EP4177439A1 - Center camshaft scroll pump - Google Patents
Center camshaft scroll pump Download PDFInfo
- Publication number
- EP4177439A1 EP4177439A1 EP22216324.8A EP22216324A EP4177439A1 EP 4177439 A1 EP4177439 A1 EP 4177439A1 EP 22216324 A EP22216324 A EP 22216324A EP 4177439 A1 EP4177439 A1 EP 4177439A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- end plate
- scroll
- scroll member
- involute
- piston
- 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
Links
- 239000012530 fluid Substances 0.000 claims abstract description 33
- 230000036316 preload Effects 0.000 claims description 4
- 238000007789 sealing Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000004519 grease Substances 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Images
Classifications
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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
- 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
- F04C18/0215—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
- 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
- F04C2240/00—Components
- F04C2240/60—Shafts
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.
- a scroll pump includes: a first scroll member, the first scroll member comprising a first end plate and a first involute extending in an axial direction from a first side of the first end plate; a second scroll member engaged with the first scroll member, the second scroll member comprising a second end plate and a second involute extending in an axial direction from a first side of the second end plate, wherein the first involute is interleaved with the second involute; a link pivotably connected to the first scroll member and pivotably connected to the second scroll member; and a camshaft having a first shaft portion having a first axis of rotation, the first shaft portion rotatably connected to the first scroll member, the camshaft further having a second shaft portion connected to the first shaft portion, the second shaft portion having a second axis of rotation parallel to and radially offset from the first axis of rotation, the second shaft portion rotatably connected to the second scroll member.
- rotation of the camshaft causes the second
- the first scroll member comprises a first pivot point
- the second scroll comprises a second pivot point
- a first portion of the link is pivotably connected to the first pivot point
- a second portion of the link is pivotably connected to the second pivot point
- the link substantially precludes rotation of the first scroll member with respect to the second scroll member.
- the first pivot point is located radially outward of the first involute.
- the second pivot point is located radially outward of the second involute.
- a motor is connected to and is configured to rotate the first shaft portion of the camshaft.
- the first scroll member defines a first bearing pocket configured to receive from a second side of the first end plate opposite the first side of the first end plate, and not from the first side of the first end plate a first bearing configured to receive the first shaft portion of the camshaft in rotating engagement therewith.
- the first involute is in sealed engagement with the second end plate and the second involute is in sealed engagement with the first end plate.
- the scroll pump also includes a first tip seal in sealing engagement with a free axial end of the first involute and with the second end plate.
- the scroll pump further includes a second tip seal in sealing engagement with a free axial end of the second involute and with the first end plate.
- a scroll pump includes: a first scroll member, the first scroll member comprising a first end plate and a first involute extending in an axial direction from a first side of the first end plate and a second scroll member engaged with the first scroll member, the second scroll member comprising a second end plate and a second involute extending in an axial direction from a first side of the second end plate.
- the first involute is interleaved with the second involute
- rotation of the camshaft causes the second scroll member to travel in an orbital path with respect to the first scroll member, thereby causing the second involute to travel in an orbital path with respect to the first involute
- the second end plate has a first side and second side opposite the first side
- the second side of the second end plate defines a cavity having a sidewall
- the second end plate defines a vent hole extending therethrough from the first side thereof to the second side thereof so that the cavity is in fluid communication with a working volume defined by cooperation of the first involute and the second involute.
- the scroll pump further includes a piston received within and in sealed engagement with the sidewall of the cavity, wherein the piston axially fixed to the second shaft portion of the camshaft.
- the first side of the second end plate defines a first exposed surface area facing the first end plate and wherein the second side of the second end plate defines a second exposed surface area within the cavity.
- the second exposed surface area is greater than the first exposed surface area.
- the second scroll member floats axially with respect to the first scroll member and the camshaft.
- fluid pressure within the working volume and the cavity exerts a net axial force on the second end plate and wherein the net axial force biases the second end plate axially toward the first end plate.
- a first face of the piston facing the second end plate is exposed to the fluid pressure and not a second face of the piston opposite the first face is not exposed to the fluid pressure.
- the piston is sealingly enclosed within the cavity, and wherein the piston defines a second vent hole.
- a first face of the piston facing the second end plate and a second face of the piston opposite the first face are exposed to the fluid pressure.
- a biasing spring configured to bias the second scroll member toward the first scroll member.
- a first tip seal disposed between the first scroll and the second end plate and a second tip seal disposed between the second scroll and the first end plate.
- the biasing spring is configured to preload the second scroll member against the fixed scroll member to sealingly engage the first tip seal with the second end plate and sealingly engage the second tip seal with the first end plate.
- the biasing spring is disposed between the moving scroll member and the piston.
- 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 16A and a second shaft portion 16B connected to, spaced from, and parallel to the first shaft portion 16A; 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 16A of the camshaft 16 is rotatably connected to the first scroll member 12.
- the second shaft portion 16B of the camshaft 16 is rotatably connected to the second scroll member 14.
- a first end 18A of the link 18 is pivotably connected to the first scroll member 12, and a second end 18B 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 16A of the camshaft 16.
- the first end plate 22 also defines a bearing pocket 28 extending into the first end plate 22. In the embodiment shown, 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 16A 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 16A 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 24A 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 24B 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 24S 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 24G configured to receive and retain the tip seal 24S.
- the first scroll member 12 defines a fluid inlet aperture or port 34 proximate a periphery of the first end 24A 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 24B 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 18A 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 54S 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 54G configured to receive and retain the second tip seal 54S.
- 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 18B 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 16A and a second shaft portion 16B.
- the first shaft portion 16A 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 16B 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 16A 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 16B 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 16B and an inner race of the second bearing 58.
- a free end of the second shaft portion 16B may define a threaded bore 76 configured to receive a fastener 78, as will be discussed further below.
- the first shaft portion 16A is received within the first bearing 30 in rotating bearing engagement therewith.
- the second shaft portion 16B 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 16A.
- the second scroll member 14 axially floats with respect to the second shaft portion 16B.
- 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 24S 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 54S 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 24S.
- 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 24S, 54S 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 18A 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 18B 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 16B 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 counterweight 88 may be proximate the base of the second shaft portion 16B of the camshaft 16, where the first shaft portion 16A of the camshaft is connected to the second portion 16B 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 16B 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 16B 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 24S, 54S 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 24S, 54S 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 24S, 54S 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 16B of the camshaft.
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Abstract
Description
- Scroll pumps are known in the art. A scroll pump typically includes first and second scroll members having respective, interleaved, first and second involutes. Typically, the 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.
- In such a scroll pump, 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.
- Also, pressure build up within the working volume of a scroll pump inherently tends to force the first and second scroll members apart from each other axially. Typically, this phenomenon is mitigated by observance of precise tolerances in the fabrication and assembly of the scroll members and camshafts. Over time, however, the foregoing components can wear outside of the tolerances and thereby lessen the efficiency of the scroll 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.
- In a preferred embodiment, a scroll pump includes: a first scroll member, the first scroll member comprising a first end plate and a first involute extending in an axial direction from a first side of the first end plate; a second scroll member engaged with the first scroll member, the second scroll member comprising a second end plate and a second involute extending in an axial direction from a first side of the second end plate, wherein the first involute is interleaved with the second involute; a link pivotably connected to the first scroll member and pivotably connected to the second scroll member; and a camshaft having a first shaft portion having a first axis of rotation, the first shaft portion rotatably connected to the first scroll member, the camshaft further having a second shaft portion connected to the first shaft portion, the second shaft portion having a second axis of rotation parallel to and radially offset from the first axis of rotation, the second shaft portion rotatably connected to the second scroll member. In this embodiment, rotation of the camshaft causes the second scroll member to travel in an orbital path with respect to the first scroll member, thereby causing the second involute to travel in an orbital path with respect to the first involute.
- In an embodiment, the first scroll member comprises a first pivot point, the second scroll comprises a second pivot point, a first portion of the link is pivotably connected to the first pivot point; and a second portion of the link is pivotably connected to the second pivot point.
- In an embodiment, the link substantially precludes rotation of the first scroll member with respect to the second scroll member.
- In an embodiment, the first pivot point is located radially outward of the first involute.
- In an embodiment, the second pivot point is located radially outward of the second involute.
- In an embodiment, a motor is connected to and is configured to rotate the first shaft portion of the camshaft.
- In an embodiment, the first scroll member defines a first bearing pocket configured to receive from a second side of the first end plate opposite the first side of the first end plate, and not from the first side of the first end plate a first bearing configured to receive the first shaft portion of the camshaft in rotating engagement therewith.
- In an embodiment, the first involute is in sealed engagement with the second end plate and the second involute is in sealed engagement with the first end plate.
- In an embodiment, the scroll pump also includes a first tip seal in sealing engagement with a free axial end of the first involute and with the second end plate.
- In an embodiment, the scroll pump further includes a second tip seal in sealing engagement with a free axial end of the second involute and with the first end plate.
- In a preferred embodiment, a scroll pump includes: a first scroll member, the first scroll member comprising a first end plate and a first involute extending in an axial direction from a first side of the first end plate and a second scroll member engaged with the first scroll member, the second scroll member comprising a second end plate and a second involute extending in an axial direction from a first side of the second end plate. In the embodiment, the first involute is interleaved with the second involute, rotation of the camshaft causes the second scroll member to travel in an orbital path with respect to the first scroll member, thereby causing the second involute to travel in an orbital path with respect to the first involute, the second end plate has a first side and second side opposite the first side, the second side of the second end plate defines a cavity having a sidewall, and the second end plate defines a vent hole extending therethrough from the first side thereof to the second side thereof so that the cavity is in fluid communication with a working volume defined by cooperation of the first involute and the second involute. In this embodiment, the scroll pump further includes a piston received within and in sealed engagement with the sidewall of the cavity, wherein the piston axially fixed to the second shaft portion of the camshaft.
- In an embodiment, the first side of the second end plate defines a first exposed surface area facing the first end plate and wherein the second side of the second end plate defines a second exposed surface area within the cavity.
- In an embodiment, the second exposed surface area is greater than the first exposed surface area.
- In an embodiment, the second scroll member floats axially with respect to the first scroll member and the camshaft.
- In an embodiment, fluid pressure within the working volume and the cavity exerts a net axial force on the second end plate and wherein the net axial force biases the second end plate axially toward the first end plate.
- In an embodiment, a first face of the piston facing the second end plate is exposed to the fluid pressure and not a second face of the piston opposite the first face is not exposed to the fluid pressure.
- In an embodiment, the piston is sealingly enclosed within the cavity, and wherein the piston defines a second vent hole.
- In an embodiment, a first face of the piston facing the second end plate and a second face of the piston opposite the first face are exposed to the fluid pressure.
- In an embodiment, a biasing spring configured to bias the second scroll member toward the first scroll member.
- In an embodiment, a first tip seal disposed between the first scroll and the second end plate and a second tip seal disposed between the second scroll and the first end plate.
- In an embodiment, the biasing spring is configured to preload the second scroll member against the fixed scroll member to sealingly engage the first tip seal with the second end plate and sealingly engage the second tip seal with the first end plate.
- In an embodiment, the biasing spring is disposed between the moving scroll member and the piston.
-
-
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 ofFig. 1 ; -
Fig. 3 is a front cross-sectional elevation view of the center camshaft scroll pump ofFig. 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 ofFig. 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 ofFig. 1 ; -
Fig. 5B is a perspective view of a second side of an orbiting scroll member of the center camshaft scroll pump ofFig. 1 ; -
Fig. 6 is a perspective view of a first side of a fixed scroll member of the center camshaft scroll pump ofFig. 1 ; -
Fig. 7 is a first exploded perspective view of the center camshaft scroll pump ofFig. 1 ; and -
Fig. 8 is a second exploded perspective view of the center camshaft scroll pump ofFig. 1 . - The drawings show an illustrative embodiment of a
scroll pump 10 according to the present disclosure. Thescroll pump 10 includes: a first (or fixed)scroll member 12; a second (or orbiting)scroll member 14; acamshaft 16 having afirst shaft portion 16A and asecond shaft portion 16B connected to, spaced from, and parallel to thefirst shaft portion 16A; alink 18; and aprime mover 20, for example, an electric motor. Thefirst scroll member 12 is in orbiting engagement with thesecond scroll member 14. Thefirst shaft portion 16A of thecamshaft 16 is rotatably connected to thefirst scroll member 12. Thesecond shaft portion 16B of thecamshaft 16 is rotatably connected to thesecond scroll member 14. Afirst end 18A of thelink 18 is pivotably connected to thefirst scroll member 12, and asecond end 18B of thelink 18 is pivotably connected to thesecond scroll member 14. Themotor 20 is configured to rotate thecamshaft 16 with respect to thefirst scroll member 12 and thesecond scroll member 14. Thelink 18 substantially precludes rotation of thesecond scroll member 14 with respect to thefirst scroll member 12 when thecamshaft 16 is rotating, so that rotation of thecamshaft 16 causes thesecond scroll member 14 to orbit with respect to thefirst scroll member 12. - The
first scroll member 12 includes afirst end plate 22 and afirst involute 24 extending axially from a first side of thefirst end plate 22. Thefirst end plate 22 defines a first shaft-receivingaperture 26 configured to receive thefirst shaft portion 16A of thecamshaft 16. Thefirst end plate 22 also defines abearing pocket 28 extending into thefirst end plate 22. In the embodiment shown, thebearing pocket 28 extends toward the first side of thefirst end plate 22 from a second side of thefirst end plate 22 opposite the first side of thefirst end plate 22. A first bearing 30 is received within the first bearingpocket 28, for example, in press-fit engagement. Aland 32 at the bottom of the bearing pocket precludes thebearing 30 from being inserted into and removed from thebearing pocket 28 from the first side of thefirst end plate 22. The first bearing 30 may abut theland 32. - Alternatively, the
bearing pocket 28 may extend into thefirst end plate 22 from the first side of thefirst end plate 22 toward the second side of thefirst end plate 22. In such an embodiment (not shown), theland 32 would preclude thebearing 30 from being inserted into and removed from thebearing pocket 28 from the second side of thefirst end plate 22. - In other embodiments, the
first aperture 26 and the bearingpocket 28 may be combined into a single feature and theland 32 may be omitted. In such embodiments, thefirst bearing 32 could be inserted into and removed from the bearingpocket 28 from the first side of thefirst end plate 22 or the second side of thefirst end plate 22. - The
first bearing 30 is configured to receive thefirst shaft portion 16A of thecamshaft 16 in rotating, bearing engagement. Thefirst bearing 30 may be a sealed bearing, and the interfaces among thefirst end plate 22, thefirst bearing 30, and thefirst shaft portion 16A of thecamshaft 16 may be substantially sealed interfaces so that thefirst bearing 32 and the foregoing interfaces are substantially airtight. - As suggested above, the
first involute 24 extends axially from the first side of thefirst end plate 22 in a direction perpendicular to thefirst end plate 22. Afirst end 24A of thefirst involute 24 proximate a periphery of thefirst involute 24 closes upon an intermediate portion of thefirst involute 24. Asecond end 24B of thefirst involute 24 proximate a center of thefirst involute 24 is free. As such, thefirst end plate 22 and thefirst involute 24 cooperate to define a space configured to receive a second involute, as will be discussed further below. Afirst tip seal 24S is provided at a free surface of thefirst involute 24 opposite thefirst end plate 22. The free end of thefirst involute 24 may define a recess or groove 24G configured to receive and retain thetip seal 24S. - The
first scroll member 12 defines a fluid inlet aperture orport 34 proximate a periphery of thefirst end 24A of thefirst involute 24. Thefluid inlet aperture 34 is configured to admit air or another fluid into thescroll pump 10 for pressurizing thereby. Thefluid inlet port 34 may extend through one or both of thefirst end plate 22 and thefirst involute 24. Thefirst scroll member 12 also defines a fluid outlet aperture orport 36 extending through thefirst end plate 22 proximate thesecond end 24B of thefirst involute 24. Thefluid outlet port 36 is configured to discharge fluid pressurized by thescroll pump 10. - The
first scroll member 12 further defines afirst pivot point 38 configured to receive an axle or pin 40 connecting thefirst end 18A of thelink 18 to thefirst scroll member 12 in pivoting engagement therewith. As shown, thefirst pivot point 38 may be embodied as a boss proximate the periphery of thefirst end plate 22 and/or radially outboard of thefirst involute 24. - The
first scroll member 12 also may include one or mountingbosses 42 configured to receive fasteners (not shown) for connecting thefirst scroll member 12 to another structure (not shown). - A
sidewall 44 extends axially from the second side of thefirst end plate 22. Thesidewall 44 cooperates with thefirst end plate 22 to define a housing configured to receive theprime mover 20, in this case an electric motor. As shown, thesidewall 44 is monolithically formed or integral with thefirst end plate 22. Anend cap 46 covers the open end of thesidewall 44. Aseal 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 asecond end plate 52 and asecond involute 54 extending from a first side of thesecond end plate 52. Thesecond end plate 52 defines a second shaft-receivingaperture 56 extending from the first side thereof to a second side thereof opposite the first side. The second shaft-receivingaperture 56 is configured to receive asecond bearing 58 therein, for example, in press-fit engagement. Thesecond end plate 52 also defines one or more vent holes 60 extending therethrough, proximate the center of thesecond end plate 52, as will be discussed further below. Anannular sidewall 62 extends axially from the second side of thesecond end plate 52, thereby defining acavity 64 extending axially from the second side of the second end plate. Thecavity 64 is configured to receive apiston 66, as will be discussed further below. Thecavity 64 may be cylindrical. - As suggested above, the
second involute 54 extends from a first side of thesecond end plate 52 in a direction perpendicular thereto. Asecond tip seal 54S is provided at a free end of thesecond involute 54. The free end of thesecond involute 54 may define a recess or groove 54G configured to receive and retain thesecond tip seal 54S. - The
second scroll member 52 further defines asecond pivot point 68 configured to receive a second axle or pin 70 connecting thesecond end 18B of thelink 18 to thesecond scroll member 14 in pivoting engagement therewith. As shown, thesecond pivot point 68 may be embodied as a boss proximate the periphery of thesecond end plate 52. - As mentioned above, the
camshaft 16 includes afirst shaft portion 16A and asecond shaft portion 16B. Thefirst shaft portion 16A defines a first axis of rotation. The first axis of rotation is perpendicular to thefirst end plate 22 and parallel to thefirst involute 24. Thesecond shaft portion 16B defines a second axis of rotation. The second axis of rotation is perpendicular to thesecond end plate 52 and parallel to thesecond involute 54. The second axis of rotation is radially offset from and parallel to the first axis of rotation. Thefirst shaft portion 16A is configured for connection to a drive shaft of theprime mover 20 for rotation therewith. In embodiments, thecamshaft 16 may be integrated and/or monolithically formed with the drive shaft of theprime mover 20. - The
second shaft portion 16B defines acircumferential groove 72 configured to receive ashaft seal 74, for example, an O-ring. Theshaft seal 74 is engaged between thesecond shaft portion 16B and an inner race of thesecond bearing 58. A free end of thesecond shaft portion 16B may define a threadedbore 76 configured to receive afastener 78, as will be discussed further below. - The
first shaft portion 16A is received within thefirst bearing 30 in rotating bearing engagement therewith. Thesecond shaft portion 16B is received within thesecond bearing 58 in rotating bearing engagement therewith. Thefirst scroll member 12 is axially fixed to thefirst shaft portion 16A. Thesecond scroll member 14 axially floats with respect to thesecond shaft portion 16B. - The
first scroll member 12 is engaged with thesecond scroll member 14 so that thefirst involute 24 is interleaved with thesecond involute 54. Thefirst tip seal 24S of thefirst scroll member 12 engages with the first side of thesecond end plate 52 of thesecond scroll member 14 in sealing engagement therewith. Similarly, thesecond tip seal 54S of thesecond scroll member 14 engages with the first side of thefirst end plate 22 of thefirst scroll member 12 in sealing engagement therewith. So assembled, the first andsecond scroll members second end plates second involutes - With the first and
second scroll members 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 thesecond end plate 52 normal to the second axis of rotation and radially inboard of thefirst involute 24, minus the surface area of the first side of thesecond end plate 52 normal to the second axis of rotation occupied by thesecond involute 54 and covered by thefirst involute 24/first tip seal 24S. Put another way, the first exposed surface area is the surface area of the first side of thesecond end plate 52 that projects against the first side of thefirst end plate 22, minus the surface area of the free end of thesecond involute 54 engaging the first side of the first end plate. A second exposed surface area of thesecond end plate 52 is exposed to fluid pressure within thecavity 64. The second exposed surface area is defined by the surface area of the second side of thesecond end plate 52 normal to the second axis of rotation within the confines of thecavity 64. The second exposed surface area is greater than the first exposed surface area so that when both sides of thesecond end plate 52 are subjected to the same fluid pressure, the net force on thesecond end plate 52 parallel to the second axis of rotation tends to bias thesecond scroll member 14 toward thefirst scroll member 12, thereby compressing the first and second tip seals 24S, 54S against the respective second andfirst end plates - As mentioned above, the
link 18 is pivotably connected to both the first andsecond scroll members link 18, which may be proximate afirst end 18A thereof, is pivotably connected to thefirst scroll member 12. Similarly, a second portion of thelink 18, which may be proximate asecond end 18B thereof, is pivotably connected to thesecond scroll member 14. So connected to the first andsecond scroll members link 18 allows thesecond scroll member 14 to orbit with respect to thefirst scroll member 12, while substantially precluding rotation of thesecond scroll member 14 with respect to thefirst scroll member 12. As shown in the drawings, thecamshaft 16 and thelink 18 are the only structures constraining the radial position of thesecond scroll member 14 with respect to thefirst scroll member 12. - As suggested above, the
piston 66 is received within thecavity 64 defined by thesecond scroll member 14. Thepiston 66 defines a third bearing-receivingaperture 80 at the center thereof. Athird bearing 82 is received in the third bearing-receivingaperture 80. Thethird bearing 82 is shown as a flanged bearing received in the third bearing-receiving aperture from a side of thepiston 66 facing away from thesecond scroll member 14. Thethird bearing 82 may be a sealed bearing that substantially precludes fluid flow therethrough. Thepiston 66 also defines agroove 84 about the perimeter thereof. Thegroove 84 is configured to receive apiston seal 86, for example, an O-ring. Thepiston seal 86 substantially precludes fluid flow between thepiston 66 and thecavity 64. - As shown, the
piston 66 is axially retained to thecamshaft 16 by asnap ring 50 received within asnap ring groove 51 defined by thecam shaft 16. More specifically, thepiston 66 and thethird bearing 82 received therein are disposed between thesnap ring 50 and thesecond scroll member 14. As such, thesnap ring 50 limits the axial travel of thethird bearing 82 and, therefore, thepiston 66, in a direction away from thesecond scroll member 14. The free end of thesecond shaft portion 16B of thecamshaft 16 may be received within the center of thethird bearing 82. Thethird bearing 82 is configured to allow thecamshaft 16 to rotate with respect to thesecond scroll member 14, while thepiston 66 remains rotationally fixed with respect to thesecond scroll member 14. - As shown, a
first counterweight 88 may be proximate the base of thesecond shaft portion 16B of thecamshaft 16, where thefirst shaft portion 16A of the camshaft is connected to thesecond portion 16B of thecamshaft 16. As shown, thefirst counterweight 88 is disposed within the interior confines of thefirst involute 24. Asecond counterweight 90 may be provided proximate the free end of thesecond shaft portion 16B of thecamshaft 16. Thesecond counterweight 90 may be connected to the end of thecamshaft 16 by afastener 78, for example, a threaded fastener, extending into the threaded bore 76 defined by the free end of thesecond shaft portion 16B of thecamshaft 16. As shown, thesecond counterweight 90 is disposed within the confines of acavity 67 defined by thepiston 66 on the side of thepiston 66 opposite thesecond end plate 52. Each of the first andsecond counterweights camshaft 16 and may axially fixed thereto, as well. - A biasing
spring 92 is disposed between the second side of thesecond end plate 52 and thepiston 66. As shown, the biasingspring 92 is an assembly of a plurality of wave washers. In embodiments, the biasingspring 92 could be a plurality of distinct wave washers, a single wave washer, an elastomer, or any other suitable biasing member. The biasingspring 92 preloads thesecond scroll member 14 away from thepiston 66 and toward thefirst scroll member 12, thereby engaging the first and second tip seals 24S, 54S with the respective, opposing second andfirst end plates spring 92 is disposed between thesecond end plate 52 and thesecond counterweight 90. In embodiments, the biasingspring 92 could be disposed between thepiston 66 and thesecond counterweight 90. - An
end cap 94 covers thecavity 67 and thepiston 66 andsecond counterweight 90 received therein. Anend cap seal 96, for example, an O-ring, may be provided between theend cap 94 and thesecond scroll member 14. - In use, the biasing
spring 92 preloads thesecond scroll member 14 toward thefirst scroll member 12, thereby engaging the first and second tip seals 24S, 54S with the respective, opposing second andfirst end plates prime mover 20 rotates thecamshaft 16. The rotatingcamshaft 16 causes thesecond scroll member 14 to orbit with respect to thefirst scroll member 12. The orbiting of thesecond scroll member 14 with respect to thefirst scroll member 12 causes the air or another fluid to be drawn into the working volume V through thefluid inlet port 34 and pumped toward thefluid outlet port 36, thereby increasing the pressure of the fluid from thefluid inlet port 34 to thefluid outlet port 36. - In the absence of the vent holes 60 defined by the
second end plate 52, the foregoing increase in fluid pressure acting against thefirst end plate 22 and the first exposed surface of thesecond end plate 52 would tend to force the first andsecond scroll members second scroll member 14 away from thefirst scroll member 12 resulting from such force could lessen the effect of the first and second tip seals 24S, 54S, thereby decreasing the efficiency of thescroll pump 10. - The 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 thepiston 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. - In the first 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 thesecond end plate 52 is greater than the first exposed surface area on the first side of thesecond end plate 52, and because thepiston 66 is fixed axially with respect to thefirst scroll member 12, the net axial force acting on thesecond end plate 52 due to the fluid pressure within the working volume V and thecavity 64 tends to bias thesecond end plate 52, and therefore thesecond scroll member 14, toward thefirst scroll member 12. This net axial force tends to increase as a function of increasing fluid pressure within the working volume V and thecavity 64. Also, because thesecond scroll member 14 floats on thesecond shaft portion 16B of thecamshaft 16, thesecond scroll member 14 may be displaced slightly toward thefirst scroll member 12 in response to the foregoing axial biasing force, thereby compressing the first and second tip seals 24S, 54S against the respective, opposing second andfirst end plates scroll pump 10. - In the second embodiment, as shown in
Fig. 7 , thepiston 66 may be provided with anoptional vent hole 98 similar to vent hole(s) 60 (theoptional vent hole 98 is absent in the first embodiment). This may be desirable where thethird bearing 82 is not a sealed a bearing. In applications where thethird bearing 82 is not a sealed bearing, pressure differential across first and second sides of thethird bearing 82 could force grease out of thethird bearing 82, potentially leading to premature wear and failure of thethird bearing 82. Providing thevent hole 98 in thepiston 66 allows for pressure equalization across thepiston 66, thereby mitigating against forcing grease out of thethird bearing 82 due to pressure differential across thethird bearing 82. In such embodiments, the equalized pressure across thesecond end plate 52 and thepiston 66 bears against theend cap 94 and theend cap seal 96. In such embodiments, in use, thesecond scroll member 14 is biased toward thefirst scroll member 12 in a manner similar to that described above. - In any of the foregoing embodiments, cooperation of the
piston 66 with thecavity 64 may provide radial support for thesecond shaft portion 16B of the camshaft. - The foregoing description and corresponding drawings refer to one or more illustrative embodiments of a scroll pump according to the present disclosure. These embodiments are illustrative, and not limiting. One skilled in the art would recognize that the disclosed embodiments could be modified in numerous ways without departing from the scope of the invention as defined by the appended claims.
Claims (12)
- A scroll pump comprising:a first scroll member, the first scroll member comprising a first end plate and a first involute extending in an axial direction from a first side of the first end plate;a second scroll member engaged with the first scroll member, the second scroll member comprising a second end plate and a second involute extending in an axial direction from a first side of the second end plate, wherein:the first involute is interleaved with the second involute,rotation of the camshaft causes the second scroll member to travel in an orbital path with respect to the first scroll member, thereby causing the second involute to travel in an orbital path with respect to the first involute,the second end plate has a first side and second side opposite the first side,the second side of the second end plate defines a cavity having a sidewall, andthe second end plate defines a vent hole extending therethrough from the first side thereof to the second side thereof so that the cavity is in fluid communication with a working volume defined by cooperation of the first involute and the second involute,the scroll pump further comprising a piston received within and in sealed engagement with the sidewall of the cavity,wherein the piston axially fixed to the second shaft portion of the camshaft.
- The scroll pump of claim 1 wherein the first side of the second end plate defines a first exposed surface area facing the first end plate and wherein the second side of the second end plate defines a second exposed surface area within the cavity.
- The scroll pump of claim 2 wherein the second exposed surface area is greater than the first exposed surface area.
- The scroll pump of claim 3 wherein the second scroll member floats axially with respect to the first scroll member and the camshaft.
- The scroll pump of claim 4 wherein fluid pressure within the working volume and the cavity exerts a net axial force on the second end plate and wherein the net axial force biases the second end plate axially toward the first end plate.
- The scroll pump of claim 5 wherein a first face of the piston facing the second end plate is exposed to the fluid pressure and not a second face of the piston opposite the first face is not exposed to the fluid pressure.
- The scroll pump of claim 5 wherein the piston is sealingly enclosed within the cavity, and wherein the piston defines a second vent hole.
- The scroll pump of claim 7 wherein a first face of the piston facing the second end plate and a second face of the piston opposite the first face are exposed to the fluid pressure.
- The scroll pump of claim 1 further comprising a biasing spring configured to bias the second scroll member toward the first scroll member.
- The scroll pump of claim 9 further comprising a first tip seal disposed between the first scroll and the second end plate and a second tip seal disposed between the second scroll and the first end plate.
- The scroll pump of claim 10 wherein the biasing spring is configured to preload the second scroll member against the fixed scroll member to sealingly engage the first tip seal with the second end plate and sealingly engage the second tip seal with the first end plate.
- The scroll pump of claim 9 wherein the biasing spring is disposed between the moving scroll member and the piston.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US202163179967P | 2021-04-26 | 2021-04-26 | |
EP22169728.7A EP4083375A3 (en) | 2021-04-26 | 2022-04-25 | Center camshaft scroll pump |
Related Parent Applications (2)
Application Number | Title | Priority Date | Filing Date |
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EP22169728.7A Division-Into EP4083375A3 (en) | 2021-04-26 | 2022-04-25 | Center camshaft scroll pump |
EP22169728.7A Division EP4083375A3 (en) | 2021-04-26 | 2022-04-25 | Center camshaft scroll pump |
Publications (1)
Publication Number | Publication Date |
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EP4177439A1 true EP4177439A1 (en) | 2023-05-10 |
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ID=81386728
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Application Number | Title | Priority Date | Filing Date |
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EP22169728.7A Pending EP4083375A3 (en) | 2021-04-26 | 2022-04-25 | Center camshaft scroll pump |
EP22216324.8A Pending EP4177439A1 (en) | 2021-04-26 | 2022-04-25 | Center camshaft scroll pump |
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Application Number | Title | Priority Date | Filing Date |
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EP22169728.7A Pending EP4083375A3 (en) | 2021-04-26 | 2022-04-25 | Center camshaft scroll pump |
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US (1) | US20220341422A1 (en) |
EP (2) | EP4083375A3 (en) |
JP (1) | JP2022168847A (en) |
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US3884599A (en) * | 1973-06-11 | 1975-05-20 | Little Inc A | Scroll-type positive fluid displacement apparatus |
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 |
US20090098001A1 (en) * | 2007-10-15 | 2009-04-16 | Scroll Laboratories, Inc. | Sealing tabs on orbiting scroll |
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DE1935621A1 (en) * | 1968-07-22 | 1970-01-29 | Leybold Heraeus Gmbh & Co Kg | Displacement pump |
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-
2022
- 2022-04-25 JP JP2022071237A patent/JP2022168847A/en active Pending
- 2022-04-25 EP EP22169728.7A patent/EP4083375A3/en active Pending
- 2022-04-25 US US17/728,546 patent/US20220341422A1/en active Pending
- 2022-04-25 EP EP22216324.8A patent/EP4177439A1/en active Pending
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US20090098001A1 (en) * | 2007-10-15 | 2009-04-16 | Scroll Laboratories, Inc. | Sealing tabs on orbiting scroll |
Also Published As
Publication number | Publication date |
---|---|
EP4083375A2 (en) | 2022-11-02 |
JP2022168847A (en) | 2022-11-08 |
US20220341422A1 (en) | 2022-10-27 |
EP4083375A3 (en) | 2023-02-15 |
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