pressure generating groove (16), the connecting groove (18), and the annular groove (19) is a land (12) having a flat surface arranged on the same plane. The flat surface of this land (12) functions as a sliding surface that substantially slides with the sliding surface (21) of the rotating sealing ring (20).

[0048] In detail, the land (12) has a land between the first dynamic pressure generating grooves (13) adjacent in the circumferential direction, a land between the first dynamic pressure generating grooves (13) adjacent in the circumferential direction and the communication groove (18), a land between the second dynamic pressure generating grooves (16) adjacent in the circumferential direction, a land between the second dynamic pressure generating grooves (16) adjacent in the circumferential direction and the communication groove (18), a land (12A) extending in the circumferential direction disposed between the first dynamic pressure generating grooves (13) and the second dynamic pressure generating grooves (16) separated in the radial direction, and an annular land on the inner diameter side of the annular groove (19), and each of these lands is arranged in a planar shape to form a flat surface of the land (12).

[0049] Next, the operation during the relative rotation of the stationary seal ring (10) and the rotating seal ring (20) in the forward direction is explained using FIG. 3.

[0050] First, when the rotating sealing ring (20) is stationary and not rotating, the fluid to be sealed (F) flows into the first dynamic pressure generating groove (13) from the opening of the end (13A) and simultaneously flows into the second dynamic pressure generating groove (16) through the communication groove (18) and the annular groove (19) from the opening on the outer diameter side of the communication groove (18). In addition, because the stationary sealing ring (10) is pushed toward the rotating sealing ring (20) by the elastic member (7), the sliding surfaces (11, 21) are in contact with each other, so there is almost no leakage of the fluid to be sealed (F) between the sliding surfaces (11, 21) into the inner space (S1).

[0051] As shown in FIG. 3, when the rotating seal ring (20) rotates relative to the stationary seal ring (10) in the forward direction, the fluid to be sealed (F) in the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) moves in the forward direction of rotation of the rotating seal ring (20) by shearing with the sliding surface (21).

[0052] Specifically, within the first dynamic pressure generating groove (13), the fluid to be sealed (F) moves from the opening of the outer diameter end (13A) toward the inner diameter end (13B) as indicated by the arrow (F1). Accordingly, the pressure increases at the end (13B) and in the vicinity thereof. That is, static pressure is generated at the end (13B) of the first dynamic pressure generating groove (13) and at the land (12A) in the vicinity thereof.

[0053] Additionally, the sliding surfaces (11, 21) are slightly separated by the force of the static pressure generated at the end (13B) of the first dynamic pressure generating groove (13) and the land (12A) nearby therefrom (not shown). Specifically, the absolute value of the static pressure generated by the first dynamic pressure generating groove (13) is greater than the absolute value of the negative pressure generated by the second dynamic pressure generating groove (16) described later.

[0054] Accordingly, the sealing fluid (F) within the first dynamic pressure generating groove (13) flows between the sliding surfaces (11, 21), mainly as indicated by the arrow (F2). By interposing the sealing fluid (F) between the sliding surfaces (11, 21) in this way, lubricity is improved even during low-speed rotation, thereby suppressing wear between the sliding surfaces (11, 21). In addition, since the floating distance between the sliding surfaces (11, 21) is small, the sealing fluid (F) leaking into the outer space (S2) is small.

[0055] In addition, at this time, since the sliding surfaces (11, 21) are slightly separated, the fluid to be sealed (F) in the connecting groove (18) and the annular groove (19) also flows into the space between the sliding surfaces (11, 21). Because of this, the fluid to be sealed (F) flows efficiently into the space between the sliding surfaces (11, 21).

[0056] Meanwhile, within the second dynamic pressure generating groove (16), the fluid to be sealed (F) moves from the outer diameter end (16B) toward the inner diameter end (16A) as indicated by the arrow (F3). Accordingly, the fluid pressure near the end (16B) becomes relatively lower than the surrounding fluid pressure. In other words, a relative negative pressure is generated near the end (16B), and the fluid to be sealed (F) between the sliding surfaces (11, 21) is sucked into the second dynamic pressure generating groove (16) as indicated by the arrow (F4).

[0057] The sealed fluid (F) sucked into the second dynamic pressure generating groove (16) is recovered into the annular groove (19). The annular groove (19) is connected to the outside space (S2) through the connecting groove (18), allowing the sealed fluid (F) to be discharged. Because of this, when more sealed fluid (F) is recovered than the amount that can be stored in the annular groove (19), the excess sealed fluid (F) is returned to the outside space (S2).

[0058] Next, the operation during the reverse relative rotation of the stationary seal ring (10) and the rotating seal ring (20) will be explained using FIG. 4.

[0059] As shown in FIG. 4, when the rotating seal ring (20) rotates relative to the stationary seal ring (10) in the reverse direction, the fluid to be sealed (F) in the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) moves in the reverse rotation direction of the rotating seal ring (20) by shearing with the sliding surface (21).

[0060] Specifically, within the first dynamic pressure generating groove (13), the fluid to be sealed (F) moves from the end (13B) on the inner diameter side toward the opening of the end (13A) on the outer diameter side, as indicated by the arrow (F1'). Accordingly, the fluid pressure near the end (13B) becomes relatively lower than the surrounding fluid pressure. In other words, a relative negative pressure is generated near the end (13B), and the fluid to be sealed (F) between the sliding surfaces (11, 21) is sucked into the first dynamic pressure generating groove (13), as indicated by the arrow (F2').

[0061] The sealed fluid (F) sucked into the first dynamic pressure generating groove (13) is returned to the outside space (S2) through the opening of the outer diameter end (13A).

[0062] Meanwhile, within the second dynamic pressure generating groove (16), the sealed fluid (F) moves from the inner end (16A) toward the outer end (16B) as indicated by the arrow (F3'). Accordingly, the pressure increases at the end (16B) and in the vicinity thereof. That is, static pressure is generated at the end (16B) of the second dynamic pressure generating groove (16) and at the land (12A) in the vicinity thereof.

[0063] Additionally, the sliding surfaces (11, 21) are slightly separated by the force of the static pressure generated at the end (16B) of the second dynamic pressure generating groove (16) and the land (12A) near it (not shown). Specifically, the absolute value of the static pressure generated by the second dynamic pressure generating groove (16) is greater than the absolute value of the negative pressure generated by the first dynamic pressure generating groove (13) mentioned above. Accordingly, the fluid to be sealed (F) within the second dynamic pressure generating groove (16) flows between the sliding surfaces (11, 21), mainly as indicated by the arrow (F4').

[0064] As described above, when the rotating sealing ring (20) rotates relative to the stationary sealing ring (10) in the forward direction, the fluid to be sealed (F) in the outer space (S2) is supplied from the end (13B) of the first dynamic pressure generating groove (13) to the sliding surfaces (11, 21). Additionally, when the rotating sealing ring (20) rotates relative to the stationary sealing ring (10) in the reverse direction, the fluid to be sealed (F) in the outer space (S2) is supplied through the connecting groove (18) and the annular groove (19) from the end (16B) of the second dynamic pressure generating groove (16) to the sliding surfaces (11, 21). Because of this, the lubricity between the sliding surfaces (11, 21) is good regardless of the relative rotation direction.

[0065] Additionally, when the rotating seal ring (20) rotates relative to the stationary seal ring (10) in the forward direction, a relative negative pressure is generated near the end (16B) of the second dynamic pressure generating groove (16), and the fluid to be sealed (F) between the sliding surfaces (11, 21) is sucked in. Also, when the rotating seal ring (20) rotates relative to the stationary seal ring (10) in the reverse direction, a relative negative pressure is generated near the end (13B) of the first dynamic pressure generating groove (13), and the fluid to be sealed (F) between the sliding surfaces (11, 21) is sucked in. Because of this, leakage of the fluid to be sealed (F) into the inner space (S1) is suppressed.

[0066] Additionally, a land (12A) extending in the circumferential direction is provided between the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16). Accordingly, since the static pressure generated at the end (13B) of the first dynamic pressure generating groove (13) and the end (16B) of the second dynamic pressure generating groove (16) is generated at the same land (12A), the separation state between the sliding surfaces (11, 21) is approximately the same regardless of the relative rotational direction.

[0067] Additionally, the end (13B) of the first dynamic pressure generating groove (13) and the end (16B) of the second dynamic pressure generating groove (16) are positioned opposite each other in the radial direction with the land (12A) in between. Accordingly, when the rotating sealing ring (20) rotates relative to the stationary sealing ring (10) in the forward direction, the sealing fluid (F) supplied from the end (13B) of the first dynamic pressure generating groove (13) to the sliding surface (11, 21) is efficiently recovered at the end (16B) of the second dynamic pressure generating groove (16) positioned oppositely. Additionally, when the rotating sealing ring (20) rotates relative to the stationary sealing ring (10) in the reverse direction, the sealing fluid (F) supplied between the sliding surfaces (11, 21) from the end (16B) of the second dynamic pressure generating groove (16) is efficiently recovered at the end (13B) of the first dynamic pressure generating groove (13) positioned oppositely. Accordingly, the static pressure is suppressed from becoming excessively high regardless of the speed of relative rotation.

[0068] Additionally, the communication groove (17) is composed of an annular groove (19) and a communication groove (18) that communicates the annular groove (19) with the outer space (S2). Accordingly, since the annular groove (19) is positioned on the inner space (S1) side rather than the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16), the sealing fluid (F) flowing between the sliding surfaces (11, 21) from the outer space (S2) toward the inner space (S1) can be reliably recovered. Furthermore, since the annular groove (19) can store a large amount of sealing fluid (F), the sealing fluid (F) is reliably supplied to the second dynamic pressure generating groove (16).

[0069] Additionally, the connecting grooves (18) are provided in multiple directions around the annular groove (19). By doing so, the fluid to be sealed (F) is efficiently introduced or drawn out from the multiple connecting grooves (18).

[0070] In addition, since a large amount of sealing fluid (F) exists in the deep groove (18), the sealing fluid (F) is easily supplied between the sliding surfaces (11, 21) that are slightly separated by relative rotation.

[0071] Additionally, the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) are spiral grooves that are inclined in the circumferential direction and extend in the radial direction. Accordingly, the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) can be arranged densely in the circumferential direction. In other words, the design freedom of the stop sealing ring (10) is high.

[0072] Additionally, the connecting groove (18) is extended so as not to intersect the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16). For example, since the connecting groove (18) is positioned to cross the land (12A) between the end (13B) of the first dynamic pressure generating groove (13) and the end (16B) of the second dynamic pressure generating groove (16), it does not interfere with the generation of dynamic pressure in the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16).

[0073] Additionally, since the connecting groove (18) extends parallel to the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16), the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) can be arranged more densely in the circumferential direction.

[0074] Example 2

[0075] Next, a mechanical seal as a sliding part according to Example 2 will be described with reference to FIG. 5. In addition, descriptions of configurations identical to or overlapping with those in Example 1 will be omitted.

[0076] In the mechanical seal of the present embodiment 2, the stop seal ring (210) has a different configuration of the conductive groove from the stop seal ring (10) of embodiment 1, and the rest of the configuration is the same as the stop seal ring (10) of embodiment 1.

[0077] As shown in FIG. 5, the conduction groove (217) of the stop seal ring (210) is composed of a communication groove (218) and an arc groove (219). The arc groove (219) extends in a circumferential direction in a clockwise direction from the inner diameter end of the communication groove (218) in a concentric shape with the stop seal ring (210). A plurality of these conduction grooves (217) are provided in the circumferential direction (three in this embodiment).

[0078] The end (16A) on the inner diameter side of each second dynamic pressure generating groove (16) is in communication with the arc groove (219).

[0079] Example 3

[0080] Next, a mechanical seal as a sliding part according to Example 3 will be described with reference to FIGS. 6 to 8. In addition, descriptions of configurations identical to or overlapping with those of Example 1 will be omitted.

[0081] In the mechanical seal of the present embodiment 3, the stop seal ring (310) has a configuration of the first dynamic pressure generating groove and the second dynamic pressure generating groove that is different from the stop seal ring (10) of embodiment 1, and the rest of the configuration is the same as the stop seal ring (10) of embodiment 1.

[0082] As shown in FIG. 6, the sliding surface (311) of the stop seal ring (310) is provided with a plurality of first dynamic pressure generating mechanisms (313), a plurality of communication grooves (18), annular grooves (19), and a plurality of second dynamic pressure generating mechanisms (316).

[0083] The first dynamic pressure generating mechanism (313) is composed of a first deep groove (313A) and a first Rayleigh step (313B) as a first dynamic pressure generating groove.

[0084] The first core (313A) has an end on the outer diameter side communicating with the outer space (S2) and extending in the inner diameter direction. The first core (313A) is formed slightly shallower than the communicating groove (18) and the annular groove (19).

[0085] The first Rayleigh step (313B) extends circumferentially in a clockwise direction from the inner diameter side of the first core (313A) in a concentric shape with the stop seal ring (310). The first Rayleigh step (313B) is formed shallower than the first core (313A).

[0086] The second dynamic pressure generating mechanism (316) is composed of a second deep groove (316A) and a second Rayleigh step (316B) as a second dynamic pressure generating groove.

[0087] The second core (316A) has an end on the inner side communicating with the annular groove (19) and extends in the outer direction. The second core (316A) is formed slightly shallower than the communicating groove (18) and the annular groove (19). Additionally, the second core (316A) is formed to the same depth as the first core (313A).

[0088] The second Rayleigh step (316B) extends circumferentially in a counterclockwise direction from the outer diameter side of the second core (316A) in a concentric shape with the stop seal ring (310). The second Rayleigh step (316B) is formed shallower than the second core (316A). Additionally, the second Rayleigh step (316B) is formed to the same depth as the first Rayleigh step (313B).

[0089] In addition, in the present embodiment 3, the first core (313A) and the second core (316A) are shown as being formed slightly shallower than the connecting groove (18) and the annular groove (19), but they may be formed at the same depth. Also, the first core (313A) and the second core (316A) may be formed at the same depth as the first Rayleigh step (313B) and the second Rayleigh step (316B).

[0090] Additionally, in the present embodiment 3, the first deep groove (313A) and the second deep groove (316A) are exemplified as being formed at the same depth, but they may be formed at different depths. Also, in the present embodiment 3, the first Rayleigh step (313B) and the second Rayleigh step (316B) are exemplified as being formed at the same depth, but they may be formed at different depths.

[0091] Next, the operation during the relative rotation of the stationary seal ring (310) and the rotating seal ring (20) (see FIG. 1) in the forward direction will be explained using FIG. 7.

[0092] As shown in FIG. 7, when the rotating seal ring (20) rotates relative to the stationary seal ring (310) in the forward direction, the fluid to be sealed (F) in the first dynamic pressure generating mechanism (313) and the second dynamic pressure generating mechanism (316) moves in the forward direction of rotation of the rotating seal ring (20) by shearing with the sliding surface (21).

[0093] Specifically, within the first dynamic pressure generating mechanism (313), the fluid to be sealed (F) in the first core (313A) moves from the connecting portion between the first core (313A) and the first Rayleigh step (313B) toward the closed end (313a) of the first Rayleigh step (313B) as indicated by the arrow (F10). Accordingly, static pressure is generated at the closed end (313a) of the first Rayleigh step (313B) and in the vicinity thereof, causing the sliding surfaces (311, 21) to separate, and at the same time, the fluid to be sealed (F) flows between the sliding surfaces (311, 21) as indicated by the arrow (F11).

[0094] Also, at this time, within the second dynamic pressure generating mechanism (316), the fluid to be sealed (F) in the second Rayleigh step (316B) moves toward the second core (316A) as indicated by the arrow (F12). Accordingly, a relative negative pressure is generated near the closed end (316a) of the second Rayleigh step (316B), and the fluid to be sealed (F) between the sliding surfaces (311, 21) is sucked into the second Rayleigh step (316B) as indicated by the arrow (F13).

[0095] Next, the operation during the reverse relative rotation of the stationary seal ring (310) and the rotating seal ring (20) (see FIG. 1) will be explained using FIG. 8.

[0096] As shown in FIG. 8, when the rotating seal ring (20) rotates relative to the stationary seal ring (310) in the reverse direction, the fluid to be sealed (F) in the first dynamic pressure generating mechanism (313) and the second dynamic pressure generating mechanism (316) moves in the reverse rotation direction of the rotating seal ring (20) by shearing with the sliding surface (21).

[0097] Specifically, within the first dynamic pressure generating mechanism (313), the fluid to be sealed (F) in the first Rayleigh step (313B) moves toward the first deep hole (313A) as indicated by the arrow (F10'). Accordingly, a relative negative pressure is generated at the closed end (313a) of the first Rayleigh step (313B) and in the vicinity thereof, causing the fluid to be sealed (F) between the sliding surfaces (311, 21) to be sucked into the first Rayleigh step (313B) as indicated by the arrow (F11').

[0098] Also, at this time, within the second dynamic pressure generating mechanism (316), the fluid to be sealed (F) in the second core (316A) moves from the connecting portion between the second core (316A) and the second Rayleigh step (316B) toward the closed end (316a) of the second Rayleigh step (316B) as indicated by the arrow (F12'). Accordingly, static pressure is generated at the closed end (316a) of the second Rayleigh step (316B) and in the vicinity thereof, causing the sliding surfaces (311, 21) to separate, and at the same time, the fluid to be sealed (F) flows into the space between the sliding surfaces (311, 21) as indicated by the arrow (F13').

[0099] In this way, in the stationary sealing ring (310) of the present embodiment 3, lubricity and sealing between the sliding surfaces (311, 21) can be achieved regardless of the relative rotational direction of the rotating sealing ring (20).

[0100] Example 4

[0101] Next, a mechanical seal as a sliding part according to Example 4 will be described with reference to FIG. 9. In addition, descriptions of configurations identical to or overlapping with those in Example 1 will be omitted.

[0102] As shown in FIG. 9, the mechanical seal of the present embodiment 4 is an outside-type seal in which a fluid to be sealed (F) exists in the inner space (S1) and an atmosphere (A) exists in the outer space (S2). In addition, in the present embodiment 4, the inner space (S1) functions as one side space and the outer space (S2) functions as the other side space.

[0103] In the mechanical seal of the present embodiment 4, the stop seal ring (410) is provided with a plurality of first dynamic pressure generating grooves (413), a plurality of communication grooves (418), an annular groove (419), and a plurality of second dynamic pressure generating grooves (416). The plurality of communication grooves (418) and the annular groove (419) form one conductive groove (417).

[0104] The first dynamic pressure generating groove (413) has an end (413B) on the inner diameter side communicating with the inner space (S1), and extends in one direction in the forward rotation direction of the rotation seal ring (20), that is, the circumferential direction, based on the communication point. Specifically, the first dynamic pressure generating groove (413) is a spiral groove that extends in an arc shape while inclined with a clockwise component from the inner diameter side toward the outer diameter side. In addition, the end (413A) on the outer diameter side of the first dynamic pressure generating groove (413) has a closed shape, that is, a closed end.

[0105] The communication groove (418) communicates with the inner space (S1) and extends in an arc shape while inclined with a clockwise component from the inner diameter side toward the outer diameter side.

[0106] The outer end of each communication groove (418) is in communication with the annular groove (419). In other words, the annular groove (419) is in communication with the inner space (S1) through each communication groove (418).

[0107] The second dynamic pressure generating groove (416) has an end (416B) on the outer diameter side that communicates with the annular groove (419), and extends in the reverse rotation direction of the rotation sealing ring (20), that is, in the other circumferential direction, based on the point of communication. Specifically, the second dynamic pressure generating groove (416) is a spiral groove that extends in an arc shape while inclined with a counterclockwise component from the outer diameter side toward the inner diameter side. In addition, the end (416A) on the inner diameter side of the second dynamic pressure generating groove (416) has a closed shape, that is, a closed end.

[0108] The mechanical seals of Examples 2 and 3 may also be outside types by placing the groove on the inner diameter side. In addition, Examples 4, 5, and 6 described later, and variations 1, 2, and 3 of Example 1 may also be outside types by placing the groove on the inner diameter side.

[0109] Example 5

[0110] Next, a mechanical seal as a sliding part according to Example 5 will be described with reference to FIGS. 10 to 12. In addition, descriptions of configurations identical to or overlapping with those in Example 1 will be omitted.

[0111] The stop seal ring (510) in the mechanical seal of this embodiment 5 is different from the stop seal ring (10) of embodiment 1 in that it is provided with a third dynamic pressure generating groove (530), and the rest of the configuration is the same as the stop seal ring (10) of embodiment 1.

[0112] As shown in FIG. 10, on the sliding surface (511) of the stop seal ring (510), a plurality of third dynamic pressure generating grooves (530) are provided in the circumferential direction at the inner diameter side of the annular groove (19), that is, at a location where the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) are not provided.

[0113] As shown in FIGS. 11 and 12, the third dynamic pressure generating groove (530) is a curved groove in which the outer diameter end communicates with the annular groove (19). In detail, the third dynamic pressure generating groove (530) has a first inclined groove portion (531) and a second inclined groove portion (532). The third dynamic pressure generating groove (530) is formed to a constant depth in the elongation direction. Additionally, the third dynamic pressure generating groove (530) is formed to the same depth as the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16), but it may be formed to a different depth.

[0114] The first inclined groove (531) is extended in the inner diameter direction while inclined in the reverse rotation direction of the rotating seal ring (20), that is, in the circumferential direction, based on the point of communication with the annular groove (19). The second inclined groove (532) is in communication with the end of the first inclined groove (531) on the inner diameter side and is extended in the inner diameter direction while inclined in the forward rotation direction of the rotating seal ring (20), that is, in the circumferential direction, based on the said point of communication.

[0115] This third dynamic pressure generating groove (530) has a corner portion (530a) formed by a side portion (531a) located in the reverse rotation direction that partitions the first inclined groove portion (531) and a side portion (532a) located in the reverse rotation direction that partitions the second inclined groove portion (532).

[0116] Additionally, one second inclined groove (532) is positioned on the inner diameter side of the corner portion (530a) of the third dynamic pressure generating groove (530) adjacent in the forward rotation direction. Additionally, the second inclined groove (532) is formed to have a longer length in the elongation direction than the first inclined groove (531). Furthermore, the closed end of the second inclined groove (532) is positioned on the forward rotation direction side than the corner portion (530a) of the third dynamic pressure generating groove (530) adjacent in the forward rotation direction.

[0117] Next, the operation during the forward relative rotation of the stationary seal ring (510) and the rotating seal ring (20) is explained using FIG. 11.

[0118] As shown in FIG. 11, when the rotating seal ring (20) rotates relative to the stationary seal ring (510) in the forward direction, the fluid to be sealed (F) moves within the first dynamic pressure generating groove (13) as indicated by the arrow (F1), and at the same time, the fluid to be sealed (F) within the first dynamic pressure generating groove (13) flows between the sliding surfaces (511, 21), mainly as indicated by the arrow (F2). Meanwhile, within the second dynamic pressure generating groove (16), the fluid to be sealed (F) moves as indicated by the arrow (F3), and at the same time, the fluid to be sealed (F) between the sliding surfaces (511, 21) is sucked into the second dynamic pressure generating groove (16) as indicated by the arrow (F4).

[0119] Also at this time, within the first inclined groove (531) of the third dynamic pressure generating groove (530), the fluid to be sealed (F) moves toward the annular groove (19) as indicated by the arrow (F5), and at the same time, within the second inclined groove (532), the fluid to be sealed (F) moves toward the closed end on the inner diameter side as indicated by the arrow (F6).

[0120] According to this, the fluid to be sealed (F) in the first inclined groove (531) moves toward the annular groove (19), and the fluid to be sealed (F) in the second inclined groove (532) is discharged between the sliding surfaces (511, 21). Because of this, the third dynamic pressure generating groove (530) becomes a relative negative pressure, and a cavitation region (C) is formed around the third dynamic pressure generating groove (530) in a circumferential direction (see the meshed portion of FIG. 11). Also, the meshed portion of FIG. 11 represents the cavitation region (C) and is illustrated with greater emphasis than the actual area.

[0121] In this way, since a cavitation region (C) is formed on the inner diameter side of the annular groove (19) in the sliding surface (511) of the stationary sealing ring (510), the fluid to be sealed (F) is prevented from moving toward the inner diameter side of the annular groove (19). Accordingly, leakage of the fluid to be sealed (F) into the inner space (S1) can be prevented, thereby additionally improving the sealing performance between the sliding surfaces (511, 21).

[0122] In addition, since the third dynamic pressure generating groove (530) has a component that extends in the radial direction, the radial width of the cavitation region (C) can be significantly increased, making it difficult for the sealed fluid (F) to leak into the inner space (S1).

[0123] Next, the operation during the reverse relative rotation of the stationary seal ring (510) and the rotating seal ring (20) will be explained using FIG. 12.

[0124] As shown in FIG. 12, when the rotating seal ring (20) rotates relative to the stationary seal ring (510) in the reverse direction, the fluid to be sealed (F) moves within the first dynamic pressure generating groove (13) as indicated by the arrow (F1'), and at the same time, the fluid to be sealed (F) between the sliding surfaces (511, 21) is sucked into the first dynamic pressure generating groove (13) as indicated by the arrow (F2'). Meanwhile, within the second dynamic pressure generating groove (16), the fluid to be sealed (F) moves as indicated by the arrow (F3'), and at the same time, the fluid to be sealed (F) within the second dynamic pressure generating groove (16) flows into the space between the sliding surfaces (511, 21), mainly as indicated by the arrow (F4').

[0125] Also, at this time, within the first inclined groove (531) of the third dynamic pressure generating groove (530), the fluid to be sealed (F) moves from the annular groove (19) toward the corner portion (530a) as indicated by the arrow (F5'), and at the same time, within the second inclined groove (532), the fluid to be sealed (F) moves from the closed end on the inner diameter side toward the corner portion (530a) as indicated by the arrow (F6').

[0126] According to this, the fluid to be sealed (F) is concentrated at the corner portion (530a) and its vicinity to generate static pressure, and at the same time, the fluid to be sealed (F) within the third dynamic pressure generating groove (530) flows between the sliding surfaces (511, 21), mainly as indicated by the arrow (F7). Accordingly, the lubricity between the sliding surfaces (511, 21) can be improved in an auxiliary manner.

[0127] In addition, since one second inclined groove (532) is positioned on the inner diameter side of the corner portion (530a) of the third dynamic pressure generating groove (530) adjacent in the forward rotation direction, the sealed fluid (F) that flows out from the corner portion (530a) between the sliding surfaces (511, 21) is recovered into one second inclined groove (532) and is difficult to leak into the inner space (S1).

[0128] Additionally, since the first inclined groove (531) is shorter than the second inclined groove (532), the corner portion (530a) of the third dynamic pressure generating groove (530) can be positioned closer to the annular groove (19). In other words, since the corner portion (530a) can be positioned further away from the inner space (S1), the fluid to be sealed (F) that leaks out from the corner portion (530a) between the sliding surfaces (511, 21) is easily recovered into the second inclined groove (532) or the annular groove (19) before reaching the inner space (S1), making it difficult for the fluid to be sealed (F) to leak further into the inner space (S1).

[0129] Example 6

[0130] Next, a mechanical seal as a sliding part according to Example 6 will be described with reference to FIG. 13. In addition, descriptions of configurations identical to or overlapping with those in Example 1 will be omitted.

[0131] The stop seal ring (610) in the mechanical seal of this embodiment 6 is different from the stop seal ring (10) of embodiment 1 in that it is provided with a third dynamic pressure generating groove (630), and the rest of the configuration is the same as the stop seal ring (10) of embodiment 1.

[0132] As shown in FIG. 13, on the sliding surface (611) of the stationary sealing ring (610), a plurality of third dynamic pressure generating grooves (630) are provided in the circumferential direction on the inner diameter side of the annular groove (19). The third dynamic pressure generating grooves (630) communicate with the annular groove (19) and extend in the inner diameter direction while inclined in the reverse rotation direction of the rotating sealing ring (20), that is, in the other circumferential direction, based on the communication point.

[0133] When the rotating seal ring (20) rotates relative to the stationary seal ring (610) in the forward direction, a relative negative pressure is generated at the closed end and near the third dynamic pressure generating groove (630). Accordingly, the sealing performance between the sliding surfaces (611, 21) can be improved in an auxiliary manner.

[0134] Additionally, when the rotating seal ring (20) rotates relative to the stationary seal ring (610) in the reverse direction, the third dynamic pressure generating groove (630) generates static pressure at its closed end and in the vicinity. Accordingly, the lubricity between the sliding surfaces (611, 21) can be improved in an auxiliary manner.

[0135] In addition, the third dynamic pressure generating groove (630) of the present embodiment 6 is exemplified as extending in the inner diameter direction while inclined in the reverse rotation direction of the rotating seal ring (20) from the connecting point of the annular groove (19), but it may also extend in the inner diameter direction while inclined in the forward rotation direction of the rotating seal ring (20) from the connecting point of the annular groove (19). In this case, lubricity can be improved during the forward rotation of the rotating seal ring (20), and sealing performance can be improved during the reverse rotation of the rotating seal ring (20).

[0136] Example 7

[0137] Next, a mechanical seal as a sliding part according to Example 7 will be described with reference to FIG. 14. In addition, descriptions of configurations identical to or overlapping with those in Example 1 will be omitted.

[0138] The stop seal ring (710) in the mechanical seal of Example 7 is different from the stop seal ring (10) of Example 1 in that it is provided with a third dynamic pressure generating groove (730), and the rest of the configuration is the same as the stop seal ring (10) of Example 1.

[0139] As shown in FIG. 14, on the sliding surface (711) of the stop seal ring (710), a plurality of third dynamic pressure generating grooves (730) are provided circumferentially on the inner diameter side of the annular groove (19). The third dynamic pressure generating grooves (730) are dimples that form a circle when viewed from the axial direction.

[0140] According to this, static pressure is generated in the third dynamic pressure generating groove (730) in any rotational direction of the rotating seal ring (20). That is, lubricity between the sliding surfaces (711, 21) can be improved in any rotational direction of the rotating seal ring (20).

[0141] In addition, the third dynamic pressure generating groove (730) is not limited to a circular shape when viewed from the axial direction, and may be an elongated hole such as a rectangular or elliptical shape when viewed from the axial direction.

[0142] Although embodiments of the present invention have been described above with reference to the drawings, the specific configuration is not limited to these embodiments, and changes or additions within the scope that do not deviate from the gist of the present invention are also included in the present invention.

[0143] For example, in the above Examples 1 to 7, a mechanical seal for automobiles was described as an example of a sliding part, but other mechanical seals such as those for general industrial machinery may also be used.

[0144] In addition, although the above embodiments 1 to 7 described examples in which the first dynamic pressure generating groove and the second dynamic pressure generating groove are provided in the stationary sealing ring, the first dynamic pressure generating groove and the second dynamic pressure generating groove may be provided in the rotating sealing ring, and the first dynamic pressure generating groove and the second dynamic pressure generating groove may be provided in one side of the stationary sealing ring and the rotating sealing ring, or on both sides.

[0145] In addition, although examples 1 to 7 described above describe cases where the communication groove and the annular groove are provided in the stationary sealing ring, the communication groove and the annular groove may be provided in the rotating sealing ring, and the communication groove and the annular groove may be provided in one side or on both sides of the stationary sealing ring and the rotating sealing ring, respectively.

[0146] In addition, in the above Examples 1 to 7, the sealed fluid side was described as the high-pressure side and the leakage side as the low-pressure side, but the sealed fluid side and the leakage side may have approximately the same pressure.

[0147] In addition, in the above Examples 1 to 7, the fluid to be sealed (F) was described as a high-pressure liquid, but it is not limited thereto and may be a gas or a mist state in which liquid and gas are mixed.

[0148] In addition, in the above Examples 1 to 7, the fluid on the leakage side was described as atmospheric (A) which is a low-pressure gas, but it is not limited thereto and may be a liquid or a high-pressure gas, or may be a mist state in which liquid and gas are mixed.

[0149] In addition, in the above embodiments 1 to 7, the first dynamic pressure generating groove and the second dynamic pressure generating groove were shown as being extended in a curved shape, but the first dynamic pressure generating groove and the second dynamic pressure generating groove may be extended in a straight shape.

[0150] In addition, in the above embodiments 1 to 7, the depths of the first dynamic pressure generating groove and the second dynamic pressure generating groove were exemplified as being constant, but the bottom surface may be formed in a slope or stepped shape so as to become shallow toward the closed end.

[0151] In addition, in the above embodiments 1 to 7, the connecting groove constituting the conducting groove is exemplified as being inclined in the circumferential direction and extended in the radial direction, but as shown in FIG. 15, the connecting groove (818) may be extended in a straight line shape in the radial direction and may be connected to the annular groove (19) and the outer space (S2).

[0152] In addition, in the above embodiments 1 to 7, a land extending in the circumferential direction is provided between the first dynamic pressure generating groove and the second dynamic pressure generating groove, and the closed ends are shown facing each other in the radial direction; however, as shown in the stop seal ring (910) of modified example 2 in FIG. 16, the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) may be arranged alternately in the circumferential direction. Furthermore, the closed end of the first dynamic pressure generating groove (13) may be positioned toward the annular groove (19) rather than the closed end of the second dynamic pressure generating groove (16).

[0153] In addition, although the above embodiments 1 to 7 illustrate a form in which a communication groove is formed on a sliding surface, the communication groove (180) may be configured such that it extends in the inner diameter direction from the outer circumference of the stop sealing ring (100) as in the modified example 3 shown in FIG. 17, and the inner diameter end extends in the axial direction and communicates with the annular groove (19). In this case, the fluid to be sealed (F) does not flow out or inflow from the communication groove (180) to the sliding surface, and the first dynamic pressure generating groove (13) and the second dynamic pressure generating groove (16) are evenly arranged in the circumferential direction. With this configuration, dynamic pressure is generated evenly in the circumferential direction.

[0154] In addition, in the above Examples 1 to 7, a form in which a first dynamic pressure generating groove and a second dynamic pressure generating groove of the same shape are provided in a circumferential direction on the stop seal ring is exemplified, but it is not limited thereto, and the stop seal ring may have a mixture of, for example, spiral grooves like those in Example 1 and Rayleigh steps like those in Example 3. Explanation of the symbols

[0155] 1; axis of rotation 2; Sleeve 4; Housing 10; Stop seal ring 11; sliding surface 12A; Land 13; First dynamic pressure generating groove (spiral groove) 13A; end (occluded end) 13B; end 16; Second dynamic pressure generating groove (spiral groove) 16B; end (occluded end) 17; Dotong Home 18; chimney groove 19; Fantasy Home 20; rotary sealing ring 21; sliding surface 313B; 1st Rayleigh Step (1st dynamic pressure generating groove) 316B; 2nd Rayleigh Step (2nd Dynamic Pressure Generation Groove) 530; 3rd dynamic pressure generating groove A; Waiting C; Cavitation zone F; sealed fluid S1; inner space (space on the other side) S2; outer space (space on one side)

Claims

Claim 1 A sliding component having a pair of sliding surfaces arranged opposite to a relative rotating location when a rotating machine is driven, wherein one sliding surface is provided with a first dynamic pressure generating groove extending in one direction in the circumferential direction in communication with one side of the inner diameter space and one side of the outer diameter space, a second dynamic pressure generating groove extending in the other direction in the circumferential direction, and a conductive groove communicating with said one side of the space, wherein the conductive groove has a groove extending in the circumferential direction and a communicating groove communicating with said circumferentially extending groove and said one side of the space, and said second dynamic pressure generating groove is arranged on the side of the space than said circumferentially extending groove and also communicates with said circumferentially extending groove. Claim 2 A sliding part according to claim 1, wherein a land extending in the circumferential direction is provided between the first dynamic pressure generating groove and the second dynamic pressure generating groove. Claim 3 In paragraph 2, the closed end of the first dynamic pressure generating groove and the closed end of the second dynamic pressure generating groove are sliding parts facing each other in the radial direction. Claim 4 In claim 1, the conductive groove is a sliding part having an annular groove as a groove extending in the circumferential direction. Claim 5 In claim 1, the first dynamic pressure generating groove and the second dynamic pressure generating groove are spiral grooves, forming a sliding part. Claim 6 In claim 5, the above-mentioned connecting groove is a sliding part that extends so as not to intersect the above-mentioned first dynamic pressure generating groove and the above-mentioned second dynamic pressure generating groove. Claim 7 A sliding component according to any one of claims 1 to 6, wherein a third dynamic pressure generating groove is provided in the space side other than the conductive groove on one sliding surface. Claim 8 In claim 7, the third dynamic pressure generating groove is a sliding part that is a curved groove communicating with the conductive groove.

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