Source: http://www.google.com/patents/US20050254982
Timestamp: 2017-01-23 03:24:43
Document Index: 92027421

Matched Legal Cases: ['art 1', 'art 2', 'art 1', 'art 2', 'art 2', 'art 2', 'art 2', 'art 2', 'art 1', 'art 2', 'art 1', 'art 1', 'art 2', 'art 1', 'art 1', 'art 2', 'art 2', 'arty 101', 'art 102', 'art 101', 'art 101', 'art 101']

Patent US20050254982 - Internal gear machine with variable capacity - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign inPatentsA fluidic machine has a fixed body, an external orbital member rotatable around a first rotational axis and internal gear teeth including a first teeth number, a transmission member rotatable around a second rotational axis, an internal orbital member supported by the transmission member, having external...http://www.google.com/patents/US20050254982?utm_source=gb-gplus-sharePatent US20050254982 - Internal gear machine with variable capacityAdvanced Patent SearchTry the new Google Patents, with machine-classified Google Scholar results, and Japanese and South Korean patents.Publication numberUS20050254982 A1Publication typeApplicationApplication numberUS 10/519,244PCT numberPCT/EP2003/006413Publication dateNov 17, 2005Filing dateJun 17, 2003Priority dateJun 26, 2002Also published asCN1666010A, CN1666010B, EP1516105A1, EP1516105B1, US7195467, WO2004003345A1Publication number10519244, 519244, PCT/2003/6413, PCT/EP/2003/006413, PCT/EP/2003/06413, PCT/EP/3/006413, PCT/EP/3/06413, PCT/EP2003/006413, PCT/EP2003/06413, PCT/EP2003006413, PCT/EP200306413, PCT/EP3/006413, PCT/EP3/06413, PCT/EP3006413, PCT/EP306413, US 2005/0254982 A1, US 2005/254982 A1, US 20050254982 A1, US 20050254982A1, US 2005254982 A1, US 2005254982A1, US-A1-20050254982, US-A1-2005254982, US2005/0254982A1, US2005/254982A1, US20050254982 A1, US20050254982A1, US2005254982 A1, US2005254982A1InventorsLeonardo CadedduOriginal AssigneeLeonardo CadedduExport CitationBiBTeX, EndNote, RefManPatent Citations (5), Referenced by (18), Classifications (19), Legal Events (3) External Links: USPTO, USPTO Assignment, EspacenetInternal gear machine with variable capacity
[0033] The machine according to the invention is represented in two exemplary embodiments forming hydraulic pumps for the circulation under pressure of the lubricant oil in an automotive engine. [0034] With reference to the first embodiment, represented in FIGS. 1 to 10, the pump includes a fixed body formed by an operative part 1 and a supporting part 2, this latter being intended to be connected to a fixed part of a vehicle, in general the engine, and to receive the operative part 1, connected to and supported by body part 2. The supporting part 2 includes two connections for the circulation circuit of the lubricant oil, namely an intake feed connection 20 and an outlet delivery connection 21. In the supporting part 2 are provided two chambers, an intake chamber 22 connected to the intake feed connection 20, and an outlet chamber 23 connected to the outlet delivery connection 21; these chambers are separated by protrusions. [0035] In the supporting part 2 there is rotatably mounted a transmission member 3 which extends outwards with a clutch pivot 30 for a member intended to actuate the pump. A seal ring 4 establishes a hermetic closure towards the exterior. The transmission member 3 rotates in the supporting part 2 with a relative hydraulic seal with respect to the protrusions separating the chambers 22 and 23. Moreover, the transmission member 3 has conformations 31 suitable for performing a distribution function among the variable spaces of the pump, described later on, and the chambers 22 and 23 connected to the intake feed connection 20 and to the outlet delivery connection 21, respectively. [0036] An internal orbital member 5, which in this embodiment has the shape of a prismatic body forming four external gear teeth, is slidably inserted within an axial cavity 32 of the transmission member 3, and this cavity 32 is shaped in a manner corresponding to the internal orbital member in order to establish both a rotational solidarity and a relative hydraulic seal between the transmission member 3 and said internal orbital member 5. This means that the internal outline of the transmission member 3 (namely, the cavity 32) corresponds to the external outline of the internal orbital member 5. Moreover, a compression spring 6 is inserted between the end of a cavity of the internal orbital member 5 and the end of the cavity 32 of the transmission member 3, and this spring aims to push outwards the internal orbital member 5. [0037] The internal orbital member 5 is engaged in an external orbital member 7, which is mounted in the operative part 1 of the pump body, and is rotatable around an axis which does not coincide with the rotational axis of the transmission member 3. The external orbital member 7 has inner gear teeth, in this case comprising five teeth, which mesh, with relative hydraulic seal, with the external gear teeth, in this case comprising four teeth, of the internal orbital member 5. Between the gear teeth of the two orbital members 5 and 7 are defined some spaces, whose volume varies during the rotation. The cooperation between the two orbital members 5 and 7, with the aid of the distribution conformations 31 of the transmission member 3, which operate among said variable volume spaces and the chambers 22 and 23 of the supporting body part 2, embodies, in a way per se known, a gear pump. [0038] In the cavity delimited by the internal gear teeth of the external orbital member 7 is engaged, axially slidable with relative hydraulic seal, a piston 8, whose external outline corresponds to the internal outline of the external orbital member 7. Piston 8 extends with a guide tang 80 in a bore of the operative body part 1 of the pump. This bore is closed towards the exterior by a plug 11, and the space 10 comprised between this plug 11 and the tang 80, through passages 12 and 24 bored in the body part 1 and in the body part 2, respectively, communicates with the intake feed connection 20, whereby the axial displacements of tang 80 with piston 8 are allowed. [0039] At the end of the cavity in the body part 1, wherein the external orbital member 7 is housed, there is hollowed a chamber 13 which, through passages 14 and 25 bored in the body part 1 and in the body part 2, respectively, communicates with the delivery outlet connection 21. Therefore, in chamber 13 dominates the delivery pressure of the pump, and this pressure acts on piston 8 and aims to push the same in the direction going towards inside the external orbital member 7. On its turn, the internal orbital member 5 is pushed by spring 6 in the direction opposite the direction now stated, whereby it always remains resting against piston 8. [0040] Until the delivery pressure, which acts on the exposed surface of piston 8, generates a force lower than the force exerted by spring 6, the internal orbital member 5 remains engaged within the external orbital member 7 for the maximum possible extension, namely, along a length equal to the difference between the axial extensions of the external orbital member 7 and of the piston 8, respectively (FIGS. 5 to 7). Thus, a swept volume of the pump is generated, that is the greatest allowed by the pump geometry. Until this condition is verified, the pump according to the invention behaves at all as a usual gear pump having the same swept volume. [0041] When, increasing the rotational speed applied to the pump, the delivery rate and the delivery pressure at the outlet increase, at a certain moment this pressure, by acting on the exposed surface of piston 8, generates a force larger than the force applied to the internal orbital member 5 by spring 6. Beginning from this moment, piston 8 penetrates into the external orbital member 7 by repelling the internal orbital member 5, which enters in part in the transmission member 3 (FIGS. 8 to 10). Therefrom it ensues a reduction of the swept volume of the pump and, therefore, a reduction of its delivery rate and of the delivery pressure. A balance is thus found, which depends on the elastic characteristics of the compression spring 6 and on the surface of piston 8 which is exposed to the delivery pressure. [0042] As it may be understood from the foregoing, the portion of both orbital members, which is active in the pumping operation and defines the swept volume of the pump, is only the mutually engaging portion thereof and this portion is delimited with relative hydraulic seal, for the external orbital member 7, by piston 8 which penetrates therein and whose external outlet corresponds to the internal outline of the external orbital member 7, and for the internal orbital member 5, by the transmission member 3 whose internal outline corresponds (with the exception of the openings 31 which determinate the distribution function) to the external outline of the internal orbital member 5 which penetrates in the transmission member 3. This swept volume may be varied within broad limits and, therefore, within as much broad limits may be varied the delivery rate of the pump. [0043] Therefore, thanks to the characteristics of the invention, by suitably determining the elastic characteristics of spring 6 and the surface of piston 8 that is exposed to the delivery pressure, it is possible to provide a desired course of the pump performance as a function of the produced delivery pressure, and therefore of the speed at which the pump is operated. It is clear that in a way at all similar it is possible to provide a desired course of the performance of a hydraulic motor as a function of the feed pressure imposed to it. [0044] Because among the moving parts of the pump it is not possible to provide an hermetic hydraulic seal, but only a relative (namely, partial) hydraulic seal, some leakages of oil take place. In order to recover these leakages, the passages 33 and 26 and an annular chamber 27 are provided in the transmission member 3 and in the body part 2, respectively, communicating with the intake connection 20. [0045] The structure of the second embodiment, represented in FIGS. 11 to 19, differs from the structure of the first embodiment in practical features intended to render more easy the manufacture and the assemblage of the machine. In this embodiment, the pump is based on the same conception of the first embodiment and operates in a manner at all equivalent, whereby it is not needed to describe in detail its structure and operation; of this second embodiment are therefore described only the differences with respect to the first embodiment. The component parts of the second embodiment which correspond to component parts of the first embodiment are designated by the same numbers of reference, increased by 100. [0046] A first noticeable difference resides in that, in the second embodiment, the member acting as a distributor among the variable volume spaces and the chambers of the fixed body is the external orbital membei 107, instead of the transmission member 3 of the first embodiment. To this aim, the external orbital member 107 has special conformations 171. As a consequence, the intake chamber 122 and the delivery chamber 123, as well as, of course, the corresponding intake feed connection 120 and delivery outlet connection 121 are located in the operative body party 101 rather than in the supporting body part 102. [0047] The structure of piston 108 is simplified, and it is no more provided with a guide tang; as a consequence, also the corformation of the operative body part 101 is correspondingly simplified, and the chamber 113 receives the required pressure through a bore 181 made in piston 108, a chamber 182 also hollowed in piston 108, and a bore 151 made in the internal orbital member 105, this latter bore communicating with the axial cavity 132 of the transmission member 103. The pressure present in the delivery chamber 123 arrives to the end of the axial cavity 132 through a longitudinal passage 115 and a radial passage 116 (FIG. 17) hollowed in the operative body part 101. Chamber 182 of piston 108, in addition to serve to the cited connection, also has the function of reducing the contact surface between the piston 108 and the internal orbital member 105. [0048] The drainage of the oil leakage towards the seal ring 104 takes place through a longitudinal passage 141, a radial passage 142 and a longitudinal bore 143, all made in the operative body part 101 of the pump. The longitudinal bore 143 opens in the low pressure connection 120. [0049] The transmission member 103 is embodied separately from the clutch pivot 130 in order to facilitate their manufacture. [0050] As it may be easily remarked, the second embodiment offers noticeable simplifications in its structure with respect to the first embodiment, though attaining an identical operation. [0051] It is to be understood that the invention is not limited to the embodiments described and illustrated as examples. Several possible changes have been described, and various others are within the capacity of a skilled person; for example, the functions of different members may be respectively exchanged, and thus one could foresee that the possibility of axial displacement against the action of pushing means be attributed to the external orbital member rather than to the internal orbital member. The pushing means, which in the more simple embodiment consist of one or more compression springs, could be replaced by other elastic members or even by hydraulic or pneumatic pushing means, which may be controlled in various manners. It is also evident that the fluidic machine, described as a hydraulic pump, could be used as a hydraulic motor by feeding to the connection 21 or 121 a feed fluid under pressure, which is then discharged at a lower pressure from the connection 20 or 120. The characteristics of such a motor, and particularly its swept volume and therefore the torque and the angular speed delivered through the transmission member 3, depend on the feed pressure. Finally, it is to be understood that, although the foreseen application of the invention prevailing concerns hydraulic machines, the invention may also find application in pneumatic machines, particularly by having recourse to autolubricant materials or to the so called “damp lubrication”. [0052] The cited changes and others, and any replacement by technically equivalent means, may be introduced in what has been described and illustrated, without departing from the spirit of the invention as defined by the appended claims. Patent CitationsCited PatentFiling datePublication dateApplicantTitleUS1486682 *Jun 11, 1923Mar 11, 1924Phillips Harry CBotary pumpUS1773211 *Sep 24, 1927Aug 19, 1930James B TuthillRotary machineUS2484789 *Apr 15, 1944Oct 11, 1949Hill LabVariable displacement pump and motorUS3687578 *Sep 4, 1970Aug 29, 1972Trw IncHydraulic pump motorUS4740142 *Aug 11, 1986Apr 26, 1988Rohs Hans GuntherVariable capacity gear pump with pressure balance for transverse forces* Cited by examinerReferenced byCiting PatentFiling datePublication dateApplicantTitleUS7184202 *Jan 28, 2005Feb 27, 2007Idc, LlcMethod and system for packaging a MEMS deviceUS7470373Mar 7, 2006Dec 30, 2008Qualcomm Mems Technologies, Inc.Optical interference display panelUS7668415Mar 25, 2005Feb 23, 2010Qualcomm Mems Technologies, Inc.Method and device for providing electronic circuitry on a backplateUS7701631Mar 7, 2005Apr 20, 2010Qualcomm Mems Technologies, Inc.Device having patterned spacers for backplates and method of making the sameUS7746537Apr 12, 2007Jun 29, 2010Qualcomm Mems Technologies, Inc.MEMS devices and processes for packaging such devicesUS7933476Feb 22, 2010Apr 26, 2011Qualcomm Mems Technologies, Inc.Method and device for providing electronic circuitry on a backplateUS7978396Dec 23, 2008Jul 12, 2011Qualcomm Mems Technologies, Inc.Optical interference display panelUS8004736May 8, 2009Aug 23, 2011Qualcomm Mems Technologies, Inc.Optical interference display panel and manufacturing method thereofUS8045835Aug 15, 2008Oct 25, 2011Qualcomm Mems Technologies, Inc.Method and device for packaging a substrateUS8090229Apr 22, 2011Jan 3, 2012Qualcomm Mems Technologies, Inc.Method and device for providing electronic circuitry on a backplateUS8115983Apr 14, 2009Feb 14, 2012Qualcomm Mems Technologies, Inc.Method and system for packaging a MEMS deviceUS8124434Jun 10, 2005Feb 28, 2012Qualcomm Mems Technologies, Inc.Method and system for packaging a displayUS8379392Oct 23, 2009Feb 19, 2013Qualcomm Mems Technologies, Inc.Light-based sealing and device packagingUS8682130Sep 13, 2011Mar 25, 2014Qualcomm Mems Technologies, Inc.Method and device for packaging a substrateUS8684712 *May 10, 2010Apr 1, 2014Toyota Jidosha Kabushiki KaishaOil pump for a vehicleUS20060077533 *Jan 28, 2005Apr 13, 2006Miles Mark WMethod and system for packaging a MEMS deviceUS20070247693 *Feb 26, 2007Oct 25, 2007Idc, LlcMethod and system for packaging a mems deviceUS20100290941 *May 10, 2010Nov 18, 2010Toyota Jidosha Kabushiki KaishaOil pump for a vehicle* Cited by examinerClassifications U.S. Classification418/61.3International ClassificationF01C1/08, F01C1/10, F01M1/16, F04C2/10, F04C14/18, F01C20/18, F04C14/20, F04C15/00Cooperative ClassificationF01C1/084, F01C20/185, F04C2/102, F01C1/103, F04C2270/18, F04C15/0073European ClassificationF01C20/18B, F01C1/08B2, F04C15/00E2F, F01C1/10DLegal EventsDateCodeEventDescriptionJan 23, 2007ASAssignmentOwner name: VHIT S.P.A., ITALYFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CADEDDU, LEONARDO;REEL/FRAME:018802/0775Effective date: 20070107Sep 20, 2010FPAYFee paymentYear of fee payment: 4Sep 22, 2014FPAYFee paymentYear of fee payment: 8RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services