WO2007019018A2 - Compresseur d'etancheite a jeu limite - Google Patents

Compresseur d'etancheite a jeu limite Download PDF

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Publication number
WO2007019018A2
WO2007019018A2 PCT/US2006/028378 US2006028378W WO2007019018A2 WO 2007019018 A2 WO2007019018 A2 WO 2007019018A2 US 2006028378 W US2006028378 W US 2006028378W WO 2007019018 A2 WO2007019018 A2 WO 2007019018A2
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WO
WIPO (PCT)
Prior art keywords
vane
rotor
assembly
rotating
centering
Prior art date
Application number
PCT/US2006/028378
Other languages
English (en)
Other versions
WO2007019018A3 (fr
Inventor
Thomas C. Edwards
Original Assignee
Edwards Thomas C
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US11/198,773 external-priority patent/US7491037B2/en
Application filed by Edwards Thomas C filed Critical Edwards Thomas C
Publication of WO2007019018A2 publication Critical patent/WO2007019018A2/fr
Publication of WO2007019018A3 publication Critical patent/WO2007019018A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers

Definitions

  • This invention relates to positive displacement rotary vane compressors and vacuum pumps and, in particular, to methods, systems, apparatus and devices that provide a mechanically-governed, positive-displacement, non-contact sealing compression or vacuum device that uses roller bearings to control the radial position of the vane and uses control rods or pins to control the axial position of the vane with respect to the rotor and the endplates.
  • Vane centering (attaining accurate axial positioning to avoid side contact between the vane ends and the stator endplates) is easily achieved through the use of ball bearings as taught, for example, in U.S. patent 5,374,172, issued on December 20, 1994 to Edwards, and entitled "Rotary UniVane Gas Compressor.” Further, axially positioning through the use ball bearings is commonly used in both alternating and direct current electric motors as well as in contact-sealing vane compressors. Also made of record is U.S. Patent 5,160,252 issued on November 3, 1992 which is a continuation-in-part of the '183 patent.
  • U. S. Patent No.6,503,071 issued on January 7, 2003 to Edwards discloses a high-speed UniVane® fluid-handling device.
  • This single vane gas displacement apparatus comprises a stator housing with a right cylindrical bore enclosing an eccentrically mounted rotor which also has a radial slot in which is movably radially positioned a single vane.
  • the vane is tethered to antifriction vane guide assemblies concentric with the housing bore. Then vane has a pre-selected center of gravity located proximate to the housing bore axis.
  • An option is to have a port in the vane for ducting high-pressure gas to the inlet side to react against the rotor slot to reduce vane contact therewith.
  • the rotor has a rotational axis and carries at least one vane which is supported by a vane guide apparatus for rotation about a stator axis which is spaced from the rotor axis a preselected amount and where both the rotor and vane have axial flat surfaces which are rotated adjacent to stationary flat surfaces of a stator or stator endplates.
  • the patent discloses a provision for axial adjustment of the vane with respect to the flat surface of the stator endplates and independently provides an adjustment of the rotor end surfaces with respect to the stator end surfaces.
  • the single vane and double vane apparatus of the present invention embody two important distinctions from the prior art UniVane® patents (5,374,172, 6,503,071, 6,623,261).
  • roller bearings are used to control the radial position of the vane
  • second, axial positioning control rods or pins are used to dictate the axial position of the vane (its 'centralization') with respect to the rotor and the endplates.
  • the prior art UniVane patents teach the use of a second set of ball bearings that simultaneously control both the radial and axial location of the vane and operate with respect to the stator endplates and not the rotor.
  • the present invention teaches specific means to achieve the practical use of both a single vane and a dual vane device in which problems of dynamic balance and precision radial vane centering is achieved through the use of roller bearings; not ball bearings.
  • the embodiments taught herein primarily encompass the application of precision rotor centering directly with respect to the stator housing, vane centering with respect to rotor (not the stator) and the dynamic balance design of the gliders required for practical single and dual vane devices.
  • a primary objective of the invention is to provide new methods, systems, apparatus and devices that provide a mechanically-governed, positive-displacement, non-contact sealing compression or vacuum device.
  • a second objective of the invention is to provide new methods, systems, apparatus and devices to provide a positive displacement rotary vane compressors and vacuum pumps that embrace the basic concept of friction reduction, and efficiency enhancement and exceedingly long operating life through the creation of specific means that result in non-contact gas sealing of the process gas.
  • a third objective of the invention is to provide new methods, systems, apparatus and devices that provide a mechanism whose moving parts exercise precision repetitive internal motion at a level of accuracy required to insure that the moving parts do not contact the static, non-moving parts of the machine and, simultaneously, maintain internal sealing clearance gaps small enough to keep internal leakage acceptably small in order to yield high efficiency.
  • a fourth objective of the invention is to provide new methods, systems, apparatus and devices to provide precision rotor centering directly with respect to the stator housing, vane centering with respect to rotor (not the stator) and the dynamic balance design of the gliders required for practical single and dual vane devices.
  • a fifth objective of the invention is to provide new methods, systems, apparatus and devices that uses roller bearings to control the radial position of the vane.
  • a sixth objective of the invention is to provide new methods, systems, apparatus and devices that uses axial positioning control rods or pins to control the axial position of the vane, its centralization, with respect to the rotor and the endplates.
  • a seventh objective of the present invention is to provide new methods, systems, apparatus and devices for a DuoVane machine wherein the second vane blocks the noise pulse inherent to the incomplete emptying of the volume at the discharge valve assembly in the MonoVane unit to provide both a quieter and considerably smaller machine.
  • An eighth objective of the present invention is to provide new methods, systems, apparatus and devices for a positive-displacement, non-contact sealing compression device for circulating hydrogen, ionized or deionized water and hydrogen or an alternative fuel.
  • a ninth objective of the present invention is to provide new methods, systems, apparatus and devices for a positive-displacement, non-contact sealing compression device for fuel cell applications for use with transportation devices, such as cars, trucks, busses and the like.
  • a tenth objective of the present invention is to provide new methods, systems, apparatus and devices for high efficiency, low-pressure, non-lubricated air compressors and hydrogen circulators.
  • An eleventh objective of the present invention is to provide new methods, systems, apparatus and devices to provide a compressor for use in life sciences, semiconductor processing, medical device, vacuum pump applications, and for pond aeration systems at golf courses.
  • a twelfth objective of the present invention is to provide new methods, systems, apparatus and devices to provide a compressor for use as a reversible refrigerant compressors, and miniature compressors and vacuum pumps.
  • a thirteenth objective of the present invention is to provide new methods, systems, apparatus and devices to provide a compressor or vacuum device that is lubricant-free.
  • a fourteenth objective of the present invention is to provide new methods, systems, apparatus and devices to provide compressor or vacuum devices that are non-contact and virtually frictionless.
  • the methods, systems, apparatus and devices of the present invention provide a positive displacement apparatus having a stator housing having an interior bore therethrough, a first and a second endplate connected to the stator housing at each end of the interior bore to form a compression or vacuum chamber.
  • a rotor having a rotor shaft is positioned in the interior bore such that one end of the rotor shaft is connected to an external power source for rotating the rotor within the interior bore.
  • a rotor centering device is used for centering the rotor with respect to the stator housing to prevent the rotating rotor from contacting the interior bore and the first and second endplates.
  • a rotating vane assembly having at least one vane and a vane centering device for connecting the rotating vane assembly to the rotor shaft and centering at least one vane with respect to the rotor.
  • the rotor centering device controls a radial position of the rotating vane assembly and the vane centering device controls an axial position of rotating vane assembly to prevent contact of the at least one vane with the stationary compression chamber components.
  • rotating vane assembly includes one vane.
  • the vane assembly includes a first and a second vane positioned approximately 180° apart, such that as the first vane and the second vane rotate the second vane blocks a noise pulse inherent to the incomplete emptying of the volume at the discharge valve assembly to provide a quieter compression apparatus.
  • the embodiments taught in the present invention described herein primarily encompass the application of precision rotor centering directly with respect to the stator housing, vane centering with respect to rotor (not the stator) and the dynamic balance design of the gliders required for practical single and dual vane devices.
  • Figs. Ia and Ib are a front view and a side view, respectively, of an orbital MonoVane device according to the present invention.
  • Figs. 2a and 2b shows a disassembled front view and side view, respectively, of the orbital MonoVane device shown in Figs. Ia and Ib, respectively.
  • Fig. 3a and 3b are a side view and corresponding front view, respectively, showing the use of roller bearings to control the radial location of the vane with respect to a rotor centered with respect to the stator and the use of a centering control rod to control the vane's axial location.
  • 3c is an expanded view showing the use of roller bearings to control the radial location of the vane with respect to a rotor centered with respect to the stator and the use of a centering control rod to control the vane's axial location in separated views.
  • Figs. 4a, 4b and 4c show alternative examples of the vane-centralizing positional control rod and the mating passage accommodating the control rod.
  • Fig. 5a shows front view of the Duo Vane embodiments of the present invention wherein the roller bearings are placed on the OD of the glider rings.
  • Fig. 5b shows a side view of the DuoVane embodiment shown in Fig. 5a.
  • Figs. 6a and 6b show expanded front and side views, respectively, of the DuoVane apparatus shown in Figs. 5a and 5b, respectively, showing additional detail.
  • Fig. 7a is a front view showing another example of the DuoVane apparatus.
  • Fig. 7b is a side view of the DuoVane machine shown in Fig. 7a.
  • Fig. 8a is a front view showing additional detail of the rotating components of the
  • Fig. 8b and 8c show a front view of the rotating vane assembly and the vane counter balance, respectively, from one side.
  • Fig. 8d and 8e show a front view of the rotating vane assembly and the vane counter balance, respectively, from an opposite side.
  • Figure 9 shows another example of the DuoVane apparatus embodiment shown in Fig. 8.
  • Fig. 10a shows yet another example of the DuoVane apparatus embodiment shown in Figs. 5a through Fig. 9.
  • Fig. 10b and 10c show a front view of the rotating vane assembly and the vane counter balance, respectively, shown in Fig. 10a from one side.
  • Fig. 1Od and 1Oe show a front view of the rotating vane assembly and the vane counter balance, respectively, shown in Fig. 1 Oa from an opposite side.
  • Fig. 11 shows yet another example of the DuoVane apparatus embodiment shown in Figs. 5a through Fig. 9.
  • axle stub 287 cross slots 10 271a snap ring 20 290 axle stubs
  • the methods, systems, apparatus and devices of the present invention provide very exact mechanical devices that rigidly holds rotating compressor parts in precision cyclic paths of continuous motion that do not engage or touch the non-rotating components.
  • the non-engagement distance, the leakage clearance is small enough to insure that the gas being processed by the compressor has only minimal leakage during inlet, compression and discharge.
  • the rotating rotor and its accompanying vane or vanes are positioned securely within their non-rotating stator such that they do not rub against the inner surfaces of this stationary cavity which includes both opposing endplates and the interior bore of the stator housing.
  • the present invention provides two new non-contact sealing compressors and variations thereof herein after called Mono Vane for the single- vane version and Duo Vane for the dual- vane version. Certain embodiments are less expensive to manufacture and
  • Il operate at much higher pressures, including refrigerant compressor pressures with the use of a lubricant.
  • Both the Mono Vane and Duo Vane embodiments use roller bearings to control the radial position of the vane and use control rods or pins to control axial positioning of 5 the vane, its 'centralization' with respect to the rotor and the endplates.
  • the prior art devices used a second set of ball bearings to simultaneously control both the radial and axial location of the vane and operated with respect to the stator endplates and not the rotor.
  • roller bearings While capable of withstanding very significant loads and are generally much less expensive than ball bearings, only position radially, they have no significant capability of constraining items in the axial direction.
  • a method for determining the structural requirements to provide apparatus and devices according to the present invention includes the following steps. First, the rotor is »0 accurately located with respect to the stator. Having the rotor location determined, the vane is precisely located with respect to the rotor, and not the stator.
  • Both the Mono Vane and the Duo Vane operate in essentially the same manner. Specifically, when the rotor shaft 100 is rotated from an external mechanical/electrical power source, air is induced into the compressor through the inlet manifold 5, is compressed in the volume of the compression chamber created by the outer diameter of the rotor 40, the internal bore of stator housing 20, the vane 50 and the sealing and confinement actions of endplates 10 and 30.
  • the discharge valve assembly opens and permits the pressurized fluid to pass through the compressor and flow through the outlet manifold 15 and flows to its particular objective as dictated by a given application or use.
  • the compressor simply pulls the gas (often, air) into itself, compresses the gas and expels it.
  • the Mono Vane and Duo Vane devices are non-contact and virtually frictionless machines that can be applied to many application and the operating parameters may be adjusted to meet the needs of the particular application.
  • the Mono Vane and Duo Vane devices may be configured for alternative flow rates, inlet pressures, boost pressures and gas density based on the application in which the device is used. More specifically, the device may be configured for a flow rate that is within a range of approximately 20 LPM up to approximately 5000 LPM.
  • the devices may be configured for an inlet pressure within a range of approximately 0 to approximately 35,000 kPa and a boost pressure of approximately 0 to approximately 250 kPa.
  • One example of an application is for fuel cell applications for use with transportation devices, such as cars, trucks, busses and the like.
  • the devices can be used for circulating hydrogen, ionized or deionized water and hydrogen or an alternative fuel.
  • Other uses include high efficiency, low-pressure, non-lubricated air compressors and hydrogen circulators, compressor for use in life sciences, semiconductor processing, medical device, vacuum pump applications, for pond aeration systems at golf courses, reversible refrigerant compressors, and miniature compressors and vacuum pumps. While a variety of application has been provided, those skilled in the art will appreciate that the devices of the present invention may be used for alternative applications.
  • Figs. Ia and Ib are a front view and a side view, respectively, of the Orbital MonoVane mechanism of the present invention.
  • the MonoVane device uses a combination of roller bearings to govern the radial vane tip position and an axial positioning element embedded in the rotor and rotor shaft and operating in concert with a mating precision radial hole in the vane to use the rotor for centering the vane.
  • the ball bearings also centralize the rotor location within the stator.
  • Figs. 2a and 2b show the separated layout of the assembly shown in Figs. Ia and Ib and, therefore, further illustrates the details of this invention embodiment.
  • the device consists principally of left endplate 10, stator 20, right endplate 30, rotor 40, and vane 50.
  • rotor shaft 100 is firmly attached to the rotor body 40 by any means known to the art. Rotor rotation occurs when sufficient power is applied to the rotor shaft 100, which is held and positioned by bearings 110.
  • the vane 50 contained within the rotor slot 44, is propelled in circular motion by the rotor 40 within the stator 20 cavity.
  • the rotor 40 can be confined to its radial and axial position by, in addition to ball bearings 110, a variety of other conventional bearings such as tapered roller bearings, combinations of roller bearings for the radial location of the rotor shaft 100 and roller thrust bearings for the rotor's axial location with respect to the stator 20, as well as roller bearing/ball thrust bearing combinations.
  • Vane axle 70 engages the axle through-hole 52 in vane 50.
  • the ends of these axles are fastened in usual ways to the inner glider races 62 that operate within the roller bearings 60 (drawn-cup caged type shown here) installed within left and right endplates 10 and 30, respectively.
  • the circular outer diameter of glider races 62 can be slightly crowned to accommodate slight misalignments of the bearings 60 and glider races 62.
  • the rollers of roller bearings 60 can also be crowned to accommodate the same conditions.
  • Vane ring spacer 82 provides additional mass to help counter-balance the mass of the vane 50 and vane axle 70.
  • Counterbalance voids 64 are shaped holes placed in glider races 62 and are sized such that they insure that the rotating vane assembly is dynamically balanced about its center of rotation.
  • Other means known to the art of dynamic balancing can be applied to balance the rotating vane subassembly. This subassembly, again consisting of the vane 50, vane axle 70 both glider races 62 and the spacer 82, controls the precise radial location of the vane tip, whose radius is coincident with the center of the vane axle 70.
  • roller bearings can take high loads, they lack the ability to control axial vane drift, a back-and-forth motion that would cause wear and friction of the vane sides against the endplates.
  • the present invention overcomes that problem through the use of a centralizing or positioning control rod 90 that is firmly attached to rotor shaft 100 as shown in Figs. 1 and 2, inserted into a hole 103 that is placed in the rotor shaft 100 in the middle of the rotor slot 44 of rotor 40.
  • this control rod 90 precisely engages vane hole 56 of vane 50 and prevents axial, side-to-side motion of the vane 50 in rotor slot 44 of rotor 40.
  • Vane axle 70 is fitted with cross-hole 72 that is large enough to accommodate both the diameter and shape of the control rod 90 and approximately +/- 15° relative angular motion between the vane 50, control rod 90 and its respective vane axle 70. While a single control rod 90 is shown, numerous other means can be substituted, such as multiple-rods or conjugate surfaces between the rotor 40 and the vane 50 that will serve to axially anchor the vane to the rotor 40.
  • Figs. 3a and 3b shows a side view and a front view, respectively, of the Mono Vane device
  • Fig. 3c is a disassembled side view of the device shown in Figs. 3a and 3b.
  • Figs. 3a, 3b and 3c show the use of roller bearings 60 to control the radial location of the vane 50 with respect to the rotor 40 which is centered with respect to the stator 20 and shows the use of a centering control rod 90 to control the vane's 50 axial location.
  • the rotor 40 is fixed with respect to the stator housing 20 as previously described.
  • the centering control rod 91 is fixed in the vane 50 and reciprocates within a precision radial hole 104 within the rotor slot 44 bottom and the rotor shaft 100.
  • the inverse variant of the control rod method is show wherein an alternative control rod 91 is fixed to the vane 50 within vane hole 57 and reciprocates within shaft hole 104 that passes through the bottom of the vane slot 54, through the rotor shaft 100 and into the void region 42,
  • This void 42 is shaped so it can both dynamically balance the rotor 40 to make up for the void 42 comprising the vane slot 44 (Fig. 2) and to accommodate the relative motion of the glider race post 80 and vane axle 70 (Fig. 1).
  • Figs. 4a and 4b shows alternative embodiments of the vane-centralizing positional control rod and the mating passage accommodating the control rod 90 and alternatively, control rod 90.
  • the control rod 90 has flattened sides wherein the flat sides reduce the positioning accuracy requirement of the location of control rod 90 and disallow inadvertent pressure build-up within the vane hole 56. This example relieves undesired forces that may arise as slight tolerance stack-ups occur between the vane hole 56, the vane 40 and the vane slot 44.
  • Fig. 4b shows a round control rod 90 used with a round hole 56 in the vane 50.
  • Fig. 4c shows that a round control rod 90 could be used within a hole 56a that is 'race track' in shape and orthogonal to the vane slot 54 to avoid stack-up of tolerances that could lead to contact friction between the control rod 92 and the hole 56a and the vane 50 within the vane slot 54.
  • Control rod 90 or alternative control rod 99 can be hollow (Fig. 4c) and be fitted with cross-holes which can be used both to relieve pressure build-up at the tips of control rods 90 (Fig. 4b) and 91 (Fig. 4a) and to distribute lubricant when used with lubricated machines. As previously described, Figs.
  • FIG. 1 and 2 show the rotor shaft 100 held in place using ball bearings 110.
  • rotor centralization requires that several dimensional conditions be met.
  • the challenge becomes the specific axial location of the bearings such that their position insures centrality of the rotor.
  • This requirement is achieved in a variety of ways, the most obvious of which involves particularly tight manufacturing tolerances so that the rotor will be in the proper place immediately upon assembly. Less accurate machining would add a requirement for the measurement and placement of selective spacers or alterative compensation components.
  • the proper placements of the bearings, and, consequentially, the rotor is a primary key to non-contact sealing in the devices of the present invention.
  • the Duo Vane machine is a two- vane version of the Mono Vane machine described above. Briefly, it contains a second similar, but not identical, set of subcomponents that enable it to carry the second vane in essentially the same way as the Mono Vane machine carries the single vane.
  • An example of a Duo Vane machine shown in Figs. 5 and 6 consists principally of left endplate 10, stator 20, right endplate 30, rotor 140, and vanes 150 and 151.
  • rotor shaft 100 is firmly attached to the rotor body 140 by any means known to the art. Rotor rotation occurs when sufficient power is applied to the rotor shaft 100, which is held and positioned by bearings 161.
  • vanes 150 and 151 contained within the rotor slots 144 and 145, respectively, are propelled in circular motion by the rotor 140 within the stator 20 cavity.
  • other subcomponents are required to insure that the vanes 150 and 151 do not rub against the stationary parts (i.e.: the stator bore and the inner surfaces of the endplates).
  • Vane axles 180 and 181 engage the axle through-hole 152 and 153 in vanes 150 and 151, respectively.
  • the ends of these axles are fastened in usual ways to the inner glider races 162 and 163 that operate within the roller bearings 161 (drawn-cup caged type shown here) installed within left and right endplates 10 and 30, respectively.
  • the circular outer diameter of glider races can be slightly crowned to accommodate slight misalignments of the bearings 161 and glider races 162 and 163.
  • the rollers of roller bearings 161 can also be crowned to accommodate the same conditions.
  • this control rod 190 precisely engage vane holes 156 and 157 of vanes 150 and 151, respectively, and prevents axial, side-to-side motion of the vanes 150 and 151 in rotor slots 144 and 145, respectively, of rotor 140.
  • addition of the second vane 151 allows nearly twice the displacement of a machine using a single vane, regardless of the type. Further, with the inclusion of a second vane 151, there is always a vane closing at the inlet port 5 slightly before the discharge port is reached by the leading vane 150. This is a very important feature from the standpoint of noise containment because as the leading vane 150 passes the discharge port 15, there is a small volume of high pressure gas that produces a noise pulse of un-expelled gas that travels back around to the outlet port. With one vane 50, the noise is able to flow out the inlet port 5 and be clearly heard.
  • the second vane 151 closes the inlet port 5 before the leading vane 150 reaches the outlet port 15.
  • the second vane 151 blocks the inherent noise pulse from reaching the environment and recovers the small previously not-discharged mass. This results in a much quieter and slightly more volumetric-efficient compressor.
  • Figs. 5 through 9 show alternative embodiments of the Duo Vane machine.
  • Figs. 5 and 6 show the use of a two-piece centering rod 191 with glider races 162 and 163 that run inside the roller bearings 161.
  • a single control is shown, because of dimensional tolerances arising between the opposing vane slots during manufacture, independent control rods 191 that can accommodate positional variations may be used for each vane 150 and 151.
  • Figs. 5a and 5b show a front and side view, respectively, of the Duo Vane (double- vane) embodiments wherein the roller bearings 161 are placed on the outside diameter of the glider rings 162 and 163.
  • Figs. 6a and 6b show an unassembled view of the machine shown in Figs. 5a and 5b, respectively, showing additional detail.
  • the Duo Vane machines shown in Figs. 5 and 6 use roller bearings 161 such that the outside circumference of the glider rings 162 and 163 ride within bearings 261 that are installed in the bearing housings of endplates 10 and 30.
  • Fig. 7 shows a similar embodiment to the embodiment shown in Figs. 5a, 5b, 6a and 6c.
  • glider rings 262 and 263 ride on the outside of the roller bearings 261.
  • the roller bearings 261 are located on a bearing mount 265 that is concentric with the inside diameter of the stator bore of stator housing 20.
  • Figs. 8a-e shows additional detail of the assembly shown in Fig. 7, without showing the non- rotating components.
  • Fig. 8a shows a front view of the rotating components of the Duo Vane assembly shown in Fig. 7b;
  • Figs. 8b and 8c show a front view of the rotating vane assembly and the vane counter balance, respectively, from one side and Figs.
  • FIG. 8d and 8e show a front view of the rotating vane assembly and the vane counter balance, respectively, from an opposite side.
  • this centering control rod 257 precisely engages vane holes of vanes 250 and 251 and prevents axial, side-to- side motion of the vanes 250 and 251 in rotor slots of rotor 240.
  • Fig. 9 shows yet another embodiment quite similar to other Duo Vane embodiments described above. The difference with the embodiment shown in Fig.
  • vane axle stubs 270 and 271 are used and, as shown, are held hi place by snap rings 270a and 271a, respectively, or any other fastening means known to the art can be used to achieve the attachment or, in some designs a fastener is not required.
  • Use of vane axle stubs relieves the need for cross-hole 72 in vane axle 70 (Fig. 1) and also slightly eases the balancing of the rotating mechanism.
  • Figs. 10 and 11 illustrate yet another embodiment also similar to the other Duo Vane embodiments described above.
  • This embodiment not only stiffens the mechanism, but also shortens the machine somewhat.
  • the four vane bearing rings 280 equipped with balance voids 282 are all identical. Note as well, that the extensions 286a of endplates 286 (only one endplate is shown) provide the inner race for the bearings 261, much as shown in Fig 7 with bearing mounts 265.
  • the axle vane positioning rods 257 are used to keep the vanes centered within the endplates 286.
  • cross-slots 287 in vanes 285 are present to accommodate clearance for the in-board set of vane bearing rings 280.
  • the rotating vane/vane glider ring assemblies must be dynamically balanced about their center of rotation. In the case of the Duo Vane machine two sets of rotating assemblies must reside with one another in a cooperative fashion. This is achieved by providing a vane axle pass-through void 275 as shown in Figs. 8 and 9, so that the second vane 251 can simultaneously receive accurate radial and axial position control and to insure collective dynamic balance of the rotating vane assemblies that is required for proper machine operation.
  • Fig. 10a shows yet another example of the Duo Vane apparatus embodiment shown in Figs. 5a through Fig. 9, Fig. 10b and 10c show a front view of the rotating vane assembly and the vane counter balance, respectively, shown in Fig. 10a from one side and Fig. 1Od and 1Oe show a front view of the rotating vane assembly and the vane counter balance, respectively, shown in Fig. 10a from an opposite side.
  • the 'hot dog' - shaped voids 276, 277 and 282 are present to counter-balance vane 251 and its companion vane axle stubs 270 and 271. While the shaped voids 276 and 277 are shown as having a 'hot dog' shape, voids having alternative shapes may be substituted. These voids 276 and 277 are sized and located to insure that the outer rotating assembly, axially speaking, the one spanning the inner rotating assembly, renders the collective center of gravity very close to the actual rotational axis of the rotating assembly, thus canceling any centripetal out-of- balance forces.
  • Voids although the voids may be somewhat different, are also required in the glider rings of the 'inner' rotating assembly. These are shown specifically in Fig. 9 as voids 276 which are, in this illustration, more pervasive (larger) than void 277 the vane axle pass through voids 275. This is because the pass-through void 275 increases the mass void required to dynamically balance the axially inner rotating vane subassembly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un compresseur d'étanchéité à jeu limité assurant directement un centrage précis du rotor dans le stator, un centrage des ailettes sur le rotor et non sur le stator, et un modèle d'équilibrage dynamique des coussinets indispensables dans le cas des dispositifs à une ou deux ailettes. Ces dispositifs utilisent des roulements à rouleaux pour commander la position radiale des ailettes, mais des tiges ou des broches pour leur positionnement axial, leur centrage par rapport au rotor et aux plateaux d'extrémité. Ces compresseurs et pompes à vide à rotor à ailettes à déplacement positif se distinguent par une réduction des frottements, un meilleur rendement, et une durée de vie considérablement prolongée. Cela s'explique par le confinement sans contact du gaz de process dans le corps des compresseurs et des pompes à rotor à ailettes. Dans un mode de réalisation, ce compresseur à déplacement positif est essentiellement destiné aux véhicules de transport.
PCT/US2006/028378 2005-08-05 2006-07-21 Compresseur d'etancheite a jeu limite WO2007019018A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US11/198,773 2005-08-05
US11/198,773 US7491037B2 (en) 2005-08-05 2005-08-05 Reversible valving system for use in pumps and compressing devices
US11/219,481 US7740460B2 (en) 2005-08-05 2005-09-02 Controlled-clearance sealing compressor devices
US11/219,481 2005-09-02

Publications (2)

Publication Number Publication Date
WO2007019018A2 true WO2007019018A2 (fr) 2007-02-15
WO2007019018A3 WO2007019018A3 (fr) 2008-07-31

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Application Number Title Priority Date Filing Date
PCT/US2006/028378 WO2007019018A2 (fr) 2005-08-05 2006-07-21 Compresseur d'etancheite a jeu limite

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WO (1) WO2007019018A2 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5374172A (en) * 1993-10-01 1994-12-20 Edwards; Thomas C. Rotary univane gas compressor
US5431551A (en) * 1993-06-17 1995-07-11 Aquino; Giovanni Rotary positive displacement device
US6268074B1 (en) * 1999-04-05 2001-07-31 General Motors Corporation Water injected fuel cell system compressor
US20030205213A1 (en) * 2001-02-01 2003-11-06 Giovanni Aquino Compressor assembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431551A (en) * 1993-06-17 1995-07-11 Aquino; Giovanni Rotary positive displacement device
US5374172A (en) * 1993-10-01 1994-12-20 Edwards; Thomas C. Rotary univane gas compressor
US6268074B1 (en) * 1999-04-05 2001-07-31 General Motors Corporation Water injected fuel cell system compressor
US20030205213A1 (en) * 2001-02-01 2003-11-06 Giovanni Aquino Compressor assembly

Also Published As

Publication number Publication date
WO2007019018A3 (fr) 2008-07-31

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