The present invention relates to an oil pump which sucks and discharges oil (lubricant oil) of an internal combustion engine (an engine) or the like, and in particular, relates to a trochoid type oil pump including an inner rotor and an outer rotor.
There has been known a trochoid type oil pump including a housing (gear case), an outer rotor which has internal teeth as being rotatably arranged in the housing, an inner rotor which has external teeth engaged with the internal teeth of the outer rotor and which defines a volume-varying pump chamber in cooperation with the outer rotor, a rotary shaft which is rotatably supported by the housing to rotate the inner rotor, two side plates which are capable of being in contact with both side faces of the inner rotor and the outer rotor in the axis line direction of the rotary shaft and being moved in the axis line direction with slight clearance formed in the axis line direction, two elastic members which are arranged in the housing to press the two side plates toward both the side faces of the inner rotor and the outer rotor, and the like. Here, even in a case that dimensional variation in the axis line direction occurs at the housing, the inner rotor, and the outer rotor with thermal expansion and the like, the elastic members continuously press the two side plates respectively to both side faces of the inner rotor and the outer rotor. Accordingly, stable volume efficiency can be obtained without causing clearance (for example, see Patent Literature 1).
The abovementioned oil pump adopts a structure that the two non-rotatable side plates are pressed directly to the rotating inner rotor and outer rotor. Therefore, slide resistance becomes large, so that large rotational torque is required to operate the oil pump. Consequently, operational load of an engine or the like is increased.
Further, the two side plates are relatively slid in a state of being continuously pressed to both the side faces of the inner rotor and the outer rotor at predetermined pressure. Therefore, in a case that the side plates are made of softer material than that of the inner rotor and the outer rotor, wear, deterioration with time, and the like are more likely to occur to cause a problem in durability.
Patent Literature 1: Japanese Utility-model Application No. 62-156057 (Japanese Utility-model Application Laid-open 1-61477) (Microfilm)
To address the above issues, an object of the present invention is to provide a durable oil pump whose volume efficiency (pumping performance) can be stabilized as preventing variation of side clearance at both the side faces of the inner rotor and the outer rotor while achieving reduction of slide resistance, reduction of operational torque, suppression of deterioration with time, and the like.
An oil pump according to the present invention includes a housing, a rotary shaft which is supported by the housing, an inner rotor which is rotated in the housing integrally with the rotary shaft, an outer rotor which is rotated in the housing as being interlocked with the inner rotor, a rotor case which is fitted into the housing and which contains the inner rotor and the outer rotor and supports an outer circumferential face of the outer rotor in a slidable manner, a side plate which is arranged to be in contact with at least one annular end face of the rotor case, and an elastic member which exerts an urging force to press the side plate to the annular end face of the rotor case.
According to the configuration, when the inner rotor is rotated along with the rotary shaft, (the outer circumferential face of) the outer rotor with which the inner rotor is in contact is rotated as being interlocked therewith to be slid on (the inner circumferential face of) the rotor case. Subsequently, oil is sucked (from an inlet port) and pressurized due to pumping action of both, and then, is discharged (from a discharge port) and fed toward various lubrication areas.
Here, the rotor case is fitted into the housing, the inner rotor and the outer rotor are arranged to be rotated in the rotor case, and the side plate is in contact with at least one annular end face of the rotor case as being urged by the elastic member in the axis line direction of the rotary shaft. Accordingly, for example, even in a case that the housing is thermally expanded, the rotor case is continuously in a state of being sandwiched between (the inner wall face at one side of) the housing and the side plate owing to the urging force of the elastic member. Therefore, both side faces of the inner rotor and the outer rotor can maintain constant clearance (side clearance) enabling to be slid between (the inner wall face at one side of) the housing and the side plate. In addition, oil leakage through the clearance can be prevented from occurring and stable volume efficiency (pumping performance) can be obtained. Further, since the urging force of the elastic member is not applied to both the side faces of the inner rotor and the outer rotor, slide resistance and operational torque can be reduced and durability can be improved compared to a conventional oil pump.
In the above configuration, it is possible to adopt a configuration that the rotor case is made of material having the same thermal expansion coefficient as that of the inner rotor and the outer rotor.
According to the configuration, even in a case that the housing, the rotor case, the inner rotor, and the outer rotor are deformed with thermal expansion and the like respectively, relative dimensional relations among the rotor case, the inner rotor, and the outer rotor can be maintained at constant. Accordingly, it is possible to maintain desired pumping performance more reliably without being influenced by thermal expansion and the like.
In the above configuration, it is possible to adopt a configuration that the side plate is made of material having the same thermal expansion coefficient as that of the housing.
According to the configuration, even when the same thermal deformation (thermal expansion) occurs at the side plate and the housing, contact relations among both the side faces of the inner rotor and the outer rotor, (the inner wall face of) the housing, and the side plate can be maintained in a desired state owing to that the side plate is urged by the elastic member in the axis line direction. In particular, when the housing and the side plate are made of light weight material or the like, there is an advantage that desired pumping performance can be maintained while achieving reduction in weight.
In the above configuration, it is possible to adopt a configuration that “Wc>Wr” is satisfied while Wc denotes a width dimension of the rotor case in the axis line direction of the rotary shaft and Wr denotes a width dimension of the inner rotor and the outer rotor in the axis line direction of the rotary shaft.
According to the configuration, both the side faces of the inner rotor and the outer rotor are maintained as being faced to (the inner wall face of) the housing and the side plate with constant clearance ΔC (=Wc−Wr) formed therebetween in a state of not being protruded from both ends (annular end faces at both sides) of the rotor case in the axis line direction. Accordingly, it is possible to ensure desired pumping performance while further reducing slide resistance.
In the above configuration, it is possible to adopt a configuration that the housing includes a housing body which has a concave portion to contain the rotor case and the side plate, and a housing cover which is coupled to close opening of the housing body.
According to the configuration, the entire assembling can be performed only by arranging the rotor case which contains the inner rotor and the outer rotor, the side plate, and the elastic member in the housing body and attaching the housing cover thereonto. Thus, assembling operation can be easily performed.
In the above configuration, it is possible to adopt a configuration that the inner rotor and the outer rotor include an upstream rotor including a first inner rotor and a first outer rotor and a downstream rotor including a second inner rotor and a second outer rotor, the upstream rotor and the downstream rotor being arranged adjacently in the axis line direction of the rotary shaft; and the rotor case includes an upstream accommodation portion which contains the upstream rotor, a downstream accommodation portion which contains the downstream rotor, and a middle wall portion which is interposed between the upstream accommodation portion and the downstream accommodation portion.
The configuration provides a two-stage trochoid pump in which the upstream rotor is arranged in the upstream accommodation portion and the downstream rotor is arranged in the downstream accommodation portion. Accordingly, as described above, while maintaining clearance (side clearance) at constant in the axis line direction, a desired discharge rate is ensured and enhanced pumping performance can be obtained as reducing a discharge resistance at high load, that is, as suppressing decrease in final discharge pressure.
Here, since the upstream accommodation portion, the downstream accommodation portion, and the middle wall portion are integrally formed in the rotor case, parts count can be reduced and handling convenience can be improved.
In the above configuration, it is possible to adopt a configuration that the inner rotor and the outer rotor include an upstream rotor including a first inner rotor and a first outer rotor and a downstream rotor including a second inner rotor and a second outer rotor, the upstream rotor and the downstream rotor being arranged adjacently in the axis line direction of the rotary shaft; the rotor case includes an upstream rotor case which contains the upstream rotor and a downstream rotor case Which contains the downstream rotor; and a spacer member is arranged between the upstream rotor case and the downstream rotor case.
The configuration provides a two-stage trochoid pump in which the upstream rotor is arranged in the upstream rotor case, the downstream rotor is arranged in the downstream rotor case, and the spacer member defines a space between the upstream rotor and the downstream rotor. Accordingly, as described above, while maintaining clearance (side clearance) at constant in the axis line direction, a desired discharge rate is ensured and enhanced pumping performance can be obtained as reducing a discharge resistance at high load, that is, as suppressing decrease in final discharge pressure.
Here, since the rotor case includes the upstream rotor case and the downstream rotor case and the separated spacer member is interposed therebetween, clearance at both side faces of the upstream rotor and clearance at both side faces of the downstream rotor can be maintained at constant independently with a high degree of accuracy.
In the above configuration, it is possible to adopt a configuration that the spacer member is made of material having the same thermal expansion coefficient as that of the housing.
According to the configuration, even when the same thermal deformation (thermal expansion) occurs at the spacer member and the housing, the spacer member is sandwiched between the upstream rotor case and the downstream rotor case via the elastically-urged side plate and (the inner wall face of) the housing. Accordingly, contact relations among both the side faces of the upstream rotor and the downstream rotor, (the inner wall face of) the housing, the spacer member, and the side plate can be maintained in a desired state. In particular, when the housing and the spacer member are made of light weight material or the like, there is an advantage that desired pumping performance can be maintained while achieving reduction in weight.
According to an oil pump having the abovementioned structure, while achieving reduction of slide resistance, reduction of operational torque, suppression of deterioration with time, and the like, volume efficiency (pumping performance) can be stabilized and durability can be improved as preventing variation of side clearance at both the side faces of the inner rotor and the outer rotor.
In the following, embodiments of the present invention will be described with reference to the attached drawings.
As illustrated in
The housing body 10 made of aluminum or the like for weight saving and the like is configured to form a concave portion for containing the side plate 50 and the rotor case 40 which contains the upstream rotor 70 and the downstream rotor 80. As illustrated in
The housing cover 20 is made of aluminum material or the like being the same as the housing body 10 for weight saving and the like. As illustrated in
The housing cover 20 is joined to the joint face 17 to close an opening of the housing body 10 while a positioning pin fitted into the positioning hole 19 is fitted into the positioning hole 26 and a positioning pin fitted into a positioning hole 45a of the rotor case 40 is fitted into the positioning hole 27. Then, the housing cover 20 is connected to the housing body 10 by screwing the bolts B into the screw holes 18 as passing through the circular holes 25 from the outer side.
As described above, the housing is structured with the housing body. 10 and the housing cover 20. Accordingly, the entire assembling can be performed by only arranging the rotor case 40 which contains the upstream rotor 70 (the first inner rotor 71 and the second outer rotor 72) and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82), the side plate 50, and the O-ring 60 in the housing body 10 and attaching the housing cover 20 thereonto. Thus, assembling operation can be easily performed.
As illustrated in
The rotor case 40 is made of steel, sintered steel, iron, or the like. As illustrated in
The cylindrical portion 41 is formed to have an outer diameter dimension so that the cylindrical portion 41 is fitted into the housing body 10 as being capable of relatively moving in the direction of the axis line S in accordance with difference between thermal deformation (expansion and contraction) amounts of the housing body 10 and the rotor case 40 while being intimately contacted to the inner circumferential face 12 of the housing body 10.
The upstream accommodation portion 42 is formed to have a dimension defining the inner circumferential face with which the first outer rotor 72 of the upstream rotor 70 is in contact rotatably (slidably) about the axis line L1.
The downstream accommodation portion 43 is formed to have a dimension defining the inner circumferential face with which the second outer rotor 82 of the downstream rotor 80 is in contact rotatably (slidably) about the axis line L2.
The inlet port 44b is formed so as to be faced to (a pump chamber P of) the upstream rotor 70 while communicating with the inlet passage 14.
The communication port 44e is configured to cause communication between the upstream rotor discharge port 44c and the downstream rotor inlet port 44d so that oil discharged from the upstream rotor 70 is introduced to the downstream rotor 80.
The rotor case 40 is assembled (fitted) to the inner circumferential face 12 of the housing body 10 in a state of containing the upstream rotor 70 in the upstream accommodation portion 42 and the downstream rotor 80 at the downstream accommodation portion 43 along with the rotary shaft 30 while the positioning pin fitted into the positioning hole 16 is fitted into the positioning hole 46a as sandwiching the O-ring 60 and the side plate 50 in cooperation with the end face 13.
Here, the upstream accommodation portion 42, the downstream accommodation portion 43, and the middle wall portion 44 are integrally formed in the rotor case 40. Accordingly parts count can be reduced and handling convenience can be improved.
The side plate 50 is made of aluminum material or the like being the same as the housing (10, 20) for weight saving and the like. As illustrated in
The side plate 50 is configured to be assembled to the housing body 10 as sandwiching the O-ring 60 at a space against the end face 13 while a positioning pin fitted into the positioning hole 16 of the housing body 10 passes through the positioning hole 53.
The O-ring 60 is formed circularly as being made of elastically-deformable rubber material or the like and is arranged between the end face 13 of the housing body 10 and the side plate 50. The O-ring 60 is assembled as being compressed by a predetermined compression amount in the direction of the axis line S to urge the side plate 50 toward the annular end face 46 of the rotor case 40.
Similarly to the rotor case 40, the upstream rotor 70 is made of steel, sintered steel, iron, or the like. As illustrated in
The first inner rotor 71 is formed as an external gear which has four crests and roots (cavities) while including a fitting hole 71a into which the shaft portion 33 of the rotary shaft 30 is fitted.
The first outer rotor 72 is formed as an internal gear which has five crests (inner teeth) and roots (cavities) to be engaged with the four crests (external teeth) and roots (cavities) of the first inner rotor 71 at the inner circumference thereof while including an outer circumferential face 72a which is slidably fitted to (the inner circumferential face of) the upstream accommodation portion 42 of the rotor case 40.
That is, the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) is a trochoid pump having four blades and five nodes.
When the first inner rotor 71 is rotated along with the rotary shaft 30 in an arrow direction about the axis line S (counterclockwise in
Similarly to the rotor case 40, the downstream rotor 80 is made of steel, sintered steel, iron, or the like. As illustrated in
The second inner rotor 81 is formed as an external gear which has four crests and roots (cavities) at the outer circumferential face thereof while including a fitting hole 81a into which the shaft portion 34 of the rotary shaft 30 is fitted.
The second outer rotor 82 is formed as an internal gear which has five crests (inner teeth) and roots (cavities) to be engaged with the four crests (external teeth) and roots (cavities) of the second inner rotor 81 at the inner circumference thereof while including an outer circumferential face 82a which is slidably fitted to (the inner circumferential face of) the downstream accommodation portion 43 of the rotor case 40.
That is, the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82) is a trochoid pump having four blades and five nodes.
When the second inner rotor 81 is rotated along with the rotary shaft 30 in an arrow direction (clockwise in
As described above, the two-stage trochoid pump including the upstream rotor 70 and the downstream rotor 80 is adopted. Accordingly, while achieving downsizing in an outer diameter dimension of the apparatus, a desired discharged rate is ensured and enhanced pumping performance can be obtained as reducing a discharge resistance at high load, that is, as suppressing decrease in final discharge pressure.
In the abovementioned structure, the rotor case 40 is fitted into the housing (10, 20), the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82) are arranged to be rotated in the rotor case 40, and the side plate 50 is in contact with the annular end face 46 at one side of the rotor case 40 as being urged by the O-ring (elastic member) 60 in the direction of the axis line S of the rotary shaft 30. Accordingly, for example, even in a case that the housing (10, 20) is thermally expanded, the rotor case 40 is continuously in a state of being sandwiched between the inner wall face of the housing (20) and the side plate 50 owing to the urging force of the O-ring 60.
Therefore, both side faces of the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) and both side faces of the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82) which are contained in the rotor case 40 can maintain constant clearance (side clearance) enabling to be slid between the inner wall face of the housing (20) and the middle wall portion 44 and between the side plate 50 and the middle wall portion 44. In addition, oil leakage through the clearance can be prevented from occurring and stable volume efficiency (pumping performance) can be obtained. Further, the urging force of the O-ring 60 is not applied to both the side faces of the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82). Accordingly, compared to a conventional oil pump, slide resistance and operational torque can be reduced and durability can be improved.
Further, the rotor case 40 is made of material having the same thermal expansion coefficient as that of the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82). Therefore, even in a case that the housing (10, 20), the rotor case 40, the upstream rotor 70, and the downstream rotor 80 are deformed with thermal expansion and the like respectively, relative dimensional relations among the rotor case 40, the upstream rotor 70, and the downstream rotor 80 can be maintained at constant. That is, the side clearance can be maintained at constant. Accordingly, it is possible to maintain desired pumping performance more reliably without being influenced by thermal expansion and the like.
Further, since the side plate 50 is made of material having the same thermal expansion coefficient as that of the housing (10, 20), the housing (10, 20) and the side plate 50 can be reduced in weight as being made of light-weight material or the like. In addition, even when the same thermal deformation (thermal expansion) occurs at the side plate 50 and the housing (10, 20), contact relations among both the side faces of the upstream rotor 70 and the downstream rotor 80, the inner wall face of the housing (20), and the side plate 50 can be maintained in a desired state owing to that the side plate 50 is urged by the O-ring 60 in the direction of the axis line S. Accordingly, it is possible to maintain desired pumping performance.
In particular, dimensional relations among the rotor case 40, the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72), and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82) are arranged to satisfy “Wc>Wr” while Wc denotes a width dimension of the rotor case 40 in the direction of the axis line S of the rotary shaft 30 and Wr denotes a width dimension of the upstream rotor 70 and the downstream rotor 80 in the direction of the axis line S of the rotary shaft 30.
According to the above, both the side faces of the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82) are maintained as being faced to the inner wall face of the housing (20) and the side plate 50 with constant clearance ΔC (=Wc−Wr) formed therebetween in a state of not being protruded from both ends (the annular end faces 45, 46 at both sides) of the rotor case 40 in the direction of the axis line S. Accordingly, it is possible to ensure desired pumping performance while further reducing slide resistance.
Next, operation of the oil pump will be described with reference to
First, when the rotary shaft 30 is rotationally driven by an engine, the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) is rotated counterclockwise in
Then, owing to continuous rotation of the upstream rotor 70, the oil sucked into the pump chamber P is pressurized. In the pressurization process, air-mixed oil is forcedly ejected outside through the ejection port 24. Further, the remaining oil is introduced to the downstream rotor 80 through the upstream rotor discharge port 44c, the communication port 44e, and the downstream rotor inlet port 44d.
Subsequently, the oil is sucked into the pump chamber P of the downstream rotor 80 through the downstream rotor inlet port 44d with clockwise rotation in
Owing to continuous rotation of the downstream rotor 80, the oil sucked into the pump chamber P is pressurized and supplied to an external lubrication area through the discharge port 52 and the discharge passage
Practically, cooperative action of the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82) causes the respective pump chambers to continuously perform sucking of oil, pressurizing of oil, ejecting of mixed air (air-mixed oil), and discharging of oil.
Here, even in a case that the housing (10, 20) is thermally expanded, the rotor case 40 is continuously in a state of being sandwiched between the inner wall face of the housing (20) and the side plate 50 owing to the urging force of the O-ring 60. Therefore, both the side faces of the upstream rotor 70 and the downstream rotor 80 contained in the rotor case 40 can maintain constant clearance (side clearance) enabling to be slid between the inner wall face of the housing (20) and the side plate 50. In addition, oil leakage through the clearance can be prevented from occurring and stable volume efficiency (pumping performance) can be obtained. Further, the urging force of the O-ring 60 is not applied to both the side faces of the upstream rotor 70 and the downstream rotor 80. Accordingly, compared to a conventional oil pump, slide resistance and operational torque can be reduced and durability can be improved.
Another embodiment of an oil pump according to the present invention is illustrated in
In this embodiment, as illustrated in
Further, a side plate 50′ is arranged to be in contact with a housing cover 20′ and the O-ring 60 is arranged as the elastic member between the housing cover 20′ and the side plate 50′.
The upstream rotor case 40′ is made of steel, sintered steel, iron, or the like. As illustrated in
A positioning hole into which a positioning pin is fitted for positioning against the spacer member 90 is formed at the annular end face 45′.
As illustrated in
The downstream rotor case 40″ is made of steel, sintered steel, iron, or the like. As illustrated in
A positioning hole into which a positioning pin is fitted for positioning against the spacer member 90 is formed at the annular end face 46′.
As illustrated in
The spacer member 90 is made of aluminum material or the like being the same as the housing (10, 20) for weight saving and the like. The spacer member 90 includes the bearing hole 44a, the inlet port 44b, the upstream rotor discharge port 44c, the downstream rotor inlet port 44d, the communication port 44e for communication, a positioning hole into which a positioning pin is fitted for positioning between the upstream rotor case 40′ and the downstream rotor case 40″, and the like.
The side plate 50′ is made of aluminum material or the like being the same as the housing (10, 20) for weight saving and the like. As illustrated in
The housing cover 20′ is made of aluminum material or the like being the same as the housing (10, 20) for weight saving and the like. As illustrated in
The present embodiment also provides a two-stage trochoid pump in which the upstream rotor 70 is arranged in the upstream rotor case 40′, the downstream rotor 80 is arranged in the downstream rotor case 40″, and the spacer member 90 defines a space between the upstream rotor 70 and the downstream rotor 80. Accordingly, as described above, while maintaining clearance (side clearance) at constant in the direction of the axis line S, a desired discharge rate is ensured and enhanced pumping performance can be obtained as reducing a discharge resistance at high load, that is, as suppressing decrease in final discharge pressure.
In particular, since the rotor case includes the upstream rotor case 40′ and the downstream rotor case 40″ and the separated spacer member 90 is interposed therebetween, clearance at both side faces of the upstream rotor 70 and clearance at both side faces of the downstream rotor 80 can be maintained at constant independently with a high degree of accuracy.
Further, since the spacer member 90 is made of material having the same thermal expansion coefficient as that of the housing (10, 20′), the spacer member 90 is sandwiched between the upstream rotor case 40′ and the downstream rotor case 40″ via the elastically-urged side plate 50′ and the inner wall face of the housing (10) even when the same thermal deformation (thermal expansion) occurs at the spacer member 90 and, the housing (10, 20′). Accordingly, contact relations among both the side faces of the upstream rotor 70 and the downstream rotor 80, the inner wall face of the housing (10), the spacer member 90, and the side plate 50′ can be maintained in a desired state. In particular, when the housing (10, 20′) and the spacer member 90 are made of light weight material or the like, desired pumping performance can be maintained while achieving reduction in weight.
In the description of the above embodiments, the present invention is applied to the two-stage trochoid pump which includes the upstream rotor 70 (the first inner rotor 71 and the first outer rotor 72) and the downstream rotor 80 (the second inner rotor 81 and the second outer rotor 82). However, not limited to the above, the present invention may be applied to a structure including one pair of an inner rotor and an outer rotor.
In the description of the above embodiments, the present invention is applied to a structure in which the housing is separated into the housing body and the housing cover. However, not limited to the above, the present invention may be applied to a structure in which a dual partitioning housing includes a first housing half body and a second housing half body which define a concave portion respectively.
In the description of the above embodiments, the oil pump is a trochoid pump. However, not limited to the above, the present invention may be adopted to an internal gear type oil pump, an external gear type oil pump, or the like.
As described above, according to the oil pump of the present invention, while achieving reduction of slide resistance, reduction of operational torque, suppression of deterioration with time, and the like, volume efficiency (pumping performance) can be stabilized and durability can be improved as preventing variation of side clearance at both the side faces of the inner rotor and the outer rotor. Accordingly, in addition to be naturally adopted to an engine which is mounted on an automobile or the like, an oil pump of the present invention is useful for motorcycles, other vehicles having an engine mounted, other mechanisms requiring pressured feeding of lubricant oil, and the like.
Number | Date | Country | Kind |
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2012-034842 | Feb 2012 | JP | national |
Filing Document | Filing Date | Country | Kind |
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PCT/JP2013/051819 | 1/29/2013 | WO | 00 |
Publishing Document | Publishing Date | Country | Kind |
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WO2013/125302 | 8/29/2013 | WO | A |
Number | Name | Date | Kind |
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4253803 | Wormmeester | Mar 1981 | A |
4540347 | Child | Sep 1985 | A |
7410349 | Ronk | Aug 2008 | B2 |
Number | Date | Country |
---|---|---|
63-186984 | Nov 1988 | JP |
1-61477 | Apr 1989 | JP |
5-89881 | Dec 1993 | JP |
6-323261 | Nov 1994 | JP |
7-247964 | Sep 1995 | JP |
8-42418 | Feb 1996 | JP |
11-50972 | Feb 1999 | JP |
11-343982 | Dec 1999 | JP |
2006-125239 | May 2006 | JP |
Entry |
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International Search Report issued Apr. 16, 2013 in International Application No. PCT/JP2013/051819. |
Number | Date | Country | |
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20150017049 A1 | Jan 2015 | US |