The present invention relates to sliding components rotating relative to each other and used for a shaft sealing device that shaft-seals a rotary shaft of a rotating machine in a seal field such as an automobile and a general industrial machine or a bearing of a rotating machine in a bearing field such as an automobile and a general industrial machine.
In the related art, a mechanical seal is an example of a shaft sealing device that shaft-seals a rotary shaft of a rotating machine such as a pump and a turbine, prevents sealing target fluid leakage, and includes two components configured to rotate relative to each other and configured such that flat end surfaces slide with each other. The mechanical seal includes a stationary seal ring as a sliding component fixed to a housing and a rotating seal ring as a sliding component fixed to and rotating together with the rotary shaft. One of the stationary and rotating seal rings is urged in the direction of the other seal ring by urging means, and the sliding surfaces thereof are rotated relative to each other. As a result, the gap between the housing and the rotary shaft is shaft-sealed (see, for example, Patent Citation 1).
In the mechanical seal, it is possible to secure an effective facing region between the seal rings and exhibit predetermined sealing performance by the facing surfaces of the seal rings facing each other in parallel.
By the way, in the mechanical seal, the facing surface of the rotating-side seal ring may be deformed so as to axially tilt, though slightly, due to the inertial force of rotation or the like. When the deformation occurs in the mechanical seal described in Patent Citation 1, the corner portion constituting the outer or inner peripheral edge portion of one of the seal rings becomes close to the flat facing surface of the other facing seal ring. Accordingly, the corner portion becomes the closest part, the point closer to the inner diameter side or the outer peripheral side than the inner corner portion of the facing surface of one of the seal rings is largely separated from the facing surface of the other seal ring, and the effective facing region between the seal rings may become extremely small in the radial direction. In other words, the problem that stable sealing performance cannot be exhibited arises in a case where the deformation of the rotating-side seal ring is large under conditions such as the presence of a large load and a high rotation speed whereas the facing surfaces of the seal rings face each other in parallel and predetermined sealing performance can be exhibited in a case where the deformation of the rotating-side seal ring is small.
The present invention has been made in view of such problems, and an object of the present invention is to provide a sliding component capable of exhibiting stable sliding performance under various conditions.
In order to solve the above problem, a sliding component according to the present invention is a sliding component comprising a first ring and a second ring which are provided with facing surfaces facing each other and relatively rotated upon a drive of a rotating machine, wherein at least the first ring is provided with a curved surface portion formed in a convex shape and constituting at least a part of the facing surface of the first ring. According to the aforesaid feature of the present invention, it is possible to secure an effective facing region in the radial direction between the first and second rings and exhibit stable sliding performance under various undesirable conditions including a condition that the facing surface of one of the first and second rings is deformed so as to axially tilt due to the inertial force of rotation or the like and as a result the convex curved surface portion on the facing surface of the first ring and the facing surface of the second facing ring close to each other.
It may be preferable that the curved surface portion is formed over a circumferential direction of the facing surface of the first ring. According to this preferable configuration, an effective facing region can be secured over the entire circumference.
It may be preferable that the curved surface portion is formed at one or both of an outer diameter end and an inner diameter end of the first ring. According to this preferable configuration, it is possible to secure an effective facing region in the radial direction between the first and second rings, even if the second ring is substantially deformed at the outer or inner diameter end thereof. In addition, even if the facing surfaces come into contact with each other, the contact can be surface contact without being line contact.
It may be preferable that the second ring is provided with a curved surface portion formed in a concave shape and constituting at least a part of the facing surface of the second ring, and the curved surface portion of the first ring is smaller in radius of curvature than the curved surface portion of the second ring. According to this preferable configuration, it is possible to reliably secure an effective facing region in the radial direction between the first and second rings with the curved surface portions close to each other.
It may be preferable that the first ring provided with the curved surface portion is disposed on a stationary side of the rotating machine. According to this preferable configuration, it is easy to predict the shape of the first ring as a stationary-side ring during use, and thus it is possible to secure an effective facing region with high accuracy with respect to the degree of deformation of the rotating-side ring.
It may be preferable that a functional groove is formed in one or both of the curved surface portion of the first ring and the facing surface of the second ring facing the curved surface portion of the first ring, the functional groove is opened at an outer diameter side or an inner diameter side of the sliding component. According to this preferable configuration, it is possible to reliably exhibit a function such as dynamic pressure generation by the functional groove in the effective facing region secured in the radial direction between the first and second rings.
It may be preferable that in the first ring provided with the functional groove, at least another functional groove is formed, the functional grooves have depths equal to each other and each has a bottom surface parallel to a surface shape of the curved surface portion, and the functional grooves overlap with each other in a radially directional view. According to this preferable configuration, the function of the functional grooves can be exhibited regardless of the degree of deformation of the rotating-side ring.
It may be preferable that the curved surface portion is constituted by a plurality of minute step portions radially formed along a circumferential direction of the facing surface of the first ring. According to this preferable configuration, a fluid is held in the plurality of step portions formed in the radial direction, a fluid film is easily formed between the facing surfaces of the first and second rings, and high slidability can be ensured.
Modes for implementing the sliding component according to the present invention will be described below based on embodiments.
The sliding component according to a first embodiment of the present invention will be described with reference to
The mechanical seal for a general industrial machine illustrated in
The stationary seal ring 10 and the rotating seal ring 20 are typically formed of a combination of SiC (hard material) or a combination of SiC (hard material) and carbon (soft material). However, the present invention is not limited thereto and any sliding material can be applied insofar as it is used as a sliding material for a mechanical seal. It should be noted that the SiC includes a sintered body using boron, aluminum, carbon, or the like as a sintering aid and a material made of two or more types of phases having different components and compositions, examples of which include SiC in which graphite particles are dispersed, reaction-sintered SiC made of SiC and Si, SiC—TiC, and SiC—TiN. As the carbon, resin-molded carbon, sintered carbon, and the like can be used, including carbon in which carbon and graphite are mixed. In addition to the above sliding materials, a metal material, a resin material, a surface modification material (coating material), a composite material, and the like can also be applied.
As illustrated in
It should be noted that the deformation of the facing surface 21 of the rotating seal ring 20 in the direction toward the facing surface 11 of the stationary seal ring 10 depends on the rotation speed and the size of the rotating seal ring 20. For example, the deformation is approximately 2 to 9 μm at a rotation speed of 45 krpm. Accordingly, it is preferable that the curved surface shape of the facing surface 11 of the stationary seal ring 10 is formed such that the height difference between the inner diameter end of the facing surface 11 closest to the facing surface 21 and the outer diameter end of the facing surface 11 farthest from the facing surface 21 of the rotating seal ring 20 during non-operation is approximately 2 to 9 μm.
As described above, the facing surface 11 has a convex curved surface shape gradually separated from the rotating seal ring 20 from the inner diameter end to the outer diameter end. Accordingly, the facing surface 11 has a particularly large inclination with respect to the direction in which the outer diameter side of the facing surface 11 is orthogonal to the rotary shaft 1 and the inclination with respect to the direction in which the inner diameter side of the facing surface 11 is orthogonal to the rotary shaft 1 is smaller than on the outer diameter side of the facing surface 11. In other words, the facing surface 11 has a small radius of curvature on the outer diameter side and a large radius of curvature on the inner diameter side. In other words, the facing surface 11 has a large curvature on the outer diameter side and a small curvature on the inner diameter side.
In addition, the curved surface shape can be formed by micromachining the mirror-finished flat facing surface 11 by laser machining or the like. The laser machining is performed by irradiating the mirror-finished stationary seal ring 10 with laser while performing a relative laser movement in the circumferential direction, and a method can be adopted in which the facing surface 11 is scraped over the entire circumference by changing the depth in the axial direction by shifting to the inner diameter or the outer diameter. According to this, a plurality of step portions 30 over the entire circumference are formed side by side in the radial direction as illustrated in
In addition, as illustrated in
As illustrated in
The dynamic pressure generation groove 13 can be formed by re-performing micromachining by laser on the facing surface 11 laser-machined into a curved surface shape. The dynamic pressure generation groove 13 is surrounded by the four surfaces of two surfaces 13b disposed side by side when viewed from the axial direction and forming circular arc-shaped side walls, a wall portion 13c forming the wall at the inner diameter end, that is, the terminal end extending while crossing the circular arc-shaped surfaces 13b, and the bottom surface 13a parallel to the facing surface 11. The outer diameter end of the dynamic pressure generation groove 13 is open to the outer diameter side of the dynamic pressure generation groove 13 (see
As illustrated in
Next, the operation of a general industrial machine during non-operation and operation will be described. As illustrated in
During the operation of the general industrial machine, the sealing target liquid F is taken into the dynamic pressure generation groove 13 to result in a state where the facing surface 21 of the rotating seal ring 20 and the facing surface 11 of the stationary seal ring 10 are slightly separated by the positive pressure generated around the wall portion 13c, which is the terminal end of the dynamic pressure generation groove 13. The state is the so-called non-contact state of the facing surfaces and leads to friction reduction.
During the operation of the general industrial machine, the rotating seal ring 20 may be deformed due to, for example, the inertial force attributable to the rotation of the rotary shaft 1, the stress attributable to the resistance or load of a component of the general industrial machine such as an impeller rotating with the rotary shaft 1, or a thermal factor attributable to sliding heat generation.
For example, the rotating seal ring 20 may be deformed so as to tilt in the direction toward the stationary seal ring 10 toward the outer diameter side, which is the free end of the rotating seal ring 20. As illustrated in
The facing surface 11 of the stationary seal ring 10 has a shape in which the part where the facing surface 21 of the rotating seal ring 20 becomes obliquely close is pre-removed in view of the deformation of the rotating seal ring 20 during the rotation. Accordingly, as is clear from
In addition, the facing surface 11 of the stationary seal ring 10 has a convex curved surface shape. Accordingly, in a state where the facing surface 11 of the stationary seal ring 10 and the facing surface 21 of the rotating seal ring 20 facing the facing surface 11 of the stationary seal ring 10 are close to each other, a part of the facing surface 11 of the stationary seal ring 10 at an angle close to the inclination angle resulting from the deformation of the facing surface 21 of the rotating seal ring 20 becomes almost parallel to the facing surface 21 of the inclined rotating seal ring 20. Specifically, the facing surface 11 of the stationary seal ring 10 has a curved surface shape around a closest part P1, which is closest to the facing surface 21 of the rotating seal ring 20 on the facing surface 11 of the stationary seal ring 10, and even on both radial sides across the closest part P1, and thus a part of the facing surface 11 of the stationary seal ring 10 becomes almost parallel to the facing surface 21 of the inclined rotating seal ring 20 without being significantly separated from the facing surface 21 of the rotating seal ring 20 and an effective facing region can be secured in the radial direction between the facing surfaces 11 and 21 of the stationary seal ring 10 and the rotating seal ring 20. As a result, the stationary seal ring 10 and the rotating seal ring 20 are capable of exhibiting stable sealing performance under various conditions.
It should be noted that the degree of deformation of the rotating seal ring 20 varies depending on external factors. For example, in a case where the inclination of the facing surface 21 of the rotating seal ring 20 is smaller than in
In this manner, the facing surface 11 of the stationary seal ring 10 has a convex curved surface shape gradually separated from the rotating seal ring 20 toward the outer diameter end from the inner diameter end, and thus it is possible to secure an effective facing region in the radial direction at all times regardless of the inclination angle of the facing surface 21 attributable to the difference in the degree of deformation of the rotating seal ring 20. In other words, the present invention can be used for general purposes in, for example, general industrial machines and automobiles of various specifications.
In addition, the facing surface 11 has a curved surface shape from the inner diameter end to the outer diameter end and is capable of finely corresponding to the inclination angle of the facing surface 21 of the rotating seal ring 20.
In addition, the facing surface 11 is provided with a curved surface-shaped part over the circumferential direction, and thus an effective facing region can be secured over the entire circumference in relation to the facing surface 21 of the rotating seal ring 20.
By the way, sealing requires contact between the surfaces or a region close to the extent of being fluid-sealable, that is, a facing region with some width in the radial direction. When the radius of curvature of the curved surface-shaped facing surface 11 of the stationary seal ring 10 is larger than, for example, the radius of curvature of the facing surface 21 of the rotating seal ring 20 that has a curved surface shape, the facing surface 11 and the facing surface 21 become closest at either the outermost diameter or the innermost diameter of the seal ring in the radial direction with the curved surface-shaped facing surface 11 of the stationary seal ring 10 and the facing surface 21 of the rotating seal ring 20 facing the curved surface-shaped facing surface 11 of the stationary seal ring 10 close to each other, the facing surface 11 and the facing surface 21 are largely separated from each other on the inner diameter side or the outer diameter side as compared with the closest part, and then it may be impossible to secure an effective facing region and perform sealing appropriately. However, the facing surface 21 of the rotating seal ring 20 in the present embodiment is formed as a flat surface orthogonal to the axial direction of the rotary shaft 1, the facing surface 11 of the stationary seal ring 10 is formed in a convex curved surface shape gradually separated from the rotating seal ring 20 toward the outer diameter end from the inner diameter end, and thus the closest point does not become the outermost diameter or the innermost diameter of the seal ring, the closest point is disposed on the outer diameter side as compared with the innermost diameter and the inner diameter side as compared with the outermost diameter of the seal ring, and close regions can be secured on both radial sides of the closest point. In addition, since the facing surface 11 of the stationary seal ring 10 is a curved surface formed along the facing surface 21 of the rotating seal ring 20, it is possible to reduce the average inter-surface distance between the facing surfaces 11 and 21 and effectively secure an effective facing region in the radial direction.
In addition, since the curved surface shape is formed for the facing surface 11 of the stationary seal ring 10, it is possible to secure an effective facing region with high responsiveness to the degree of deformation of the rotating seal ring 20.
In addition, since the dynamic pressure generation groove 13 is formed at the curved surface-shaped part of the facing surface 11 of the stationary seal ring 10, the function of dynamic pressure generation can be effectively exhibited in the effective facing region secured in the radial direction between the stationary seal ring 10 and the rotating seal ring 20.
In addition, the dynamic pressure generation groove 13 has the bottom surface 13a parallel to the surface shape of the land 12 of the facing surface 11, the plurality of dynamic pressure generation grooves 13 are radially formed at the same depth, and thus the function of dynamic pressure generation can be effectively exhibited regardless of the degree of deformation of the rotating seal ring 20.
In addition, the curved surface shape of the facing surface 11 of the stationary seal ring 10 has the minute step portion 30 in the radial direction from a microscopic viewpoint, and thus the sealing target liquid F is held in the step portion 30, a fluid film can be easily formed between the facing surface 11 of the stationary seal ring 10 and the facing surface 21 of the rotating seal ring 20, and high slidability and sealability can be ensured.
Next, the sliding component according to a second embodiment of the present invention will be described with reference to
As illustrated in
Although embodiments of the present invention have been described above with reference to the drawings, the specific configurations are not limited to the embodiments and any changes or additions within the gist of the present invention are included in the present invention.
For example, although the facing surface 21 of the rotating seal ring 20 is a flat surface orthogonal to the axial direction of the rotary shaft 1 in the first embodiment, only one point is closest in the radial direction, even if the facing surface 21 of the rotating seal ring 20 has a concave curved surface shape, insofar as the facing surface 21 of the rotating seal ring 20 is larger in radius of curvature than the facing surface 11 of the stationary seal ring 10, and thus it is possible to effectively secure an effective facing region in the radial direction.
In another configuration, a rotating seal ring having an axially convex curved surface portion as in the second embodiment may face a stationary seal ring having an axially convex curved surface portion as in the first embodiment. In this case, sliding performance can be ensured regardless of the inclination angle between the facing surfaces of the stationary and rotating seal rings and damage attributable to stress concentration can be prevented.
In the first embodiment, the facing surface 11 of the stationary seal ring 10 has a convex curved surface shape gradually separated from the rotating seal ring from the inner diameter end toward the outer diameter end from the outer diameter end to the inner diameter end. However, the present invention is not limited thereto and the facing surface 11 of the stationary seal ring 10 may have a convex curved surface shape gradually separated from the rotating seal ring from the outer diameter end toward the inner diameter end from the outer diameter end to the inner diameter end of the facing surface 11. In addition, there is no need for the entire facing surface to constitute the curved surface portion. For example, the curved surface portion may be formed so as to extend to the radial middle portion from the outer or inner diameter end of the facing surface 11 and the curved surface portion may not be formed in the entire radial direction.
In addition, the curved surface portion formed on the facing surface 11 may be on both sides in the radial direction while leaving the flat surface radially extending to the middle portion between the outer and inner diameter ends of the facing surface 11 or either the outer diameter end or the inner diameter end of the facing surface 11.
In addition, the groove in the facing surface such as the dynamic pressure generation groove may be formed in the facing surface of the rotating seal ring instead of the facing surface of the stationary seal ring or may be formed in both the facing surface of the stationary seal ring and the facing surface of the rotating seal ring.
In addition, the groove in the facing surface of the stationary seal ring or the facing surface of the rotating seal ring may not be the dynamic pressure generation groove and may be a functional groove having another function such as a Rayleigh step.
In addition, the groove such as the dynamic pressure generation groove may be omitted insofar as the mechanical seal in which the sliding component is used is not in an aspect in which the facing surface of the stationary seal ring and the facing surface of the rotating seal ring are not in contact with each other.
In addition, the sliding component of the present invention is not limited to the inside-type mechanical seal that seals a sealing target fluid to leak from the outer peripheral side of the facing surface toward the inner peripheral side. The sliding component of the present invention can be used for an outside-type mechanical seal that seals a sealing target fluid to leak from the inner peripheral side of a facing surface toward the outer peripheral side.
In addition, although a liquid has been described as an example of the sealing target fluid sealed by the sliding component of the present invention, the liquid may be replaced with a gas. Further, although an example in which the sealing target fluid side is higher in pressure than the atmospheric side has been described, the fluid pressure relationship between the inner and outer diameter sides of the sliding component is not limited thereto and the pressures may be equal to each other.
In addition, the sliding component of the present invention can be used for a bearing such as a thrust bearing.
Number | Date | Country | Kind |
---|---|---|---|
2019-082965 | Apr 2019 | JP | national |
Filing Document | Filing Date | Country | Kind |
---|---|---|---|
PCT/JP2020/017170 | 4/21/2020 | WO |
Publishing Document | Publishing Date | Country | Kind |
---|---|---|---|
WO2020/218286 | 10/29/2020 | WO | A |
Number | Name | Date | Kind |
---|---|---|---|
3085808 | Williams | Apr 1963 | A |
3232680 | Clark | Feb 1966 | A |
3410565 | Williams | Nov 1968 | A |
3499653 | Gardner | Mar 1970 | A |
3527465 | Guinard | Sep 1970 | A |
3656227 | Weinand | Apr 1972 | A |
3804424 | Gardner | Apr 1974 | A |
3905606 | Florjancic | Sep 1975 | A |
4406466 | Geary, Jr. | Sep 1983 | A |
4407512 | Trytek | Oct 1983 | A |
4486026 | Furumura et al. | Dec 1984 | A |
4799693 | Johnston | Jan 1989 | A |
4836561 | Lebeck | Jun 1989 | A |
5092612 | Victor | Mar 1992 | A |
5201531 | Lai | Apr 1993 | A |
5222743 | Goldswain | Jun 1993 | A |
5246295 | Ide | Sep 1993 | A |
5441283 | Pecht et al. | Aug 1995 | A |
5492341 | Pecht | Feb 1996 | A |
5498007 | Kulkarni | Mar 1996 | A |
5501470 | Fuse | Mar 1996 | A |
5556111 | Sedy | Sep 1996 | A |
5702110 | Sedy | Dec 1997 | A |
5895051 | Bowers | Apr 1999 | A |
6446976 | Key | Sep 2002 | B1 |
6575470 | Gacek | Jun 2003 | B1 |
9587745 | Itadani et al. | Mar 2017 | B2 |
9829109 | Itadani et al. | Nov 2017 | B2 |
9845887 | Hoppe | Dec 2017 | B2 |
9951873 | Inoue et al. | Apr 2018 | B2 |
10072759 | Inoue et al. | Sep 2018 | B2 |
10113648 | Inoue et al. | Oct 2018 | B2 |
10487948 | Inoue et al. | Nov 2019 | B2 |
10495228 | Itadani et al. | Dec 2019 | B2 |
10704417 | Tokunaga et al. | Jul 2020 | B2 |
10781924 | Inoue et al. | Sep 2020 | B2 |
10883603 | Inoue et al. | Jan 2021 | B2 |
10883604 | Inoue et al. | Jan 2021 | B2 |
20020093141 | Wang | Jul 2002 | A1 |
20030178781 | Tejima | Sep 2003 | A1 |
20040080112 | Tejima | Apr 2004 | A1 |
20050212217 | Tejima | Sep 2005 | A1 |
20080100001 | Flaherty | May 2008 | A1 |
20080272552 | Zheng | Nov 2008 | A1 |
20100066027 | Vasagar | Mar 2010 | A1 |
20110101616 | Teshima | May 2011 | A1 |
20130209011 | Tokunaga | Aug 2013 | A1 |
20150123350 | Itadani | May 2015 | A1 |
20150377297 | Tokunaga et al. | Dec 2015 | A1 |
20160033045 | Itadani et al. | Feb 2016 | A1 |
20170234431 | Katori et al. | Aug 2017 | A1 |
20180238452 | Shaw | Aug 2018 | A1 |
20190178386 | Arai | Jun 2019 | A1 |
20190301522 | Negishi et al. | Oct 2019 | A1 |
Number | Date | Country |
---|---|---|
101749431 | Jun 2010 | CN |
36 19 489 | Dec 1987 | DE |
2570614 | Mar 2013 | EP |
2626604 | Aug 2013 | EP |
36-6305 | May 1961 | JP |
S49-33614 | Sep 1974 | JP |
S54-77305 | Jun 1979 | JP |
S55-177549 | Dec 1980 | JP |
58-109771 | Jun 1983 | JP |
58-137667 | Aug 1983 | JP |
S59-58252 | Apr 1984 | JP |
6037463 | Feb 1985 | JP |
S60-107461 | Jul 1985 | JP |
S6182177 | May 1986 | JP |
S63-033027 | Mar 1988 | JP |
S63-190975 | Aug 1988 | JP |
H01133572 | Sep 1989 | JP |
2-236067 | Sep 1990 | JP |
H04-73 | Jan 1992 | JP |
H04-145267 | May 1992 | JP |
H07-55016 | Mar 1995 | JP |
H08-89489 | Apr 1996 | JP |
H09-503276 | Mar 1997 | JP |
H09-329247 | Dec 1997 | JP |
H10-38093 | Feb 1998 | JP |
H10-281299 | Oct 1998 | JP |
2003-343741 | Dec 2003 | JP |
2005-188651 | Jul 2005 | JP |
2006-022834 | Jan 2006 | JP |
2009-250378 | Oct 2009 | JP |
2012-2295 | Jan 2012 | JP |
5271858 | May 2013 | JP |
2016-80090 | May 2016 | JP |
2017-141961 | Aug 2017 | JP |
6444492 | Dec 2018 | JP |
WO 9506832 | Mar 1995 | WO |
WO 2012046749 | Apr 2012 | WO |
WO 2014148316 | Sep 2014 | WO |
WO 2016035860 | Mar 2016 | WO |
WO 2016167262 | Oct 2016 | WO |
WO 2017002774 | Jan 2017 | WO |
WO 2018034197 | Feb 2018 | WO |
WO 2018105505 | Jun 2018 | WO |
Entry |
---|
Korean Office Action issued in related application 10-2021-7036306, dated Mar. 21, 2023, with English translation, 11 pages. |
European Search Report issued in related application No. 20794826.6, dated Nov. 14, 2022, 6 pages. |
International Preliminary Report on Patentability issued in application No. PCT/JP2020/017170, dated Nov. 4, 2021 (6 pgs). |
Definition of groove by Merriam Webster. |
Chinese Office Action issued in application No. 201380070532.6 (with translation), dated Jan. 28, 2016 (13 pgs). |
Chinese Office Action issued in application No. 201380070532.6 (with translation), dated Sep. 20, 2016 (12 pgs). |
Second Office Action issued by the State Intellectual Property Office of China, dated Aug. 29, 2016, for Chinese counterpart application No. 201480002574.0, 8 pages. |
First Notification of Reason for Refusal issued by the State Intellectual Property Office of China, dated Dec. 24, 2015, with a search report for Chinese counterpart application No. 201480002574.0, 11 pages. |
Office Action issued in U.S. Appl. No. 14/431,733, dated Apr. 29, 2016 (22 pgs). |
Office Action issued in U.S. Appl. No. 14/431,733, dated Aug. 18, 2017 (13 pgs). |
Office Action issued in U.S. Appl. No. 14/431,733, dated Mar. 31, 2017 (14 pgs). |
Office Action issued in U.S. Appl. No. 14/431,733, dated Oct. 6, 2016 (12 pgs). |
Office Action issued in U.S. Appl. No. 15/419,989, dated Jan. 26, 2018 (20 pgs). |
Office Action issued in U.S. Appl. No. 15/419,970, dated May 11, 2018 (17 pgs). |
Office Action issued in U.S. Appl. No. 15/419,970, dated Jan. 23, 2018 (21 pgs). |
Office Action issued in U.S. Appl. No. 15/842,862, dated Jun. 5, 2019 (37 pgs). |
Office Action issued in U.S. Appl. No. 15/842,855, dated Mar. 12, 2020 (11 pgs). |
Office Action issued in U.S. Appl. No. 15/842,855, dated Jun. 29, 2020, 16 pages. |
Office Action issued in U.S. Appl. No. 15/842,858, dated Mar. 31, 2020 (10 pgs). |
Office Action issued in U.S. Appl. No. 15/842,859, dated Apr. 8, 2020 (12 pgs). |
Notice of Allowance issued in U.S. Appl. No. 15/419,970, dated Aug. 9, 2018 (16 pgs). |
Notice of Allowance issued in U.S. Appl. No. 14/431,733, dated Feb. 23, 2018 (22 pgs). |
Notice of Allowance issued in U.S. Appl. No. 15/419,989, dated Jul. 23, 2018 (11 pgs). |
Notice of Allowance issued in U.S. Appl. No. 15/842,862, dated Sep. 30, 2019, 15 pages. |
Japanese Office Action (w/translation) issued in application 2018-159877, dated Jun. 13, 2019 (7 pgs). |
International Search Report issued in application No. PCT/JP2013/084029, dated Mar. 25, 2014 (4 pgs). |
International Preliminary Report on Patentability issued in application No. PCT/JP2013/084029, dated Nov. 5, 2015 (8 pgs). |
International Search Report and Written Opinion issued in PCT/JP2014/050402, dated Feb. 10, 2014, with English translation, 12 pages. |
International Preliminary Report on Patentability issued in PCT/JP2014/050402, dated Jul. 21, 2015, 4 pages. |
International Search Report and Written Opinion issued in PCT/JP2019/045728, dated Dec. 17, 2019, with English translation, 13 pages. |
International Preliminary Report on Patentability issued in PCT/JP2019/045728, dated May 25, 2021, 7 pages. |
International Search Report and Written Opinion issued in PCT/JP2019/047890, dated Feb. 10, 2020, with English translation, 13 pages. |
International Preliminary Report on Patentability issued in PCT/JP2019/047890, dated Aug. 10, 2021, 7 pages. |
International Search Report and Written Opinion issued in PCT/JP2019/049870, dated Mar. 10, 2020, with English translation, 13 pages. |
International Preliminary Report on Patentability issued in PCT/JP2019/049870, dated Jun. 16, 2021, 7 pages. |
International Search Report and Written Opinion issued in PCT/JP2020/005260, dated Apr. 7, 2020, with English translation, 16 pages. |
International Preliminary Report on Patentability issued in PCT/JP2020/005260, dated Aug. 10, 2021, 9 pages. |
International Search Report and Written Opinion issued in PCT/JP2020/006421, dated Apr. 21, 2020, with English translation, 13 pages. |
International Preliminary Report on Patentability issued in PCT/JP2020/006421, dated Aug. 10, 2021, 6 pages. |
International Search Report and Written Opinion issued in PCT/JP2020/017170, dated Jun. 2, 2020, with English translation, 13 pages. |
European Official Action issued in related application No. 20794826.6, dated Jul. 19, 2023, 5 pages. |
Number | Date | Country | |
---|---|---|---|
20220196152 A1 | Jun 2022 | US |