EP0012615A1 - Improvements in scroll type fluid compressor units - Google Patents
Improvements in scroll type fluid compressor units Download PDFInfo
- Publication number
- EP0012615A1 EP0012615A1 EP79302900A EP79302900A EP0012615A1 EP 0012615 A1 EP0012615 A1 EP 0012615A1 EP 79302900 A EP79302900 A EP 79302900A EP 79302900 A EP79302900 A EP 79302900A EP 0012615 A1 EP0012615 A1 EP 0012615A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fluid
- end plate
- orbiting scroll
- affixed
- scroll member
- 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.)
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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
- 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
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
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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
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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
- F04C2230/00—Manufacture
- F04C2230/20—Manufacture essentially without removing material
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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
- F04C2230/00—Manufacture
- F04C2230/40—Heat treatment
- F04C2230/41—Hardening; Annealing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2230/00—Manufacture
- F05B2230/20—Manufacture essentially without removing material
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2230/00—Manufacture
- F05B2230/40—Heat treatment
- F05B2230/41—Hardening; Annealing
Definitions
- This invention relates to scroll type fluid compressor units.
- a scroll type apparatus has been well known in the prior art as disclosed in, for example, U.S. Patent No. 801,182, and others, which comprises two scroll members each having an end plate and a spiroidal or involute spiral element. These scroll members are so maintained angularly and radially offset that their spiral elements interfit to make a plurality of line contacts between their spiral curved surfaces, thereby to seal off and define at least one fluid pocket. The relative orbital motion of these scroll members shifts the line contacts along the spiral curved surfaces and, therefore, the volume of the fluid pocket increases or decreases in dependence on the direction of the orbital motion. Therefore, a scroll type apparatus is suitable for handling fluids or for compressing, expanding or pumping them.
- a scroll type compressor In comparison with conventional compressors of a piston type, a scroll type compressor has some advantages such as less number of parts, continuous compression of fluid and others. But, there have been several problems; primarily sealing of the fluid pocket, wearing of the spiral elements, and inlet and outlet porting.
- the scroll members and other parts can be made of aluminium or aluminium alloy. If the scroll members are made of aluminium or an aluminium alloy, the sealing of the fluid pockets becomes insufficient owing to wearing.
- a scroll type fluid compressor unit including a compressor housing having a fluid inlet port and a fluid outlet port, a fixed scroll member fixedly disposed within said compressor housing and having first end plate means to which first wrap means are affixed, and an orbiting scroll member orbitally disposed within said compressor housing and having second end plate means to which second wrap means are affixed, said first and second wrap means interfitting, being at a predetermined angular relationship, and having a plurality of line contacts so as to define at least one sealed off fluid pocket which moves with reduction in volume thereof upon orbital motion of said orbiting scroll member, thereby to compress the fluid in the pocket, wherein said fixed and orbiting scroll members are each formed of aluminium or an aluminium alloy, and at least one of the fixed and orbiting members has at least the surface of its wrap means and the end surface of its end plate means on which said wrap means are affixed formed of a material having anti-wearing properties.
- One embodiment of the invention is an improved compressor unit of the scroll type which has excellent sealing and anti-wearing properties.
- the dimensional accuracy of the scroll members is readily secured. Friction between the scroll members is reduced.
- One embodiment of the invention is a scroll type fluid compressor unit which includes a compressor housing having a fluid inlet port and a fluid outlet port.
- a fixed scroll member fixedly disposed which comprises first plate means to which first wrap means are affixed.
- An orbiting scroll member is orbitally disposed within the housing and comprises second end plate means to which second wrap means are affixed.
- the first and second wrap means interfit at a predetermined angular relationship to make a plurality of line contacts to define at least one sealed off fluid pocket.
- the fluid pocket moves with reduction of volume thereof by the orbital motion of the orbiting scroll member.
- the fluid in the pocket is thereby compressed.
- the first and second scroll members are made of aluminium or an aluminium alloy.
- One of the scroll members is treated by surface hardening the entire surface of its wrap means and the end surface of its end plate means on which the wrap means are affixed.
- copper plating In order to effect the surface hardening, copper plating, anodic oxidation coating or hard chromium plating may be employed.
- At least one -of scroll members is made of a high silicon aluminium alloy.
- the entire surface of the scroll member has an anti-wearing property because many silicon crystals are dispersed in the surface. Therefore, a surface hardening treatment is not necessary.
- one of scroll members is coated with a polytetrafluoroethylene coating.
- the other scroll member is treated by the surface hardening, as above described.
- the other scroll member is made of a high silicon aluminium alloy, such a surface hardening treatment is not necessary.
- a refrigerant compressor unit 10 of an embodiment shown includes a compressor housing comprising a front end plate 11, a rear end plate 12 and a cylindrical body 13 connecting between those end plates.
- Rear end plate 12 is shown formed integral with the cylindrical body and is provided with a fluid inlet port 14 and a fluid outlet port 15 formed therethrough.
- a drive shaft 17 is rotatably supported by a radial needle bearing 16 in front end plate 11.
- Front end plate 11 has a sleeve portion 18 projecting on the front surface thereof and surrounding drive shaft 17 to define a shaft seal cavity 181. Within the shaft seal cavity, a shaft seal assembly 19 is assembled on drive shaft 17.
- a pulley 20 is rotatably mounted on sleeve portion 18 and is connected with drive shaft 17 to transmit an external drive power source (not shovm) to drive shaft 17 through belt means (not shown) wound around pulley 20.
- a disk rotor 21 is fixedly mounted on an inner end of drive shaft 17 and is born on the inner surface of front end plate 11 through a thrust needle bearing 22 which is disposed concentric with drive shaft 17.
- Disk rotor 21 is provided with a drive pin 23 projecting on the rear surface thereof. Drive pin 23 is radially offset from drive shaft 17 by a predetermined length.
- Reference numerals 24 and 25 represent a pair of interfitting orbiting and fixed scroll members.
- Orbiting scroll member 24 includes an end circular plate 241 and a wrap means or spiral element 242 affixed onto one end surface of the end plate.
- End plate 241 is provided with a boss 243 projecting on the other end surface thereof.
- Drive pin 23 is fitted into boss 243 with a radial needle bearing 26 therebetween, so that orbiting scroll member 24 is rotatably supported on drive pin 23.
- a hollow member 27 having a radial flange 271 is fitted onto boss 243 non-rotatably by means of key and keyway connection.
- Radial flange 271 is supported on the rear end surface of disk rotor 21 by a thrust needle bearing 28 which is disposed concentric with drive pin 23.
- the axial length of hollow member 27 is equal to, or more than, the axial length of boss 243, so that the thrust load from orbiting scroll member 24 is supported on front end plate 11 through disk rotor 21. Therefore, the rotation of drive shaft 17 effects the orbital motion of orbiting scroll member 24 together with hollow member 27. Namely, orbiting scroll member 24 moves along a circle of a radius of the length between drive shaft 17 and drive pin 23.
- Means 29 for preventing orbiting scroll member 24 from rotating during the orbital motion is disposed between end plate 241 of orbiting scroll member 24 and radial flange 271 of hollow member 27.
- hollow member 27 comprises a cylindrical portion 272 having. a rectangular outer contour, on which a rectangular slider member 291 is fitted slidable in a radial direction.
- Rectangular slider member 291 has a rectangular hole with one pair of parallel sides equal to one pair of parallel sides of the outer rectangle of cylindrical portion 272 and with the other pair of parallel sides longer than the other pair of sides of rectangular cylindrical portion 272 by at least twice length between drive shaft 27 and drive pin 23. Accordingly, slider member 291 is slidable on hollow member 27 in a radial direction along the longer parallel sides of the rectangular hole.
- Slider member 291 is also fitted into a ring like member 292 which is non-rotatably fixed on the inner surface of cylindrical body 13 of the compressor housing by key and keyway connection (shown at 293 in Fig. 2).
- the central hole of ring like member 292 is a rectangular hole with one pair of parallel sides equal to one pair of parallel sides of the outer rectangle of slider member 291 and with the other pair of parallel sides longer than the other parallel sides of the same outer rectangle by at least twice length between drive shaft 17 and drive pin 23, so that slider member 291 may be slidable within ring like member 292 in a radial direction perpendicular to the slide direction of it on hollow member 27.
- hollow member 27 is permitted to move in two radial directions perpendicular to one another and, therefore, moves along a circle as a result of movement in the two radial directions but is prevented fr,om rotation. Therefore, the eccentric movement of drive pin 23 by the rotation of drive shaft 17 effects the orbital motion of orbiting scroll member 24 together with hollow member 27 without rotation.
- the ring like member has a central hole permitting hollow member to axially pass therethrough and is formed with a depression in an end surface for receiving and slidably guide slider member 291.
- This construction of the ring like member permits the ring like member itself to be thin.
- the other fixed scroll member 25 also comprises an end circular plate 251 and a wrap means or spiral element 252 affixed on one end surface of the end plate.
- End plate 251 is provided with a hole or a discharge port 253 formed at a position corresponding to the center of the spiral elements, and with an annular projection 254 on the rear end surface around discharge port 253.
- Rear end plate 12 is provided with an annular projection 121 on the inner surface thereof around outlet port 15.
- the outer radius of annular projection 121 is selected slightly shorter than the inner radius of annular projection 254.
- Annular projection 121 is cut away along the outer edge of the projecting end to define an annular recess 122.
- An annular elastic material for example, a rubber ring 30 is fitted into annular recess 122 and is compressedly held between interfitted annular projections 121 and 254, so that fixed scroll member 25 is elastically supported on annular projection 121 of the rear end plate.
- Rubber ring 30 serves as a seal for sealing off a chamber 31 defined by annular projections 121 and 254 from the interior space 131 of the compressor housing. Chamber 31 connects between outlet port 15 and discharge port of fixed scroll member 25.
- End plate 251 of fixed scroll member 25 is formed with a plurality of cut away portions 255 at its rear peripheral edge.
- a plurality of projections 132 are formed on the inner surface of cylindrical body 13 of the compressor housing and are mated i 4 to ' cut away portions 255, so that fixed scroll member 25 is non-rotatably disposed within the compressor housing. Gaps 32 is maintained between the inner wall of cylindrical body 13 and the peripheral end of fixed scroll member 25, and, therefore, a chamber portion 33 surrounding annular projections 121 and 254 does not form a sealed off chamber within interior space 131 of the compressor housing. Chamber portion 33 communicates with inlet port 14.
- the introduced fluid is taken into fluid pockets 1 and 2 (which are shown at dotted regions) which are defined by line contacts between orbiting spiral element 242 and fixed spiral element 252, as shown in Fig. 3a.
- the line contacts shift by the orbital motion of orbiting spiral element 242 and, therefore, fluid pockets 1 and 2 angularly and radially move toward the center of spiral elements and decrease their volume, as shown in.Figs. 3b-3d. Therefore, the fluid in each pocket is compressed.
- fluid is again taken into new formed fluid pockets 1 and 2, while old pockets connected together to form a reduced pocket and the already taken and compressed fluid is discharged from the pocket through discharge port 253.
- disk rotor 21 fixedly mounted on drive shaft 17 is supported through thrust bearing 22 on front end plate 11, drive shaft 17 is securely and non-vibratingly supported by the use of a single needle bearing as a radial bearing.
- annular elastic material 30, fixed and orbiting scroll members 25 and 24, rotation preventing means 29, hollow member 27, bearings 26 and 28, and a pre- assembly of drive pin 23, disk rotor 21, bearings 16 and 22, drive shaft 17 and front end plate 11, are inserted in this order into cylindrical body 13 having rear end plate 12, and the compressor is completed by securing front end plate 11 onto cylindrical body 13 by bolt means 34.
- the radial sealing force at each line contact between fixed and orbiting spiral elements 252 and 242 is determined by the radius of the orbital motion of orbiting scroll member 24 or the offset length between drive shaft 17 and drive pin 23, and the pitch and thickness of each of fixed and orbiting spiral elements 252 and 242.
- the distance between drive shaft 17 and drive pin 23 is preferably selected slightly larger than the half of the dimensional difference between the pitch of each spiral element and the total dimension..of thickness of fixed and orbiting spiral elements.
- both scroll members 24 and 25 are made of aluminum or aluminum alloy by forging, casting or die casting, to make the compressor unit light.
- aluminum alloy of No. 6051 in JIS (Japanese Industrial Standards) H 4140, which comprises by weight 0.40-0.8 % Si, up to 0.7 % Fe, 0.15-0.40 % Cu, up to 0.15 % Mn, 0.8-1.2 % Mg, 0.04-0.35 % Cr, up to 0.25 % Zn, up to 0.15 % Ti, and the balance essentially A1, is preferably used.
- JIS Japanese Industrial Standards
- aluminum alloy of AC2A by JIS, H 5202 which comprises 3.5-4.5 % Cu, 4.0-5.0 % Si, up to 0.2 % Mg, up to 0.5 % Zn, up to 0.8 % Fe, up to 0.5 % Mn, up to 0.2 % Ti and the balance of Al, is preferably used.
- aluminum alloy of ADC 10 in JIS H 5302 (which comprises 2.0-4.0 % Cu, 7.5-9.5 % Si, up to 0.3 % Mg, up to 1.0 % Zn, up to 1.3 % Fe, up to 0.5 % Mn, up to 0.5 % Ni, up to 0.3 % Sn and the balance of Al), or ADC 12 in JIS H 5302 (which comprises 1.5-3.5 % Cu, 9.6-12.0 % Si, up to 0.3 % Mg, up to 1.0 % Zn, up to 1.3 % Fe, up to 0.5 % Mn, up to 0.5 % Ni, up to 0.3 % Sn and the balance of Al) is preferably used.
- At least one of scroll members of aluminum or aluminum alloy is treated by surface hardening at its at least surface area in slidingly contact with one another, in this invention.
- orbiting scroll member 24 is treated by surface hardening as shown at 35.
- hard chromium plating, copper plating, and anodic oxidation coating can be selectively used. Since these treatments are well known per se in the prior art of aluminum and aluminum alloy surface treating technique, the description as to the concrete processes for producing such surface hardened coatings on to aluminum or aluminum alloy scroll members is omitted for the purpose of simplification of the description.
- surface hardened coating 35 such as plated hard chromium coating, plated copper coating, or anodic oxidation coating on orbiting scroll member 24, establishes a reduced friction at contact portions between both scroll members 24 and 25. Therefore, not only orbiting scroll member 24 but also fixed scroll member 25 are protected from wearing due to sliding contact therebetween, so that the sealing of fluid pockets is maintained during long use.
- Such a surface hardening treatment may be performed onto not orbiting scroll member 24 but fixed scroll member 25.
- the application onto both scroll members is also preferable.
- scroll members is made of high silicon aluminum alloy or anti-wearing aluminum alloy including high silicon such as about 12-25 wt%, such surface hardening treatment is not necessary.
- the dimensional accuracy is obtained by machining.
- the machined surface is subjected by exposure of many silicon crystals, so that the surface has an anti-wearing property.
- Anti-wearing aluminum alloy like this is known as disclosed in U.S. Patent No. 3,514,286.
- a polytetrafluoro- ethylene coating may be used onto the scroll member as shown in Fig. 4.
- fixed scroll member 25 is coated by a surface hardening coating 36 similar to the coating 35 in Fig. 1, and orbiting scroll member 24 is coated by a polytetrafluoroethylene coating 37.
- the surface hardening coating is not necessary.
- a scroll type compressor. unit is obtained according to this invention, which is light and wherein the sealing of fluid pockets between both scroll members is maintained for a long time use. Furthermore, since scroll members are made light, dynamic unbalance is reduced. Moreover, the dimensional accuracy of scroll members can be readily obtained so that the sealing of fluid pockets is further secured.
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Abstract
A scroll type fluid compressor unit wherein, to lighten the unit, orbiting and fixed scroll members are made of aluminium or aluminium alloy. At least one of the scroll members (24) is subjected to surface hardening (35) by copper plating, hard chromium plating or anodic oxidation to reduce wear due to sliding contact between the scroll members. The sealing of fluid pockets between the scroll members is thus maintained during long use of the compressor unit. A surface hardening coating may be applied to one of scroll members and the other scroll member may be coated by a polytetrafluoroethylene coating. In this arrangement, the sliding friction between both scroll members is further reduced.
In order to avoid a surface hardening treatment, at least one of scroll members may be made of anti-wearing aluminium alloy which includes, by weight. 12-25% Si. The scroll member made of such an anti-wearing aluminium alloy is machined to obtain a desired dimensional accuracy and the machined surface, owing to the exposure of many silicon crystals, has a surface anti-wearing property.
Description
- This invention relates to scroll type fluid compressor units.
- A scroll type apparatus has been well known in the prior art as disclosed in, for example, U.S. Patent No. 801,182, and others, which comprises two scroll members each having an end plate and a spiroidal or involute spiral element. These scroll members are so maintained angularly and radially offset that their spiral elements interfit to make a plurality of line contacts between their spiral curved surfaces, thereby to seal off and define at least one fluid pocket. The relative orbital motion of these scroll members shifts the line contacts along the spiral curved surfaces and, therefore, the volume of the fluid pocket increases or decreases in dependence on the direction of the orbital motion. Therefore, a scroll type apparatus is suitable for handling fluids or for compressing, expanding or pumping them.
- In comparison with conventional compressors of a piston type, a scroll type compressor has some advantages such as less number of parts, continuous compression of fluid and others. But, there have been several problems; primarily sealing of the fluid pocket, wearing of the spiral elements, and inlet and outlet porting.
- Although there have been many patents, for example, U.S. Patents Nos. 3,884,599, 3,924,977, 3,994,633, 3,994,635, and 3,994,636 in order to resolve these and other problems, the resultant compressor is complicated in construction and in production. Specifically, the problems of wearing of the scroll members and of friction between the scroll members are not resolved sufficiently.
- Since a compressor of this type is compact and relatively light, it is advantageously used for a refrigerant compressor of an air conditioning system for an automobile. In such applications, since the compressor is desirably light, the scroll members and other parts can be made of aluminium or aluminium alloy. If the scroll members are made of aluminium or an aluminium alloy, the sealing of the fluid pockets becomes insufficient owing to wearing.
- According to the present invention there is provided a scroll type fluid compressor unit including a compressor housing having a fluid inlet port and a fluid outlet port, a fixed scroll member fixedly disposed within said compressor housing and having first end plate means to which first wrap means are affixed, and an orbiting scroll member orbitally disposed within said compressor housing and having second end plate means to which second wrap means are affixed, said first and second wrap means interfitting, being at a predetermined angular relationship, and having a plurality of line contacts so as to define at least one sealed off fluid pocket which moves with reduction in volume thereof upon orbital motion of said orbiting scroll member, thereby to compress the fluid in the pocket, wherein said fixed and orbiting scroll members are each formed of aluminium or an aluminium alloy, and at least one of the fixed and orbiting members has at least the surface of its wrap means and the end surface of its end plate means on which said wrap means are affixed formed of a material having anti-wearing properties.
- One embodiment of the invention is an improved compressor unit of the scroll type which has excellent sealing and anti-wearing properties. The dimensional accuracy of the scroll members is readily secured. Friction between the scroll members is reduced.
- One embodiment of the invention is a scroll type fluid compressor unit which includes a compressor housing having a fluid inlet port and a fluid outlet port. Within the housing, a fixed scroll member fixedly disposed which comprises first plate means to which first wrap means are affixed. An orbiting scroll member is orbitally disposed within the housing and comprises second end plate means to which second wrap means are affixed. The first and second wrap means interfit at a predetermined angular relationship to make a plurality of line contacts to define at least one sealed off fluid pocket. The fluid pocket moves with reduction of volume thereof by the orbital motion of the orbiting scroll member. The fluid in the pocket is thereby compressed. The first and second scroll members are made of aluminium or an aluminium alloy. One of the scroll members is treated by surface hardening the entire surface of its wrap means and the end surface of its end plate means on which the wrap means are affixed.
- In order to effect the surface hardening, copper plating, anodic oxidation coating or hard chromium plating may be employed.
- In a further embodiment of the invention, at least one -of scroll members is made of a high silicon aluminium alloy. The entire surface of the scroll member has an anti-wearing property because many silicon crystals are dispersed in the surface. Therefore, a surface hardening treatment is not necessary.
- In a further embodiment of the invention, one of scroll members is coated with a polytetrafluoroethylene coating. The other scroll member is treated by the surface hardening, as above described. Alternatively, if the other scroll member is made of a high silicon aluminium alloy, such a surface hardening treatment is not necessary.
- The invention will now be described, by way of example, y with reference to the accompanying drawings, in which:-
-
- Fig. 1 shows a vertical sectional view of a compressor unit of a scroll type according to an embodiment of this invention;
- Fig. 2 is a cross-sectional view taken along line II-II in Fig. 1;
- Figs. 3a-3d are schematic views for illustrating movement of interfitting spiral elements to compress fluid; and
- Fig. 4 is a vertical sectional view of another embodiment of this invention.
- Referring to Fig. 1, a
refrigerant compressor unit 10 of an embodiment shown includes a compressor housing comprising a front end plate 11, arear end plate 12 and acylindrical body 13 connecting between those end plates.Rear end plate 12 is shown formed integral with the cylindrical body and is provided with afluid inlet port 14 and afluid outlet port 15 formed therethrough. Adrive shaft 17 is rotatably supported by a radial needle bearing 16 in front end plate 11. Front end plate 11 has asleeve portion 18 projecting on the front surface thereof and surroundingdrive shaft 17 to define ashaft seal cavity 181. Within the shaft seal cavity, ashaft seal assembly 19 is assembled ondrive shaft 17. Apulley 20 is rotatably mounted onsleeve portion 18 and is connected withdrive shaft 17 to transmit an external drive power source (not shovm) to driveshaft 17 through belt means (not shown) wound aroundpulley 20. Adisk rotor 21 is fixedly mounted on an inner end ofdrive shaft 17 and is born on the inner surface of front end plate 11 through a thrust needle bearing 22 which is disposed concentric withdrive shaft 17.Disk rotor 21 is provided with adrive pin 23 projecting on the rear surface thereof.Drive pin 23 is radially offset fromdrive shaft 17 by a predetermined length. -
Reference numerals Orbiting scroll member 24 includes an endcircular plate 241 and a wrap means orspiral element 242 affixed onto one end surface of the end plate.End plate 241 is provided with aboss 243 projecting on the other end surface thereof.Drive pin 23 is fitted intoboss 243 with a radial needle bearing 26 therebetween, so that orbitingscroll member 24 is rotatably supported ondrive pin 23. - A
hollow member 27 having aradial flange 271 is fitted ontoboss 243 non-rotatably by means of key and keyway connection.Radial flange 271 is supported on the rear end surface ofdisk rotor 21 by a thrust needle bearing 28 which is disposed concentric withdrive pin 23. The axial length ofhollow member 27 is equal to, or more than, the axial length ofboss 243, so that the thrust load from orbitingscroll member 24 is supported on front end plate 11 throughdisk rotor 21. Therefore, the rotation ofdrive shaft 17 effects the orbital motion of orbitingscroll member 24 together withhollow member 27. Namely, orbitingscroll member 24 moves along a circle of a radius of the length betweendrive shaft 17 and drivepin 23. - Means 29 for preventing orbiting
scroll member 24 from rotating during the orbital motion is disposed betweenend plate 241 of orbitingscroll member 24 andradial flange 271 ofhollow member 27. - Referring to Fig. 2 in addition to Fig. 1,
hollow member 27 comprises acylindrical portion 272 having. a rectangular outer contour, on which arectangular slider member 291 is fitted slidable in a radial direction.Rectangular slider member 291 has a rectangular hole with one pair of parallel sides equal to one pair of parallel sides of the outer rectangle ofcylindrical portion 272 and with the other pair of parallel sides longer than the other pair of sides of rectangularcylindrical portion 272 by at least twice length betweendrive shaft 27 and drivepin 23. Accordingly,slider member 291 is slidable onhollow member 27 in a radial direction along the longer parallel sides of the rectangular hole.Slider member 291 is also fitted into a ring likemember 292 which is non-rotatably fixed on the inner surface ofcylindrical body 13 of the compressor housing by key and keyway connection (shown at 293 in Fig. 2). The central hole of ring likemember 292 is a rectangular hole with one pair of parallel sides equal to one pair of parallel sides of the outer rectangle ofslider member 291 and with the other pair of parallel sides longer than the other parallel sides of the same outer rectangle by at least twice length betweendrive shaft 17 and drivepin 23, so thatslider member 291 may be slidable within ring likemember 292 in a radial direction perpendicular to the slide direction of it onhollow member 27. - Accordingly,
hollow member 27 is permitted to move in two radial directions perpendicular to one another and, therefore, moves along a circle as a result of movement in the two radial directions but is prevented fr,om rotation. Therefore, the eccentric movement ofdrive pin 23 by the rotation ofdrive shaft 17 effects the orbital motion of orbitingscroll member 24 together withhollow member 27 without rotation. - In another construction of ring like
member 292, the ring like member has a central hole permitting hollow member to axially pass therethrough and is formed with a depression in an end surface for receiving and slidablyguide slider member 291. This construction of the ring like member permits the ring like member itself to be thin. - The other
fixed scroll member 25 also comprises an endcircular plate 251 and a wrap means orspiral element 252 affixed on one end surface of the end plate.End plate 251 is provided with a hole or adischarge port 253 formed at a position corresponding to the center of the spiral elements, and with anannular projection 254 on the rear end surface arounddischarge port 253. -
Rear end plate 12 is provided with an annular projection 121 on the inner surface thereof aroundoutlet port 15. The outer radius of annular projection 121 is selected slightly shorter than the inner radius ofannular projection 254. Annular projection 121 is cut away along the outer edge of the projecting end to define anannular recess 122. An annular elastic material, for example, arubber ring 30 is fitted intoannular recess 122 and is compressedly held between interfittedannular projections 121 and 254, so that fixedscroll member 25 is elastically supported on annular projection 121 of the rear end plate.Rubber ring 30 serves as a seal for sealing off achamber 31 defined byannular projections 121 and 254 from theinterior space 131 of the compressor housing.Chamber 31 connects betweenoutlet port 15 and discharge port offixed scroll member 25. -
End plate 251 of fixedscroll member 25 is formed with a plurality of cut awayportions 255 at its rear peripheral edge. A plurality ofprojections 132 are formed on the inner surface ofcylindrical body 13 of the compressor housing and are mated i4to'cut awayportions 255, so that fixedscroll member 25 is non-rotatably disposed within the compressor housing.Gaps 32 is maintained between the inner wall ofcylindrical body 13 and the peripheral end of fixedscroll member 25, and, therefore, achamber portion 33 surroundingannular projections 121 and 254 does not form a sealed off chamber withininterior space 131 of the compressor housing.Chamber portion 33 communicates withinlet port 14. - In operation, when
drive shaft 17 is rotated by an external drive power source (not shown) throughpulley 20,drive pin 23 moves eccentrically to effect the orbital motion of orbitingscroll member 24. The rotation of orbitingscroll member 24 is prevented byrotation preventing means 29. The orbital motion of orbitingscroll member 24 compresses the fluid introduced intointerior space 131 throughinlet port 14,chamber portion 33, andgaps 32, and the compressed gas is discharged-fromoutlet port 15 throughdischarge port 253 andchamber 31. - Referring to Figs. 3a-3d, the introduced fluid is taken into
fluid pockets 1 and 2 (which are shown at dotted regions) which are defined by line contacts between orbitingspiral element 242 and fixedspiral element 252, as shown in Fig. 3a. The line contacts shift by the orbital motion of orbitingspiral element 242 and, therefore,fluid pockets fluid pockets discharge port 253. - In the arrangement as above described, since fixed
scroll member 25 is axially urged toward orbitingscroll member 24 by the restoring force ofcompressed rubber ring 30, sealing betweenend plate 241 of orbitingscroll member 24 and the axial end of fixedspiral element 252, and betweenend plate 251 of fixedscroll member 25 and the axial end of orbitingspiral element 242 is secured. And the sealing is reinforced by a fluid pressure discharged intochamber 31. The axial load for securing the sealing is supported ondisk rotor 21 through orbitingscroll member 24,hollow member 27 havingradial flange 271, and thrustbearing 28, and is further supported throughdisk rotor 21 and thrust bearing 22 on front end plate 11 which is secured onto the front end ofcylindrical body 13 of compressor housing. Therefore, any deflection of moving parts is prevented during operation of the compressor, so that the vibration of compressor and abnormal wearing of each parts may be prevented. Sincedisk rotor 21 fixedly mounted ondrive shaft 17 is supported through thrust bearing 22 on front end plate 11,drive shaft 17 is securely and non-vibratingly supported by the use of a single needle bearing as a radial bearing. - In the arrangement of the compressor as above described, assembling operation of the compressor is very simple; annular
elastic material 30, fixed and orbitingscroll members hollow member 27,bearings drive pin 23,disk rotor 21,bearings drive shaft 17 and front end plate 11, are inserted in this order intocylindrical body 13 havingrear end plate 12, and the compressor is completed by securing front end plate 11 ontocylindrical body 13 by bolt means 34. - The above described compressor arrangement is proposed in a copending patent application by the same applicant filed on September 3, 1979 under Application No. 79301808.6.
- Considering sealing of fluid pockets in the compressor as above described, the radial sealing force at each line contact between fixed and orbiting
spiral elements scroll member 24 or the offset length betweendrive shaft 17 and drivepin 23, and the pitch and thickness of each of fixed and orbitingspiral elements drive shaft 17 and drivepin 23 is preferably selected slightly larger than the half of the dimensional difference between the pitch of each spiral element and the total dimension..of thickness of fixed and orbiting spiral elements. This arrangement is permitted by the fact thatfixed scroll member 25 is radially movably supported bycompressed rubber ring 30. The sufficient radial sealing is established, even at the initial use of the compressor as assembled. - The reasonable radial sealing is completed after contact surfaces of both spiral elements wear by friction during use to get to fit to one another.
- According to this invention, both
scroll members - In case of forging, for example, aluminum alloy of No. 6051, in JIS (Japanese Industrial Standards) H 4140, which comprises by weight 0.40-0.8 % Si, up to 0.7 % Fe, 0.15-0.40 % Cu, up to 0.15 % Mn, 0.8-1.2 % Mg, 0.04-0.35 % Cr, up to 0.25 % Zn, up to 0.15 % Ti, and the balance essentially A1, is preferably used.
- In case of casting, aluminum alloy of AC2A by JIS, H 5202 which comprises 3.5-4.5 % Cu, 4.0-5.0 % Si, up to 0.2 % Mg, up to 0.5 % Zn, up to 0.8 % Fe, up to 0.5 % Mn, up to 0.2 % Ti and the balance of Al, is preferably used.
- In case of die casting, aluminum alloy of
ADC 10 in JIS H 5302 (which comprises 2.0-4.0 % Cu, 7.5-9.5 % Si, up to 0.3 % Mg, up to 1.0 % Zn, up to 1.3 % Fe, up to 0.5 % Mn, up to 0.5 % Ni, up to 0.3 % Sn and the balance of Al), orADC 12 in JIS H 5302 (which comprises 1.5-3.5 % Cu, 9.6-12.0 % Si, up to 0.3 % Mg, up to 1.0 % Zn, up to 1.3 % Fe, up to 0.5 % Mn, up to 0.5 % Ni, up to 0.3 % Sn and the balance of Al) is preferably used. - Since aluminum and aluminum alloy tend to wear by friction, the sealing of fluid pockets becomes imperfect by the use of the compressor.
- Therefore, at least one of scroll members of aluminum or aluminum alloy is treated by surface hardening at its at least surface area in slidingly contact with one another, in this invention.
- In the embodiment of Figs. 1 and 2, orbiting
scroll member 24 is treated by surface hardening as shown at 35. - As the surface hardening treatment, hard chromium plating, copper plating, and anodic oxidation coating can be selectively used. Since these treatments are well known per se in the prior art of aluminum and aluminum alloy surface treating technique, the description as to the concrete processes for producing such surface hardened coatings on to aluminum or aluminum alloy scroll members is omitted for the purpose of simplification of the description.
- The existence of surface hardened
coating 35, such as plated hard chromium coating, plated copper coating, or anodic oxidation coating on orbitingscroll member 24, establishes a reduced friction at contact portions between bothscroll members scroll member 24 but also fixedscroll member 25 are protected from wearing due to sliding contact therebetween, so that the sealing of fluid pockets is maintained during long use. - Furthermore, since the thickness of the coating can be controlled in above described surface hardening treatments, as is well known, the dimensional accuracy of orbiting
scroll member 24 can be readily obtained. - Such a surface hardening treatment may be performed onto not orbiting
scroll member 24 but fixedscroll member 25. The application onto both scroll members is also preferable. - If at least one of scroll members is made of high silicon aluminum alloy or anti-wearing aluminum alloy including high silicon such as about 12-25 wt%, such surface hardening treatment is not necessary. The dimensional accuracy is obtained by machining. The machined surface is subjected by exposure of many silicon crystals, so that the surface has an anti-wearing property.
- Anti-wearing aluminum alloy like this is known as disclosed in U.S. Patent No. 3,514,286.
- If the above mentioned surface hardening treatment is not applied onto one of scroll members, a polytetrafluoro- ethylene coating may be used onto the scroll member as shown in Fig. 4.
- Referring to Fig. 4, fixed
scroll member 25 is coated by asurface hardening coating 36 similar to thecoating 35 in Fig. 1, and orbitingscroll member 24 is coated by apolytetrafluoroethylene coating 37. - It is natural that the surface hardening coating and the polytetrafluoroethylene coating are applied onto orbiting
scroll member 24 and fixedscroll member 25, respectively. - The employment of the surface hardening coating and the polytetrafluoroethylene coating further reduces the contacting friction between both scroll members. Thus, the sealing of fluid pockets can be maintained during a longer time period.
- If the anti-wearing aluminum alloy as above described is used for at least one of scroll members, the surface hardening coating is not necessary.
- As above described, a scroll type compressor. unit is obtained according to this invention, which is light and wherein the sealing of fluid pockets between both scroll members is maintained for a long time use. Furthermore, since scroll members are made light, dynamic unbalance is reduced. Moreover, the dimensional accuracy of scroll members can be readily obtained so that the sealing of fluid pockets is further secured.
- This invention has been described in connection with preferred embodiments, but these are merely for example only and this invention is not restricted thereto. It will be easily understood by those skilled in the art that the other variations and modifications can be easily made within the scope of this invention.
Claims (11)
1. A scroll type fluid compressor unit including a compressor housing having a fluid inlet port and a fluid outlet port, a fixed scroll member fixedly disposed within said compressor housing and having first end plate means to which first wrap means are affixed, and an orbiting scroll member orbitally disposed within said compressor housing and having second end plate means to which second wrap means are affixed, said first and second wrap means interfitting being at a predetermined angular relationship, and having a plurality of line contacts so as to define at least one sealed off fluid pocket which moves with a reduction in volume thereof upon orbital motion of said orbiting scroll member, thereby to compress the fluid in the pocket, wherein said fixed and orbiting scroll members are each formed of aluminium or an aluminium alloy, and at least one of the fixed and orbiting members has at least the surface of its wrap means and the end surface of its end plate means on which said wrap means are affixed formed of a material having anti-wearing properties.
2. A scroll type fluid compressor unit including a compressor housing having a fluid inlet port and a fluid outlet port, a fixed scroll member fixedly disposed within said compressor housing and having first end plate means to which first wrap means are affixed, and an orbiting scroll member orbitally disposed within said compressor housing and having second end plate means to which second wrap means are affixed, said first and second wrap means interfitting at a predetermined ' angular relationship to make a plurality of line contacts to define at least one sealed off fluid pocket which moves with reduction of volume thereof by the orbital motion of said orbiting scroll member, thereby to compress the fluid in the pocket, wherein said fixed and orbiting scroll members are each formed of aluminium or an aluminium alloy, and at least one of said fixed and orbiting scroll members has the surface of its wrap means and the end surface of its end plate means on which said wrap means are affixed surface hardened.
3. A unit as claimed in Claim 2, wherein said surfaces have been surface hardened by copper plating.
4. A unit as claimed in Claim 2, wherein said surfaces have been surface hardened by anodic oxidation coating.
5. A unit as claimed in Claim 2, wherein said surfaces have been surface hardened by hard chromium plating.
6. A scroll type fluid compressor unit including a compressor housing having a fluid inlet port and a fluid outlet port, a fixed scroll member fixedly disposed within said compressor housing and having first end plate means to which first wrap means are affixed, and an orbiting scroll member orbitally disposed within said compressor housing and having second end plate means to which second wrap means are affixed, said first and second wrap means interfitting, being at a predetermined angular relationship and having a plurality of line contacts so as to define at least one sealed off fluid pocket which moves with a reduction in volume thereof upon orbital motion of said orbiting scroll member, thereby to compress the fluid in the pocket, wherein said fixed and orbiting scroll members are formed of an aluminium alloy, and at least one of said fixed and orbiting scroll members is formed of a high silicon aluminium alloy.
7. A scroll type fluid compressor unit including a compressor housing having a fluid inlet port and a fluid outlet port, a fixed scroll member fixedly disposed within said compressor housing and having first end plate means to which first wrap means are affixed, and an orbiting scroll member orbitally disposed within said compressor housing and having second end plate means to which second wrap means are affixed, said first and second wrap means interfitting, being at a predetermined angular relationship, and having a plurality of line contacts so as to define at least one sealed off fluid pocket which moves with a reduction in volume thereof upon orbital motion of said orbiting scroll member, thereby to compress the fluid in the pocket, wherein said fixed and orbiting scroll members are forced of aluminium alloy, one of said fixed and orbiting scroll members has the surface of its wrap means and the end surface of its end plate on which said wrap means is affixed surface hardened, and the other of said scroll members has a polytetrafluoroethylene coating on the surface of its wrap means and the end surface of its end plate on which said wrap means are affixed.
8. A unit as claimed in Claim 7, wherein said surfaces have been hardened by copper plating.
9. A unit as claimed in Claim 7, wherein said surfaces have been hardened by anodic oxidation coating.
10. A unit as claimed in Claim 7, wherein said surfaces have been hardened by hard chromium plating.
11. A unit as claimed in Claim 6, wherein the other of said scroll members has a polytetrafluoroethylene coating on the surface of its wrap means and the end surface of its end plate on which said wrap means are affixed.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP155590/78 | 1978-12-15 | ||
JP15559178A JPS5581295A (en) | 1978-12-15 | 1978-12-15 | Positive-displacement fluid compressor |
JP155591/78 | 1978-12-15 | ||
JP15559078A JPS5581294A (en) | 1978-12-15 | 1978-12-15 | Positive-displacement fluid compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
EP0012615A1 true EP0012615A1 (en) | 1980-06-25 |
Family
ID=26483544
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP79302900A Withdrawn EP0012615A1 (en) | 1978-12-15 | 1979-12-14 | Improvements in scroll type fluid compressor units |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0012615A1 (en) |
AU (1) | AU5375079A (en) |
Cited By (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0065426A2 (en) * | 1981-05-20 | 1982-11-24 | Sanden Corporation | Scroll manufacturing tool |
EP0066426A2 (en) * | 1981-05-20 | 1982-12-08 | Sanden Corporation | Scroll manufacturing tool |
EP0075053A1 (en) * | 1981-09-22 | 1983-03-30 | Sanden Corporation | Wear-resisting means for scroll-type fluid-displacement apparatuses |
EP0122067A1 (en) * | 1983-03-15 | 1984-10-17 | Sanden Corporation | A scroll type fluid displacement apparatus with surface treated spiral element |
EP0122722A1 (en) * | 1983-03-15 | 1984-10-24 | Sanden Corporation | Axial sealing device for a scroll type fluid displacement apparatus |
DE3402548A1 (en) * | 1984-01-26 | 1985-08-01 | Leybold-Heraeus GmbH, 5000 Köln | Positive displacement machine |
GB2167131A (en) * | 1984-11-19 | 1986-05-21 | Sanden Corp | Scroll-type rotary fluid-machine |
US4645436A (en) * | 1984-11-19 | 1987-02-24 | Sanden Corporation | Scroll type fluid displacement apparatus with improved anti-wear device |
EP0267559A1 (en) * | 1986-11-08 | 1988-05-18 | Wankel GmbH | Rotary piston blower |
EP0286341A2 (en) * | 1987-04-04 | 1988-10-12 | Sanden Corporation | Scroll type compressor |
EP0350790A2 (en) * | 1988-07-08 | 1990-01-17 | Sanden Corporation | Scroll type compressor |
EP0467492A1 (en) * | 1990-07-16 | 1992-01-22 | Mitsubishi Jukogyo Kabushiki Kaisha | Compressor |
DE4404054A1 (en) * | 1993-02-09 | 1994-08-11 | Toyoda Automatic Loom Works | Refrigerant spiral compressor with casing protection devices |
BE1010426A3 (en) * | 1996-07-16 | 1998-07-07 | Atlas Copco Airpower Nv | Method for manufacturing a helical compressor |
US5791886A (en) * | 1995-10-20 | 1998-08-11 | Sanden Corporation | Scroll type fluid displacement apparatus with an axial seal plate |
US6033194A (en) * | 1996-06-24 | 2000-03-07 | Sanden Corporation | Scroll-type fluid displacement apparatus with anti-wear plate mechanism |
GB2548607A (en) * | 2016-03-23 | 2017-09-27 | Edwards Ltd | Scroll pump tip sealing |
US11359628B2 (en) * | 2017-04-28 | 2022-06-14 | Shanghai Highly New Energy Technology Co., Ltd. | Scroll compressor including retaining wall housing electrical machinery mechanism |
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US2519588A (en) * | 1943-12-24 | 1950-08-22 | Borg Warner | Pump housing |
US3552895A (en) * | 1969-05-14 | 1971-01-05 | Lear Siegler Inc | Dry rotary vane pump |
US3888746A (en) * | 1974-01-04 | 1975-06-10 | Ford Motor Co | Method of providing an intermediate steel layer for chrome plating on rotor housings |
FR2272277A1 (en) * | 1974-05-24 | 1975-12-19 | Unus Dei F Lli Rossato V Et S | Rotary-piston air compressor - has sliders made from polyamide with spherical bronze powder charge and molybdenum disulphide |
US3986799A (en) * | 1975-11-03 | 1976-10-19 | Arthur D. Little, Inc. | Fluid-cooled, scroll-type, positive fluid displacement apparatus |
FR2363010A1 (en) * | 1976-08-24 | 1978-03-24 | Bosch Gmbh Robert | FUEL ELECTRIC PUMP |
-
1979
- 1979-12-12 AU AU53750/79A patent/AU5375079A/en not_active Abandoned
- 1979-12-14 EP EP79302900A patent/EP0012615A1/en not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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US2519588A (en) * | 1943-12-24 | 1950-08-22 | Borg Warner | Pump housing |
US3552895A (en) * | 1969-05-14 | 1971-01-05 | Lear Siegler Inc | Dry rotary vane pump |
US3888746A (en) * | 1974-01-04 | 1975-06-10 | Ford Motor Co | Method of providing an intermediate steel layer for chrome plating on rotor housings |
FR2272277A1 (en) * | 1974-05-24 | 1975-12-19 | Unus Dei F Lli Rossato V Et S | Rotary-piston air compressor - has sliders made from polyamide with spherical bronze powder charge and molybdenum disulphide |
US3986799A (en) * | 1975-11-03 | 1976-10-19 | Arthur D. Little, Inc. | Fluid-cooled, scroll-type, positive fluid displacement apparatus |
FR2363010A1 (en) * | 1976-08-24 | 1978-03-24 | Bosch Gmbh Robert | FUEL ELECTRIC PUMP |
Cited By (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0065426A2 (en) * | 1981-05-20 | 1982-11-24 | Sanden Corporation | Scroll manufacturing tool |
EP0066426A2 (en) * | 1981-05-20 | 1982-12-08 | Sanden Corporation | Scroll manufacturing tool |
EP0065426A3 (en) * | 1981-05-20 | 1983-08-17 | Sanden Corporation | Scroll manufacturing tool |
EP0066426A3 (en) * | 1981-05-20 | 1983-08-24 | Sanden Corporation | Scroll manufacturing tool |
EP0075053A1 (en) * | 1981-09-22 | 1983-03-30 | Sanden Corporation | Wear-resisting means for scroll-type fluid-displacement apparatuses |
EP0122722A1 (en) * | 1983-03-15 | 1984-10-24 | Sanden Corporation | Axial sealing device for a scroll type fluid displacement apparatus |
EP0122067A1 (en) * | 1983-03-15 | 1984-10-17 | Sanden Corporation | A scroll type fluid displacement apparatus with surface treated spiral element |
US4540355A (en) * | 1983-03-15 | 1985-09-10 | Sanden Corporation | Axial sealing device for a scroll-type fluid displacement apparatus |
US4956058A (en) * | 1983-03-15 | 1990-09-11 | Sanden Corporation | Scroll type fluid displacement apparatus with surface treated spiral element |
DE3402548A1 (en) * | 1984-01-26 | 1985-08-01 | Leybold-Heraeus GmbH, 5000 Köln | Positive displacement machine |
GB2167131A (en) * | 1984-11-19 | 1986-05-21 | Sanden Corp | Scroll-type rotary fluid-machine |
FR2574866A1 (en) * | 1984-11-19 | 1986-06-20 | Sanden Corp | SPIRAL TYPE FLUID DISPLACEMENT APPARATUS PROVIDED WITH AN ARBOR SUPPORT MECHANISM |
US4645436A (en) * | 1984-11-19 | 1987-02-24 | Sanden Corporation | Scroll type fluid displacement apparatus with improved anti-wear device |
EP0267559A1 (en) * | 1986-11-08 | 1988-05-18 | Wankel GmbH | Rotary piston blower |
EP0286341A3 (en) * | 1987-04-04 | 1989-06-14 | Sanden Corporation | Scroll type compressor |
EP0286341A2 (en) * | 1987-04-04 | 1988-10-12 | Sanden Corporation | Scroll type compressor |
EP0350790A2 (en) * | 1988-07-08 | 1990-01-17 | Sanden Corporation | Scroll type compressor |
EP0350790A3 (en) * | 1988-07-08 | 1990-05-16 | Sanden Corporation | Scroll type compressor |
US5015163A (en) * | 1988-07-08 | 1991-05-14 | Sanden Corporation | Scroll type compressor with radially outer support for fixed end plate |
AU623413B2 (en) * | 1988-07-08 | 1992-05-14 | Sanden Corporation | Scroll type compressor |
EP0467492A1 (en) * | 1990-07-16 | 1992-01-22 | Mitsubishi Jukogyo Kabushiki Kaisha | Compressor |
DE4404054A1 (en) * | 1993-02-09 | 1994-08-11 | Toyoda Automatic Loom Works | Refrigerant spiral compressor with casing protection devices |
US5791886A (en) * | 1995-10-20 | 1998-08-11 | Sanden Corporation | Scroll type fluid displacement apparatus with an axial seal plate |
US6033194A (en) * | 1996-06-24 | 2000-03-07 | Sanden Corporation | Scroll-type fluid displacement apparatus with anti-wear plate mechanism |
BE1010426A3 (en) * | 1996-07-16 | 1998-07-07 | Atlas Copco Airpower Nv | Method for manufacturing a helical compressor |
GB2548607A (en) * | 2016-03-23 | 2017-09-27 | Edwards Ltd | Scroll pump tip sealing |
GB2548607B (en) * | 2016-03-23 | 2020-05-06 | Edwards Ltd | Scroll pump tip sealing |
US11359628B2 (en) * | 2017-04-28 | 2022-06-14 | Shanghai Highly New Energy Technology Co., Ltd. | Scroll compressor including retaining wall housing electrical machinery mechanism |
Also Published As
Publication number | Publication date |
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AU5375079A (en) | 1980-07-10 |
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Inventor name: TERAUCHI, KIYOSHI Inventor name: FUKUSIMA, EIZI |