CN104265601A - Multistage Compressor And Oscillating Piston - Google Patents
Multistage Compressor And Oscillating Piston Download PDFInfo
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- CN104265601A CN104265601A CN201410400163.9A CN201410400163A CN104265601A CN 104265601 A CN104265601 A CN 104265601A CN 201410400163 A CN201410400163 A CN 201410400163A CN 104265601 A CN104265601 A CN 104265601A
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Abstract
A multi-staged compressor includes a low-pressure compressor (A), a high-pressure compressor (B) connected with the low-pressure compressor (A), a swing piston (3) slidably installed in a cylinder (1) of the low-pressure compressor (A), and a swing piston (4) slidably installed in a cylinder (2) of the high-pressure compressor (B). The swing piston (4) of high-pressure compressor (B) is installed with a lip-shaped ring (14) having a seal part (15) connected to the inner surface of the above-mentioned cylinder (2) in the high-pressure zone and capable of elastically deforming till a seal effect is generated.
Description
The application is the applying date is on June 30th, 2010, invention and created name is multistage compressor and oscillating-piston, application number are the divisional application of this application of 201010221388.X.
Technical field
The present invention relates to the multistage compressor and the oscillating-piston that are boosted to high pressure by multiple compressor from low pressure successively.
Background technique
In multistage compressor, atmospheric air, by the compressor compresses of low pressure, thereafter, is further compressed by the compressor of high pressure by the air compressed, boosts to high pressure.
As the piston that compressor uses, there are known the piston of common cylinder type that adopts such as Reciprocating engine and carry out reciprocal oscillating-piston while swinging in cylinder.The piston portion of cylinder type piston moves along the axle center of cylinder, therefore working stability, but complex structure and price is high.On the other hand, the structure of oscillating-piston simply and more cheap.But because oscillating-piston is the structure that piston portion swings in cylinder, the space therefore between piston portion and cylinder changes.Therefore, when in oscillating-piston, space becomes maximum, this space is larger than the space between the piston portion of cylinder type piston and cylinder.Therefore, in oscillating-piston, the lip circle being arranged on piston portion must be soft.But, when the oscillating-piston of this structure is used for the high pressure side of multistage compressor, lip circle cannot withstand high pressures loading and be out of shape, air spills from the space between lip circle and cylinder, compression efficiency reduce.Be the compressor of oscillating-piston for low pressure mostly, the compressor of high pressure adopts the example of cylinder type piston in the past.
The structure of oscillating-piston is simple conversely speaking, and therefore fault is also few, and price is also cheap.Therefore, it is desirable on high-tension side compressor, also to adopt oscillating-piston.Patent Document 1 discloses the compressor that high pressure side also adopts the structure of oscillating-piston.In the structure of patent documentation 1, overlap the cast plate-like support ring of plastic wall thickness in the back side of lip circle, support ring is a little from piston portion pull-out, by the excessive deformation adopting said structure to prevent lip circle.
Patent documentation 1 JP-A-2003-222077
In the structure of patent document 1, support ring withstand high pressures.But the external diameter of support ring and the internal diameter of cylinder do not have covering part.That is, the part of the change in space when not tackling piston portion oscillating motion between piston portion and cylinder.Further, the size of pull-out part that support ring is given prominence to from the outer circumferential face of piston portion must be the size in the space of the centre in the space minimum and maximum when swinging of reply piston portion.Therefore, when above-mentioned space becomes maximum, be difficult to the distortion fully preventing lip circle.
Summary of the invention
More than one embodiment of the present invention provides by improving lip circle and adopts the multistage compressor of oscillating-piston at low voltage side compressor and high side compressors both sides and also can tackle the oscillating-piston of high pressure.
According to more than one embodiment of the present invention, multistage compressor has: low voltage side compressor A; The high side compressors B be connected with above-mentioned low voltage side compressor A; Slidably be configured in the oscillating-piston 3 in the cylinder 1 of low voltage side compressor A; And the oscillating-piston 4 be slidably configured in the cylinder 2 of high side compressors B.The oscillating-piston 4 of high side compressors B has lip circle 14, and the internal surface that above-mentioned lip circle 14 has in high-pressure area with above-mentioned cylinder 2 contacts, can resiliently deformable to the sealed department 15 of the degree sealed.
According to said structure, in low voltage side compressor and high side compressors, the interior pressure of cylinder is completely different, in high pressure side, larger pressure is applied to the lip circle of oscillating-piston, but the sealed department of this lip circle at least contacts with the internal surface of cylinder in high-pressure area, can resiliently deformable to the degree sealed, therefore, it is possible to pressurized air by the compressor compresses by low voltage side boosts to more high pressure sending by high-tension side compressor.Therefore, it is possible to provide the multistage compressor of the oscillating-piston that can adopt in low voltage side and on high-tension side compressor.
In addition, the external diameter of the piston portion 8 of the oscillating-piston 4 of high side compressors B also can be less than the external diameter of the piston portion 7 of the oscillating-piston 3 of low voltage side compressor A.
According to this structure, the compressive load on high-tension side piston portion can not become large sharp compared with the compressive load of low voltage side, therefore, it is possible to make multistage compression successfully operate.
In addition, the angle of oscillation α determined by the stroke L of the oscillating-piston 4 of high side compressors B and the distance from the O1 to the center O2 of sealed department of swing rotary center is less than the angle of oscillation determined by the stroke of the oscillating-piston 3 of low voltage side compressor A and the distance from swing rotary center to the center of sealed department.
According to this structure, during high pressure, oscillating-piston swings hardly, therefore easily guarantees the sealing of oscillating-piston.
In addition, the external diameter of the lip circle 14 of the oscillating-piston 4 of high side compressors B is less relative to the covering amount of the internal diameter of cylinder 1 than the external diameter of the lip circle 13 of the oscillating-piston 3 of low voltage side compressor A relative to the covering amount of the internal diameter of cylinder 2.
According to this structure, become when the lip circle of on high-tension side oscillating-piston is subject to high pressure and be difficult to carry out resiliently deformable, be therefore difficult to produce Leakage Gas from the part of distortion, the pressure producing sealed department reduce or the possibility of poor sealing little.In addition, because the slip resistance of high pressure cylinder and lip circle diminishes, when therefore being inserted by high pressure side oscillating-piston and be assembled into high pressure side cylinder, resistance is little, thus improves assembling performance.
In addition, the lip circle 13,14 of above-mentioned oscillating-piston 3,4 also can be complete cycle continuous print shape, and the bilabial of the lip circle 14 of the oscillating-piston 4 of high side compressors B also can be less than the bilabial of the lip circle 13 of the oscillating-piston 3 of low voltage side compressor A.
According to this structure, the bilabial that the bilabial of the lip circle at least sealed in high-pressure area of on high-tension side oscillating-piston is formed as the lip circle of the oscillating-piston than low voltage side is low, therefore the elasticity of on high-tension side lip circle is also low, uprises for the pressure expanded laterally.Therefore, on high-tension side lip circle is difficult to distortion when being subject to High Pressure, and the possibility producing the poor sealing that air leakage causes is little.
In addition, because the slip resistance of high pressure side cylinder and lip circle diminishes, when therefore being inserted by high pressure side oscillating-piston and be assembled into high pressure side cylinder, resistance is little, thus improves assembling performance.
In addition, the lip circle 14 of the oscillating-piston 4 of high side compressors B also can have the high-pressure area sealed department 16 sealed in high-pressure area and the area of low pressure sealed department 17 sealed in area of low pressure.
According to this structure, during low-pressure state, be difficult to resiliently deformable at the high-pressure area sealed department of high-pressure area effect, but area of low pressure sealed department resiliently deformable in a low voltage state, sufficient sealing effect can be guaranteed.Therefore, even if diminish for the back pressure rising of lip circle in a high voltage state, the pushing force of cylinder is reduced, effectively can prevent the wearing and tearing of lip circle.
In addition, according to more than one embodiment of the present invention, oscillating-piston 4, has: be wholely set in the front end of connecting rod 6 and the piston main body 18 of the plate-like swung in cylinder 2; Be located at the top of piston main body 18, the ring-shaped pressuring plate 20 less than piston main body 18 diameter; And be located between piston main body 18 and ring-shaped pressuring plate 20, the lip circle 14 nonmetal processed between packed-piston main body 18 and cylinder 2 internal surface.The base portion 25 and standing up from the outer circumference end of base portion 25 that above-mentioned lip circle 14 has the cast tabular be clamped between piston main body 18 and ring-shaped pressuring plate 20 is formed and lip 15 between packed-piston main body 18 and cylinder 2 internal surface.The size r2+t that the radius of curvature r2 of the inside angle part 28 that the radius of curvature r1 of the outer corners 27 that base portion 25 contacts with two outer side surfaces of lip 15 contacts with two inner side surfaces of lip 15 than base portion 25 adds the thickness t of lip circle 14 is little.
According to this structure, can diminish in piston main body, space between cylinder and lip circle.Therefore, the volume in bight relatively becomes large, even if apply to press from the cylinder of the top of piston main body, also can reduce the stress that interior pressure produces.Consequently can suppress the distortion of lip circle well.Further, even if press liter in cylinder, the power expanded laterally due to lip is little, and the wear extent of lip circle reduces.
In addition, the most external diameter of above-mentioned lip circle 14 also can be larger than the internal diameter of cylinder 2.When the most external diameter of above-mentioned lip circle 14 also can tilt maximum than piston main body 18, the major diameter of the ellipse of the internal surface of the cylinder 2 of contact is large.
According to this structure, lip circle produces the part hidden relative to cylinder surfaces, therefore, it is possible to effectively between sealing cylinder and oscillating-piston.
In addition, the lower surface 30 of the base portion 25 of above-mentioned lip circle 14 also can contact with the upper surface face of piston main body 18 from the position 29a of the radial direction corresponding to the inner end 28a of above-mentioned inside angle part 28 towards cylinder 2 side.
According to this structure, can be able to be suppressed to less in piston main body, space between cylinder and lip circle.
In addition, under the state that above-mentioned oscillating-piston 4 does not tilt relative to cylinder 2, the position 29b that lip circle 14 also can contact from the prolongation 31a of at least upper surface 31 of base portion 25 with the internal surface of above-mentioned cylinder 2, towards the upper end side of lip circle 14, contacts with 2, above-mentioned cylinder.
According to this structure, under the state that oscillating-piston does not tilt relative to cylinder, the outboard end of outer corners is compared above-mentioned upper surface and is extended corresponding position and be positioned at downside, therefore, it is possible to be suppressed to less by the piston main body of connecting rod, space between cylinder and lip circle.
In addition, when described oscillating-piston 4 tilts maximum, in the upside that the space of piston main body 18 and cylinder 2 is little, the periphery of above-mentioned lip circle 14 also can contact with cylinder 2 in the position 29c of the above-below direction corresponding to the outboard end 28b than above-mentioned inside angle part 28 region on the lower.
According to this structure, the piston main body of connecting rod, the space between lip circle and cylinder diminish.Further, covering amount when tilting maximum is abundant, and the power therefore expanded laterally is supplemented by the elasticity of lip, can guarantee sealing.
In addition, when described oscillating-piston 4 tilts maximum, in the side that the space of piston main body 18 and cylinder 2 is large, the space D1 between the lip 15 of above-mentioned lip circle 14 and ring-shaped pressuring plate 20 also can be less than the space D2 between piston main body 18 top and cylinder 2.
According to this structure, even if when above-mentioned oscillating-piston tilts maximum, piston main body or ring-shaped pressuring plate also directly can not encounter cylinder.In addition, the amount of plastic deformation of ring-shaped pressuring plate can be suppressed.
In addition, also can be formed with small space Q between the lip 15 of above-mentioned lip circle 14 and ring-shaped pressuring plate 20, the outer circumferential face 33 of above-mentioned ring-shaped pressuring plate 20 also can the roughly spherical surface configuration roughly the same with the internal diameter of above-mentioned cylinder 2 by diameter be formed.
According to this structure, the pressure increase produced by the inertia of the oscillating motion based on oscillating-piston, effectively can be suppressed lip circle or ring-shaped pressuring plate push cylinder and are out of shape, prevent repeated stress, can prevent the fatigue of lip circle.
In addition, the upper surface 31 of the base portion 25 of above-mentioned lip circle 14 also can, at the inner end 28a of the curved surface than above-mentioned inside angle part 28 away from the position of central side, start to contact with the lower surface of ring-shaped pressuring plate 20.
According to this structure, inner end and the contact straight portion started between position become the estranged region of the lower surface of not contact ring pressing plate, and stress is disperseed, and are difficult on bight, produce stress and concentrate.
In addition, above-mentioned ring-shaped pressuring plate 20 and piston main body 18 also directly can abut in the inner side of the base portion 25 of lip circle 14.
According to this structure, the interval between ring-shaped pressuring plate and piston main body becomes constant, and therefore lip circle can not be clipped by excessive pushing force and be out of shape.Further, ring-shaped pressuring plate also can not float from piston main body.Therefore, it is possible to relax the stress for fixed-use bolt, tightening torque can be maintained.
In addition, above-mentioned ring-shaped pressuring plate 20 and piston main body 18 also when effect has the pressure of using state, can abut via medium material inside the base portion 25 of lip circle 14.
According to this structure, stress is disperseed, and is difficult on bight, produce stress and concentrates.
In addition, ring-shaped pressuring plate 20 also can have the circular protrusion 34 of the base portion 25 of pushing lip circle 14.
According to this structure, the circular protrusion brute force of ring-shaped pressuring plate is pressed to the contact surface portions with the base portion of lip circle, thus circular protrusion cuts above-mentioned contact surface portions.Therefore, prevent the movement of lip circle on piston main body, fix lip circle effectively.And can well between packed-piston portion and cylinder.
In addition, the circular protrusion 35 of the opening edge portion of the central portion of the base portion 25 boosting lip circle 14 also can be formed at the upper surface of above-mentioned piston main body 18.
According to this structure, the upper surface of piston main body is formed the circular protrusion of the opening edge portion of the central portion of the base portion boosting lip circle, therefore the opening edge portion of lip circle is boosted by ring-type ridge, can eliminate the space between base portion and ring-shaped pressuring plate, the interior pressure of the upper room of cylinder can not drain to the lower room of the bottom of piston portion.
In addition, it is comparatively large that above-mentioned connecting rod 6 also can be formed as width at swaying direction, and the direction orthogonal with the width direction of connecting rod 6 also can be formed with deformation suppression section 36, and this deformation suppression section 36 also can engage with the lower surface of piston main body 18.
According to this structure, be formed as width by connecting rod at swaying direction comparatively large, piston main body is difficult to distortion on swaying direction.Further, owing to being formed with deformation suppression section on connecting rod, connecting rod is also strengthened on the direction orthogonal with its swaying direction, and piston main body is also difficult to distortion in the direction in which.The distortion of distortion on swaying direction and the direction orthogonal with it of the piston main body that pressure causes differs widely.Therefore, fixed-use bolt produces large stress.But, this stress can be reduced by the deformation suppression section of ribbed.
In addition, the outer circumferential face of at least one party of above-mentioned piston main body 18 and ring-shaped pressuring plate 20 also can be provided with have equal with lip circle 14 more than guard block 37a, 37b of nonmetal system of intensity.
In general, when lip circle continues exceeding engineering time to use, there are the wearing and tearing of lip circle, metal piston main body or ring-shaped pressuring plate directly cause impaired with cylinder contact and rubbing mutually, the danger of compression efficiency reduction or fault.But according to this structure, by arranging guard block, before piston main body or ring-shaped pressuring plate contact, guard block directly and cylinder contact, can not produce the problem that piston main body or ring-shaped pressuring plate directly contact with cylinder surfaces and rub, can protect cylinder.
In addition, according to more than one embodiment of the present invention, oscillating-piston 4, has: be wholely set in the front end of connecting rod 6 and the piston main body 18a of the plate-like swung in cylinder 2; Be located at the top of piston main body 18a, the lining pressing plate 20a slightly less than piston main body 18a diameter; Be located between piston main body 18a and lining pressing plate 20a, the lining 38 between packed-piston main body 18a and cylinder 2 internal surface; And be located at the piston ring 39 of periphery of above-mentioned lining pressing plate 20a.The roughly spherical surface configuration of the degree that outer circumferential face is identical with the internal diameter of above-mentioned cylinder 2 by diameter or diameter is slightly less than the internal diameter of above-mentioned cylinder 2 of above-mentioned lining 38 is formed.The roughly spherical surface configuration of the degree that outer circumferential face is identical with the internal diameter of above-mentioned cylinder 2 by diameter or diameter is slightly less than the internal diameter of above-mentioned cylinder 2 of above-mentioned piston ring 39 is formed.A part for above-mentioned piston ring 39 is cut off, and is incorporated in having play in the accommodating groove 42 on the periphery being formed at above-mentioned lining pressing plate 20a.
According to this structure, lining is made up of the roughly spherical surface configuration of the degree that diameter is identical with the internal diameter of cylinder or diameter is slightly less than the internal diameter of cylinder with the outer circumferential face of piston ring.By this spherical shape, the pressure increase produced by the inertia of the oscillating motion based on oscillating-piston, effectively can suppress due to pushing force when lining or lining pressing plate pushing cylinder and be out of shape, repeated stress can be prevented in addition, the fatigue of lining can be prevented.
Further, piston ring is not continuous print, and a part is cut-off, is incorporated in having play in the accommodating groove that the periphery of lining pressing plate is formed.Therefore, piston ring radially can stretch in accommodating groove.Therefore, when piston main body is subject to back pressure, piston ring is pushed expansion outward, even if therefore piston main body tilts, also can maintain linear sealing by lining.In addition, from intensity, there is sufficient thickness, relaxed tolerance of size significantly.
Other characteristic sum effects can be learnt from the record of embodiment and claim.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of multistage (secondary) compressor of exemplary embodiments of the present invention.
Fig. 2 (a) ~ Fig. 2 (g) is the central cross sectional view of the various modes of the lip circle of exemplary embodiments of the present invention respectively.
Fig. 3 (a) and Fig. 3 (b) is the sectional view representing the form reducing angle of oscillation, and Fig. 3 (c) is the sectional view of the form of the oscillating-piston representing common angle of oscillation.
Fig. 4 is the sectional view of the major component of high pressure oscillating-piston.
Fig. 5 is the enlarged view that a part (outer corners) for the oscillating-piston of Altered Graphs 4 carries out representing.
Fig. 6 (a) and Fig. 6 (b) is the central cross sectional view of the lip circle of other modes respectively.
Fig. 7 is the sectional view of state when representing that the oscillating-piston of Fig. 4 tilts maximum.
Fig. 8 (a) is the front view of other modes of the deformation suppression section representing connecting rod, and Fig. 8 (b) is the side view of the connecting rod of Fig. 8 (a).
Fig. 9 (a) is the front view of other modes of the deformation suppression section representing connecting rod, and Fig. 9 (b) is the sectional elevation of the connecting rod of Fig. 9 (a).
Figure 10 is the sectional view of oscillating-piston when being provided with guard block.
Figure 11 is the sectional view of other mode of executions representing oscillating-piston.
Figure 12 is the perspective view of the air compressor of multistage (secondary) compressor being equipped with exemplary embodiments.
Embodiment
Fig. 1 represents multistage (secondary) compressor.This multistage compressor connects low voltage side compressor A and high side compressors B and forms, swingable and be accommodated with oscillating-piston 3,4 slidably in the cylinder 1,2 of above-mentioned each compressor A, B.In each oscillating-piston 3,4, be provided with the piston portion 7,8 of plate-like integratedly in the front end (small end) of connecting rod 5,6.Be formed at the bent axle 12 bearing hole 10,11 on the eccentric position of the base portion (large end) of connecting rod 5,6 being supported with the central part being configured at apparatus main body.Bent axle 12 is passive by not shown rotating driving device to be connected.
In above-mentioned compressor A, B, by the rotation of bent axle 12, oscillating-piston 3 to-and-fro motion of the compressor A of low pressure (once pressing) side, the air be taken in the cylinder 1 of low voltage side is compressed, and is admitted to the cylinder 2 of the compressor B of high pressure (secondary pressure) side.This pressurized air is further compressed by the to-and-fro motion of on high-tension side piston 4, boosts into high pressure.The air of the high pressure obtained is sent to utilizing pneumatically operated various device or instrument.
The oscillating-piston 4 of on high-tension side compressor has following structure characteristic.
First, the external diameter of the piston portion 8 of on high-tension side oscillating-piston 4 is formed as less than the piston portion 7 of the oscillating-piston 3 of low voltage side.This sharply can not increase compared with the compressive load of the piston portion 7 of low voltage side relative to the compressive load of on high-tension side piston portion 8 to make.
The periphery of the piston portion 7,8 of above-mentioned each oscillating-piston 3,4 is provided with the lip circle 13,14 between packed-piston 3,4 and cylinder 1,2.Lip circle 13,14 is formed by teflon or rotten teflon, copper or bell metal powder, spherical carbon element or carbon fiber, nonmetallic material that the composition of molybdenum dioxide is formed specifically by synthetic resin, synthetic rubber etc., is the parts that complete cycle does not have continuous print jaggy circular.
The internal surface that the lip circle 14 of the oscillating-piston 4 of on high-tension side compressor has in high-pressure area with cylinder 2 contacts, can resiliently deformable to the sealed department (lip) of the degree sealed.
Therefore, above-mentioned lip circle 14 has the feature of following structure.
That is, the external diameter of above-mentioned lip circle 14 is formed as at least little relative to the covering amount of the internal diameter of cylinder 1 than the external diameter of the lip circle 13 of the oscillating-piston 3 of low voltage side relative to the covering amount of the internal diameter of cylinder 2.This be due to the covering part of lip circle 14 large time, inevitable elasticity is also high, becomes soft, therefore exists when being subject to the interior pressure of high pressure and is easily out of shape, produce Leakage Gas by the part of being out of shape, the danger of generation poor sealing.Therefore, by making the covering amount of the lip circle 14 of on high-tension side oscillating-piston 4 at least less than low voltage side, thus resiliently deformable is difficult to when being set to and being subject to high pressure.
And then the height (bilabial) being formed at the lip 15 of the periphery of on high-tension side lip circle 14 is formed as at least low than the bilabial of the lip circle 14 of low voltage side.
When this is also due to bilabial height, elasticity also uprises, and is easily out of shape when being subject to the effect of high pressure, there is the possibility of the poor sealing that Leakage Gas causes, and is also in order to piston portion 8 operation be received in cylinder 2 is become easy.
The height of the lip 15 of on high-tension side lip circle 14 is formed as lower than low voltage side, therefore elasticity is also low, pressure for expanding laterally uprises, even if the effect being therefore subject to high pressure is also difficult to distortion, the possibility that the poor sealing that therefore stress reduces or air leakage causes occurs is little.In addition, the operation be received in cylinder 2 by lip circle 14 during assembling is not difficult.Lip 15 can be received into the relation between area that contractile force in cylinder 2 contacts with the internal surface of cylinder 2 due to the loading of shrinking lip 15 and lip 15 during operation, be set as compared with during low pressure within ± 10%.
In addition, in the lip circle 14 of on high-tension side oscillating-piston, as shown in Fig. 2 (a), require that at least there is above-mentioned covering amount and bilabial, but when compressor start etc., the pressure on high-tension side cylinder 2 does not fully rise, when becoming low-pressure state, be difficult to resiliently deformable at the lip 15 of the lip circle 14 of high-pressure area effect, therefore exist because the difference of condition cannot play the possibility of sealing.Therefore, as shown in Fig. 2 (b), the lower seal portion 16 being preferably arranged on the high-pressure area of the path that high-pressure area seals on the lip 15 of above-mentioned lip circle 14 integratedly and the top seal portion 17 of the area of low pressure in large footpath sealed in area of low pressure.Lower seal portion 16 is formed as heavy wall, and on the other hand, top seal portion 17 is formed as thin-walled, than being easier to resiliently deformable.Stepped part 18 is formed between lower seal portion 16 and top seal portion 17.
According to above-mentioned lip coil structures, when low-pressure state, be difficult to resiliently deformable in the lower seal portion 16 of the lip circle 14 of high-pressure area effect, but top seal portion 17 resiliently deformable in a low voltage state, sufficient sealing effect can be guaranteed.So, also can play sealing in a low voltage state, even if therefore in a high voltage state, rise relative to the back pressure of lip circle 14 and diminish, the pushing force for cylinder 2 reduces, and effectively can prevent the wearing and tearing of lip circle 14.
In addition, the layout structure in lower seal portion 16 and top seal portion 17 is not limited to aforesaid way.Such as, as shown in Fig. 2 (c), also can not arrange step between top seal portion 17 and lower seal portion 16, upper and lower sealed department 16,17 is continuous print structure.As shown in Fig. 2 (d), also can be top seal portion 17 laterally counter go out formed, and easily there is resiliently deformable.As shown in Fig. 2 (e), also top seal portion 17 can be formed as the structure of the shape directly extended from lower seal portion 16.
In addition, may not be the structure forming top seal portion 17 with the top in lower seal portion 16 continuously, and also can be as shown in Fig. 2 (f), lower seal portion 16 and top seal portion 17 are formed respectively, and top seal portion 17 is formed from giving prominence to obliquely upward by paracentral inner side than lower seal portion 16.The upper end of above-mentioned sealed department 17 extends to form the top in lower seal portion 16, and the height in top seal portion 17 is higher.Therefore, top seal portion 17 resiliently deformable easier than lower seal portion 16, can tackle low pressure.In this case, also can be configured to as shown in Fig. 2 (g), top seal portion 16 is high pressure use, and lower seal portion 17 is low pressure use.
In addition, in order to tackle high pressure, except the shape of lip circle 14, can also be set to that the angle of oscillation of the oscillating-piston 4 of on high-tension side compressor is less than the angle of oscillation of the oscillating-piston 3 of the compressor of low voltage side.Angle of oscillation α by the stroke L of oscillating-piston 4 namely from the distance the central shaft P of connecting rod 6 to swing rotary center O1, decide with the distance from the O1 to the center O2 of the sealed department of lip circle 14 of swing rotary center.In order to reduce angle of oscillation α, as shown in Fig. 3 (a), do not change the stroke L of oscillating-piston 4, and increase by the length of the connecting rod 6 shown in the distance from the O1 to the center O2 of sealed department of swing rotary center, or as shown in Fig. 3 (b), do not change the length of connecting rod 6, reduce the stroke L of oscillating-piston 4.
In addition, Fig. 3 (c) is the reference drawing of the maximum inclination state representing the oscillating-piston 4 reduced before angle of oscillation.In Fig. 3 (c), α 0 represents angle of oscillation, and L0 represents stroke.
Secondly, the structure for the oscillating-piston of reply high pressure is described in detail.
Fig. 4 is on high-tension side oscillating-piston, and this oscillating-piston 4 has: be wholely set in the front end of connecting rod 6 and the piston main body 18 of the plate-like of sliding while swing in cylinder 2; Be located at the top of piston main body 18 and the diameter ring-shaped pressuring plate 20 slightly less than piston main body 18; Be located between piston main body 18 and ring-shaped pressuring plate 20, to the lip circle 14 sealed between cylinder 2 internal surface.Lip circle 14 is formed by the nonmetallic material such as synthetic resin, synthetic rubber.
Circular depressions 21 is formed at the upper surface of piston main body 18.On the other hand, ring-shaped pressuring plate 20 is toroidal, gives prominence to be formed with circular protrusions 22 in central lower.Further, the circular protrusions 22 of ring-shaped pressuring plate 20 is fitted to the inner side of the circular depressions 21 of piston main body 18, by the fixed-use bolt 23 inserted from top, ring-shaped pressuring plate 20 is fixed on the upper surface of piston main body 18.Lip circle 14 is formed as circular, under the state of circular protrusions 22 that central portion 24 (with reference to Fig. 2 (a)) is fitted to ring-shaped pressuring plate 20, is sandwiched between the ring-shaped pressuring plate 20 on top and the piston main body 18 of bottom and is fixed.
Lip circle 14 is by the base portion 25 of the cast tabular be clamped between piston main body 18 and ring-shaped pressuring plate 20; And stand up obliquely upward from the outer circumference end of base portion 25 and formed, the lip 15 sealed between piston main body 18 and the internal surface of cylinder 2 is formed.Further, between base portion 25 and lip 15, the bight 26 that section is arc-shaped bend is formed with.As shown in Figure 5, the inside angle part 28 that the outer corners 27 contacted with two outer side surfaces of lip 15 by base portion 25 and base portion 25 contact with two inner side surfaces of lip 15 is formed in this bight 26.Further, between the thickness t of the radius of curvature r1 of outer corners 27 and the radius of curvature r2 of inside angle part 28 and lip circle 14, there is following relation.
R1 < r2+t, to be namely formed as being added than the radius of curvature r2 of inside angle part 28 and the thickness t of lip circle 14 size obtained little for the radius of curvature r1 of outer corners 27.That is, the thickness in bight 26 be set to than the base portion 25 of lip circle 14 and the thickness of lip 15 large.The radius of curvature of outer corners 27 also can be 0.
In addition, as shown in Fig. 6 (a), the shape in bight may not be curve, but the chamfer shape of straight line, outer corners 27 is also set to that chamfering is larger than the chamfering of inside angle part 28.Or also can as shown in Fig. 6 (b), less (outer corners 27 is little curvature, and the curvature of inside angle part 28 is 0) that the curvature in bight set is to make the thickness of the Thickness Ratio base portion 25 in bight 26, lip 15 large.
Thus, press the stress of generation to diminish in the top from piston main body 18, the distortion that interior pressure can be suppressed to produce, can reduce the space S between the piston main body 18 of connecting rod, cylinder 2 and lip circle 14.
In addition, the most external diameter of lip circle 14 is larger than the internal diameter of cylinder 2.Further illustrate, when lip circle 14 is formed as tilting maximum than piston main body 18, the major diameter of the ellipse of the internal surface of the cylinder 2 of contact is large.So, lip circle 14 has the part hidden cylinder 2, therefore, it is possible to effectively between sealing cylinder 2 and oscillating-piston 3.In order to be difficult to resiliently deformable when accepting high pressure, the covering amount being formed as the lip circle 14 of the oscillating-piston 3 than low voltage side is little.
And then, under the state of Fig. 4 and Fig. 5 do not tilted relative to cylinder 2 at oscillating-piston 4, the lower surface 30 of the base portion 25 of above-mentioned lip circle 14 contacts with the upper surface face of piston main body 18 on region to cylinder 2 side of the position 29a at least intersected vertically with inner end 28a of the curved surface from above-mentioned inside angle part 28.
Further, the position 29b that lip circle 14 at least contacts from the prolongation 31a of the upper surface 31 of base portion 25 with the internal surface of cylinder 2 contacts with 2, cylinder to upper end.In addition, the outer corners 27 of Fig. 5 is expressed as more bending than the outer corners 27 of Fig. 4.
As mentioned above, the inner end 27a of outer corners 27 is at least positioned at than above-mentioned intersection area 29a in the outer part, similarly, the outboard end 27b of outer corners 27 at least extends corresponding position 29b than above-mentioned upper surface and is positioned at downside, must be less therefore, it is possible to space S between the piston main body 18 of connecting rod 3, cylinder 2 and lip circle 14 is suppressed.
Then, as shown in Fig. 3 (c) and Fig. 7, when oscillating-piston tilts maximum, the lip circle 14 of upside and the space of cylinder 2 diminish, but when this state, contacting with cylinder 2 than with the position 29c region on the lower that the outboard end 28b of inside angle part 28 vertically intersects.
According to said structure, namely the internal surface of lip circle 14 and cylinder 2 comprises the base portion 25 of Thickness Ratio lip circle 14 bight large with the thickness of lip 15 region in the region at least comprising bight contacts.So, to be worked by the inertia that oscillating-piston 4 tilts or inclination movement causes and the pushing force towards transverse direction towards cylinder 2 produced is born by the side, bight of above-mentioned zone and lip circle 14, thus the excessive deformation of lip 15 can be suppressed well, overall intensity can be guaranteed.In addition, even if press liter in cylinder 2, the power expanded laterally due to lip 15 is lower, and therefore the wear extent of lip circle 14 reduces.In addition, can guarantee covering amount when tilting maximum fully, the power therefore expanded laterally is supplemented by the elasticity of lip 15, can guarantee sealing.
But as shown in Figure 7, when tilting maximum, the space D1 between the lip 15 of above-mentioned lip circle 14 and ring-shaped pressuring plate 20 is space below the D2 between piston main body 18 top and cylinder 2.Therefore, even if when tilting maximum, piston main body 18 or ring-shaped pressuring plate 20 directly can not encounter cylinder.In addition, the amount of plastic deformation of ring-shaped pressuring plate 20 can be suppressed.
In addition, as shown in Figure 5, the upper surface 31 of the base portion 25 of lip circle 14, the position leaving appropriate intervals I compared with the inner end 28a of the curved surface with above-mentioned inside angle part 28 to central side contacts with the lower surface of ring-shaped pressuring plate 20.Inner end 28a and above-mentioned contact start to be straight portion 32 between position, and this straight portion 32 is configured to the discontiguous estranged region with the lower surface of ring-shaped pressuring plate 20.Its reason is, if directly contacted with ring-shaped pressuring plate 20 at above-mentioned inner end 28a, then stress concentrates on bight 26.Estranged region I is set outside bight 26, thus dispersive stress, stress can be made to concentrate cannot be produced.
Further, between the inner peripheral surface and the outer circumferential face of ring-shaped pressuring plate 20 of the lip 15 of lip circle 14, small gap Q is formed with.Being assembled under the state in cylinder 2, such as, when diameter is the lip circle of 41mm, the gap Q between lip 15 and ring-shaped pressuring plate 20 is preferably below 1mm.If more than 1mm, the distortion quantitative change of lip circle is large, with the slip resistance of cylinder 2 and repeated stress large, the wear extent of lip circle 14 increases.
And then oscillating-piston 4 oscillating motion in cylinder 2, therefore at least the outer circumferential face 33 of ring-shaped pressuring plate 20 is formed as the roughly spherical surface configuration centered by the center that lip circle 14 carries out the sealed department sealed.The size of spherical of the outer circumferential face of regulation ring-shaped pressuring plate 20 is sizes identical with the internal diameter of cylinder 2 or than the spherical shape of diameter with the degree more smaller than it.In addition, above-mentioned spherical shape can only be formed at ring-shaped pressuring plate 20, also can be formed at the outer circumferential face comprising lip circle 14 and piston main body 18.
Be formed as roughly spherical by surface configuration, the pressure increase produced by the inertia of the oscillating motion based on oscillating-piston 4, lip circle 14 or ring-shaped pressuring plate 20 effectively can be suppressed to be pressed to cylinder 2 and to be out of shape, repeated stress can be prevented, prevent the fatigue of lip circle 14.
Further, as shown in Figure 4, the upper surface of the lower surface of the circular protrusions 22 of ring-shaped pressuring plate 20 and the circular depressions 21 of piston main body 18 directly abuts in the inner side of the base portion 25 of lip circle 14.Therefore, the alternate constant between ring-shaped pressuring plate 20 and piston main body 18.This interval is less than the thickness of base portion 25, but its pushing force is constant, and base portion 25 can not be out of shape by the clamping of excessive pushing force.In addition, ring-shaped pressuring plate 20 can not float from piston main body 18, therefore the pressure increase produced by the inertia based on the oscillating motion of oscillating-piston 4, the stress towards fixed-use bolt 23 produced when lip circle 14 or ring-shaped pressuring plate 20 push cylinder 20 is relaxed, and can maintain tightening torque.
In addition, ring-shaped pressuring plate 20 and piston main body 18 are not limited to the mode of directly abutting.When effect has the pressure of using state, also can be configured to abut via medium material (not shown) in the inner side of the base portion 25 of lip circle 14.As medium material, can be the such parts of sheet metal, also can use by the time through and the binder of sclerosis.
And then, on the lower surface of ring-shaped pressuring plate 20, as shown in Figure 5, be formed with the circular protrusion 34 of the face contacting part of the base portion 25 of pressing and lip circle 14.Ring-shaped pressuring plate 20 is fastened on piston main body 18 by fixed-use bolt 23, the circular protrusion 34 of ring-shaped pressuring plate 20 is pressed to the face contacting part with the base portion 24 of lip circle 14 by brute force, circular protrusion 34 cuts above-mentioned contacting part thus, can prevent lip circle 14 from moving on piston main body 18, fix lip circle 14 effectively.And can well between packed-piston portion and cylinder 2.
In addition, preferably rising height is higher than the oscillating-piston 4 of the compressor of low voltage side for the oscillating-piston 4 of on high-tension side compressor.
In addition, be formed with ring-type ridge 35 at the upper surface of piston main body 18, this ring-type ridge 35 boosts the opening edge portion of the central portion of the circle that the central part of the base portion 25 of lip circle 14 is formed in the edge, periphery of this circular depressions 21.
Thus, the opening edge portion of lip circle 14 is boosted by ring-type ridge 35, therefore, it is possible to eliminate the space between base portion 25 and ring-shaped pressuring plate 20, seal effectively, the interior pressure of the upper room of cylinder 2 can not leak into the lower room of the bottom of piston portion 8.
Secondly, connecting rod, as shown in Fig. 3 (c) etc., swaying direction is formed as width larger, and then on the direction orthogonal with the width direction of connecting rod 6, as shown in Figure 4, be formed with the deformation suppression section 36 of ribbed, this deformation suppression section 36 engages with the lower surface of piston main body 18.Connecting rod 6 is formed as wider width on swaying direction, and piston main body 18 is also difficult to distortion on swaying direction thus.Further, owing to being formed with deformation suppression section 36 on connecting rod 6, therefore connecting rod 6 is reinforced on the direction orthogonal with its swaying direction, and piston main body 18 is also difficult to distortion in the direction in which.The distortion of the piston main body 18 that pressure causes differs widely in the distortion in swaying direction and the direction orthogonal with it.Therefore, fixed-use bolt 23 produces large stress.But, this stress can be reduced by the deformation suppression section 36 of ribbed.
In addition, deformation suppression section 36 is as shown in Fig. 8 (a) and Fig. 8 (b), also can be configured to be formed as width on the swaying direction of connecting rod 6 larger, but narrow in large tip side, broaden in small end side, and on the direction orthogonal with width direction, be formed with deformation suppression section 36 in large tip side.In addition, as shown in Fig. 9 (a) and Fig. 9 (b), also connecting rod 6 and deformation suppression section 36 can be formed as is the section cross of formed objects from large end to small end.
In addition, as shown in Figure 10, also can the outer circumferential face of piston main body 18 and ring-shaped pressuring plate 20 arrange have equal with lip circle 14 more than guard block 37a, 37b of nonmetal system of intensity.There is the situation exceeding and also continue engineering time to use in lip circle 14, in this case, there is lip circle 14 and wear and tear, metal piston main body 18 or ring-shaped pressuring plate 20 directly contact with cylinder 2 and rub mutually cause impaired, the danger of compression efficiency reduction or fault.But; by arranging guard block 37a, 37b of being made up of the nonmetallic material same with lip circle 14; before piston main body 18 or ring-shaped pressuring plate 20 contact; guard block 37a, 37b directly contact with cylinder 2; piston main body 18 or ring-shaped pressuring plate 20 can not be produced directly contact with cylinder 2 internal surface and the problem that rubs, cylinder 2 can be protected.In addition, guard block also can be configured to the side that only arranges in 37a, 37b.
Figure 11 represents other mode of executions of the oscillating-piston of reply high pressure, and the basic comprising of this oscillating-piston 4 is identical with aforesaid way, has: be wholely set in the front end of connecting rod 6 and the piston main body 18a of the plate-like of sliding while swing in cylinder 2; Be located at the top of piston main body 18a, the lining pressing plate 20a slightly less than piston main body 18a diameter; Be located between piston main body 18a and lining pressing plate 20a, the lining 38 be made up of the sealed department sealed between cylinder 2 internal surface; And be located at the piston ring 39 of periphery of above-mentioned lining pressing plate 20a.Piston main body 18a and lining pressing plate 20a is the parts being equivalent to above-mentioned piston main body 18 and ring-shaped pressuring plate 20 respectively.In addition, lining pressing plate 20a is identical with piston main body 18 with the ring-shaped pressuring plate 20 of aforesaid way with the mounting type of piston main body 18a.
The roughly spherical surface configuration of the degree that outer circumferential face 40 is identical with the internal diameter of cylinder 2 by diameter or diameter is slightly less than the internal diameter of cylinder 2 of lining 38 is formed.By this spherical shape, the pressure increase produced by the inertia of the oscillating motion based on oscillating-piston 4, effectively can suppress due to pushing force when lining 38 or lining pressing plate 20a pushing cylinder and be out of shape, repeated stress can be prevented in addition, the fatigue of lining 38 can be prevented.
In addition, piston ring 39 is not continuous print, and a part is cut-off, is incorporated in having play in the accommodating groove 42 that the periphery of ring-shaped pressuring plate 20 is formed.Therefore, piston ring 39 radially can stretch in accommodating groove 42.Therefore, when piston main body 18a and lining pressing plate 20a is subject to back pressure, piston ring 39 is pushed expansion outward, even if therefore piston main body 18a and lining pressing plate 20a tilts, also can maintain linear sealing by lining 38.In addition, from intensity, there is sufficient thickness, relaxed tolerance of size significantly.
Lining 38 and piston ring 39 are also made up of the nonmetallic material same with guard block 37.In addition, the side face of piston ring 39 is also roughly sphere.
In addition, Figure 12 is the air compressor being equipped with above-mentioned multistage compressor, and 43 is motors, and 44 is multistage compressors.The air compressed at the compressor 47 of low voltage side is fed on high-tension side compressor 46 by airduct 45, and this pressurized air is compressed by high-tension side compressor 46 further, is stored in air tank 49 by airduct 48.Further, the printed base plate 50 of the controlling component being provided with motor is configured with in the bottom of above-mentioned air compressor.Be configured with control apparatus 52 in the bottom of printed base plate 50, both sides bend upward in addition.This curved part 51 have prevent substrate entirety counter go out and guarantee intensity, and promote the function of heat radiation inside these both sides of distinguished and admirable mistake produced by cooling fan 53.In addition, although not shown at the lower surface of printed base plate 50, implement embedding processing.
Claims (14)
1. an oscillating-piston (4), has:
Be wholely set in the front end of connecting rod (6) and the piston main body (18) of the plate-like swung in cylinder (2);
Be located at the top of piston main body (18), the ring-shaped pressuring plate (20) less than piston main body (18) diameter; And
Be located between piston main body (18) and ring-shaped pressuring plate (20), the lip circle (14) nonmetal processed between packed-piston main body (18) and cylinder (2) internal surface,
The base portion (25) and standing up from the outer circumference end of base portion (25) that above-mentioned lip circle (14) has the cast tabular be clamped between piston main body (18) and ring-shaped pressuring plate (20) is formed and lip (15) between packed-piston main body (18) and cylinder (2) internal surface
The size (r2+t) that the radius of curvature (r2) of the inside angle part (28) that the radius of curvature (r1) of the outer corners (27) that base portion (25) contacts with two outer side surfaces of lip (15) contacts with two inner side surfaces of lip (15) than base portion (25) adds the thickness (t) of lip circle (14) is little.
2. oscillating-piston according to claim 1 (4), is characterized in that,
The most external diameter of above-mentioned lip circle (14) is larger than the internal diameter of cylinder (2), and when tilting maximum than piston main body (18), the major diameter of the ellipse of the internal surface of the cylinder (2) of contact is large.
3. oscillating-piston according to claim 1 (4), is characterized in that,
The lower surface (30) of the base portion (25) of above-mentioned lip circle (14) contacts from the upper surface face of position (29a) towards cylinder (2) side with piston main body (18) of the radial direction corresponding to the inner end (28a) of above-mentioned inside angle part (28).
4. oscillating-piston according to claim 1 (4), is characterized in that,
Under the state that above-mentioned oscillating-piston (4) does not tilt relative to cylinder (2), lip circle (14), from the position (29b) that the prolongation (31a) of at least upper surface (31) of base portion (25) contacts with the internal surface of above-mentioned cylinder (2) towards the upper end side of lip circle (14), contacts with above-mentioned cylinder (2) face.
5. oscillating-piston according to claim 1 (4), is characterized in that,
When described oscillating-piston (4) tilts maximum, in the upside that the space of cylinder main body (18) and cylinder (2) is little, in region on the lower, the position (29c) of the above-below direction corresponding to the outboard end (28b) than above-mentioned inside angle part (28), the periphery of above-mentioned lip circle (14) contacts with cylinder (2).
6. oscillating-piston according to claim 1 (4), is characterized in that,
When described oscillating-piston (4) tilts maximum, in the side that the space of cylinder main body (18) and cylinder (2) is large, the lip (15) of above-mentioned lip circle (14) and the space (D1) of ring-shaped pressuring plate (20) less than the space (D2) between cylinder main body (18) top and cylinder (2).
7. oscillating-piston according to claim 1 (4), is characterized in that,
Small space (Q) is formed between the lip (15) of above-mentioned lip circle (14) and ring-shaped pressuring plate (20),
The roughly spherical surface configuration that the outer circumferential face (33) of above-mentioned ring-shaped pressuring plate (20) is roughly the same with the internal diameter of above-mentioned cylinder (2) by diameter is formed.
8. oscillating-piston according to claim 1 (4), is characterized in that,
The upper surface (31) of the base portion (25) of above-mentioned lip circle (14), starts to contact with the lower surface of ring-shaped pressuring plate (20) away from the position of central side at the inner end (28a) of the curved surface than above-mentioned inside angle part (28).
9. oscillating-piston according to claim 1 (4), is characterized in that,
Above-mentioned ring-shaped pressuring plate (20) directly abuts with the inner side of piston main body (18) at the base portion (25) of lip circle (14).
10. oscillating-piston according to claim 1 (4), is characterized in that,
Above-mentioned ring-shaped pressuring plate (20) and piston main body (18) are when effect has the pressure of using state, and base portion (25) inner side in lip circle (14) abuts via medium material.
11. oscillating-pistons according to claim 1 (4), is characterized in that,
Ring-shaped pressuring plate (20) has the circular protrusion (34) of the base portion (25) of pushing lip circle (14).
12. oscillating-pistons according to claim 1 (4), is characterized in that,
The circular protrusion (35) of the opening edge portion of the central portion of the base portion (25) boosting lip circle (14) is formed at the upper surface of above-mentioned piston main body (18).
13. oscillating-pistons according to claim 1 (4), is characterized in that,
It is larger that above-mentioned connecting rod (6) is formed as width at swaying direction, and be formed with deformation suppression section (36) on the direction orthogonal with the width direction of connecting rod (6), this deformation suppression section (36) engages with the lower surface of piston main body (18).
14. oscillating-pistons according to claim 1 (4), is characterized in that,
The outer circumferential face of at least one party of above-mentioned piston main body (18) and ring-shaped pressuring plate (20) is provided with have equal with lip circle (14) more than the guard block (37a, 37b) of nonmetal system of intensity.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009157645A JP5617196B2 (en) | 2009-07-02 | 2009-07-02 | Multistage compressor |
| JP2009-157645 | 2009-07-02 | ||
| CN201010221388.XA CN101943152B (en) | 2009-07-02 | 2010-06-30 | Multistage compressor and oscillating piston |
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| CN201010221388.XA Division CN101943152B (en) | 2009-07-02 | 2010-06-30 | Multistage compressor and oscillating piston |
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| CN104265601B CN104265601B (en) | 2016-08-24 |
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| CN201010221388.XA Active CN101943152B (en) | 2009-07-02 | 2010-06-30 | Multistage compressor and oscillating piston |
| CN201410400163.9A Active CN104265601B (en) | 2009-07-02 | 2010-06-30 | Oscillating-piston |
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| JP (1) | JP5617196B2 (en) |
| CN (2) | CN101943152B (en) |
| TW (1) | TWI500851B (en) |
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| JP5380353B2 (en) * | 2010-04-14 | 2014-01-08 | 株式会社日立産機システム | Reciprocating compressor |
| JP5733994B2 (en) * | 2011-01-20 | 2015-06-10 | アルバック機工株式会社 | piston |
| CN102927006A (en) * | 2012-07-18 | 2013-02-13 | 上海旭岛汽车零部件有限公司 | Swing piston type electric vacuum pump |
| JP5993644B2 (en) * | 2012-07-20 | 2016-09-14 | 株式会社日立産機システム | Reciprocating compressor |
| CN102927007A (en) * | 2012-09-19 | 2013-02-13 | 上海旭岛汽车零部件有限公司 | Swing piston type electrical vacuum pump |
| JP5723943B2 (en) * | 2013-09-20 | 2015-05-27 | 株式会社日立産機システム | Reciprocating compressor |
| CN104196699B (en) * | 2014-08-21 | 2017-06-16 | 吉林省三和电气***工程有限公司 | A kind of gas boosting pump |
| JP6929042B2 (en) * | 2016-11-10 | 2021-09-01 | 株式会社デンソーテン | Air compressor and deposit remover |
| JP7050283B2 (en) * | 2018-01-09 | 2022-04-08 | 株式会社イズミ技研 | Oilless compressor |
| CN110778770B (en) * | 2018-07-31 | 2022-07-01 | 浙江三花智能控制股份有限公司 | Gas proportional valve |
| CN108825469A (en) * | 2018-08-15 | 2018-11-16 | 安徽士必达液压器材有限公司 | A kind of super-pressure pump high-low pressure piston component |
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| JP2011012603A (en) | 2011-01-20 |
| TWI500851B (en) | 2015-09-21 |
| CN101943152B (en) | 2015-01-14 |
| JP5617196B2 (en) | 2014-11-05 |
| TW201102503A (en) | 2011-01-16 |
| CN104265601B (en) | 2016-08-24 |
| CN101943152A (en) | 2011-01-12 |
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