| 序号 | 专利名 | 申请号 | 申请日 | 公开（公告）号 | 公开（公告）日 | 发明人 |
|---|---|---|---|---|---|---|
| 121 | Rotary machine equipped with a thrust balancing arrangement | US391525 | 1989-07-20 | US4915514A | 1990-04-10 | Frits Soderlund |
| A housing (1) of a rotary machine comprises a low-pressure side (2) and a high-pressure side (3), working-fluid inlet and outlet channels, and at least one rotor (7), which when the machine is working is urged by a working fluid towards the low-pressure side (2). The rotor includes a thrust balancing arrangement (15, 16) for relieving the load on the thrust bearings (11) of the machine, through the medium of an auxiliary bearing (17) and in dependence on pressure fluid supplied to the thrust balancing arrangement, the pressure of which fluid is contingent on the operating conditions of the machine. A relatively large part of the axial load is taken-up by an auxiliary thrust bearing (17), which is readily replaceable. The auxiliary bearing (17) is mounted on an outermost part of the rotor journal shaft (18), on the high-pressure side (3) of the rotor, between a detachable locking device (27) for the auxiliary bearing (17) and the thrust balancing arrangement. The thrust balancing arrangement is located inwards of the auxiliary thrust bearing and includes two annular piston-cylinder parts (15, 16) which are axially extendible and which are located in a cylindrical recess (14) in the housing (1). | ||||||
| 122 | Scroll-type fluid transferring machine with slanted thrust bearing | US935295 | 1986-11-26 | US4761122A | 1988-08-02 | Tetsuzo Matsugi; Tsutomu Inaba; Norihide Kobayashi |
| A scroll-type fluid transferring machine of an improved construction, in which the bottom surface of the base plate of the orbiting scroll member and the bearing surface of the thrust bearing are well adapted even under a thrusting force during compression of the operating fluid, such scroll-type fluid transferring machine having a feature such that the surface of the thrust bearing to support the base plate of the orbiting scroll member, or the surface of the base plate of the scroll member supported by the thrust bearing is slanted in the radial direction so as to form the surface thereof in a center-concaved shape, wherein the inner peripheral side is concave with respect to the outer peripheral side at a very small distance in the axial direction, or that an axial projection which is concentric with the thrust bearing and has a narrow width in the radial direction is provided between the opposed surfaces of the thrust bearing and the bearing frame in the vicinity of the center part in the radial direction between the inner peripheral side and the outer peripheral side of the thrust bearing, and further space gaps are provided between the mutually opposed surfaces at the inner peripheral side and the outer peripheral side of the projection. | ||||||
| 123 | Rotary vane device with two pressure chambers for each vane | US528416 | 1983-09-01 | US4505654A | 1985-03-19 | Laurence C. Dean, Jr.; Louis J. Cardinale |
| A fluid pressure energy translating device of the sliding vane type comprising a cam ring including an internal contour, a rotor having a plurality of vanes rotatable therewith and slidable relative thereto in slots in the rotor with one end of each vane engaging the internal contour. The rotor and internal contour cooperate to define one or more pumping chambers between the periphery of the rotor and the cam contour through which the vanes pass carrying fluid from an inlet port to an outlet port. At least one cheek plate is associated with the body and rotor. Two pressure chambers are formed for each vane and each vane has two surfaces, one in each chamber, both being effective under pressure in the respective chambers to urge the vanes into engagement with the cam. A generally annular internal feed passage is formed entirely within the rotor and communicates with one set of the pressure chambers. A radial passage is provided on each vane extending from the tip of the base thereof, so that cyclically changing pressure is supplied to the other set of chambers. Arcuate grooves are provided in the face of the cheek plate in the dwell zones, and a hydrostatic pressure pad is associated with the opposite face of the cheek plate and circumscribes the arcuate grooves. An opening extends from the arcuate grooves through the cheek plate to the hydrostatic area. | ||||||
| 124 | Scroll fluid apparatus with an arcuate recess adjacent the stationary wrap | US314459 | 1981-10-23 | US4443166A | 1984-04-17 | Masato Ikegawa; Kenji Tojo; Masao Shiibayashi |
| A scroll fluid apparatus including two scroll members, with one scroll member having a wrap and an annular portion located outside the wrap and having a height corresponding to the height of the wrap. The annular portion is contiguous at its surface in the form of a land with the surface of the wrap for a circumferential extent of within 180 degrees from the terminating end of the wrap, and a strip-shaped recess is formed in the land, with the strip-shaped form having an end portion maintained in communication with a low pressure zone surrounded by the annular portion of the scroll member. | ||||||
| 125 | Orbiting fluid displacement apparatus with counterweight attachment | US318313 | 1981-11-04 | US4439118A | 1984-03-27 | Takayuki Iimori |
| A scroll type fluid displacement apparatus, in particular, a compressor of an orbiting piston type is disclosed. The compressor includes a housing with a fluid inlet port and a fluid outlet port. A fixed scroll member with first end plate and first spiral element is fixed relative to the housing. An orbiting scroll member with second end plate and second spiral element is disposed for orbiting motion in the housing. The first and second spiral elements interfit with one another at an angular and radial offset to make a plurality of line contacts to define at least one pair of sealed off fluid pockets. A drive pin is eccentrically disposed at an inner end of the drive shaft. The orbiting scroll member has a boss which rotatably supports a bushing. An eccentric hole is formed in the bushing and the drive pin is received within this hole. The center of drive pin is located on an opposite side to the center of the drive shaft with regard to a straight line, which passes through the center of the bushing and is perpendicular to a connecting line passing through the center of the drive shaft and the center of the bushing. The center of the drive pin is also beyond the connecting line in the direction of rotation of the drive shaft. A separate balance weight is attached to the bushing at its end surface by a fastener which can limit the amount of swing angle of bushing. The balance weight cancels a centrifugal force which arises because of the orbital motion of the scroll and the bushing. | ||||||
| 126 | Rotary displacement turbine engine with vacuum relief valve means | US81820 | 1979-10-04 | US4417859A | 1983-11-29 | Frank C. Praner |
| An external combustion engine is disclosed of the type including two or more circular rotors rotatably supported, one of the rotors acting as a power rotor and rotating in tangential contact with the other sealing rotor. The power rotor is formed with a radially projecting piston passing into a mating recess with the sealing rotor at a corresponding circumferential location. Steam or other working fluid is admitted via an intake port located opposite one face of the power rotor to cause rotation of the power rotor by expansion of the fluid in a working chamber defined by the space behind the piston. As the power rotor continues to rotate, the working chamber passes into communication with an exhaust port preparator to another power stroke. A vacuum relief port is provided at an intermediate location which relieves any vacuum condition which develops behind the piston during part throttle operating conditions of the engine. A pressure balancing groove is located on a face of the power rotor and pressurized with working fluid to balance the pressure acting on the power rotor by the location of the intake port on the opposite face of the power rotor. An absorber chamber is provided downstream of the throttle valve and upstream of the intake port to smooth out the pressure forces created by intermittent flow of fluid through the intake port. An elliptical port throttle valve design is disclosed which minimizes the wire drawing effect of the working fluid acting on the valve member during operation of the valve. A special rotor sealing surface treatment is disclosed comprising a series of slight depressions or holes formed in the mating faces of the power rotor and which generate a sealing due to condensation of the escaping steam in the surface indentations. Two and three rotor versions of the engine are described as well as one, two, and four power stroke per revolution embodiments. | ||||||
| 127 | Rolling thrust bearing for use in a scroll machine | US329148 | 1981-12-10 | US4415318A | 1983-11-15 | Arthur L. Butterworth; David H. Eber |
| A rolling thrust bearing for use in a scroll type positive fluid displacement apparatus is disclosed. In the invention, a plurality of ball bearings spaced apart in cavities formed in a bearing cage are operative to transmit an axial force between a supporting frame and an orbiting scroll member. The bearing cage rotates within a groove in which it is seated due to frictional forces between its flank surfaces and the sides of the groove. In a first embodiment, the diameter of the cavities is substantially larger than the diameter of the ball bearings, and the bearings are free to orbit within the cavities as the bearing cage rotates. In the second embodiment, the cavities are only slightly larger in diameter than the ball bearings, but the radial width of the bearing cage is substantially less than the width of the groove, and the bearing cage and the ball bearings together describe an epicycloidal path about the central axis of the bearing cage. In both embodiments, the ball bearings seated within the cavities contact adjacent bearing races over a constanty changing portion of their surface. This substantially extends the operational life of the thrust bearing. | ||||||
| 128 | Internal gear machine with rotary pressure balanced valve disc | US254385 | 1981-04-15 | US4411607A | 1983-10-25 | Peter Wusthof; Johann Schneider |
| A hydraulic internal gear machine includes a positive displacement unit for working liquid constituted by a rotary outer gear and an inner gear surrounding the outer gear and being in mesh therewith at one point to define a plurality of increasing liquid displacement chambers. The chambers are laterally bounded by a rotary disc which cooperates with a stationary control plate. The disc and the control plates are formed respectively with flow control openings for admitting pressure liquid into a half of the chambers and for discharging the liquid from the other half of the number of chambers. To compensate for the tilting moment acting on the rotary disc, the interface between the rotary disc and the control chamber is provided with arcuate recessed sections communicating with the openings in the rotary disc to apply pressurized liquid in the displacement chambers against both sides of the rotary disc. | ||||||
| 129 | Rotary piston engine | US555501 | 1975-03-05 | US4032268A | 1977-06-28 | Felix Wankel |
| A rotary piston engine is provided which is suitable for working or conveying media in the form of hot deposit-forming gases or vapors. The engine comprises a housing and a rotor mounted rotatably within the housing. The clearance between the rotor and the housing increases as the engine temperature decreases and decreases as the engine temperature increases. This can be achieved by making the rotor of a material having a higher coefficient of expansion than the material of the housing, and/or by cooling the rotor to a lesser extent than the housing. | ||||||
| 130 | Rotary fluid pressure device and thrust absorbing arrangement therefor | US658330 | 1976-02-17 | US4021161A | 1977-05-03 | Hugh L. McDermott |
| A rotary fluid pressure device of the type including a gerotor gear set having an externally-toothed rotor orbiting and rotating within an internally-toothed stator. An intermediate shaft has one end in splined engagement with the rotor and the other end defining a large set of internal splines. The device includes an output shaft assembly, also defining a large set of internal splines, with a large dogbone shaft transmitting torque between the intermediate shaft and the output shaft assembly. A portion of the housing disposed between the gerotor gear set and the end of the intermediate shaft defining the internal splines is engaged by the enlarged portion of the intermediate shaft, resulting in large and random axial forces being exerted by the intermediate shaft. To absorb such thrust forces, a wear ring is seated within a recess formed in the housing portion and includes an annular wear surface defining an axis substantially coincidental with the axis of the internally-toothed stator. During operation, with the intermediate shaft orbiting and rotating, the wear surface is engaged by a stop surface on the intermediate shaft. With the wear surface having an average diameter equal to N (the number of internal teeth on the stator) multiplied by 2E (where E is the eccentricity of the gerotor), rubbing action and the resulting wear occurring conventionally between the stop surface and the wear surface is eliminated and the engagement occurring therebetween is substantially pure rolling motion. | ||||||
| 131 | Fluid-cooled, scroll-type, positive fluid displacement apparatus | US627854 | 1975-11-03 | US3986799A | 1976-10-19 | John E. McCullough |
| Cooling means are provided for the stationary and orbiting scroll members of scroll-type apparatus. These cooling means comprise fluid coolant channels in the end plates and in the involute wraps of the scroll members and means to circulate a fluid coolant therethrough. In the case of the stationary scroll member the coolant may be water, oil or the like; while in the case of the orbiting scroll member the coolant is the lubricating oil used to lubricate a thrust bearing and the coupling means. The resulting effective cooling of the scroll members makes it possible to form scroll apparatus in large sizes. | ||||||
| 132 | Scroll-type positive fluid displacement apparatus | US36890773 | 1973-06-11 | US3884599A | 1975-05-20 | YOUNG NIELS O; MCCULLOUGH JOHN E |
| A positive fluid displacement apparatus employing scroll members having interfitting spiroidal wraps angularly and radially offset such that as the spiral centers experience an orbiting motion, they define one or more moving fluid pockets of variable volume. The zones of lowest and highest pressures are connected to fluid ports. Radial sealing is accomplished with minimum wear by using a driving mechanism which provides a centripetal radial force adapted to oppose a fraction of the centrifugal force acting on the orbiting scroll member. The line contact sealing force between the wraps of the scroll members constitutes the sole radial constraining force. Coupling means which are separate from the driving means, and hence from the radial constraining means, are provided to maintain the desired angular relationship between scroll members. Axial sealing is attained by withdrawing a portion of fluid from the zone of highest pressure and using this high-pressure fluid to generate axial sealing forces. The apparatus may serve as a compressor, expander or pump.
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| 133 | Composite variable oil pressure relief and compressor unload valve assembly | US3759636D | 1972-03-13 | US3759636A | 1973-09-18 | SCHAEFER D; MORIN J |
| An axially shiftable piston is pressure biased by screw compressor oil pressure to a position closing off communication between the intake and the discharge sides of an axial screw compressor but is biased to the unload position by the compressor discharge and a biasing spring acting on the same. The piston carries a fixed or variable oil pressure relief valve to vary the compressor oil pressure with change in compressor thrust load which, in turn, varies with the compressor discharge pressure.
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| 134 | Balancing mechanism for fluid translating device | US3695789D | 1970-04-13 | US3695789A | 1972-10-03 | JANSSON BIRGER F |
| A fluid translating device having a rotor rotatably mounted within a bore in a camblock that is supported within a housing. The rotor is spaced from the bore to define an annular space and has plates extending from opposite ends thereof with the end portions of the side plates being in overlapping spaced relationship with the opposed surfaces of the camblock. The opposed surfaces of the camblock have a plurality of circumferentially spaced recesses formed therein with each of the recesses communicating with the annular space through a slot. Thus, fluid being translated between inlet and outlet ports flows in the spaces between the end portions of the plate and the adjacent surfaces of the camblock and seals the annular space, while some of the pressure fluid is received in the respective recesses to maintain the camblock in a centered position between the respective end portions of the plates. In one embodiment, the recesses are arcuate and located on a common diameter greater than the diameter of the bore. In an alternate embodiment, the recesses are arcuate and one end of each recess is closer to the surface of the bore than the opposite end while the camblock has cutout portions extending from the bore surface and from the outer surface, so that all portions of the plate end portions are exposed to the fluid. In a further embodiment, the recesses are substantially longitudinal and extend chordally of the center of the bore. The camblock also has surfaces adjacent the housing opening which are beveled from a center point to produce substantial line contact between the housing opening and the camblock.
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| 135 | Axial limit means for male and female spline teeth in an orbital connection | US3657903D | 1970-12-15 | US3657903A | 1972-04-25 | WOODLING GEORGE V |
| Male and female spline teeth in an orbital connection between an orbital shaft and fluid pressure operating means are limited against relative axial movement by axial limit means comprising side member means held in facing relation to a side of said fluid pressure operating means. The side member means includes a shaft opening having a reference axis. The orbital shaft extends through said shaft opening and has a rotational movement about its own shaft axis and an orbital movement about said reference axis of said shaft opening. The side member means has stop wall means extending outwardly from said shaft opening. The orbital shaft has a shoulder with face wall means abuttably engaging the stop wall means to limit relative axial movement between the male and female spline teeth.
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| 136 | Pressurized roller means in a fluid pressure device | US3591320D | 1969-04-08 | US3591320A | 1971-07-06 | WOODLING GEORGE V |
| The pressurized roller means is featured in a stator-rotor mechanism having stator and rotor means, the latter of which having a rotational movement about its own axis and an orbital movement about the axis of the stator means. The stator means includes a plurality of cylindrical roller means journaled respectively in a plurality of open journal pockets. A minor cylindrical portion of the respective roller means is exposed through the open pockets. The exposed, minor cylindrical portions constitute internal teeth for the stator means. Upon relative movement between the stator means and the rotor means, the rotor means is disposed to contact the exposed, minor cylindrical portions, whereby they may rotate and thus convert what would otherwise be a sliding contact into a roller contact. A major cylindrical portion of the roller means is held in the respective pockets by a confronting wall which circumferentially embraces a major portion of the pockets. A substantially fluidtight clearance space is provided between the confronting wall and a major portion of the roller means. Pressurized fluid is conducted to this clearance space for fluidically supporting the roller means in the pockets.
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| 137 | Thrust balancing in rotary machines | US56447366 | 1966-06-23 | US3388854A | 1968-06-18 | KRISTOFER OLOFSSON HANS; IVAR TRULSSON SVEN |
| 1,177,236. Bearings. ATLAS COPCO A.B. 6 June, 1967 [23 June, 1966], No. 26046/67. Heading F2A. [Also in Division F1] In a rotary compressor, a rotor 6 is supported at one end by a roller bearing 8 and biased towards a gear casing 2 by an annular wavyspring 35 acting upon a ball-bearing 9, axial thrust exerted on the latter by the spring and the working fluid acting on the rotor being partially balanced by an opposing axial thrust of an annular piston 36 to which pressure is applied through a pipe connection 40, thus minimizing the load on the bearing 9. It is indicated that the piston may be fixed relative to the casing of the compressor and a cylinder 37 therefor rendered movable axially. | ||||||
| 138 | Thrust balancing | US23448662 | 1962-10-31 | US3161349A | 1964-12-15 | BENEDICTUS SCHIBBYE LAURITZ |
| 139 | 축방향 스러스트 밸런스를 위한 유압 시스템이 제공된 나선형 톱니를 포함한 기어 펌프 또는 유압 기어 모터 | KR1020147032370 | 2014-05-20 | KR101664646B1 | 2016-10-11 | 페레티,스테파노; 페르시치,다니로 |
| 샤프트(10)에결합된제1 톱니휠(1), 제1 톱니휠(1)과결합하고샤프트(20)에결합된제2 톱니휠(2), 톱니휠의샤프트(10, 20)를회전방식으로지지하는지지부(4, 5), 입구유체덕트및 출구유체덕트를형성하고지지부(4, 5)를수용하는케이스(3), 전방플랜지(6) - 상기전방플랜지로부터샤프트의돌출부분(13)이전방을향하여돌출되고제1 톱니휠의샤프트(10)에연결되며샤프트의상기돌출부분(13)은모터(M) 또는로드에연결됨 - , 및케이스(3)에고정된후방뚜껑(7) - 상기톱니휠(1, 2)의톱니는나선형타입임 - 을포함하는기어펌프또는유압기어모터(100, 200)로서, 상기기어펌프또는유압기어모터(100, 200)는전방플랜지(6)와케이스(3) 사이에배치된중간플랜지(8) - 상기중간플랜지(8)는연결덕트(82)에의해입구또는출구유체덕트에연결된제1 챔버(80)를포함함 - , 및제1 톱니휠의샤프트(10)에대한운동전달을허용하고제1 톱니휠에가해진축방향힘(A)을보상하기위한방식으로제1 톱니휠의샤프트(10)의부분(T)에삽입되고중간플랜지의제1 챔버(80) 내에장착된보상링(9) - 상기보상링은실린더(90)로부터반경방향으로돌출되는칼라(91) 및내부가빈 실린더(90)를포함하고칼라(91)와실린더(90)의외부직경(d1, d2)은제1 톱니휠에가해진축방향힘(A)을보상하도록선택됨 - 을포함한다. | ||||||
| 140 | 축방향 스러스트 밸런스를 위한 유압 시스템이 제공된 나선형 톱니를 포함한 기어 펌프 또는 유압 기어 모터 | KR1020147032370 | 2014-05-20 | KR1020150009973A | 2015-01-27 | 페레티,스테파노; 페르시치,다니로 |
| 샤프트(10)에 결합된 제1 톱니 휠(1), 제1 톱니 휠(1)과 결합하고 샤프트(20)에 결합된 제2 톱니 휠(2), 톱니 휠의 샤프트(10, 20)를 회전 방식으로 지지하는 지지부(4, 5), 입구 유체 덕트 및 출구 유체 덕트를 형성하고 지지부(4, 5)를 수용하는 케이스(3), 전방 플랜지(6) - 상기 전방 플랜지로부터 샤프트의 돌출 부분(13)이 전방을 향하여 돌출되고 제1 톱니 휠의 샤프트(10)에 연결되며 샤프트의 상기 돌출 부분(13)은 모터(M) 또는 로드에 연결됨 - , 및 케이스(3)에 고정된 후방 뚜껑(7) - 상기 톱니 휠(1, 2)의 톱니는 나선형 타입임 - 을 포함하는 기어 펌프 또는 유압 기어 모터(100, 200)로서, 상기 기어 펌프 또는 유압 기어 모터(100, 200)는 전방 플랜지(6)와 케이스(3) 사이에 배치된 중간 플랜지(8) - 상기 중간 플랜지(8)는 연결 덕트(82)에 의해 입구 또는 출구 유체 덕트에 연결된 제1 챔버(80)를 포함함 - , 및 제1 톱니 휠의 샤프트(10)에 대한 운동 전달을 허용하고 제1 톱니 휠에 가해진 축방향 힘(A)을 보상하기 위한 방식으로 제1 톱니 휠의 샤프트(10)의 부분(T)에 삽입되고 중간 플랜지의 제1 챔버(80) 내에 장착된 보상 링(9) - 상기 보상 링은 실린더(90)로부터 반경방향으로 돌출되는 칼라(91) 및 내부가 빈 실린더(90)를 포함하고 칼라(91)와 실린더(90)의 외부 직경(d1, d2)은 제1 톱니 휠에 가해진 축방향 힘(A)을 보상하도록 선택됨 - 을 포함한다. | ||||||
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