US20220341422A1 - Center camshaft scroll pump - Google Patents

Center camshaft scroll pump Download PDF

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Publication number
US20220341422A1
US20220341422A1 US17/728,546 US202217728546A US2022341422A1 US 20220341422 A1 US20220341422 A1 US 20220341422A1 US 202217728546 A US202217728546 A US 202217728546A US 2022341422 A1 US2022341422 A1 US 2022341422A1
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US
United States
Prior art keywords
scroll
end plate
scroll member
involute
pump
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
US17/728,546
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English (en)
Inventor
Anatoliy NITSA
Terry Chung
David A. Dzioba
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Dabir Surfaces Inc
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Dabir Surfaces Inc
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Publication date
Application filed by Dabir Surfaces Inc filed Critical Dabir Surfaces Inc
Priority to US17/728,546 priority Critical patent/US20220341422A1/en
Publication of US20220341422A1 publication Critical patent/US20220341422A1/en
Pending legal-status Critical Current

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    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids 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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/08—Axially-movable sealings for working fluids
    • 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
    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/063—Rotary-piston pumps specially adapted for elastic fluids 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 with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F04C18/067—Rotary-piston pumps specially adapted for elastic fluids 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 with coaxially-mounted members having continuously-changing circumferential spacing between them having cam-and-follower type drive
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • a scroll pump typically includes first and second scroll members having respective, interleaved, first and second involutes.
  • first and second scroll members are connected by three camshafts and an eccentric drive mechanism configured to move the second scroll member through an orbital path with respect to the first scroll member.
  • the movement of the second scroll member with respect to the first scroll member may be constrained at as many as four points, namely, the three camshafts and the eccentric drive mechanism.
  • This high level of constraint requires precise fabrication and assembly of the foregoing components in order to control interference among the several points of constraint, which interference may result in inefficiency, high rate of wear, and other concerns during operation of the pump.
  • the present disclosure is directed to a scroll pump with fewer points of constraint to reduce complexity in fabrication and assembly, and configured to compensate for working pressure tending to axially separate the first and second scroll members to thereby reduce wear and improve the pump's operating efficiency.
  • FIG. 1 is an upper perspective view of an illustrative center camshaft scroll pump according to the present disclosure
  • FIG. 2 is a top plan view of the center camshaft scroll pump of FIG. 1 ;
  • FIG. 3 is a front cross-sectional elevation view of the center camshaft scroll pump of FIG. 1 taken through section A-A;
  • FIG. 4 is an enlarged cross-sectional front elevation view of a portion of the center camshaft scroll pump of FIG. 1 taken through section B-B;
  • FIG. 5A is a perspective view of a first side of an orbiting scroll member of the center camshaft scroll pump of FIG. 1 ;
  • FIG. 5B is a perspective view of a second side of an orbiting scroll member of the center camshaft scroll pump of FIG. 1 ;
  • FIG. 6 is a perspective view of a first side of a fixed scroll member of the center camshaft scroll pump of FIG. 1 ;
  • FIG. 7 is a first exploded perspective view of the center camshaft scroll pump of FIG. 1 ;
  • FIG. 8 is a second exploded perspective view of the center camshaft scroll pump of FIG. 1 .
  • the drawings show an illustrative embodiment of a scroll pump 10 according to the present disclosure.
  • the scroll pump 10 includes: a first (or fixed) scroll member 12 ; a second (or orbiting) scroll member 14 ; a camshaft 16 having a first shaft portion 16 A and a second shaft portion 16 B connected to, spaced from, and parallel to the first shaft portion 16 A; a link 18 ; and a prime mover 20 , for example, an electric motor.
  • the first scroll member 12 is in orbiting engagement with the second scroll member 14 .
  • the first shaft portion 16 A of the camshaft 16 is rotatably connected to the first scroll member 12 .
  • the second shaft portion 16 B of the camshaft 16 is rotatably connected to the second scroll member 14 .
  • a first end 18 A of the link 18 is pivotably connected to the first scroll member 12
  • a second end 18 B of the link 18 is pivotably connected to the second scroll member 14 .
  • the motor 20 is configured to rotate the camshaft 16 with respect to the first scroll member 12 and the second scroll member 14 .
  • the link 18 substantially precludes rotation of the second scroll member 14 with respect to the first scroll member 12 when the camshaft 16 is rotating, so that rotation of the camshaft 16 causes the second scroll member 14 to orbit with respect to the first scroll member 12 .
  • the first scroll member 12 includes a first end plate 22 and a first involute 24 extending axially from a first side of the first end plate 22 .
  • the first end plate 22 defines a first shaft-receiving aperture 26 configured to receive the first shaft portion 16 A of the camshaft 16 .
  • the first end plate 22 also defines a bearing pocket 28 extending into the first end plate 22 .
  • the bearing pocket 28 extends toward the first side of the first end plate 22 from a second side of the first end plate 22 opposite the first side of the first end plate 22 .
  • a first bearing 30 is received within the first bearing pocket 28 , for example, in press-fit engagement.
  • a land 32 at the bottom of the bearing pocket precludes the bearing 30 from being inserted into and removed from the bearing pocket 28 from the first side of the first end plate 22 .
  • the first bearing 30 may abut the land 32 .
  • the bearing pocket 28 may extend into the first end plate 22 from the first side of the first end plate 22 toward the second side of the first end plate 22 .
  • the land 32 would preclude the bearing 30 from being inserted into and removed from the bearing pocket 28 from the second side of the first end plate 22 .
  • first aperture 26 and the bearing pocket 28 may be combined into a single feature and the land 32 may be omitted.
  • the first bearing 32 could be inserted into and removed from the bearing pocket 28 from the first side of the first end plate 22 or the second side of the first end plate 22 .
  • the first bearing 30 is configured to receive the first shaft portion 16 A of the camshaft 16 in rotating, bearing engagement.
  • the first bearing 30 may be a sealed bearing, and the interfaces among the first end plate 22 , the first bearing 30 , and the first shaft portion 16 A of the camshaft 16 may be substantially sealed interfaces so that the first bearing 32 and the foregoing interfaces are substantially airtight.
  • the first involute 24 extends axially from the first side of the first end plate 22 in a direction perpendicular to the first end plate 22 .
  • a first end 24 A of the first involute 24 proximate a periphery of the first involute 24 closes upon an intermediate portion of the first involute 24 .
  • a second end 24 B of the first involute 24 proximate a center of the first involute 24 is free.
  • the first end plate 22 and the first involute 24 cooperate to define a space configured to receive a second involute, as will be discussed further below.
  • a first tip seal 24 S is provided at a free surface of the first involute 24 opposite the first end plate 22 .
  • the free end of the first involute 24 may define a recess or groove 24 G configured to receive and retain the tip seal 24 S.
  • the first scroll member 12 defines a fluid inlet aperture or port 34 proximate a periphery of the first end 24 A of the first involute 24 .
  • the fluid inlet aperture 34 is configured to admit air or another fluid into the scroll pump 10 for pressurizing thereby.
  • the fluid inlet port 34 may extend through one or both of the first end plate 22 and the first involute 24 .
  • the first scroll member 12 also defines a fluid outlet aperture or port 36 extending through the first end plate 22 proximate the second end 24 B of the first involute 24 .
  • the fluid outlet port 36 is configured to discharge fluid pressurized by the scroll pump 10 .
  • the first scroll member 12 further defines a first pivot point 38 configured to receive an axle or pin 40 connecting the first end 18 A of the link 18 to the first scroll member 12 in pivoting engagement therewith.
  • the first pivot point 38 may be embodied as a boss proximate the periphery of the first end plate 22 and/or radially outboard of the first involute 24 .
  • the first scroll member 12 also may include one or mounting bosses 42 configured to receive fasteners (not shown) for connecting the first scroll member 12 to another structure (not shown).
  • a sidewall 44 extends axially from the second side of the first end plate 22 .
  • the sidewall 44 cooperates with the first end plate 22 to define a housing configured to receive the prime mover 20 , in this case an electric motor.
  • the sidewall 44 is monolithically formed or integral with the first end plate 22 .
  • An end cap 46 covers the open end of the sidewall 44 .
  • a seal 48 for example, an O-ring, may be provided between the housing wall and the end cap so that the interior of the housing is substantially air-tight.
  • the second scroll member 14 includes a second end plate 52 and a second involute 54 extending from a first side of the second end plate 52 .
  • the second end plate 52 defines a second shaft-receiving aperture 56 extending from the first side thereof to a second side thereof opposite the first side.
  • the second shaft-receiving aperture 56 is configured to receive a second bearing 58 therein, for example, in press-fit engagement.
  • the second end plate 52 also defines one or more vent holes 60 extending therethrough, proximate the center of the second end plate 52 , as will be discussed further below.
  • An annular sidewall 62 extends axially from the second side of the second end plate 52 , thereby defining a cavity 64 extending axially from the second side of the second end plate.
  • the cavity 64 is configured to receive a piston 66 , as will be discussed further below.
  • the cavity 64 may be cylindrical.
  • the second involute 54 extends from a first side of the second end plate 52 in a direction perpendicular thereto.
  • a second tip seal 54 S is provided at a free end of the second involute 54 .
  • the free end of the second involute 54 may define a recess or groove 54 G configured to receive and retain the second tip seal 54 S.
  • the second scroll member 52 further defines a second pivot point 68 configured to receive a second axle or pin 70 connecting the second end 18 B of the link 18 to the second scroll member 14 in pivoting engagement therewith.
  • the second pivot point 68 may be embodied as a boss proximate the periphery of the second end plate 52 .
  • the camshaft 16 includes a first shaft portion 16 A and a second shaft portion 16 B.
  • the first shaft portion 16 A defines a first axis of rotation.
  • the first axis of rotation is perpendicular to the first end plate 22 and parallel to the first involute 24 .
  • the second shaft portion 16 B defines a second axis of rotation.
  • the second axis of rotation is perpendicular to the second end plate 52 and parallel to the second involute 54 .
  • the second axis of rotation is radially offset from and parallel to the first axis of rotation.
  • the first shaft portion 16 A is configured for connection to a drive shaft of the prime mover 20 for rotation therewith.
  • the camshaft 16 may be integrated and/or monolithically formed with the drive shaft of the prime mover 20 .
  • the second shaft portion 16 B defines a circumferential groove 72 configured to receive a shaft seal 74 , for example, an O-ring.
  • the shaft seal 74 is engaged between the second shaft portion 16 B and an inner race of the second bearing 58 .
  • a free end of the second shaft portion 16 B may define a threaded bore 76 configured to receive a fastener 78 , as will be discussed further below.
  • the first shaft portion 16 A is received within the first bearing 30 in rotating bearing engagement therewith.
  • the second shaft portion 16 B is received within the second bearing 58 in rotating bearing engagement therewith.
  • the first scroll member 12 is axially fixed to the first shaft portion 16 A.
  • the second scroll member 14 axially floats with respect to the second shaft portion 16 B.
  • the first scroll member 12 is engaged with the second scroll member 14 so that the first involute 24 is interleaved with the second involute 54 .
  • the first tip seal 24 S of the first scroll member 12 engages with the first side of the second end plate 52 of the second scroll member 14 in sealing engagement therewith.
  • the second tip seal 54 S of the second scroll member 14 engages with the first side of the first end plate 22 of the first scroll member 12 in sealing engagement therewith. So assembled, the first and second scroll members 12 , 14 define a working volume V substantially bounded by the first and second end plates 22 , 52 and the first and second involutes 24 , 54 .
  • a first exposed surface area of the second end plate 52 is exposed to fluid pressure within the working volume V.
  • the first exposed surface area is defined by the surface area of the first side of the second end plate 52 normal to the second axis of rotation and radially inboard of the first involute 24 , minus the surface area of the first side of the second end plate 52 normal to the second axis of rotation occupied by the second involute 54 and covered by the first involute 24 /first tip seal 24 S.
  • the first exposed surface area is the surface area of the first side of the second end plate 52 that projects against the first side of the first end plate 22 , minus the surface area of the free end of the second involute 54 engaging the first side of the first end plate.
  • a second exposed surface area of the second end plate 52 is exposed to fluid pressure within the cavity 64 .
  • the second exposed surface area is defined by the surface area of the second side of the second end plate 52 normal to the second axis of rotation within the confines of the cavity 64 .
  • the second exposed surface area is greater than the first exposed surface area so that when both sides of the second end plate 52 are subjected to the same fluid pressure, the net force on the second end plate 52 parallel to the second axis of rotation tends to bias the second scroll member 14 toward the first scroll member 12 , thereby compressing the first and second tip seals 24 S, 54 S against the respective second and first end plates 52 , 22 .
  • the link 18 is pivotably connected to both the first and second scroll members 12 , 14 . More specifically, a first portion of the link 18 , which may be proximate a first end 18 A thereof, is pivotably connected to the first scroll member 12 . Similarly, a second portion of the link 18 , which may be proximate a second end 18 B thereof, is pivotably connected to the second scroll member 14 . So connected to the first and second scroll members 12 , 14 , the link 18 allows the second scroll member 14 to orbit with respect to the first scroll member 12 , while substantially precluding rotation of the second scroll member 14 with respect to the first scroll member 12 . As shown in the drawings, the camshaft 16 and the link 18 are the only structures constraining the radial position of the second scroll member 14 with respect to the first scroll member 12 .
  • the piston 66 is received within the cavity 64 defined by the second scroll member 14 .
  • the piston 66 defines a third bearing-receiving aperture 80 at the center thereof.
  • a third bearing 82 is received in the third bearing-receiving aperture 80 .
  • the third bearing 82 is shown as a flanged bearing received in the third bearing-receiving aperture from a side of the piston 66 facing away from the second scroll member 14 .
  • the third bearing 82 may be a sealed bearing that substantially precludes fluid flow therethrough.
  • the piston 66 also defines a groove 84 about the perimeter thereof.
  • the groove 84 is configured to receive a piston seal 86 , for example, an O-ring.
  • the piston seal 86 substantially precludes fluid flow between the piston 66 and the cavity 64 .
  • the piston 66 is axially retained to the camshaft 16 by a snap ring 50 received within a snap ring groove 51 defined by the cam shaft 16 . More specifically, the piston 66 and the third bearing 82 received therein are disposed between the snap ring 50 and the second scroll member 14 . As such, the snap ring 50 limits the axial travel of the third bearing 82 and, therefore, the piston 66 , in a direction away from the second scroll member 14 . The free end of the second shaft portion 16 B of the camshaft 16 may be received within the center of the third bearing 82 .
  • the third bearing 82 is configured to allow the camshaft 16 to rotate with respect to the second scroll member 14 , while the piston 66 remains rotationally fixed with respect to the second scroll member 14 .
  • a first counter weight 88 may be proximate the base of the second shaft portion 16 B of the camshaft 16 , where the first shaft portion 16 A of the camshaft is connected to the second portion 16 B of the camshaft 16 . As shown, the first counterweight 88 is disposed within the interior confines of the first involute 24 .
  • a second counterweight 90 may be provided proximate the free end of the second shaft portion 16 B of the camshaft 16 . The second counterweight 90 may be connected to the end of the camshaft 16 by a fastener 78 , for example, a threaded fastener, extending into the threaded bore 76 defined by the free end of the second shaft portion 16 B of the camshaft 16 .
  • the second counterweight 90 is disposed within the confines of a cavity 67 defined by the piston 66 on the side of the piston 66 opposite the second end plate 52 .
  • Each of the first and second counterweights 88 , 90 is rotationally fixed to the camshaft 16 and may axially fixed thereto, as well.
  • a biasing spring 92 is disposed between the second side of the second end plate 52 and the piston 66 .
  • the biasing spring 92 is an assembly of a plurality of wave washers.
  • the biasing spring 92 could be a plurality of distinct wave washers, a single wave washer, an elastomer, or any other suitable biasing member.
  • the biasing spring 92 preloads the second scroll member 14 away from the piston 66 and toward the first scroll member 12 , thereby engaging the first and second tip seals 24 S, 54 S with the respective, opposing second and first end plates 52 , 22 .
  • the biasing spring 92 is disposed between the second end plate 52 and the second counterweight 90 .
  • the biasing spring 92 could be disposed between the piston 66 and the second counterweight 90 .
  • An end cap 94 covers the cavity 67 and the piston 66 and second counterweight 90 received therein.
  • An end cap seal 96 for example, an O-ring, may be provided between the end cap 94 and the second scroll member 14 .
  • the biasing spring 92 preloads the second scroll member 14 toward the first scroll member 12 , thereby engaging the first and second tip seals 24 S, 54 S with the respective, opposing second and first end plates 52 , 22 .
  • the prime mover 20 rotates the camshaft 16 .
  • the rotating camshaft 16 causes the second scroll member 14 to orbit with respect to the first scroll member 12 .
  • the orbiting of the second scroll member 14 with respect to the first scroll member 12 causes the air or another fluid to be drawn into the working volume V through the fluid inlet port 34 and pumped toward the fluid outlet port 36 , thereby increasing the pressure of the fluid from the fluid inlet port 34 to the fluid outlet port 36 .
  • vent holes 60 mitigate this phenomenon by equalizing the fluid pressure on the first and second opposed sides of the second end plate 52 and by applying this equalized pressure to the surface of the piston 66 facing the second end plate 52 (and to the piston seal 86 ) in a first embodiment or to the end cap 94 (and to the end cap seal 96 ) in a second embodiment.
  • the equalized pressure is applied against the piston 66 . Because force equals pressure times area, because the second exposed surface area on the second side of the second end plate 52 is greater than the first exposed surface area on the first side of the second end plate 52 , and because the piston 66 is fixed axially with respect to the first scroll member 12 , the net axial force acting on the second end plate 52 due to the fluid pressure within the working volume V and the cavity 64 tends to bias the second end plate 52 , and therefore the second scroll member 14 , toward the first scroll member 12 . This net axial force tends to increase as a function of increasing fluid pressure within the working volume V and the cavity 64 .
  • the second scroll member 14 may be displaced slightly toward the first scroll member 12 in response to the foregoing axial biasing force, thereby compressing the first and second tip seals 24 S, 54 S against the respective, opposing second and first end plates 52 , 22 , and thereby promoting operational efficiency of the scroll pump 10 .
  • the piston 66 may be provided with an optional vent hole 98 similar to vent hole(s) 60 (the optional vent hole 98 is absent in the first embodiment). This may be desirable where the third bearing 82 is not a sealed a bearing. In applications where the third bearing 82 is not a sealed bearing, pressure differential across first and second sides of the third bearing 82 could force grease out of the third bearing 82 , potentially leading to premature wear and failure of the third bearing 82 . Providing the vent hole 98 in the piston 66 allows for pressure equalization across the piston 66 , thereby mitigating against forcing grease out of the third bearing 82 due to pressure differential across the third bearing 82 .
  • the equalized pressure across the second end plate 52 and the piston 66 bears against the end cap 94 and the end cap seal 96 .
  • the second scroll member 14 is biased toward the first scroll member 12 in a manner similar to that described above.
  • cooperation of the piston 66 with the cavity 64 may provide radial support for the second shaft portion 16 B of the camshaft.

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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)
US17/728,546 2021-04-26 2022-04-25 Center camshaft scroll pump Pending US20220341422A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US17/728,546 US20220341422A1 (en) 2021-04-26 2022-04-25 Center camshaft scroll pump

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US202163179967P 2021-04-26 2021-04-26
US17/728,546 US20220341422A1 (en) 2021-04-26 2022-04-25 Center camshaft scroll pump

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US (1) US20220341422A1 (ja)
EP (2) EP4083375A3 (ja)
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Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3600114A (en) * 1968-07-22 1971-08-17 Leybold Heraeus Verwaltung Involute pump
US3884599A (en) * 1973-06-11 1975-05-20 Little Inc A Scroll-type positive fluid displacement apparatus
US4609334A (en) * 1982-12-23 1986-09-02 Copeland Corporation Scroll-type machine with rotation controlling means and specific wrap shape
JPS6350691A (ja) * 1986-08-16 1988-03-03 Tokico Ltd 無給油式スクロ−ル圧縮機
US4993928A (en) * 1989-10-10 1991-02-19 Carrier Corporation Scroll compressor with dual pocket axial compliance
US5085565A (en) * 1990-09-24 1992-02-04 Carrier Corporation Axially compliant scroll with rotating pressure chambers
US5129798A (en) * 1991-02-12 1992-07-14 American Standard Inc. Co-rotational scroll apparatus with improved scroll member biasing
US5258046A (en) * 1991-02-13 1993-11-02 Iwata Air Compressor Mfg. Co., Ltd. Scroll-type fluid machinery with seals for the discharge port and wraps
US5593295A (en) * 1995-04-19 1997-01-14 Bristol Compressors, Inc. Scroll compressor construction having an axial compliance mechanism
US6030192A (en) * 1994-12-23 2000-02-29 Bristol Compressors, Inc. Scroll compressor having bearing structure in the orbiting scroll to eliminate tipping forces
US6322340B1 (en) * 1999-06-08 2001-11-27 Mitsubishi Heavy Industries, Ltd. Scroll compressor having a divided orbiting scroll end plate
US20070172373A1 (en) * 2006-01-26 2007-07-26 Scroll Laboratories, Llc Scroll-type fluid displacement apparatus with fully compliant floating scrolls
US20080069713A1 (en) * 2006-09-15 2008-03-20 Copeland Corporation Scroll compressor with discharge valve
US20090098001A1 (en) * 2007-10-15 2009-04-16 Scroll Laboratories, Inc. Sealing tabs on orbiting scroll
US20190338775A1 (en) * 2018-05-04 2019-11-07 Lg Electronics Inc. Motor-operated compressor
US20200072203A1 (en) * 2018-08-31 2020-03-05 Lg Electronics Inc. Motor operated compressor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9912212D0 (en) * 1999-05-26 1999-07-28 Boc Group Plc Scroll-type apparatus

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3600114A (en) * 1968-07-22 1971-08-17 Leybold Heraeus Verwaltung Involute pump
US3884599A (en) * 1973-06-11 1975-05-20 Little Inc A Scroll-type positive fluid displacement apparatus
US4609334A (en) * 1982-12-23 1986-09-02 Copeland Corporation Scroll-type machine with rotation controlling means and specific wrap shape
JPS6350691A (ja) * 1986-08-16 1988-03-03 Tokico Ltd 無給油式スクロ−ル圧縮機
US4993928A (en) * 1989-10-10 1991-02-19 Carrier Corporation Scroll compressor with dual pocket axial compliance
US5085565A (en) * 1990-09-24 1992-02-04 Carrier Corporation Axially compliant scroll with rotating pressure chambers
US5129798A (en) * 1991-02-12 1992-07-14 American Standard Inc. Co-rotational scroll apparatus with improved scroll member biasing
US5258046A (en) * 1991-02-13 1993-11-02 Iwata Air Compressor Mfg. Co., Ltd. Scroll-type fluid machinery with seals for the discharge port and wraps
US6030192A (en) * 1994-12-23 2000-02-29 Bristol Compressors, Inc. Scroll compressor having bearing structure in the orbiting scroll to eliminate tipping forces
US5593295A (en) * 1995-04-19 1997-01-14 Bristol Compressors, Inc. Scroll compressor construction having an axial compliance mechanism
US6322340B1 (en) * 1999-06-08 2001-11-27 Mitsubishi Heavy Industries, Ltd. Scroll compressor having a divided orbiting scroll end plate
US20070172373A1 (en) * 2006-01-26 2007-07-26 Scroll Laboratories, Llc Scroll-type fluid displacement apparatus with fully compliant floating scrolls
US20080069713A1 (en) * 2006-09-15 2008-03-20 Copeland Corporation Scroll compressor with discharge valve
US20090098001A1 (en) * 2007-10-15 2009-04-16 Scroll Laboratories, Inc. Sealing tabs on orbiting scroll
US20190338775A1 (en) * 2018-05-04 2019-11-07 Lg Electronics Inc. Motor-operated compressor
US20200072203A1 (en) * 2018-08-31 2020-03-05 Lg Electronics Inc. Motor operated compressor

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EP4083375A2 (en) 2022-11-02
JP2022168847A (ja) 2022-11-08
EP4083375A3 (en) 2023-02-15
EP4177439A1 (en) 2023-05-10

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