CN200964870Y - Rotary vane piston - Google Patents
Rotary vane piston Download PDFInfo
- Publication number
- CN200964870Y CN200964870Y CNU2006200668540U CN200620066854U CN200964870Y CN 200964870 Y CN200964870 Y CN 200964870Y CN U2006200668540 U CNU2006200668540 U CN U2006200668540U CN 200620066854 U CN200620066854 U CN 200620066854U CN 200964870 Y CN200964870 Y CN 200964870Y
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- rotor
- blade
- skid
- carrier board
- slide rail
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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Abstract
The utility model discloses a rotary vane piston which can be applied to a compressor or an engine. By improving the force of vanes, the utility model increases the radial protruding quantity of the vanes, thus increases the volume of a work chamber, and obtains high compression ratio and higher exhaust quantity. The utility model includes a cylinder body, a rotor which is eccentrically arranged in the inner chamber of the cylinder body and the vanes which reciprocate along the radial direction of the rotor in the vane trough of the rotor; two ends of the cylinder body are provided with an end cover; the profile surface of the internal wall of the cylinder body is a cylindrical surface; the two ends of the rotor is provided with a moment bearing plate which is coaxially synchronously rotated with the rotor; the diameter of the moment bearing plate is larger than the diameter of the rotor; the end surface of the moment bearing plate is sealed by gas with the end part in the internal wall of the cylinder body; the moment bearing plate is provided with a trough mouth; the upper and lower end of the vanes outspread into the trough mouth and keep gas sealing contact with the side wall of the trough mouth. The vanes are subject to the air pressure force at higher side surface; the air pressure is directly or indirectly transmitted to the rotor by the moment bearing plate to make the extension range of the vanes in the rotor be increased to close to the theoretic maximum value of the structure.
Description
Technical field
The utility model relates to a kind of rotation blade piston, especially for the piston of rotary-vane engine or compressor.
Background technique
The motor that adopts reciprocating piston is at present most widely used general, explosive motor that technology is the most ripe, but because its intrinsic structural type, and the vibration that exists the to-and-fro motion inertia of piston and valve to be produced makes its rotating speed and power per liter be difficult to promote again.Though the vibration that wankel three-apexed rotor formula motor has structurally avoided reciprocal inertia to produce, aspects such as its manufacture cost, fuel economy all far away from reciprocating-piston engine, therefore are not widely used.
The rotation blade piston mechanism is to grow up at the conceptive of many primitives sliding blade apparatus that propose of La Maierli (Ramelli) in 1588, utilize the moving vane on the eccentric rotor in cylinder body, to rotate, make the variation of swept volume generating period, thereby make the gas acting in the swept volume.The vibration that it has avoided reciprocal inertia to produce has been widely used in fields such as compressor, pump, gas motor.But the problem that present rotation blade piston is mainly deposited is: the line style sealing configuration between blade and cylinder wall is at the operating mode therapeutic method to keep the adverse qi flowing downward poor sealing than highpressure, the serious wear between blade and cylinder wall, between blade and the rotor vane groove.These problems cause the energy loss of rotation blade piston serious, have limited the Economy of use and the life-span of piston.The single stage compression pressure of rotation blade piston compressor is difficult to surpass 2MPa at present.Adopt the motor of rotation blade piston, its hermetic seal is bad and wear problems is more outstanding, this makes the stretch out amplitude of blade in rotor can not establish too greatly, cause active chamber narrow, its effective discharge is far below the air displacement of the reciprocating piston of same cylinder size, limited the power per liter of motor greatly, in addition, narrow crescent shape active chamber can influence intake efficiency, adopt and strengthen suction port, improve the intake efficiency method and can increase the volume of primitive when finishing air inlet again for increasing power, cause compression ratio to descend, thereby the thermal efficiency of motor is reduced.Therefore, the performance of existing rotation blade reciprocating engine is not promoted and is used far away from traditional Reciprocating engine and wankel three-apexed rotor formula motor.
The model utility content
The technical problems to be solved in the utility model provides a kind of rotation blade piston that can be used for compressor or motor, it is by improving the stressed of blade, increase the amount of extending radially out of blade, thereby increase working chamber volume, make its working chamber volume can approach the theoretical maximum of structure, obtain higher compression ratio and higher air displacement.
The realization the technical solution of the utility model is: a kind of rotation blade piston, comprise cylinder body, be eccentrically set on inner chamber of cylinder block rotor and can be along the reciprocating blade of rotor radial in epitrochanterian blade groove, the two ends of cylinder body are provided with end cap, it is characterized in that: described inboard wall of cylinder block profile is the cylndrical surface, the two ends of described rotor are provided with and rotor coaxial and synchronous rotating moment carrier board, the diameter of described moment carrier board is greater than root diameter, the moment carrier board is provided with notch, described blade stretches in this notch at two ends up and down, and keeps hermetic seal to contact with the sidewall of notch.Stressed in order further to improve, be provided with rolling groove at the notch place of moment carrier board, be provided with rolling element in the rolling groove, blade, notch, the rolling element three cooperation of rolling mutually.Because the structure that adopts the moment carrier board and roll and cooperate, the higher side atmospheric pressure that blade is subjected to directly or indirectly is delivered on the rotor by the moment carrier board, thereby avoided the strong friction between blade and the rotor vane groove, the theoretical maximum (root diameter can reduce in other words) that simultaneously the stretch out amplitude of blade in rotor is increased to approach structure; For the cylinder inner wall face is the piston of cylndrical surface, and the volume of active chamber can increase to 1/3 (approaching the theoretical maximum of structure) of cylinder inner cavity volume, thereby makes compression ratio and the power per liter can be near the theoretical maximum of structure.
Simultaneously, in the hinge joint of the front end of blade movable skid is arranged, its cardan axle and rotor center axle are parallel to each other; Described skid has one and adapts with inboard wall of cylinder block and the cambered surface of hermetic seal mutually, also is provided with the skid guiding device with the coaxial setting in cylinder body cylndrical surface in the cylinder body, and this skid guiding device comprises and the rotor ring skid slide rail of rotation synchronously at least.
When being applied to motor, sled makes the primitive of holding one's breath have less minimum volume, thereby can obtain higher compression ratio with the air inlet of rotor rotation through energy earlier closing primitive behind the suction port.Its compression ratio equals the maximum volume of the primitive that surrounded by cylinder inner wall, rotor, moment carrier board and adjacent vanes and the ratio of the minimum volume of the primitive of holding one's breath, the air displacement of above-mentioned piston is the gas volume that the suction port that rotates a circle of rotor sucks, the maximum volume that equals primitive multiply by the primitive number, and the maximum volume Vm of primitive equals under the situation of the thickness of disregarding blade and blade sled: Vm=HR
2[e ρ+arcsin (ρ sina)-(1-e)
2A].Wherein: H is the height of cylinder inner wall profile, and R is the radius of cylinder inner wall profile, and r is a rotor radius, e=1-r/R; ρ=ecosa+ (1-e
2Sin
2A)
1/2A be between the adjacent blades angle 1/2.In the utility model, the r/R minimum value of rotation blade piston can approach 2/3, is 6 piston for the blade number, and its air displacement is Vp=6Vm ≈ 5.3HR
2, so its air displacement can substantially exceed the air displacement Vp '=pHR of the reciprocating piston of same cylinder size
2≈ 3.14HR
2
Owing to adopted the structure of above-mentioned skid, make piston contact with the line style of inboard wall of cylinder block and be improved to sled and contact with the face type of cylinder inner wall by traditional blade, favourable and improve hermetic seal and reduce wear.This also is another technical problem to be solved in the utility model: a kind of piston that weares and teares between blade and the cylinder wall that reduces is provided, avoid between blade and cylinder wall bad the problem of serious wear between blade and cylinder wall, between blade and the rotor vane groove than the hermetic seal under the highpressure operating mode.
Specifically, the skid slide rail of skid guiding device is arranged between inboard wall of cylinder block and the skid and hermetic seal mutually, be provided with the guide ring coaxial with inboard wall of cylinder block between described end cap and the moment carrier board, the upper-end surface of blade and/or lower end surface are provided with the guide way tangent with described guide ring.Can be further with the axis and the coaxial setting of the hinging shaft of skid of described guide way, guide ring directly is opened on the end cap, and perhaps guide ring passes through the guide way activity orientation above the moment carrier board.Also can further annular groove be set on the guide ring (when groove is groove, be equivalent to the combination of two concentric guide rings), wherein guide way is directional post or arc radius and the consistent guide pad of described groove radius, or fluted on the guide way, guide way and guide ring tabling.
Or the skid slide rail of described skid guiding device is arranged between rotor and the inboard wall of cylinder block, the upper and lower end face of described skid is provided with arc radius and the consistent groove of skid slide rail radius, slide rail and described groove tabling.
Wherein, be provided with lubricant openings with the corresponding position of skid on the skid slide rail; Described skid slide rail is provided with the synchromesh gear that is parallel to each other with the moment carrier board, described moment carrier board be provided with along the rotor axis circumference evenly distribute and with synchromesh gear number of teeth corresponding synchronous tooth, this synchronous tooth and synchromesh gear are meshing with each other.
Also can not adopt the skid slide rail in the utility model, only between described end cap and moment carrier board, be provided with the guide ring coaxial, coaxially on the skid cardan axle be provided with the guide way tangent with described guide ring with inboard wall of cylinder block.
In the utility model, when described rolling groove is groove on the thickness direction of moment carrier board, between moment carrier board and rotor end-face, rotor cover is set, hermetic seal between rotor cover surface and the inboard wall of cylinder block port part, be provided with blade groove with the corresponding position of blade on the described rotor cover, be filled with lubricant oil in the space between rotor cover and the end cap.Perhaps moment carrier board and rotor cover are made of one.
The utility model compared with prior art, its major advantage is that it can avoid between blade and cylinder wall bad than the hermetic seal under the highpressure operating mode, the problem of serious wear between blade and cylinder wall, between blade and the rotor vane groove, and its working chamber volume can approach the theoretical maximum of structure, can obtain higher compression ratio and higher air displacement.It shifts the side pressure to blade by moment carrier board and rolling element are set, make blade can attenuate or the amplitude of stretching out increase, perhaps root diameter can reduce, thereby increases the volume of active chamber; Utilize the acting in conjunction of skid, skid slide rail and/or guide ring in addition, improve friction and hermetic seal between blade and the inboard wall of cylinder block.Secondly, because the skid slide rail rotates synchronously along inboard wall of cylinder block and rotor, make skid move reciprocatingly with respect to the sled guide rail, therefore the average speed of related movement between the sled guide rail is far smaller than the average movement velocity of the outer end of blade with respect to cylinder inner wall in blade sled and the cylinder, and the wearing and tearing between the interior sled guide rail of blade sled and cylinder are reduced greatly.
Description of drawings
Below in conjunction with the drawings and specific embodiments the utility model rotation blade piston is further described.
Fig. 1 is embodiment 1 the stereogram of observing from the top, northeast;
Fig. 2 is the stereogram that Fig. 1 observes from the northeast by east top;
Fig. 3 is the sectional view of Fig. 1;
Fig. 4 is the sectional view along A-A line among Fig. 3;
Fig. 5 is the sectional view along C-C line among Fig. 3;
Fig. 6 is the sectional view along D-D line among Fig. 3;
Fig. 7 is the stereogram of Fig. 1 middle part sub-unit annexation, wherein sled slide rail 11, synchromesh gear 10 has been done biopsy cavity marker devices;
Fig. 8 is the stereogram of Fig. 1 middle part sub-unit annexation, wherein blade guide ring 3 has been done biopsy cavity marker devices;
Fig. 9 is the stereogram of embodiment's 2 middle part sub-unit annexations, wherein blade 6, synchromesh gear 10 has been done biopsy cavity marker devices;
Figure 10 is the stereogram of embodiment's 3,4 middle part sub-unit annexations, wherein guide ring 3, moment slide plate 2, the outer section of blade 6b, rotor cover 9 has been done biopsy cavity marker devices;
Figure 11 is the stereogram that comprises guide ring 3, cylinder inner wall 12, sled 15, hinging shaft 26, guide pad 27, suction port 17, relief opening 14 annexations among the embodiment 4.
Embodiment
Present embodiment is used for compressor, as accompanying drawing 1 to piston shown in Figure 6, cylinder block 1 is made up of with nested cylinder inner cavity within it water jacket 18, inboard wall of cylinder block 12 profiles are the cylndrical surface, have suction port 14 on the cylinder block 1, (be used for motor: suction port is 17 to relief opening 17, relief opening is 14), rotor 13 off-centre place cylinder inner cavity, clockwise direction rotation (being used for motor) by Fig. 3 by rotation counterclockwise, cylinder block 1 both sides are fixed with cylinder end caps 20, rotor bearing 21 is arranged on the cylinder end caps 20, rotor 13 rotatably is supported on the rotor bearing 21 by rotor main shaft 22, it is the step surface 30 at center that the two ends of inner chamber of cylinder block are arranged with the rotor axis, rotor cover 9 is fixed on the two ends of rotor 13, and cooperate the step surface 30 that covers the inner chamber of cylinder block both sides, cylinder inner cavity 12 with hermetic seal, rotor 13 and rotor cover 9 surround active chamber; The outside of rotor cover 9 is fixed with moment carrier board 8; Rotor cover 9 and moment carrier board 8 rotate jointly with rotor 13; Have blade groove 16,16a on rotor 13 and the moment carrier board 8, have blade notch 7 on the rotor cover 9, blade 6 is contained in the blade groove 16 of rotor 13, and in two ends extend to blade groove 16a on the moment carrier board 8; Blade 6 is divided into three sections along rotor axial thus: be in blade 6 stage casings in the cylinder inner cavity 12 and upper and lower end reach rotor cover 9 outsides by the blade notch 7 of rotor cover 9 the outer section 6b of blade; Need hermetic seal to cooperate between blade groove 16 on blade 6 and the rotor 13, the blade notch 7 on the rotor cover 9; On moment carrier board 8, radially be provided with rolling groove 31, rolling groove 31 is that groove is (when it is blind groove at moment carrier board thickness direction, can cancel rotor cover 9, and make hermetic seal between moment carrier board 8 and the step surface 30), rolling element 4 (as roller or ball) is installed in the rolling groove 31, is to roll between the section 6b outward with moment carrier board 8, blade to cooperate.Perhaps, the side of section 6b is provided with moment slide plate 2 outside blade, is rolling between rolling element 4 and moment carrier board 8, the moment slide plate 2 and cooperates, further to alleviate the wearing and tearing to blade.This structure, the higher side atmospheric pressure that blade 6 is subjected to is delivered on the rotor 13 by rolling element 4 and square carrier board 8, thereby avoided the strong friction between blade 6 and the rotor vane groove 16, also made the stretch out amplitude of blade 6 in rotor 13 approach the theoretical maximum of structure simultaneously; For the cylinder inner wall face is this piston of cylndrical surface, and the volume of active chamber can increase to 1/3 of cylinder inner cavity volume, makes compression ratio and the power per liter can be near the theoretical maximum of structure.
Near hinge joint on the limit of cylinder inner wall 12 blade sled 15 is arranged in blade 6 stage casings; The side that sled 15 is pressed close to cylinder inner wall 12 is the arc surface that matches with cylinder inner wall 12 faces.Like this, piston is contacted with the line style of cylinder inner wall by traditional blade and is improved to blade sled 15 and contacts with the face type of cylinder inner wall 12, favourable with improve hermetic seal and reduce wear.
Between blade 6 and blade groove 16, the blade notch 7 pneumatic seal is arranged, cylinder inner wall 12 axial both sides are set with sled slide rail 11, and there is the seal ring with rotor cover 9 maintenance hermetic seals in the outside of sled slide rail 11.Skid slide rail edge is provided with the synchromesh gear 10 coaxial and that be arranged in parallel with respect to rotor cover 9 with slide rail, rotor cover 9 end faces that combine with moment carrier board 8 be provided with along rotor 13 axle center circumference evenly distribute and with synchromesh gear 10 number of teeth corresponding synchronous teeth 24, this synchronous tooth 24 is meshing with each other with synchromesh gear 10.Sled slide rail 11 keeps synchronously but the out-of-alignment rotation with rotor 13 by synchromesh gear 10, epitrochanterian synchronous tooth 24.Also can have the lubricant openings 23 identical with blade 6 quantity on the sled slide rail 11 in the cylinder, and skid is designed to as shown in Figure 7 shaped as frame, lubricant openings 23 can be covered in by blade sled 15 in the process that rotor 13 rotates a circle all the time like this.The side of section 6b is provided with directional post 5 outside blade, blade guide ring 3 is set directly on the cylinder end caps 20, perhaps under blade quantity is equal to or greater than 3 situation, can be above moment carrier board 8 by directional post 5 activity orientation, directional post 5 rotated along the slip of guide ring 3 outsides or together with guide ring 3 when rotor 13 rotated.Perhaps as shown in Figure 8, the groove 3b of annular is set at the end face of guide ring 3, this annular groove 3b has circular trace, outside blade, with the coaxial position of skid hinging shaft directional post 5 is set on the end face of section 6b, directional post 5 slides in groove 3b, and this round ring guide groove 3b or guide ring 3 with simple geometric shape can more easily make blade sled 15 and skid slide rail 11 internal surfaces keep accurate sliding contact, guarantee existing good hermetic seal, less friction is arranged again.
In the present embodiment, as shown in Figure 2, the internal diameter of sled slide rail 11 is equal to or slightly less than the internal diameter of cylinder inner wall 12, blade guide ring 3 slides by the surface that directional post 5, blade 6 make blade sled 15 be close to sled slide rail 11 in the cylinder, guide ring 3 can guarantee that blade sled 15 is pasting cylinder inner wall 12 and sliding, and can guarantee that again blade sled 15 does not have strong friction with cylinder inner wall 12.Because sled slide rail 11 rotates synchronously with rotor 13, so sled 15 is to move reciprocatingly with respect to sled slide rail 11 in the cylinder, and its maximum speed of related movement and blade 6 outer ends with respect to the ratio between the maximum speed of related movement of cylinder inner wall 12 are: (R
1-R
2)/(2R
1-R
2)＜4/9, wherein: R
1Be inboard wall of cylinder block radius, R
2Be rotor radius, and 2/3R
1＜R
2＜R
1, so the average speed of related movement between the sled guide rail 11 is far smaller than the average movement velocity of the outer end of blade with respect to inboard wall of cylinder block in blade sled 15 and the cylinder, makes the wearing and tearing between blade sled 15 and the sled guide rail 11 less; Lubricant openings 23 in the cylinder on the sled guide rail 11 can make lubricant oil flow into the surface of contact between the sled guide rail 11 in blade sled 15 and the cylinder, forms oil film on sled slide rail 11 surfaces, has further reduced the wearing and tearing between them.
Above-mentioned mode of execution is owing to have only an active chamber, in the rotary course of rotor 13, can not both have compression stroke, has expansion stroke again, so its piston in motor as combustion gas expansion, acting, its rotor 13 is pressed the counter clockwise direction rotation of Fig. 3, suction port is 17, relief opening is 14, and it and another finish that mixed gas sucks, the piston mechanism of compression function constitutes the external-compression type motor.For this piston applications in motor, its compression ratio equals by inboard wall of cylinder block 12, rotor 13, the ratio of the maximum volume of the primitive that rotor endcap 9 and adjacent vanes 6 surround and the minimum volume of the primitive of holding one's breath, because the profile of skid 15 is a shaped as frame as shown in Figure 8, have on the skid 15 one towards the cambered surface length of rotor sense of rotation one side greater than the part of the cambered surface length of rotor sense of rotation one side dorsad, also be that sled 15 becomes longer to a side of rotor 13 sense of rotation in the Position Design corresponding to blade stage casing 6b, blade sled 15 is with the air inlet of rotor 13 rotations through energy earlier closing primitive behind the suction port like this, make the less minimum volume of having of the primitive of holding one's breath, thereby can obtain higher compression ratio.The air displacement of above-mentioned piston is a rotor 13 by the clockwise direction of Fig. 3 gas volume that the suction port of piston sucks that rotates a circle, the maximum volume that equals primitive multiply by the primitive number, the maximum volume of primitive: Vm=HR under the situation of the thickness of disregarding blade and blade sled
2[e ρ+arcsin (ρ sina)-(1-e)
2A].For the blade number be 6, the piston of r/R=0.8, its air displacement is Vp=6Vm ≈ 3.13HR
2, approach the air displacement Vp '=pHR of the reciprocating piston of same cylinder size
2, when the r/R of rotation blade piston approached 0.66, its air displacement maximum value can approach Vpmax ≈ 5.3HR2, so its air displacement can substantially exceed the air displacement of the reciprocating piston of same cylinder size.
Embodiment 2:
As shown in Figure 9, embodiment 2 is with embodiment 1 difference, the mode of structure difference of skid slide rail 11, skid slide rail 11 is arranged between rotor 13 and the inboard wall of cylinder block 12, the upper and lower end face of skid 15 is provided with the arc radius telescoping groove 25 consistent with skid slide rail 11 radiuses, skid slide rail 11 and telescoping groove 25 tablings.Synchromesh gear 10 on the skid slide rail 11 and rotor 13 are with the identical synchronous rotation that turns to angular velocity; Sled 15 is with sled slide rail 11 and is slidingly matched.The directional post that is adopted, the guide ring structure among the embodiment 1 also adopted in the upper and lower end face of the outer section of blade 6b, certainly, because the telescoping groove 32 on the skid has spacing effect, so these structures also can be omitted in embodiment 2.Sled slide rail 11 guarantees that accurately sled 15 has accurate contact to slide on cylinder inner wall 12 surfaces, can guarantee existing good hermetic seal under lubricated condition between blade sled 15 and the cylinder inner wall 12 better, and less friction is arranged again.
Embodiment 3:
As shown in Figure 10, embodiment 3 is with embodiment 1 difference, the guide way structure difference that it adopts, its guide way be arc radius with guide ring 3 on the consistent guide pad 27 of groove 3b radius, and the center of guide pad 27 is connected with the cardan axle of skid 15 is coaxial.In the process of rotor rotation, guide ring 3 cooperates with guide pad 27, can guarantee good cooperating between skid 15 and the skid slide rail 11, and reduces the friction between skid 15 and the inboard wall of cylinder block 12.
Embodiment 4:
Shown in accompanying drawing 10,11, embodiment 4 is with embodiment 3 difference, it has cancelled skid slide rail 11, hermetic seal cooperates between skid 15 and the inboard wall of cylinder block 12, the structure that has kept guide ring 3 and guide pad among the embodiment 3, and the center of guide pad 27 is connected with the cardan axle of skid 15 coaxial 26.Wherein the groove on the guide ring 3 can be a groove also, and when it was groove, guide ring 3 was equivalent to the combination of two concentric guide rings.In the process of rotor rotation, guide ring 3 cooperates with guide pad 27, has fettered the movement locus of sled 15, can make between sled 15 and the cylinder inner wall 12 to reach best cooperating through break-in, promptly reaches the optimal balance point between hermetic seal and friction.
Claims (10)
1, a kind of rotation blade piston, comprise cylinder body, be eccentrically set on inner chamber of cylinder block rotor and can be along the reciprocating blade of rotor radial in epitrochanterian blade groove, the two ends of cylinder body are provided with end cap, it is characterized in that: described inboard wall of cylinder block profile is the cylndrical surface, the two ends of described rotor are provided with and rotor coaxial and synchronous rotating moment carrier board, the diameter of moment carrier board is greater than root diameter, hermetic seal between the end face of moment carrier board and the inboard wall of cylinder block port part, the moment carrier board is provided with notch, described blade stretches in this notch at two ends up and down, and keeps hermetic seal to contact with the sidewall of notch.
2, piston according to claim 1 is characterized in that: the front end hinge joint of described blade has movable skid, and its cardan axle and rotor center axle are parallel to each other; Described skid has one and adapts with inboard wall of cylinder block and the cambered surface of hermetic seal mutually, is provided with the skid guiding device with the coaxial setting in cylinder body cylndrical surface in the described cylinder body, and described skid guiding device comprises and the rotor ring skid slide rail of rotation synchronously at least.
3, piston according to claim 2, it is characterized in that: described skid slide rail is arranged between inboard wall of cylinder block and the skid and hermetic seal mutually, be provided with the guide ring coaxial with inboard wall of cylinder block between described end cap and the moment carrier board, the upper-end surface of blade and/or lower end surface are provided with the guide way tangent with described guide ring.
4, piston according to claim 3 is characterized in that: the axis of described guide way is coaxial with the hinging shaft of skid, and guide ring directly is opened on the end cap, and perhaps guide ring passes through the guide way activity orientation between end cap and moment carrier board; Described guide ring is provided with annular groove, or fluted on the described guide way, guide way and guide ring tabling.
5, piston according to claim 4 is characterized in that: described skid slide rail is arranged between rotor and the inboard wall of cylinder block, and the upper and lower end face of described skid is provided with arc radius and the consistent groove of skid slide rail radius, slide rail and described groove tabling.
6, according to each described piston of claim 2 to 5, it is characterized in that: described skid slide rail edge is provided with the synchromesh gear coaxial and that be parallel to each other with the moment carrier board with slide rail, described moment carrier board be provided with along the rotor axis circumference evenly distribute and with synchromesh gear number of teeth corresponding synchronous tooth, this synchronous tooth and synchromesh gear are meshing with each other; Be provided with lubricant openings with the corresponding position of skid on the described skid slide rail.
7, piston according to claim 2 is characterized in that: the front end hinge joint of described blade has movable skid, and its cardan axle and rotor center axle are parallel to each other; Described skid has one and adapts with inboard wall of cylinder block and the cambered surface of hermetic seal mutually, be provided with the guide ring coaxial between described end cap and the moment carrier board with inboard wall of cylinder block, guide ring is provided with the annular groove of rounded track, the coaxial arcuate guide piece that matches with this annular groove that is provided with on the skid cardan axle, guide ring is nested with on guide pad.
8, according to claim 1 to 5 or 7 each described pistons, it is characterized in that: the notch place of described moment carrier board is provided with rolling groove, is provided with rolling element in the rolling groove, blade, notch, the rolling element three cooperation of rolling mutually.
9, piston according to claim 8 is characterized in that: be filled with lubricant oil in described blade groove, the notch and between moment board and the end cap.
10, piston according to claim 9 is characterized in that: between moment carrier board and the rotor end-face rotor cover is set, hermetic seal between rotor cover surface and the inboard wall of cylinder block port part is provided with blade groove with the corresponding position of blade on the described rotor cover.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200668540U CN200964870Y (en) | 2006-10-31 | 2006-10-31 | Rotary vane piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200668540U CN200964870Y (en) | 2006-10-31 | 2006-10-31 | Rotary vane piston |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN200964870Y true CN200964870Y (en) | 2007-10-24 |
Family
ID=38868884
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2006200668540U Expired - Lifetime CN200964870Y (en) | 2006-10-31 | 2006-10-31 | Rotary vane piston |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN200964870Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100513748C (en) * | 2006-10-31 | 2009-07-15 | 黄庆培 | Piston device with rotary blade |
| CN105209762A (en) * | 2013-11-22 | 2015-12-30 | 三樱工业株式会社 | Negative pressure pump and cylinder head cover |
| CN106285928A (en) * | 2016-10-17 | 2017-01-04 | 龙建 | Piston stops the continuous rotary engine of dynamic formula |
| WO2017107228A1 (en) * | 2015-12-25 | 2017-06-29 | 常州市金坛翰广科技有限公司 | Rotary-vane vacuum pump |
| CN111608851A (en) * | 2019-11-19 | 2020-09-01 | 李光惠 | Hydraulic power device with swinging blades |
-
2006
- 2006-10-31 CN CNU2006200668540U patent/CN200964870Y/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100513748C (en) * | 2006-10-31 | 2009-07-15 | 黄庆培 | Piston device with rotary blade |
| CN105209762A (en) * | 2013-11-22 | 2015-12-30 | 三樱工业株式会社 | Negative pressure pump and cylinder head cover |
| CN105209762B (en) * | 2013-11-22 | 2016-12-21 | 三樱工业株式会社 | Negative pressure pump and cylinder-head cover |
| WO2017107228A1 (en) * | 2015-12-25 | 2017-06-29 | 常州市金坛翰广科技有限公司 | Rotary-vane vacuum pump |
| CN106285928A (en) * | 2016-10-17 | 2017-01-04 | 龙建 | Piston stops the continuous rotary engine of dynamic formula |
| CN111608851A (en) * | 2019-11-19 | 2020-09-01 | 李光惠 | Hydraulic power device with swinging blades |
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