US20140017109A1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- US20140017109A1 US20140017109A1 US14/006,596 US201214006596A US2014017109A1 US 20140017109 A1 US20140017109 A1 US 20140017109A1 US 201214006596 A US201214006596 A US 201214006596A US 2014017109 A1 US2014017109 A1 US 2014017109A1
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- United States
- Prior art keywords
- seal
- scroll
- orbiting
- fixed scroll
- orbiting scroll
- 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.)
- Abandoned
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Classifications
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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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
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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
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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
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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
- F04C18/0223—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 with symmetrical double wraps
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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
- F04C18/0246—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
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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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
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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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
Definitions
- the present invention relates to a scroll compressor.
- FIG. 7 A prior art scroll compressor, or pump, 10 is shown in FIG. 7 .
- the pump 10 comprises a pump housing 12 and a drive shaft 14 having an eccentric shaft portion 16 .
- the shaft 14 is driven by a motor 18 and the eccentric shaft portion is connected to an orbiting scroll 20 so that during use rotation of the shaft imparts an orbiting motion to the orbiting scroll relative to a fixed scroll 22 for pumping fluid along a fluid flow path between a pump inlet 24 and pump outlet 26 of the compressor.
- the fixed scroll 22 comprises a scroll wall 28 which extends perpendicularly to a generally circular base plate 30 and has an axial end face, or surface, 29 .
- the orbiting scroll 20 comprises a scroll wall 34 which extends perpendicularly to a generally circular base plate 37 and has an axial end face, or surface, 35 .
- the orbiting scroll wall 34 cooperates, or meshes, with the fixed scroll wall 28 during orbiting movement of the orbiting scroll. Relative orbital movement of the scrolls causes a volume of gas to be trapped between the scrolls and pumped from the inlet to the outlet.
- a scroll pump may be a dry pump and not lubricated.
- the space between the axial ends 29 , 35 of a scroll wall of one scroll and the base plate 30 , 37 of the other scroll is sealed by sealing arrangement, which generally comprise tip seals.
- the tip seals close the gap between scrolls caused by manufacturing and operating tolerances, and reduce the leakage to an acceptable level.
- tip seals suffer from the generation of tip seal dust and require a period of bedding in before achieving operational requirements. Further, in a normal scroll pump, tip seals require replacement at regular intervals after they become worn.
- FIG. 6 An enlarged cross-section through a portion of the fixed scroll 22 showing the tip seal 36 in more detail is shown in FIG. 6 .
- the tip seal 36 has an aspect ratio of axial length to radial width which is 1:1. That is, the radial width of the tip seal is equal to the axial length of the tip seal so that as shown in cross-section in FIG. 6 the tip seal has a square cross-section. Accordingly, the tip seal is relatively stiff in a radial direction.
- the tip seal is located in a channel 38 at the axial end of the fixed scroll wall. There is a small axial gap between an axial end of the tip seal 36 and the base of the channel 38 so that in use fluid occupying the gap forces the tip seal axially towards the base plate 37 of the orbiting scroll. Accordingly, the tip seal is supported on a cushion of fluid which serves to urge the seal towards an opposing seal surface. Additionally, and although not shown in FIG. 6 , there is a radial clearance between the tip seal and the inner radial facing surfaces of the channel. During relative orbiting motion of the scrolls, the seal is urged against one inner radial surface for part of its motion and against the other inner radial surface for another part of its motion. As the seal moves between these positions, leakage is increased because there is a leakage path formed from one side of the seal to the other side of the seal. The tip seal 36 which is relatively stiff in the radial direction changes position in the channel relatively slowly thereby increasing leakage.
- the present invention seeks at least to mitigate one or more of the problems associated with the prior art.
- the present invention provides a scroll compressor comprising: an orbiting scroll having an orbiting scroll wall extending axially from an orbiting scroll plate towards a fixed scroll; a fixed scroll having an fixed scroll wall extending axially from a fixed scroll plate towards the orbiting scroll; and an axially extending drive shaft having an eccentric shaft portion so that rotation of the eccentric shaft portion imparts an orbiting motion to the orbiting scroll relative to the fixed scroll; wherein an axial end portion of the orbiting scroll wall has a first seal for sealing between the orbiting scroll wall and the fixed scroll plate, and an axial end portion of the fixed scroll wall has a second seal for sealing between the fixed scroll wall and the orbiting scroll plate; and wherein the first seal or the second seal has an aspect ratio of axial length to radial width which is 1 : 1 . 25 or greater.
- FIG. 1 shows a section through part of a fixed scroll of a scroll compressor
- FIGS. 2 and 3 show enlarged views of a tip seal as shown in FIG. 1 in first and second locations in a channel;
- FIGS. 4 and 5 show a plan view of part of a prior art scroll wall and seal and a plan view of part of a scroll wall and seal according to an embodiment
- FIG. 6 is a section through part of a fixed scroll of a prior art scroll compressor.
- FIG. 7 shows a schematic diagram of a prior art scroll compressor.
- FIG. 1 A section through part of a fixed scroll 50 is shown in FIG. 1 .
- the fixed scroll 50 forms part of a scroll compressor embodying the invention which is similar in construction and operation to the prior art scroll compressor shown in FIG. 7 , except for those aspects shown in FIGS. 1 to 5 and described below. For the sake of brevity therefore, the structure and operation of the whole scroll compressor will not be described again in detail.
- the fixed scroll 50 shown in FIG. 1 comprises a fixed scroll plate 52 and a fixed scroll wall 54 extending generally perpendicularly therefrom typically in the form of an involute.
- the scroll wall may form an involute over only a portion of its length, usually its radially inner portion.
- the axial end of the fixed scroll wall comprises a channel 56 in which a tip seal 58 is located for sealing against an orbiting scroll 60 shown in FIGS. 2 and 3 .
- the tip seal 58 When the tip seal is installed, the tip seal 58 has an aspect ratio of axial length to radial width which is greater than 1:1.25. That is, where the ratio is x (axial length):y (radial width), and x equals 1, y is 1.25 or greater. As shown in FIGS. 1 to 3 , the axial length is similar to the length shown in FIG. 4 , however tip seal 58 is thinner in the radial direction and therefore lighter and more flexible. In the embodiment shown the ratio is 1:1.5 and depending on pumping requirements, the tip seal has an axial extent and radial width in the range from about 1.8 mm and 1.2 mm to 4 mm and 2.6 mm respectively. It will be seen therefore that the aspect ratio may be more than 1:2.
- tip seal 58 When manufacturing the tip seal 58 from the materials used currently, the wear rate & tip-seal life (pressure-velocity regime) remains generally unchanged. Additionally, tip seal 58 shows shorter bedding-in or stabilization times. The tip seal 58 is thinner, and therefore more flexible, in the radial direction; in addition, its sectional area is smaller, making it also more flexible in the axial direction. Therefore it demonstrates better capability of presenting its full axial end face 62 against the orbiting scroll. Accordingly, most if not all of the axial face becomes bedded in quickly during initial use.
- the axial end face 62 occupies relatively less area than the axial end face of the prior art tip seal, less dust is generated due to abrasion against the orbiting scroll during use. As dust generated during use must be periodically removed, less dust generation decreases the cost of ownership. Further, in the prior art where the tip seal is relatively stiff in the radial direction, only a portion or corner of the axial end face may be presented to the orbiting scroll. It will be appreciated that whilst in the embodiment the axial end face is smaller than the axial end face in the prior art, a more flexible seal is better able to present its entire end face to the orbiting scroll whereas in the prior art only a corner of the scroll end face may be presented to the orbiting scroll.
- FIGS. 4 and 5 show respectively a plan view of a portion of a tip seal in a groove of a scroll wall for a prior art arrangement and an arrangement in accordance with an embodiment of the invention.
- the scroll wall is spiral, for the sake of explanation the scroll wall has been shown as linear.
- a portion of a tip seal therefore is driven against a radially inner side of the groove when it is at an upstream portion of a trapped pocket and against a radially outer side of the groove when it is at a downstream portion of a trapped pocket.
- first portions 68 , 70 of the tip seals are located at the radially inner side 72 of the groove 74 and second portions 76 , 78 of the tip seals are located at the radially outer side 80 of the groove.
- intermediate portions 82 , 84 of the tip seals 36 , 58 bridge the gap between the radially inner side 72 and the radially outer side 80 of the groove.
- Fluid can leak across the tip seals at the intermediate portions, since there is a leakage path which extends between the tip seals and the radially inner side 72 of the groove, underneath the tip seals and between the tip seals and the radially outer side 80 of the groove. That is, at the intermediate portions 82 , 84 the tip seal does not block the seepage path by pressing against one of the sides of the groove.
- the prior art tip seal 36 has a larger radial width to axial depth and is therefore relatively stiff in the radial direction. Consequently, the length of the intermediate portions 82 are longer meaning that more leakage occurs.
- the tip seal 58 has a smaller radial width to axial depth and is therefore relatively flexible in the radial direction. Consequently, the length of the intermediate portions 84 are shorter meaning that less leakage occurs.
- a further advantage of the present embodiment is that the space occupied by the tip seal is smaller in the radial direction and therefore scroll wall thickness is reduced. Accordingly, as shown in FIG. 1 , six wraps are shown whereas in FIG. 6 only five wraps are shown. Therefore, for a pump of any given size, the present embodiment allows increased pumping capability because more wraps equates to a longer pumping path between inlet and exhaust, which increases compression. Alternatively the embodiment allows similar pumping capability in a smaller pump. In this latter regard, a pump which occupies less volume than the prior art is generally less expensive to manufacture as it requires less material and occupies a smaller foot-print when in use.
- FIGS. 2 and 3 show the radial clearance R between a portion of tip seal 58 and the radial sides 72 , 80 of the channel or groove 74 .
- the clearance has been exaggerated in the Figures for the purposes of explanation.
- the tip-seal is pressure-loaded against the counter-face 62 of the orbiting scroll 60 by the gas that occupies the space G underneath the seal.
- the seal is urged against the sides of the channel by a combination of pressure differential in the radial direction and friction against the counter-face as the orbiting scroll orbits.
- the seal is located in the position shown in either FIG. 2 or 3 , or is in the process of moving between the two shown positions. That is, the first portions 70 of the tip seal 58 are located at the radially inner side 72 of the channel in FIG. 2 and the second portions 78 of the tip seal are located at the radially outer side 80 of the channel in FIG. 3 .
- a seepage path is formed across the tip seal causing leakage.
- the seepage path extends along one radial face of the tip seal, across gap G and along an opposing radial face of the tip seal.
- tip seal 58 is more flexible in the radial direction than in the prior art, it moves between the two shown positions more quickly and therefore less leakage occurs.
- one or both of the tip seals may have increased aspect ratio of more than 1:1.25.
- the aspect ratio is approximately the same along the full length of the each tip seals, however one or both of the tips seals may have different aspect ratios along their lengths.
- a scroll compressor Whilst a scroll compressor is typically operated for pumping fluid, instead it can operated as a generator for generating electrical energy when pressurized fluid is used to rotate the orbiting scroll relative to the fixed scroll.
- the present invention is intended to cover use of the scroll compressor for pumping and energy generation.
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Abstract
A scroll compressor 10 may include an orbiting scroll having an orbiting scroll wall extending axially from an orbiting scroll plate towards a fixed scroll; a fixed scroll having a fixed scroll wall extending axially from a fixed scroll plate towards the orbiting scroll; and an axially extending drive shaft having an eccentric shaft portion so that rotation of the eccentric shaft portion imparts an orbiting motion to the orbiting scroll relative to the fixed scroll. An axial end portion of the orbiting scroll wall has a first seal for sealing between the orbiting scroll wall and the fixed scroll plate, and an axial end portion of the fixed scroll wall has a second seal for sealing between the fixed scroll wall and the orbiting scroll plate; and the first seal or the second seal has an aspect ratio of axial length to radial width which is 1:1.25 or greater.
Description
- This application is a national stage entry under 35 U.S.C. §371 of PCT Application No. PCT/GB2012/050445, filed Feb. 28, 2012, which claims the benefit of British Application No. 1105297.4, filed Mar. 29, 2011. The entire contents of PCT Application No. PCT/GB2012/050445 and British Patent Application No. 1105297.4 are incorporated herein by reference.
- The present invention relates to a scroll compressor.
- A prior art scroll compressor, or pump, 10 is shown in
FIG. 7 . Thepump 10 comprises apump housing 12 and adrive shaft 14 having aneccentric shaft portion 16. Theshaft 14 is driven by amotor 18 and the eccentric shaft portion is connected to an orbitingscroll 20 so that during use rotation of the shaft imparts an orbiting motion to the orbiting scroll relative to afixed scroll 22 for pumping fluid along a fluid flow path between apump inlet 24 andpump outlet 26 of the compressor. - The
fixed scroll 22 comprises ascroll wall 28 which extends perpendicularly to a generallycircular base plate 30 and has an axial end face, or surface, 29. Theorbiting scroll 20 comprises ascroll wall 34 which extends perpendicularly to a generallycircular base plate 37 and has an axial end face, or surface, 35. The orbitingscroll wall 34 cooperates, or meshes, with the fixedscroll wall 28 during orbiting movement of the orbiting scroll. Relative orbital movement of the scrolls causes a volume of gas to be trapped between the scrolls and pumped from the inlet to the outlet. - A scroll pump may be a dry pump and not lubricated. In this case, in order to prevent back leakage, the space between the
axial ends base plate - An enlarged cross-section through a portion of the
fixed scroll 22 showing thetip seal 36 in more detail is shown inFIG. 6 . Thetip seal 36 has an aspect ratio of axial length to radial width which is 1:1. That is, the radial width of the tip seal is equal to the axial length of the tip seal so that as shown in cross-section inFIG. 6 the tip seal has a square cross-section. Accordingly, the tip seal is relatively stiff in a radial direction. - The tip seal is located in a
channel 38 at the axial end of the fixed scroll wall. There is a small axial gap between an axial end of thetip seal 36 and the base of thechannel 38 so that in use fluid occupying the gap forces the tip seal axially towards thebase plate 37 of the orbiting scroll. Accordingly, the tip seal is supported on a cushion of fluid which serves to urge the seal towards an opposing seal surface. Additionally, and although not shown inFIG. 6 , there is a radial clearance between the tip seal and the inner radial facing surfaces of the channel. During relative orbiting motion of the scrolls, the seal is urged against one inner radial surface for part of its motion and against the other inner radial surface for another part of its motion. As the seal moves between these positions, leakage is increased because there is a leakage path formed from one side of the seal to the other side of the seal. Thetip seal 36 which is relatively stiff in the radial direction changes position in the channel relatively slowly thereby increasing leakage. - The present invention seeks at least to mitigate one or more of the problems associated with the prior art.
- The present invention provides a scroll compressor comprising: an orbiting scroll having an orbiting scroll wall extending axially from an orbiting scroll plate towards a fixed scroll; a fixed scroll having an fixed scroll wall extending axially from a fixed scroll plate towards the orbiting scroll; and an axially extending drive shaft having an eccentric shaft portion so that rotation of the eccentric shaft portion imparts an orbiting motion to the orbiting scroll relative to the fixed scroll; wherein an axial end portion of the orbiting scroll wall has a first seal for sealing between the orbiting scroll wall and the fixed scroll plate, and an axial end portion of the fixed scroll wall has a second seal for sealing between the fixed scroll wall and the orbiting scroll plate; and wherein the first seal or the second seal has an aspect ratio of axial length to radial width which is 1: 1.25 or greater.
- Other preferred and/or optional aspects of the invention are defined in the accompanying claims.
- In order that the present invention may be well understood, an embodiment thereof, which is given by way of example only, will now be described with reference to the accompanying drawings, in which:
-
FIG. 1 shows a section through part of a fixed scroll of a scroll compressor; -
FIGS. 2 and 3 show enlarged views of a tip seal as shown inFIG. 1 in first and second locations in a channel; -
FIGS. 4 and 5 show a plan view of part of a prior art scroll wall and seal and a plan view of part of a scroll wall and seal according to an embodiment; -
FIG. 6 is a section through part of a fixed scroll of a prior art scroll compressor; and -
FIG. 7 shows a schematic diagram of a prior art scroll compressor. - A section through part of a
fixed scroll 50 is shown inFIG. 1 . Thefixed scroll 50 forms part of a scroll compressor embodying the invention which is similar in construction and operation to the prior art scroll compressor shown inFIG. 7 , except for those aspects shown inFIGS. 1 to 5 and described below. For the sake of brevity therefore, the structure and operation of the whole scroll compressor will not be described again in detail. - The
fixed scroll 50 shown inFIG. 1 comprises afixed scroll plate 52 and afixed scroll wall 54 extending generally perpendicularly therefrom typically in the form of an involute. Alternatively, in scroll pumps which are multi-start, the scroll wall may form an involute over only a portion of its length, usually its radially inner portion. The axial end of the fixed scroll wall comprises achannel 56 in which atip seal 58 is located for sealing against an orbitingscroll 60 shown inFIGS. 2 and 3 . - The description herein refers to the tip seal of the fixed scroll. It will be appreciated however that additionally or alternatively a similar tip seal arrangement may be provided for the orbiting scroll.
- When the tip seal is installed, the
tip seal 58 has an aspect ratio of axial length to radial width which is greater than 1:1.25. That is, where the ratio is x (axial length):y (radial width), and x equals 1, y is 1.25 or greater. As shown inFIGS. 1 to 3 , the axial length is similar to the length shown inFIG. 4 , howevertip seal 58 is thinner in the radial direction and therefore lighter and more flexible. In the embodiment shown the ratio is 1:1.5 and depending on pumping requirements, the tip seal has an axial extent and radial width in the range from about 1.8 mm and 1.2 mm to 4 mm and 2.6 mm respectively. It will be seen therefore that the aspect ratio may be more than 1:2. - The arrangement shown offers a number of advantages over the prior art. When manufacturing the
tip seal 58 from the materials used currently, the wear rate & tip-seal life (pressure-velocity regime) remains generally unchanged. Additionally,tip seal 58 shows shorter bedding-in or stabilization times. Thetip seal 58 is thinner, and therefore more flexible, in the radial direction; in addition, its sectional area is smaller, making it also more flexible in the axial direction. Therefore it demonstrates better capability of presenting its fullaxial end face 62 against the orbiting scroll. Accordingly, most if not all of the axial face becomes bedded in quickly during initial use. - As the
axial end face 62 occupies relatively less area than the axial end face of the prior art tip seal, less dust is generated due to abrasion against the orbiting scroll during use. As dust generated during use must be periodically removed, less dust generation decreases the cost of ownership. Further, in the prior art where the tip seal is relatively stiff in the radial direction, only a portion or corner of the axial end face may be presented to the orbiting scroll. It will be appreciated that whilst in the embodiment the axial end face is smaller than the axial end face in the prior art, a more flexible seal is better able to present its entire end face to the orbiting scroll whereas in the prior art only a corner of the scroll end face may be presented to the orbiting scroll. -
FIGS. 4 and 5 show respectively a plan view of a portion of a tip seal in a groove of a scroll wall for a prior art arrangement and an arrangement in accordance with an embodiment of the invention. In both Figures, although the scroll wall is spiral, for the sake of explanation the scroll wall has been shown as linear. - In both
FIGS. 4 and 5 , during orbiting motion of ascroll wall scroll walls tip seal - In more detail, when considering the full length of the tip seals 36, 58 at any given time during use of the pump,
first portions inner side 72 of thegroove 74 andsecond portions outer side 80 of the groove. In between first and second portions,intermediate portions inner side 72 and the radiallyouter side 80 of the groove. Fluid can leak across the tip seals at the intermediate portions, since there is a leakage path which extends between the tip seals and the radiallyinner side 72 of the groove, underneath the tip seals and between the tip seals and the radiallyouter side 80 of the groove. That is, at theintermediate portions art tip seal 36 has a larger radial width to axial depth and is therefore relatively stiff in the radial direction. Consequently, the length of theintermediate portions 82 are longer meaning that more leakage occurs. Thetip seal 58 has a smaller radial width to axial depth and is therefore relatively flexible in the radial direction. Consequently, the length of theintermediate portions 84 are shorter meaning that less leakage occurs. - A further advantage of the present embodiment is that the space occupied by the tip seal is smaller in the radial direction and therefore scroll wall thickness is reduced. Accordingly, as shown in
FIG. 1 , six wraps are shown whereas inFIG. 6 only five wraps are shown. Therefore, for a pump of any given size, the present embodiment allows increased pumping capability because more wraps equates to a longer pumping path between inlet and exhaust, which increases compression. Alternatively the embodiment allows similar pumping capability in a smaller pump. In this latter regard, a pump which occupies less volume than the prior art is generally less expensive to manufacture as it requires less material and occupies a smaller foot-print when in use. -
FIGS. 2 and 3 show the radial clearance R between a portion oftip seal 58 and theradial sides groove 74. The clearance has been exaggerated in the Figures for the purposes of explanation. The tip-seal is pressure-loaded against thecounter-face 62 of the orbitingscroll 60 by the gas that occupies the space G underneath the seal. The seal is urged against the sides of the channel by a combination of pressure differential in the radial direction and friction against the counter-face as the orbiting scroll orbits. - As described above, at different points along the length of a single tip-
seal 58, the seal is located in the position shown in eitherFIG. 2 or 3, or is in the process of moving between the two shown positions. That is, thefirst portions 70 of thetip seal 58 are located at the radiallyinner side 72 of the channel inFIG. 2 and thesecond portions 78 of the tip seal are located at the radiallyouter side 80 of the channel inFIG. 3 . When the tip seal is between the two shown positions a seepage path is formed across the tip seal causing leakage. The seepage path extends along one radial face of the tip seal, across gap G and along an opposing radial face of the tip seal. Astip seal 58 is more flexible in the radial direction than in the prior art, it moves between the two shown positions more quickly and therefore less leakage occurs. - As indicated above, one or both of the tip seals may have increased aspect ratio of more than 1:1.25. Preferably, the aspect ratio is approximately the same along the full length of the each tip seals, however one or both of the tips seals may have different aspect ratios along their lengths.
- Whilst a scroll compressor is typically operated for pumping fluid, instead it can operated as a generator for generating electrical energy when pressurized fluid is used to rotate the orbiting scroll relative to the fixed scroll. The present invention is intended to cover use of the scroll compressor for pumping and energy generation.
Claims (18)
1. A scroll compressor comprising:
an orbiting scroll;
a fixed scroll having a fixed scroll wall extending axially from a fixed scroll plate towards the orbiting scroll, wherein the orbiting scroll has an orbiting scroll wall extending axially from an orbiting scroll plate towards the fixed scroll; and
an axially extending drive shaft having an eccentric shaft portion so that rotation of the eccentric shaft portion imparts an orbiting motion to the orbiting scroll relative to the fixed scroll, wherein an axial end portion of the orbiting scroll wall has a first seal for sealing between the orbiting scroll wall and the fixed scroll plate, and an axial end portion of the fixed scroll wall has a second seal for sealing between the fixed scroll wall and the orbiting scroll plate; and wherein the first seal or the second seal has an aspect ratio of axial length to radial width which is 1:1.25 or greater.
2. The scroll compressor of claim 1 , wherein the aspect ratio of the first seal or the second seal is 1:1.25 or greater over an entire involute from a pump inlet to a pump outlet.
3. The scroll compressor of claim 1 , wherein the first seal has an aspect ratio of axial length to radial width which is 1:1.25 or greater, and wherein the second seal has an aspect ratio of axial length to radial width which is 1:1.25 or greater.
4. The scroll compressor of claim 1 , wherein the aspect ratio is 1:1.5 or greater.
5. The scroll compressor of claim 1 , wherein an axial end portion of the orbiting scroll wall has a channel for locating the first seal, and wherein an axial end portion of the fixed scroll wall has a channel for locating the second seal.
6. A seal for a scroll compressor comprising an orbiting scroll; a fixed scroll having a fixed scroll wall extending axially from a fixed scroll plate towards the orbiting scroll, wherein the orbiting scroll has an orbiting scroll wall extending axially from an orbiting scroll plate towards the fixed scroll; and
an axially extending drive shaft having an eccentric shaft portion so that rotation of the eccentric shaft portion imparts an orbiting motion to the orbiting scroll relative to the fixed scroll, wherein the seal comprises:
an aspect ratio of axial length to radial width which is 1:1.25 or greater, and wherein the seal is configured to extend between the orbiting scroll wall and the fixed scroll plate and form a seal therebetween.
7. The seal of claim 6 , wherein the aspect ratio is 1:1.25 or greater over an entire involute from a pump inlet to a pump outlet.
8. The seal of claim 6 , wherein the aspect ratio is 1:1.5 or greater.
9. The seal of claim 6 , wherein the seal is configured to be located in a channel of an axial end portion of the orbiting scroll wall.
10. A seal for a scroll compressor comprising an orbiting scroll; a fixed scroll having a fixed scroll wall extending axially from a fixed scroll plate towards the orbiting scroll, wherein the orbiting scroll has an orbiting scroll wall extending axially from an orbiting scroll plate towards the fixed scroll; and an axially extending drive shaft having an eccentric shaft portion so that rotation of the eccentric shaft portion imparts an orbiting motion to the orbiting scroll relative to the fixed scroll, wherein the seal comprises:
an aspect ratio of axial length to radial width which is 1:1.25 or greater, and wherein the seal is configured to extend between the fixed scroll wall and the orbiting scroll plate and form a seal therebetween.
11. The seal of claim 10 , wherein the aspect ratio is 1:1.25 or greater over an entire involute from a pump inlet to a pump outlet.
12. The seal of claim 10 , wherein the aspect ratio is 1:1.5 or greater.
13. The seal of claim 10 , wherein the seal is configured to be located in a channel of an axial end portion of the fixed scroll wall.
14. The scroll compressor of claim 2 , wherein the first seal and the second seal have has an aspect ratio of axial length to radial width which is 1:1.25 or greater, and wherein the second seal has an aspect ratio of axial length to radial width which is 1:1.25 or greater.
15. The scroll compressor of claim 2 , wherein the aspect ratio is 1:1.5 or greater.
16. The scroll compressor of claim 2 , wherein an axial end portion of the orbiting scroll wall has a channel for locating the first seal, and wherein an axial end portion of the fixed scroll wall has a channel for locating the second seal.
17. The scroll compressor of claim 3 , wherein an axial end portion of the orbiting scroll wall has a channel for locating the first seal, and wherein an axial end portion of the fixed scroll wall has a channel for locating the second seal.
18. The scroll compressor of claim 4 , wherein an axial end portion of the orbiting scroll wall has a channel for locating the first seal, and wherein an axial end portion of the fixed scroll wall has a channel for locating the second seal.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB1105297.4A GB2489469B (en) | 2011-03-29 | 2011-03-29 | Scroll compressor |
GB1105297.4 | 2011-03-29 | ||
PCT/GB2012/050445 WO2012131317A1 (en) | 2011-03-29 | 2012-02-28 | Scroll compressor |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB2012/050445 A-371-Of-International WO2012131317A1 (en) | 2011-03-29 | 2012-02-28 | Scroll compressor |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/688,677 Continuation US9938975B2 (en) | 2011-03-29 | 2015-04-16 | Scroll compressor including seal with axial length that is greater than radial width |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140017109A1 true US20140017109A1 (en) | 2014-01-16 |
Family
ID=44067585
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/006,596 Abandoned US20140017109A1 (en) | 2011-03-29 | 2012-02-28 | Scroll compressor |
US14/688,677 Active US9938975B2 (en) | 2011-03-29 | 2015-04-16 | Scroll compressor including seal with axial length that is greater than radial width |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/688,677 Active US9938975B2 (en) | 2011-03-29 | 2015-04-16 | Scroll compressor including seal with axial length that is greater than radial width |
Country Status (9)
Country | Link |
---|---|
US (2) | US20140017109A1 (en) |
EP (1) | EP2691652B1 (en) |
JP (1) | JP2014509706A (en) |
KR (1) | KR20140007930A (en) |
CN (1) | CN103502647B (en) |
CA (1) | CA2830142C (en) |
GB (1) | GB2489469B (en) |
TW (1) | TWI605196B (en) |
WO (1) | WO2012131317A1 (en) |
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US9938975B2 (en) | 2011-03-29 | 2018-04-10 | Edwards Limited | Scroll compressor including seal with axial length that is greater than radial width |
WO2021176222A1 (en) * | 2020-03-05 | 2021-09-10 | Edwards Limited | Scroll pump apparatus and method |
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-
2011
- 2011-03-29 GB GB1105297.4A patent/GB2489469B/en active Active
-
2012
- 2012-02-28 WO PCT/GB2012/050445 patent/WO2012131317A1/en active Application Filing
- 2012-02-28 KR KR1020137025445A patent/KR20140007930A/en not_active Application Discontinuation
- 2012-02-28 CA CA2830142A patent/CA2830142C/en active Active
- 2012-02-28 EP EP12707129.8A patent/EP2691652B1/en active Active
- 2012-02-28 US US14/006,596 patent/US20140017109A1/en not_active Abandoned
- 2012-02-28 CN CN201280016160.4A patent/CN103502647B/en not_active Ceased
- 2012-02-28 JP JP2014501710A patent/JP2014509706A/en active Pending
- 2012-03-21 TW TW101109736A patent/TWI605196B/en not_active IP Right Cessation
-
2015
- 2015-04-16 US US14/688,677 patent/US9938975B2/en active Active
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9938975B2 (en) | 2011-03-29 | 2018-04-10 | Edwards Limited | Scroll compressor including seal with axial length that is greater than radial width |
WO2021176222A1 (en) * | 2020-03-05 | 2021-09-10 | Edwards Limited | Scroll pump apparatus and method |
Also Published As
Publication number | Publication date |
---|---|
CA2830142A1 (en) | 2012-10-04 |
GB2489469A (en) | 2012-10-03 |
GB2489469B (en) | 2017-10-18 |
CA2830142C (en) | 2019-05-21 |
WO2012131317A1 (en) | 2012-10-04 |
TW201248016A (en) | 2012-12-01 |
TWI605196B (en) | 2017-11-11 |
JP2014509706A (en) | 2014-04-21 |
CN103502647B (en) | 2016-12-07 |
GB201105297D0 (en) | 2011-05-11 |
US9938975B2 (en) | 2018-04-10 |
CN103502647A (en) | 2014-01-08 |
US20150219101A1 (en) | 2015-08-06 |
EP2691652B1 (en) | 2020-09-23 |
KR20140007930A (en) | 2014-01-20 |
EP2691652A1 (en) | 2014-02-05 |
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