US3924977A - Positive fluid displacement apparatus - Google Patents

Positive fluid displacement apparatus Download PDF

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Publication number
US3924977A
US3924977A US408912A US40891273A US3924977A US 3924977 A US3924977 A US 3924977A US 408912 A US408912 A US 408912A US 40891273 A US40891273 A US 40891273A US 3924977 A US3924977 A US 3924977A
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United States
Prior art keywords
accordance
displacement apparatus
radial
fluid displacement
force
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Expired - Lifetime
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US408912A
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English (en)
Inventor
John E Mccullough
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Arthur D Little Inc
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Arthur D Little Inc
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Priority claimed from US368907A external-priority patent/US3884599A/en
Application filed by Arthur D Little Inc filed Critical Arthur D Little Inc
Priority to US408912A priority Critical patent/US3924977A/en
Priority to CA201,738A priority patent/CA1018955A/en
Priority to FR7420035A priority patent/FR2232674B1/fr
Priority to GB2569574A priority patent/GB1447607A/en
Priority to JP49065109A priority patent/JPS5749721B2/ja
Priority to SE7407610A priority patent/SE408217B/xx
Priority to DE19742428228 priority patent/DE2428228A1/de
Priority to IT68834/74A priority patent/IT1011949B/it
Publication of US3924977A publication Critical patent/US3924977A/en
Application granted granted Critical
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    • 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
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F01C21/003—Systems for the equilibration of forces acting on the elements of the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet

Definitions

  • ABSTRACT 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 pressure are connected to fluid ports.
  • Radial sealing is accomplished with minimum wear by linking the orbiting scroll member to the driving mechanism through a radially compliant mechanical linking means which also incorporates means to counteract at least a fraction of the centrifugal force exerted by the orbiting of the orbiting scroll member. If essentially all of the centrifugal force is counteracted, then the compliant mechanical linking means is designed to supply the necessary radial sealing force.
  • Coupling means which are separate from the driving means, and hence from the radial constraining force, are provided to maintain the desired angular relationship between scroll members and to provide one opposing force for axial sealing.
  • This invention relates to fluid displacement appara tus and more particularly to apparatus for handling fluids to compress, expand or pump them.
  • the positive displacement pumps or compressors of the vane type have rubbing speeds proportional to the radius of the vanes and the vanes rub at varying angles. Furthermore, the vanes'operate within a housing of fixed axial length so that any wear upon their flat surface ends will always act to increase the clearance, and hence, the blow-by or leakage of the apparatus.
  • the positive-displacement pumps and compressors of the rotary type are typically constructed to have the rotating components movable between end plates, an arrangement which demands close tolerances to reduce blow-by while permitting free rotation. Wear between the rotating components and end plates increases blowby, a fact which requires the adjustment of the spacings of the end plates through the use of screws and very precisely constructed gaskets in the form of shims.
  • the gaskets may not, however, be able to withstand corrosive fluids or fluids at extremetemperatures, e.g., cryogenic liquids or hot gases. Furthermore, these gaskets require precisely located edges to prevent injury by the moving vanes, a fact which adds to the delicacy of assembling the apparatus.
  • the apparatus of this invention whichmeets these requirements is based on the use of scroll members having wraps which make moving contacts to define moving isolated volumes, called pockets, which .carry the fluid to be handled.
  • the contacts which define these pockets fomied between scroll members are ofv two types: line contacts between spiral cylindrical wrap surfaces, and area contacts between plane surfaces.
  • the volume of a sealed pocket changes as it moves. At any one instant of time, there will be at least one sealed pocket.
  • spirals are angularly and radially offset to contact one another along at least one pair of line contacts such 'as between spiral curved surfaces.
  • a pair of line contacts will lie approximately upon one radius drawn outwardly from the central region of the scrolls.
  • the fluid volume so formed therefore extends all the way around the central region of the scrolls.
  • the pocket or fluid volume will not extend the full 360 but because of special porting arrangements will subtend a smaller angle about the central region of the scrolls.
  • the pockets define fluid volumes the angular position of which varies with relative orbiting of the spiral centers; and all pockets maintain the same relative angular position. As the contact lines shift along the scroll surfaces, the pockets thus formed experience a change in volume. The resulting zones of lowest and highest pressures are connected to fluid ports.
  • the scroll apparatus of this invention possesses features making it possible to reduce the outside diameter of the scroll members while attaining desired compression ratios. Among such features are wraps which may be configured to control delivery of fluid into and discharge of fluid from the apparatus.
  • the required flexible linking .of the orbiting scroll with its driving means comprises means defining a cylindrical drive surface associated with the orbiting scroll member having an orbit radius R,,,. and a scroll driving means defining a cylindrical driving surface with an orbit radius R,,,,,,.
  • the driving surface is designed to drive the orbiting scroll member through line contact with the cylindrical drive surface by virtue of the fact that R is less than R
  • a centripetal radial force is provided to oppose a fraction of the centrifugal force acting on the orbiting scroll member, and the difference between this centirpetal radial force and the normal centrifugal force acting upon the orbiting scroll member appears as the only contact force, e.g., radial sealing force, between the scroll members.
  • This embodiment of a flexible linking of orbiting scroll member to the driving mechanism is particularly suitable for smaller-size, relative low-load machines where simplicity of construction and minimization of the number of parts is desirable.
  • Another object of this invention is to provide scrolltype apparatus of the character described which places no load on the drive motor when used as a compressor or pump during start-up and shut-down and which permits the use of conventional journal or ball bearing elements to carry the drive loads with acceptable wear life.
  • This invention has as yet another object the providing of a scroll-type compressor which is capable of achieving near isothermal compression by virtue of relatively large internal heat transfer capability, which has excellent volumetric efficiency, which is capable of operating at relatively low noise levels, which has a sealed inlet volume, and which is suitable for highand lowspeed operation and for mounting directly to a motor to utilize the drive motors bearings.
  • the scroll apparatus of this invention provides means to control the radial contacting forces such that radial sealing is continuously and effectively attained even with wear or when noncompressibles are temporarily present.
  • This means to control radial contacting comprises means to counterbalance at least a fraction of the centrifugal force acting upon the orbiting scroll member and radially compliant mechanical linking means between the orbiting scroll and its drive means.
  • the radially compliant mechanical linking means is capable of providing a centripetal force to counterbalance a fraction of the centrifugal force thereby having a portion of the centrifugal force available for achieving controlled radial sealing.
  • the compliant mechanical linking means incorporates mechanical springs to counteract a portion of the centrifugal force.
  • means separate from the radially compliant mechanical linking means e.g., counterweights, are provided to counterbalance all or nearly all of the centrifugal forces acting upon the orbiting scroll member and the radially compliant linking.
  • radial sealing force may be made independent of changes in pressure at the inlet and outlet of the machine and of variations in operational speed.
  • the scroll members are angularly positioned by a coupling of the sliding friction type or rolling element type; the radially compliant linking means may be a slide-link or swing-link; either one or both of the scroll members may be cooled and the contacting surfaces may be lubricated if desired.
  • FIGS. 1-4 are diagrams of exemplary spiral wraps, one moving in a circular orbit with respect to the other, illustrating the manner in which a device incorporating such spiral members can achieve compression of a gas;
  • FIG. 5 is a longitudinal cross section of a compressor constructed in accordance with this invention incorporating a sliding friction type coupling, a swing-link and springs to counterbalance a fraction of the centrifugal force acting on the orbiting scroll member;
  • FIG. 6 is a fragmentary cross section of the fixed scroll member illustrating in detail one embodiment of an axial sealing force generating means
  • FIG. 7 is an end view of the fixed scroll member showing the back or external side of the end plate and the location of coolant passages drilled in the end plate;
  • FIG. 8 is an end view of a portion of the front or internal side of the end plate of the fixed scroll member illustrating the lubricant groove in the wrap end and the introduction of a lubricant into the groove;
  • FIG. 9 is a cross section through plane 9-9 of FIG. 7 showingthe lubricant inlet line
  • FIG. 10 is a cross section through the scroll wraps taken through plane 1010 of FIG. 5;
  • FIG. 11 is a fragmentary end view of the front or external side of the end plate of the orbiting scroll member showing the coupling key
  • FIG. 12 is a top plan view of one embodiment of a scroll coupling member
  • FIG. 13 is a cross section of the coupling member of FIG. 12 taken through plane 13l3 of that figure;
  • FIG. 14 is a cross section of the coupling member of FIG. 12 taken through plane l4-l4 of that figure;
  • FIG. 15 is a plan view of the inside surface of the housing frame support member showing the coupling member keys and lubricant channels;
  • FIG. 16 is a cross section through plane 1616 of the housing back plate of FIG. 15;
  • FIG. 17 is a top plan view of another embodiment of a coupling member designed to make rolling contact with the housing frame and orbiting scroll member;
  • FIG. 18 is a fragmentary cross section showing the coupling member in place between the housing frame and the orbiting scroll member
  • FIG. 19 is a plan view of a swing-link assembly serving as the compliant mechanical linking means between the orbiting scroll member and the driving means;
  • FIg. 20 illustrates a modification of the swing-link of FIG. 19
  • FIGS. 21-23 are cross section, end and side views of a sliding block assembly serving as the complicant mechanical linking means between the orbiting scroll member and the driving means;
  • FIG. 24 is a cross section through the main drive shaft through plane 24-24 of FIG. 5 showing the configuration of the centrifugal force counterbalancing weights used to eliminate vibration.
  • the scroll-type apparatus operates by moving a sealed pocket of fluid taken from one region into another region which may be at a different pressure. If the fluid is compressed while being moved from a lower to higher pressure region, the apparatus serves as a compressor; if from a higher to lower pressure region it serves as an expander; and if the fluid volume remain essentially constant independent of pressure then the apparatus serves as a pump.
  • the sealed pocket of fluid is bounded by two parallel planes defined by end plates, and by two cylindrical surfaces defined by the involute of a circle or other suitably curved configuration.
  • the scroll members have parallel axes since in only this way can the continuous sealing contact between the plane surface of the scroll members be maintained.
  • a sealed pocket moves between these parallel planes as the two lines of contact between the cylindrical surfaces move.
  • the lines of contact move because one cylindrical element, e.g., a scroll member, moves over the other. This is accomplished, for example, by maintaining one scroll fixed and oribiting the other scroll.
  • the positive fluid displacement apparatus is a compressor and that one scroll member is fixed while the other scroll member orbits in a circular ath.
  • FIGS. 1-4 may be considered to be end views of a compressor wherein the end plates are removed and only the wraps of the scroll members are shown.
  • scroll member will be used to designate the component which is comprised of both the end plate and the elements which define the contacting surfaces making movable line contacts.
  • wrap will be used to designate the elements making movable line contacts. These wraps have a configuration, e.g., an involute of a circle (involute spiral), arc of a circle, etc., and they have both height and thickness. The thickness may vary over the arc length of the wrap.
  • a stationary scroll member wrap 10 in the form of an involute spiral having axis 1 1 and a movable scroll member wrap 12in the form of another involute spiral of the same pitch as spiral l0 and having axis 13 constitute the components which define the moving sealed fluid pocket 14 which is crosshatched for ease of identification.
  • the involute spirals l0 and 12 may be generated, for example, by wrapping a string around a reference circle having radius R The distance between corresponding points of adjacent wraps of each spiral is equal to the circumference of the generating circle. This distance between corresponding points of adjacent wraps of any scroll member is also the pitch, P.
  • the two scroll members can be made to touch at a number of points, for example in FIG. 1, the points A, B, C
  • wrap has a shape characterized by two congruent involute spirals 17 and 18 and wrap 12 has a shape characterized by two congruent involute spirals 19 and 20.
  • congruency results from the fact that one scroll pattern can be brought into coincidence with the other by a simple rotation of one-half turn or less about its axis, followed by a small translation to bring their centers together.
  • the thicknesses, t, of the spiral walls are shown to be identical, although this is not necessary.
  • the wraps may take a number of different configurations and may vary in the number of turns used.
  • the end plate (not shown in FIGS. 1-4) to which stationary wrap 10 is fixed has a ,highpressure fluid port 21 and as the moving wrap 12 is orbited the fluid pocket 14 shifts counterclockwise and decreases in volume to increase the fluid pressure.
  • the fluid volume is opened into port 21 to begin the discharge of high-pressure fluid and this discharge of the high-pressure fluid is continued as shown in FIG. 4 until such time as the moving wrap has completed it orbit about circle and is ready to seal off a new volume for compression and delivery as shown in FIG. 1.
  • the movable scroll 12 will be driven to orbit in a clockwise direction under the force of the fluid pressure, delivering mechanical energy in the form of rotary motion as the fluid pockets expand to increasing volume.
  • the device is an expansion engine and may be used, if desired, to develop refrigeration.
  • radial sealing is required to maintain a seal along the line contacts made by the cylindrical surfaces of the wraps of the scroll members as the orbiting scroll is orbited.
  • the principal forces which inherently determine radial sealing of the scroll members comprise tangential forces due to the reaction of the fluid within the scroll volume which is resolved by mechanical radial constraints and centrifugal forces due to the orbiting of the orbiting scroll member. In addition to these inherent forces, other external forces may be supplied.
  • the disadvantages associated with scroll apparatus of the prior art are eliminated or minimized by counterbalancing all or a portion of the centrifugal forces acting upon the orbiting scroll and by linking the orbiting scroll to the drive means through a radially compliant mechanical linkage. If all of the centrifugal forces are counterbalanced. then the compliant mechanical linkage is designed to provide a radial force component of a desired magnitude to achieve radial sealing. If less than all of the centrifugal forces are counterbalanced, that fraction which is not counterbalanced is used to provide radial sealing. Axial sealing is accomplished by two opposing forces acting on the scroll members.
  • the first of these forces is a biasing means, including fluid pressure acting on the fixed scroll member and the second force acts upon the orbiting scroll through the coupling means located externally of the scroll pockets and arranged to oppose the force of the biasing means.
  • the coupling means which maintains the desired angular relationship of the scroll members functions independently of the radial sealing forces which are independently controlled to minimize wear of the line contacts between the wraps of the scroll members and to be able to compensate for noncompressible contaminants which may accidentally enter the fluid pockets.
  • FIG. 5 A compressor constructed in accordance with this invention is shown in longitudinal cross section in FIG. 5. Reference should also be had to FIGS. 616, 19 and 24 where indicated. In all of the drawings like reference numerals are used to refer to like elements.
  • the fixed scroll member generally indicated at 10 is comprised of an end plate 11; a wrap 12, which makes more than three revolutions (see FIG. 10) and 9 terminates in an enlarged peripheral section 13; an annular sealing ring member 14; and a central ported extension 15.
  • Within extension 15 is a high-pressure fluid passage 16 and extending into it is an connector tube 17, aligned on the machine axis 18, for connecting a high-pressure line, not shown.
  • the orbiting scroll member generally indicated at 20, comprises an end plate 21 and a wrap 22, which makes more than three revolutions and terminates in an enlarged peripheral section 23 (FIG. 10).
  • the end surface 25 of the fixed scroll member wraps l2 and 13 must make sealing contact with the internal surface 26 of the end plate 21 of the orbiting scroll; and in like manner, the end surface 27 of the orbiting scroll member wraps 22 and 23 must make sealing contact with the internal surface 28 of the fixed scroll member.
  • the wraps of the two scroll members In order to achieve radial sealing the wraps of the two scroll members must make rolling line contacts, e.g., 29, 30 and 31 of FIG. 10. Innermost fluid pocket 35 defines the zone of highest pressure while plenum chamber 36, defined around the wraps, comprises the zone of lowest pressure.
  • the fluid pockets, e.g., 37, 38 and 39 are at intermediate pressures increasing toward the center pocket 35. This zone of highest pressure communicates with a high-pressure line through fluid passage 16 and connector tube 17.
  • the low-pressure plenum chamber 36 communicates through one or more low-pressure ports 40 with a lowpressure fluid source or reservoir. If the apparatus is a compressor, low-pressure fluid is brought in through low-pressure port 40 and compressed fluid is delivered through a suitable conduit connected to connector tube 17. If, on the other hand, the apparatus is used as an expander, high-pressure fluid is brought in through passage 16 and expanded low-pressure fluid is discharged through one or more low-pressure ports 40.
  • FIG. 10 illustrates but one design of the scroll wraps which may be used in the apparatus. It is also within the scope of this invention to use, for example, wraps of more or less than three revolutions, wraps which are configured as other than true spiroids (e. g., arcsoof circle) and wraps which have their innermost ends configured to control the volume of the highest-pressure pocket.
  • wraps of more or less than three revolutions wraps which are configured as other than true spiroids (e. g., arcsoof circle) and wraps which have their innermost ends configured to control the volume of the highest-pressure pocket.
  • the scroll apparatus is contained within a housing, generally indicated at 45, which in the embodiment of FIG. 5 comprises a front housing cover plate 46 affixed through screws 47 to housing back plate 48 which in turn is covered by a back cover 49.
  • Low-pressure port 40 is cut through the front cover plate 46.
  • the fixed scroll member 10 is mounted on and aligned in front housing cover plate 46 through annular sealing ring member 14 and central ported extension 15 which are affixed to, or preferably integral with, the external surface of end plate 11.
  • Front housing cover plate 46 has an internally disposed mounting ring 56 and a central opening 57, each of which are grooved to hold elastomeric sealing rings 58 and 59, these sealing rings providing a seal with ring member 14 and extension 15.
  • the annular sealing ring member 14 terminates short of the inner surface 60 of front cover plate 46 to define a shallow annular spacing 61 into which is placed a wave spring washer 62 biased to apply an axial force on the fixed scroll member 10. The force thus applied constitutes a portion of the axial sealing force required.
  • a high-pressure fluid into spacing 61 and into annular fluid sealing chamber 63 (defined between ring 14 and extension 15) through fluid port 64 which is, in turn, connected to a source of high-pressure fluid, not shown.
  • This source of high-pressure fluid may be an external one, e.g., nitrogen from a storage tank, or it may be the zone of highest pressure of the apparatus, e.g.,
  • fluid communication means (not shown) must be provided between pocket 35 and fluid sealing chamber 63. If the high-pressure fluid is to be supplied from the zone of highest pressure within the machine (i.e., from pocket 35) then the-axial force provided by the wave spring washer 62 must be sufficient to provide sealing during start-up since little, if any, high-pressure fluid will be available from pocket 35 during this period of operation. If, however, as in the case of the embodiment of FIGS. 5 and 6, the high-pressure axial sealing fluid is applied from an external source, the sealing fluid may be introduced into sealing chamber 63 prior to start-up and continued subsequent to shut-down.
  • the fixed scroll member is angularly positioned relative to the front housing cover plate 46 and is thereby maintained fixed with respect to the housing frame. This is accomplished through the use of locking means generally indicated at 70.
  • the locking means of FIG. 5 permits minor adjustments to be made during assembly or operatingin angularly locating the fixed scroll so that it may be placed at the optimum angle.
  • This locking means comprises a bolt 71 with threads 72 and a head 73 to which a pin 74 is fixed eccentric to the bolt axis.
  • a nut 75 engaging threads 72 serves to hold the bolt in the front plate.
  • Pin 74 engages a notch 76 cut into the back of end plate 11 (See FIG. 7).
  • the locking means may be a simple constant-diameter pin extending from within front cover 46 into notch 76, in which case the angular position of the fixed scroll member is not adjustable.
  • the scroll members are cooled by circulating a coolant through end plate 1 1 of the fixed sc-roll member as can best be seen in FIG. 7 which is an end view of the external surface 80 of end plate 11.
  • FIG. 7 is an end view of the external surface 80 of end plate 11.
  • a series of interconnecting passages 81 forming a conduit network are drilled in end plate 11 and they are connected through suitable connectors 82 and 83 to fluid conduits (not shown) capable of introducing a coolant into and withdrawing it from the coolant passage network.
  • a lubricant is provided to lubricate the contacting ends 25 of the fixed scroll member wraps.
  • the contacting spiraling end surface 25 of the continuous wraps 12 and 13 have an oil channel 84 cut into it.
  • a suitable lubricant is delivered to the outermost part of the channel through a line 85 connected to a passage 86 drilled into enlarged wrap 13 and extending to channel 84.
  • the lubricant is forced through channel 84 which follows the entire wrap and any excess eventually drains by gravity to the bottom of the housing to be withdrawn through oil drain port 87.
  • Lubrication of the contacting wrap ends may not be required, particularly in such cases where the wrap and end plate surfaces are of a self-lubricating nature or are 1 1 not subject to intolerable wear, or where the size and mode of operation either does not require or even prohibits the introduction of lubricants into the system.
  • the orbiting scroll member must be prevented from moving angularly with respect to the fixed scroll member and with respect to the frame of the housing; and it must be driven in an orbit in a way to counteract all or a portion of the centrifugal force developed in its orbiting while providing the required radial sealing forces.
  • this coupling member comprises an annular ring 91 with an IV-shaped cross section.
  • the front surface 92 faces the orbiting scroll; and in keeping with this terminology, the opposite surface, called the back surface 93, faces the inside wall 94 of an internal supporting frame member 95 of the housing.
  • Front surface 92 has two oppositely disposed keyways 96 and 97 cut into it (FIG. 12); and back surface 93 also has two oppositely disposed keyways 98 and 99 cut into it.
  • FIGS. and 11 are a plan view of internal surface 94 of housing frame member 95 showing the position of keys 106 and 107 mounted through countersunk screws 108 (FIG. 16) into recesses 109 and 110, respectively, cut into surface 94. These keys 106 and 107 slidingly engage keyways 98 and 99.
  • the coupling member 130 is an annular ring constructed with essentially the same cross section as the coupling member 90 of FIGS. 12 and 13, and it has keyways 9699 as described above. It is, however.
  • each set comprising a plurality of rolls 134 contacting the front face 135 of the coupling and surface of the orbiting scroll member, and a plurality of rolls 136 contacting the back face 137 of the coupler and surface 94 of the support frame member 95.
  • Rolls 134 and 136 are oriented at right angles to each other and their axes are oriented to be normal to the axis of the keyway cut in the surface which they contact. Thus each roll is positioned to travel with the coupling member as it moves in the directions indicated by the arrows.
  • FIGS. 12-18 show keyways in the coupling means and slidingly engageable keys in the orbiting scroll member and housing frame, it is also within the scope of this invention to reverse this arrangement and affix the keys to the coupling means and locate the keyways in the orbiting scroll member and the housing frame.
  • FIGS. 5 and 19-23 Several embodiments of suitable mechanisms for driving the orbiting scroll member with the desired radial compliance to attain a predetermined sealing force are illustrated in FIGS. 5 and 19-23.
  • the radial compliant means may take one of several forms. Moreover, it is possible to choose between several operating modes, i.e., counterbalancing a fraction of the centrifugal force and using that fraction which is not counterbalanced as a radial sealing force, or counterbalancing essentially all of the centrifugal force and incorporating into the mechanical compliant linkage, means to provide a radially outward force which can alone serve as the radial sealing force.
  • the radially compliant mechanical linkage is a swing-link, while in FIGS. 2l-23 it is a sliding-block linkage. Both of these embodiments may use springs in compression to counteract all or a part of the centrifugal force, or they may use counterweights in place of or in addition to the springs.
  • the orbiting scroll member In order to attain radial compliance, the orbiting scroll member must have the ability to move inwardly or outwardly relative to the machine axis in response to gradual wear of the scroll wraps or to encounter noncompressible objects such as a slug of liquid, accumulated wear debris or ingested dirt particles.
  • This radial compliance feature also allows the use of less perfect geometry scrolls in that it allows the orbiting scroll member to ride inside of the fixed scroll member and adjust its trajectory, as required, to suit the geometries of the wraps of the two scrolls.
  • a ball bearing is mounted on the axial drive shaft of the orbiting scroll member and the outer periphery of this ball bearing is connected to a crank mechanism with a swing-link.
  • the axis of the swing-link in FIG. 19 is shown to the nominally perpendicular to the eccentricity radius of the orbiting scroll member.
  • the orbiting scroll member swings radially outward under the action of centrifugal force acting on its center of mass.
  • the orbiting scroll member is confined to a given locus of motion by virtue of contact with the wrap of the fixed scroll member.
  • the radial contact force between the orbiting and fixed scroll members is adjusted by the use of mechanical springs, or equivalent devices, to counteract some predetermined fraction of the centrifugal force exerted on the orbiting scroll member.
  • the orbiting scroll is driven by the main drive shaft 140 which is mounted in the backcover plate through a bearing 141.
  • a crank 142 Affixed to main drive shaft 140 is a crank 142 to which a connecting rod 143 is pivotally mounted through connecting rod pin 144.
  • This connecting rod is affixed to the orbiting scroll member through a stub shaft 145 by means of snap ring 15 1 and ball bearing 146 retained by an inner race 147 and outer race 148 mounted on ring 149 of the connecting rod.
  • the axis of shaft 145 is designated in FIG. 19 by the numeral 150.
  • the axis of the main shaft and of the machine is the same as that of the fixed scroll member and is therefore designated by the numeral 18.
  • the distance between the orbiting scroll axis 150 and the machine axis 18 is R the orbit radius.
  • main shaft 140 is shown attached to a motor 152 of a type suitable to rotate shaft 140.
  • the element 152 may be considered to be any suitable work absorbing means, e.g., another compressor, or a brake in the case of an expansion engine used to develop refrigeration.
  • the swing-link which is comprised of the connecting rod, ball bearing assembly, and pin is connected to the crank through one or more springs in compression as shown in FIG. 19.
  • a T-bolt 155 is attached to connecting rod 143 and extends through the wall of crank 142 which has a shallow well 156 on its external surface to seat concentric springs 157 and 158 held in compression by means of a spring retainer 159 adjustably affixed to T-bolt 155 by means of nut 160.
  • Springs 157 and 158 are preloaded to a desired force through turning nut 160. The number of springs and the degree of preloading may be so chosen as to overcome a predetermined fraction of the centrifugal force exerted on the orbiting scroll member while it is achieving full running eccentricity.
  • the springs in effect pull back on the swing-link and thereby exert a centripetal force on the orbiting scroll member, the difference between the centrifugal and centripetal forces being in essence equal to the radial sealing force.
  • the radial sealing force may be adjusted by adjusting the degree of preloading of the springs.
  • the axis of the swing-link is oriented perpendicular to the eccentricity radius of the orbiting scroll member. This has the advantage that the radial sealing force does not vary with changes in the inlet and outlet conditions of the machine.
  • Modifications of the swing-link embodiment of FIG. 19 are possible and within the scope of this invention.
  • a counterweight may be affixed to the spring retainer 159, or alternatively, the spring retainer itself may be configured to serve as such a counterweight.
  • the springs e.g., 157 and 158 or a single spring
  • this modification permits accurate control of the radial sealing force.
  • the combination of springs and counterweight allows the radial sealing force to be independent of changes in pressure at the inert and outlet of the machine as well as of variations in operating speed.
  • FIG. 20 Two additional modifications of the swing-link are illustrated in FIG. 20.
  • the springs are replaced by a counterweight 163 which is affixed to or integral with the ring 149 of the connecting rod 143 and extends beyond opening 164 in crank 142.
  • counterweight 163 is designed to counterbalance a fraction of the centrifugal force exerted on the orbiting scroll member, the remaining fraction being used to provide a radial sealing force of a predetermined magnitude.
  • counterweight 163 serves in the same role as springs 157 and 158.
  • the second modification illustrated in FIG. 20, which is equally applicable to the swing-link embodiment of FIG. 19, is the orientation of the axis of the swing-like to form an angle less than with the eccentricity radius of the orbiting scroll. This is evident from the shift in position of swing-link pivot axis 144 relative to axes 18 and 150. Reducing this angle has the advantage of reducing the size of the counterweight, or spring, required to counteract the centrifugal force acting upon the orbiting scroll member; but it does mean that the resulting radial sealing force is somewhat dependent upon machine inlet and outlet pressure variations.
  • crank 1 80 provides a flat contacting surface 181 adapted for slidable engagement with surface 182 of sliding block 183 which slides in a groove defined within crank 180, (FIG. 23).
  • Sliding block 183 is affixed to flanged stub shaft 184 or orbiting scroll member 20 through a bearing assembly, comprised of an inner race 192, an outer race 193 and ball bearings 194, held by retaining member 195 affixed to the back side 196 of sliding block 183.
  • Crank is preferably linked to sliding block 183 through compression spring 186 (FIG. 21) which is anchored to the inner wall 187 of a chamber 188 cut into the sliding block and to a spring support 189 which is an integral extension of crank 180 extending into chamber 188.
  • This spring 186 serves the same role as springs 157 and 158 of the embodiment of FIG.
  • counterweight 190 is shown affixed to sliding block 183 in FIG. 22.
  • the sliding block linkage of FIGS. 2123 is preferably used with the coupling member of FIGS. and 12, i.e., where the coupling member makes sliding friction contact with the housing frame and orbiting scroll member.
  • the advantage of the sliding block linkage is that it can carry the axial restraining force to be exerted on the orbiting scroll member so that the coupling is unloaded in the axial direction and therefore consumes less power.
  • the driving mechanism also has oppositely disposed counterweights comprising a primary counterweight 170 affixed through screws 171 to the shoulder 172 of crank 142 and a secondary counterweight 173 affixed through screws 174 to a flanged extension 175 of crank 142.
  • the counterweights are so configured with respect to size and are so positioned on the crank to eliminate vibrations in the running of the machine. It will be noted that the larger, primary counterweight 170 is positioned to exert a centrifugal force in the same direction as the centripetal force of springs 157 and 158 (FIG. 19).
  • the gas to be expanded is introduced into the high-pressure port 16 and withdrawn into a low-pressure reservoir through one or more low-pressure ports.
  • the attainment of axial and radial sealing is the same as when the apparatus is used as a compressor.
  • a positive fluid displacement apparatus into which a fluid is introduced through an inlet port for circulation therethrough and subsequently withdrawn through a discharge port, in which two scroll members being maintained at a desired angular relationship and having Wraps which make a plurality of moving line contacts to seal off and define at least one moving pocket of variable volume and zones of different fluid pressure when one of said scroll members is driven by driving means to orbit within said other of said scroll members while maintaining a fixed angular relationship therewith, and wherein said driving means associated with said one of said scroll members includes means to provide a centripetal radial force adapted to oppose a fraction of the centrifugal force acting upon said one of said scroll members, the improvement comprising radially compliant mechanical linking means between said driving means and said one of said scroll members.
  • said radially compliant mechanical linking means including said means to provide said centripetal radial force of a magnitude to control the radial sealing force between said scroll members at a level to minimize both wear and internal fluid leakage.
  • a positive fluid displacement apparatus in accordance with claim 3 wherein said swing-link means includes compression spring means to provide said centripetal radial force.
  • a positive fluid displacement apparatus in accordance with claim 7 wherein said radially compliant mechanical linking means comprises swing-link means having compression spring means to provide said centripetal force and counterweight means as said means to provide a separate controllable radial sealing force.
  • a positive fluid displacement apparatus in accordance with claim 7 wherein said radially compliant mechanical linking means comprises sliding-block linkage means having compression spring means to provide said centripetal force and counterweight means as said means to provide a separate controllable radial sealing force.
  • a positive fluid displacement apparatus into which fluid is introduced through an inlet port for circulation therethrough and subsequently withdrawn through a discharge port, comprising in combination a. an orbiting scroll member and a fixed scroll member each having end plate means to which are affixed wrap means which, when said orbiting scroll member is orbited with respect to said fixed scroll member, make moving line contacts to seal off and define at least one moving fluid pocket of variable volume and zones of different fluid pressure and l7 develop radial constraints;
  • centrifugal force counterbalancing means associated with said mechanical linking means. and adapted to counterbalance at least a fraction ofthe centrifugal force acting upon said orbiting scroll member;
  • coupling means adapted to prevent relative angular motion of said scroll members, said coupling means being separate and distinct from said scroll drive means whereby said radial constraints within said apparatus are limited to said moving line contacts between said wraps and are controlled through said radially compliant mechanical linking means.
  • centrifugal force counterbalancing means counterbalances less than all of said centrifugal force and that fraction of said centrifugal force which is not counterbalanced constitutes the radial sealing force between said wraps.
  • a positive fluid displacement apparatus in accordance with claim 11 wherein said radially compliant mechanical linking means is a swing-link and said centrifugal force counterbalancing means are compression spring means.
  • a positive fluid displacement apparatus in accordance with claim 11 wherein said radial compliant mechanical linking means is a sliding-block link and said centrifugal force counterbalancing means are compression spring means.
  • centrifugal force counterbalancing means counterbalances essentially all of said centrifugal'force and includes radial sealing force means to provide a separate controllable radial sealing force.
  • a positive fluid displacement apparatus in accordance with claim 16 wherein said radially compliant mechanical linking means is a swing-link and said centrifugal force counterbalancing means and said radial sealing force means are compression spring means.
  • main drive shaft means the axis of which is the axis of said fixed scroll member and is parallel to and spaced from the axis of said orbiting scroll member, the distance between said axes being the oper- 4 ational orbit radius of said orbiting scroll member;
  • centrifugal force counterbalancing means associated with said mechanical linking means adapted to counterbalance at least a fraction of the centrifugal force acting upon said orbiting scroll member;
  • housing means including frame, support means, defining a fluid chamber within which said scroll members are located.
  • a positive fluid displacement apparatus in accordance with claim 21 including counterweight means attached to said crank means to minimize or eliminate vibration in said apparatus.
  • a positive fluid displacement apparatus in accordance with claim 21 including means to circulate a coolant within the end plate of said fixed scroll memthe wrap means of said fixed scroll member has shallow lubricant channel means therein, and said apparatus includes means to introduce a lubricant into said channel means.
  • a positive fluid displacement apparatus in accordance with claim 21 including locking means to lock said fixed scroll member to said housing means, said locking means being adjustable whereby the angular orientation of said scroll member may be adjusted within said housing.
  • a positive fluid displacement apparatus in accordance with claim 21 having fluid inlet portmeans associated with the zone of lowest pressure and fluid discharge port means associated with the zone of highest pressure and means to rotate said main drive shaft means, whereby said apparatus is a compressor.
  • a positive fluid displacement apparatus in accordance with claim 21 having fluid inlet port means associated with the zone of highest pressure and-fluid discharge port means associated with the zone of lowest pressure and work absorbing means connected to said main drive shaft means, whereby said apparatus in an further characterized by having shallow lubricant channels on each of its surfaces and passage meansproviding fluid communication between said channels.
  • a positive fluid displacement apparatus in accordance with claim 31 including sets of roller means, each comprising a plurality of rollers, interposed between one surface of said coupling means and said end plate of said orbiting scroll member and between the other surface of said coupling means and said frame support means, said roller means being so oriented that the axes of said rollers contacting any one surface of said coupling means are normal tothe axis of said keyways on that surface.
  • centrifugal force counterbalancing means counterbalances less than all of said centrifugal force and that fraction of said centrifugal force which is not counterbalanced constitutes said radial sealing force.
  • centrifugal force counterbalancing means counterbalances essentially all of said centrifugal force and includes radial sealing force means to provide a separate controllable radial sealing force.
  • a positive fluid displacement apparatus in accordance with claim 44 wherein said fluid force applying means comprises a fluid chamber positioned to exert fluid pressure upon the end plate of said fluid scroll member and means to deliver high-pressure fluid to said fluid chamber.
  • a positive fluid displacement apparatus in accordance with claim 46 wherein said means to deliver high-pressure fluid to said fluid chamber comprises conduit means providing fluid communication between an external source of. a high-pressure fluid and said fluid chamber.
  • A- positive fluid displacement apparatus in accordance with claim 46 wherein said means to deliver high-pressure fluid to said fluid chamber comprises conduit means providing fluid communication between the zone of highest pressure and said fluid chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
US408912A 1973-06-11 1973-10-23 Positive fluid displacement apparatus Expired - Lifetime US3924977A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US408912A US3924977A (en) 1973-06-11 1973-10-23 Positive fluid displacement apparatus
CA201,738A CA1018955A (en) 1973-10-23 1974-06-05 Positive fluid displacement apparatus
JP49065109A JPS5749721B2 (ja) 1973-06-11 1974-06-10
GB2569574A GB1447607A (en) 1973-06-11 1974-06-10 Scroll type rotary fluid handling apparatus
FR7420035A FR2232674B1 (ja) 1973-06-11 1974-06-10
SE7407610A SE408217B (sv) 1973-06-11 1974-06-10 Fluidmaskin
DE19742428228 DE2428228A1 (de) 1973-06-11 1974-06-11 Vorrichtung zum foerdern bzw. behandeln eines fluids
IT68834/74A IT1011949B (it) 1973-06-11 1974-06-11 Dispositivo del tipo a chiocciola funzionante da compressore o pompa

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US368907A US3884599A (en) 1973-06-11 1973-06-11 Scroll-type positive fluid displacement apparatus
US408912A US3924977A (en) 1973-06-11 1973-10-23 Positive fluid displacement apparatus

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US3924977A true US3924977A (en) 1975-12-09

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US408912A Expired - Lifetime US3924977A (en) 1973-06-11 1973-10-23 Positive fluid displacement apparatus

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US (1) US3924977A (ja)
JP (1) JPS5749721B2 (ja)
DE (1) DE2428228A1 (ja)
FR (1) FR2232674B1 (ja)
GB (1) GB1447607A (ja)
IT (1) IT1011949B (ja)
SE (1) SE408217B (ja)

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Publication number Publication date
DE2428228A1 (de) 1975-01-02
DE2428228C2 (ja) 1989-05-18
SE7407610L (ja) 1974-12-12
GB1447607A (en) 1976-08-25
FR2232674B1 (ja) 1978-01-13
SE408217B (sv) 1979-05-21
FR2232674A1 (ja) 1975-01-03
IT1011949B (it) 1977-02-10
JPS5032512A (ja) 1975-03-29
JPS5749721B2 (ja) 1982-10-23

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