EP2236829A1 - Versiegelungs-spiralverdichter - Google Patents

Versiegelungs-spiralverdichter Download PDF

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Publication number
EP2236829A1
EP2236829A1 EP09705815A EP09705815A EP2236829A1 EP 2236829 A1 EP2236829 A1 EP 2236829A1 EP 09705815 A EP09705815 A EP 09705815A EP 09705815 A EP09705815 A EP 09705815A EP 2236829 A1 EP2236829 A1 EP 2236829A1
Authority
EP
European Patent Office
Prior art keywords
bearing bracket
scroll compressor
housing
welded
center
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.)
Granted
Application number
EP09705815A
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English (en)
French (fr)
Other versions
EP2236829A4 (de
EP2236829B1 (de
Inventor
Hajime Sato
Yoshiyuki Kimata
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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Publication date
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Publication of EP2236829A1 publication Critical patent/EP2236829A1/de
Publication of EP2236829A4 publication Critical patent/EP2236829A4/de
Application granted granted Critical
Publication of EP2236829B1 publication Critical patent/EP2236829B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F04C2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F04C2230/231—Manufacture essentially without removing material by permanently joining parts together by welding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present invention relates to hermetic scroll compressors in which a sealed housing accommodates a scroll compressor and an electric motor for driving the scroll compressor.
  • a hermetic scroll compressor in which a bearing case is bolted to a bearing bracket to incorporate a scroll compressor therein has a feature that it is not affected by distortion caused by plug welding or caulking, thus making centering easy, though it requires installation of the bearing bracket.
  • a hermetic scroll compressor in which a bearing bracket is directly bonded to the inner circumferential surface of a sealed housing by welding or the like, as shown in Patent Citation 1 and a hermetic scroll compressor in which a sealed housing is divided into upper and lower housings by a bearing bracket disposed therebetween, and the divided upper and lower housings are bonded to the bearing bracket, as shown in Patent Citation 2, have been proposed as examples of the hermetic scroll compressors having the above configuration.
  • Patent Citation 1 Japanese Unexamined Patent Application, Publication No. Hei 5-99168 (see FIG. 1 )
  • Patent Citation 2 Japanese Unexamined Patent Application, Publication No. 2000-97173 (see FIG. 1 )
  • the bearing bracket is bonded to the inner circumferential surface of the sealed housing by welding or the like.
  • the working efficiency is low because the bearing bracket is welded to the inner circumference.
  • the housings divided into the upper and lower housings are bonded to the bearing bracket.
  • Patent Citation 2 does not specifically teach or suggest a bracket structure or a welding structure for easily and efficiently welding the divided housings to the bearing bracket, taking into consideration the working efficiency and the manufacturability, or a configuration utilizing the features achieved by the divided housings. Thus, there are still many problems.
  • the present invention has been made in view of the above-described circumstances, and an object thereof is, when a structure in which a sealed housing is divided by disposing a bearing bracket is employed, to provide a hermetic scroll compressor that can improve the assembly precision, the manufacturability, and the ease of assembly and that can easily realize housings having different diameters according to the necessity.
  • a hermetic scroll compressor of the present invention is a hermetic scroll compressor in which an electric motor is mounted at a lower part in a sealed housing and a scroll compressor driven by the electric motor is mounted at an upper part in the sealed housing.
  • the sealed housing includes a cylindrical center housing that is sealed by a lower housing at the lower end and accommodates the electric motor securely mounted therein, a ring-like bearing bracket provided at the upper end of the center housing, and an upper housing that is provided on the bearing bracket, seals the upper part of the center housing, and accommodates the scroll compressor.
  • the bearing bracket has first and second welded portions provided at an outer circumferential portion thereof, to which ends of the center and upper housings are fitted and to which the housings are welded from the outer circumference side, and a bearing case in which the scroll compressor is incorporated is securely mounted on the top surface of the bearing bracket with bolts.
  • the bearing bracket divides the sealed housing into the center housing accommodating the electric motor and the upper housing accommodating the scroll compressor, finishing of the top surface of the bearing bracket where the bearing case, in which the scroll compressor is incorporated, is securely mounted can be easily performed. That is, it is possible for finishing to be performed after the bearing bracket is welded to the center housing and while the top surface of the bearing bracket is exposed. Thus, it is possible to simplify finishing, such as machining the top surface, and to eliminate the thermal deformation caused by welding. Accordingly, it is possible to increase the assembly precision of the scroll compressor securely mounted on the top surface of the bearing bracket and to improve the manufacturability and ease of assembly thereof.
  • the ends of the center and upper housings are fitted to the first and second welded portions of the bearing bracket and the housings are welded from the outer circumference side, it is possible to simplify the welding operation and to eliminate or simplify the weld bead treatment, thereby improving the manufacturability. Furthermore, because it is possible to make the center and upper housings welded to the first and second welded portions through the bearing bracket have different diameters, the diameters of the center and upper housings can be easily differentiated according to the capacity (size) or the like of the electric motor and scroll compressor to be accommodated therein.
  • the above-described hermetic scroll compressor of the present invention may be configured such that the bearing bracket has the first welded portion to which the end of the upper housing is fitted from the outside and the second welded portion to which the end of the center housing is fitted from the inside.
  • the upper housing fitted to the first welded portion from the outside can be welded from the outer circumference side to the outer circumferential surface of the bearing bracket to which the center housing is fitted from the inside and is welded to the second welded portion from the outer circumference side
  • the top surface of the bearing bracket can be finished while the center and upper housings are fitted to the first and second welded portions of the bearing bracket from the outside and the inside, respectively, and are welded from outer circumference side, and while the bearing bracket is welded to the center housing. Accordingly, it is possible to simplify the welding operations and the finishing of the top surface and to eliminate or simplify the weld bead treatment, thereby improving the manufacturability.
  • any one of the above-described hermetic scroll compressors of the present invention may be configured such that the bearing bracket is provided with bolt holes for fixing the bearing case, the bolt holes being processed after the bearing bracket is welded to the center housing.
  • any one of the above-described hermetic scroll compressors of the present invention may be configured such that the top surface of the bearing bracket is provided with at least one gas-channel groove extending radially from the inner circumferential surface toward the outer circumference.
  • the gas channel that introduces intake gas from the center housing side into the scroll compressor is formed of the gas-channel groove provided on the top surface of the bearing bracket so as to extend radially from the inner circumferential surface toward the outer circumference, the intake gas can be introduced from a position closer to the center of the housing. Accordingly, it becomes possible to introduce more gas from the central area where the amount of gas component is large, while avoiding introducing gas from the outer circumferential area of the housing where the oil content tends to be high. Thus, the oil circulation rate (OCR) to the refrigeration cycle side can be reduced.
  • OCR oil circulation rate
  • the above-described hermetic scroll compressor of the present invention may be configured such that the inner circumferential surface of the bearing bracket is provided with a tapered surface widening upward, at least at the entirety or part of the position where the gas-channel groove is provided.
  • any one of the above-described hermetic scroll compressors of the present invention may be configured such that the bearing bracket is provided with a slit extending radially from the inner circumferential surface toward the outer circumference, and the slit, by being sealed by the bearing case at the inner circumference side, forms on the outer circumference side a wiring channel for a motor lead wire connected to the electric motor.
  • the bearing bracket is provided with the radially extending slit, and the inner circumference side thereof is closed by the bearing case to form the wiring channel for the motor lead wire on the outer circumference side, it is possible to easily form the wiring channel having a minimum channel area and capable of preventing bypassing of the intake gas, without providing a through-hole. Accordingly, wiring and leading out of the motor lead wire to be connected to the electric motor can be simplified.
  • any one of the above-described hermetic scroll compressors of the present invention may be configured such that the first and second welded portions have diameters different from each other, and the center and upper housings having different diameters are welded to the first and second welded portions.
  • the center and upper housings having different diameters can be welded thereto.
  • the diameters of the center housing accommodating the electric motor and the upper housing accommodating the scroll compressor different, enabling an electric motor capable of achieving necessary output power or a scroll compressor capable of achieving necessary capacity to be arbitrarily selected, without being limited by the diameters of the housings. Accordingly, it is possible to increase the design flexibility and expand the extent of use of common components, when selecting the motor capacity or the compressor capacity.
  • the above-described hermetic scroll compressor of the present invention may be configured such that the bearing bracket is formed in a shape protruding toward the housing having a smaller diameter among the center and upper housings.
  • the bearing bracket is formed in a shape protruding toward the housing having a smaller diameter, even when the diameters of the center and upper housings are significantly different, it is possible to reduce stress concentration on the bearing bracket and to easily ensure the pressure-resisting strength of the sealed housing. Accordingly, while the present invention can reduce the capacity of the compressor by using high-pressure, high-density refrigerant, it can be effectively applied to a hermetic scroll compressor that requires a high-output electric motor.
  • finishing can be performed after the bearing bracket is welded to the center housing and while the top surface of the bearing bracket is exposed, it is possible to simplify finishing, such as machining the top surface, and to eliminate the thermal deformation caused by welding.
  • finishing such as machining the top surface
  • thermal deformation caused by welding it is possible to increase the assembly precision of the scroll compressor securely mounted on the top surface of the bearing bracket and to improve the manufacturability and ease of assembly thereof.
  • ends of the center and upper housings are fitted to the first and second welded portions of the bearing bracket, and the housings are welded from the outer circumference side, it is possible to simplify the welding operation and to eliminate or simplify the weld bead treatment, thereby improving the manufacturability.
  • the center and upper housings welded to the first and second welded portions through the bearing bracket have different diameters
  • the diameters of the center and upper housings can be easily differentiated according to the capacity (size) or the like of the electric motor and scroll compressor to be accommodated therein.
  • FIGS. 1 to 6 A first embodiment of the present invention will be described below using FIGS. 1 to 6 .
  • FIG. 1 shows a longitudinal sectional view of a two-stage compressor 1 for refrigeration air-conditioning that uses a hermetic scroll compressor according to the first embodiment of the present invention.
  • a hermetic scroll compressor 3 according to the first embodiment of the present invention will be described taking as an example the two-stage compressor 1, configured by using a rotary compressor 2 on a low-stage side and a scroll compressor 3 on a high-stage side
  • the present invention is of course applicable to a single-stage hermetic scroll compressor or a multi-stage hermetic scroll compressor in which scroll compressors are used on both the low-stage side and the high-stage side.
  • the two-stage compressor 1 using the hermetic scroll compressor 3 includes a sealed housing 10.
  • the sealed housing 10 consists of a cylindrical center housing 10A, a ring-like bearing bracket 11 provided on the center housing 10A and welded thereto over the entire circumference, a lower housing 10B that seals the bottom of the center housing 10A, and an upper housing 10C that seals the top of the center housing 10A and is provided on the bearing bracket 11 and welded thereto over the entire circumference.
  • An electric motor 4 consisting of a stator 5 and a rotor 6 is securely mounted at substantially the central part in the center housing 10A.
  • a rotary shaft (crank shaft) 7 is integrally connected to the rotor 6.
  • the rotary compressor 2 on the low-stage side is mounted below the electric motor 4.
  • the rotary compressor 2 on the low-stage side is configured to include a cylinder body 21 that has a cylinder chamber 20 and is securely mounted in the center housing 10A; an upper bearing 22 and a lower bearing 23 that are securely mounted above and below the cylinder body 21 to seal the top and bottom of the cylinder chamber 20; a rotor 24 that is fitted to a crank portion 7A of the rotary shaft 7 and rotates on the inner circumferential surface of the cylinder chamber 20; and a blade and a blade holding spring (not shown) that divide the inside of the cylinder chamber 20 into an intake side and a discharge side.
  • This rotary compressor 2 is configured to take in a low-pressure refrigerant gas (working gas) into the cylinder chamber 20 through an intake tube 25, compress the refrigerant gas to an intermediate pressure via rotation of the rotor 24, discharge the gas into discharge chambers 26 and 27 formed thereabove and therebelow using an upper bearing 22 and a lower bearing 23, merge the gas in the discharge chamber 26, and discharge the gas into the center housing 10A.
  • This intermediate-pressure refrigerant gas circulates through a gas channel hole 6A or the like provided in the rotor 6 of the electric motor 4, is guided to a space above the electric motor 4, and is then taken into the scroll compressor 3 on the high-stage side to be subjected to two-stage compression.
  • the scroll compressor 3 on the high-stage side is provided in the upper housing 10C.
  • the scroll compressor 3 includes a bearing case 31 (also referred to as a frame member or a support member) that has a bearing 30 for supporting the rotary shaft (crank shaft) 7 and is securely mounted on a top surface 51 of the bearing bracket 11 (see FIGS. 4A and 4B ) with bolts 12, and a fixed scroll member 32 and an orbiting scroll member 33 that respectively have spiral-shaped wraps 32B and 33B provided upright on end plates 32A and 33A and that form a pair of compression chambers 34 by being mounted onto the bearing case 31 in such a manner that the spiral-shaped wraps 32B and 33B are meshed with each other.
  • the scroll compressor 3 is configured to include an orbit boss portion 33C that connects the orbiting scroll member 33 and an eccentric pin 7B of the rotary shaft 7 through a drive bush 13 to allow the orbiting scroll member 33 to orbitally revolve; a self-rotation preventing mechanism 35 that is provided between the orbiting scroll member 33 and the bearing case 31 to allow the orbiting scroll member 33 to orbitally revolve while preventing self rotation thereof; a discharge reed valve 36 provided on the back surface side of the fixed scroll member 32 to open and close a discharge port 32C; a discharge cover 38 securely mounted on the back surface side of the fixed scroll member 32 so as to surround the discharge reed valve 36 and form an oil-separation chamber 37; an outlet tube 39 connected to the central portion of the discharge cover 38, through which the compressed high-pressure gas is discharged outside; and an oil-separation mechanism 40 that is mounted in the oil-separation chamber 37 and separates oil from compressed gas by centrifugation.
  • the scroll compressor 3 is configured to take intermediate-pressure refrigerant gas compressed by the rotary compressor 2 on the low-stage side and discharged into the sealed housing 10 into the compression chambers 34, compress the intermediate-pressure refrigerant gas to a higher pressure state through a compression operation performed by orbital revolution of the orbiting scroll member 33, and then discharge the gas into the oil-separation chamber 37 in the discharge cover 38 through the discharge reed valve 36.
  • This high-temperature, high-pressure refrigerant gas is sent to the outside of the two-stage compressor 1, i.e., toward the refrigeration cycle side, through the outlet tube 39, after oil in the gas is separated by the oil-separation mechanism 40 in the oil-separation chamber 37.
  • a known displacement-type oil-supply pump 14 is incorporated between the bottom end of the rotary shaft (crank shaft) 7 and the lower bearing 23 of the rotary compressor 2 on the low-stage side.
  • This displacement-type oil-supply pump 14 is configured to pump up lubricant oil 15 filled in the bottom of the sealed housing 10 and forcibly supply the lubricant oil 15 to portions requiring lubrication, such as bearing portions of the rotary compressor 2 and scroll compressor 3, through an oil-supply hole 16 provided in the rotary shaft 7.
  • the oil supplied by the oil-supply pump 14 and lubricating the scroll compressor 3 and the oil separated by the oil-separation mechanism 40 pass through oil drop holes 41, 42, and 43 provided in the fixed scroll member 32 and bearing case 31 and flow from an oil discharge pipe 44 connected to the bearing bracket 11 to the bottom of the sealed housing 10.
  • a pressure-reduction mechanism (not shown) is disposed in the oil drop hole 41 from the oil-separation mechanism 40.
  • the sealed housing 10 is configured to include the cylindrical center housing 10A accommodating the electric motor 4 and the upper housing 10C accommodating the scroll compressor 3 and sealing the top of the center housing 10A, the housings being welded into a single part with the bearing bracket 11 therebetween.
  • the bearing bracket 11 is a ring-like bracket made of a flat plate and has a flange portion 50 that extends downward at a right angle at the bottom of the outer circumference thereof.
  • the top surface 51 of the bearing bracket 11 serves as a bearing surface where the bearing case 31 of the scroll compressor 3 is securely mounted with the bolts 12, and a plurality of (in this embodiment, six) bolt holes 52 with which the bolts 12 are engaged are bored therein at equal intervals.
  • a pipe hole 53 to which the above-described oil discharge pipe 44 is connected is provided in the top surface 51 of the bearing bracket 11.
  • a first welded portion 54 to which the lower end of the upper housing 10C is fitted from the outside is formed on the outer circumference of the upper half portion, and a second welded portion 55 to which the upper end of the center housing 10A is fitted from the inside is formed on the inner circumference of the flange portion 50.
  • the structure is configured such that the ends of the upper housing 10C and center housing 10A are fitted to the first welded portion 54 and the second welded portion 55, respectively, and, in another step, they are welded from the outer circumference side, as indicated by arrows A and B shown in FIG. 2 .
  • a plurality of gas-channel grooves 56 having a certain depth (see FIG. 3B ) and extending radially from the inner circumferential surface toward the outer circumference are provided in the top surface 51 of the bearing bracket 11.
  • These gas-channel grooves 56 guide the gas taken in from the inner circumference side of the bearing bracket 11 toward the outer circumference and, as shown in FIG. 5 , constitute intake gas channels 17 that are continuous from the inside of the center housing 10A to the compression chambers 34 of the scroll compressor 3, by being combined with corresponding gas-channel grooves 31A provided in the bottom surface and outer circumferential surface of the bearing case 31 securely mounted on the bearing bracket 11.
  • the upper half portion of the inner circumferential surface of the bearing bracket 11 is a tapered surface 57 widening upward.
  • this tapered surface 57 can be provided over the entire circumference of the inner circumferential surface (this embodiment), it does not necessarily need to be provided over the entire circumference, and it may be provided at least at a position corresponding to the gas-channel grooves 56. Also with respect to the height direction (thickness direction), not only the upper half portion, but also the entire area in the thickness direction between the top and bottom surfaces may be tapered.
  • the bearing bracket 11 has a slit 58 provided radially from the inner circumferential surface toward the outer circumference and penetrating from the top to bottom, at one location on the circumference. As shown in FIG. 6 , this slit 58 is configured to be closed at the inner circumference side by the bearing case 31 securely mounted on the bearing bracket 11 and to allow the upper side and lower side of the bearing bracket 11 to communicate with each other at part of the outer circumference side to form a wiring channel 59 through which a motor lead wire 19 (U-V-W wire) for supplying electricity to the electric motor 4 through a glass-sealed terminal 18 (see FIG. 1 ) passes.
  • U-V-W wire motor lead wire 19
  • center housing 10A, upper housing 10C, and bearing bracket 11 finishing of the top surface 51 of the bearing bracket 11 (flat-surface machining of the bearing surface) and processing of the bolt holes 52 and pipe hole 53 are performed after one end of the center housing 10A is fitted to the second welded portion 55 of the bearing bracket 11 and is welded over the entire circumference thereof, so that distortion due to thermal deformation during welding, misalignment of the centers of the holes, and the like are prevented.
  • the bearing case 31 is mounted on the thus-finished top surface 51 of the bearing bracket 11, and then, the components of the scroll compressor 3 are mounted thereto.
  • the upper housing 10C is fitted to the first welded portion 54 of the bearing bracket 11 and is welded over the entire circumference thereof.
  • the gas-channel grooves 56 and the slit 58 provided in the bearing bracket 11 do not penetrate through to the extreme outer circumferential surface of the bearing bracket 11, so that no portion penetrates through to the outer circumferential surface.
  • a configuration that can ensure strength against deformation during welding or the like as much as possible is achieved.
  • the inside diameter ⁇ 2 of the upper housing 10C accommodating the scroll compressor 3 is slightly larger than the inside diameter ⁇ 1 of the center housing 10A accommodating the electric motor 4 ( ⁇ 1 ⁇ ⁇ 2), and the diameters of the first welded portion 54 and the second welded portion 55 of the bearing bracket 11 have the same relationship.
  • the divided center housing 10A and the upper housing 10C do not necessarily have to have the same diameters, but they may of course have the same diameters.
  • this embodiment provides the following advantages.
  • Low-temperature, low-pressure refrigerant gas taken into the cylinder chamber 20 of the rotary compressor 2 on the low-stage side through the intake tube 25 is compressed by the rotation of the rotor 24 to an intermediate pressure and is then discharged into the discharge chambers 26 and 27.
  • This intermediate-pressure refrigerant gas is merged in the discharge chamber 26 and is then discharged into the space below the electric motor 4, from where it circulates through the gas channel hole 6A and the like provided in the rotor 6 of the electric motor 4 and flows to the space above the electric motor 4.
  • the intermediate-pressure refrigerant gas flowing to the space above the electric motor 4 passes through the intake gas channels 17 formed of the gas-channel grooves 31A and 56 provided in the outer surface of the bearing case 31 and in the top surface 51 of the bearing bracket 11 so as to extend radially from the central region of the center housing 10A, and is taken into the compression chambers 34 formed between the fixed scroll member 32 and the orbiting scroll member 33.
  • This intermediate-pressure refrigerant gas is subjected to two-stage compression to a high-temperature, high-pressure state through a compression operation performed by orbital revolution of the orbiting scroll member 33 and is then discharged from the discharge port 32C into the discharge cover 38 through the discharge reed valve 36.
  • part of the lubricant oil 15 supplied by the oil-supply pump 14 and used for lubricating the rotary compressor 2 is entrained in the refrigerant gas and is discharged into the center housing 10A together with the intermediate-pressure refrigerant gas. Furthermore, part of the lubricant oil 15 supplied to the scroll compressor 3 through the oil-supply hole 16 to lubricate the scroll compressor 3 and flowing down through the oil drop holes 43 and 42 and the oil discharge pipe 44 to the bottom in the sealed housing 10 is entrained in this intermediate-pressure refrigerant gas.
  • the intermediate-pressure refrigerant gas in which the lubricant oil 15 is entrained is taken into the scroll compressor 3 to be compressed while containing oil. Then, it is turned into a high-temperature, high-pressure gas and is discharged from the discharge port 32C together with the oil.
  • This high-temperature, high-pressure compressed gas containing oil is discharged to the refrigeration cycle side from the outlet tube 39 connected to the central portion of the discharge cover 38, after the oil is separated by centrifugation in the centrifugal oil-separation mechanism 40 provided in the oil-separation chamber 37 in the discharge cover 38. Accordingly, the oil circulation rate (OCR) of the lubricant oil 15 circulated to the refrigeration cycle side is reduced, improving the system efficiency and solving the problem of lubricant oil shortage in the compressor 1.
  • the oil separated in the oil-separation chamber 37 is reduced to a low pressure by the pressure-reduction mechanism in the oil drop hole 41 and is allowed to flow through the oil drop hole 42 and the oil discharge pipe 44 to the bottom of the sealed housing 10.
  • the sealed housing 10 is configured to be divided, above and below the bearing bracket 11 to which the bearing case 31 is securely mounted, into the upper housing accommodating the scroll compressor 3 and the center housing 10A accommodating the electric motor 4.
  • finishing such as machining and processing of the bolt holes 52 and pipe hole 53, can be performed after the bearing bracket 11 is welded to the center housing 10A and while the top surface 51 of the bearing bracket 11 is exposed.
  • first welded portion 54 and the second welded portion 55 are provided on the outer circumference of the bearing bracket 11, so that the ends of the upper housing 10C and center housing 10A can be fitted to the first and second welded portions 54 and 55 from the outside and the inside, respectively, and so that the housings 10A and 10C can be welded thereto from the outer circumference side, it is possible to facilitate positioning during welding, as well as the welding operation itself, and to eliminate or simplify the weld bead treatment, thereby improving the manufacturability.
  • the center housing 10A and upper housing 10C welded to the first welded portion 54 and the second welded portion 55 through the bearing bracket 11 have different diameters. That is, because the center housing 10A and the upper housing 10C do not necessarily need to have the same diameters, the diameters of the center housing 10A and the upper housing 10C can be appropriately differentiated according to the capacity (size) or the like of the electric motor 4 and scroll compressor 3 to be accommodated therein.
  • the intake gas channels 17 are formed of the plurality of gas-channel grooves 56 provided in the top surface 51 of the bearing bracket 11 so as to extend radially from the inner circumferential surface toward the outer circumference and the gas-channel grooves 31A provided in the outer surface of the bearing case 31 so as to correspond to the gas-channel grooves 56, the intake gas channels 17 having a sufficient channel area can be formed from the central region of the sealed housing 10 toward the outer circumference.
  • the intake gas in the center housing 10A can be introduced from a position closer to the center of the housing. Accordingly, it becomes possible to introduce more gas from the central area where the amount of gas component is large, while avoiding introducing gas from the outer circumferential area of the housing where the oil content tends to be high.
  • the oil circulation rate (OCR) to the refrigeration cycle side can be reduced.
  • the gas channel area can be further increased and the intake gas can be smoothly guided to the radially extending gas-channel grooves 56, i.e., the intake gas channels 17, along the tapered surface 57. Accordingly, pressure loss of the intake gas in the intake gas channels 17 can be reduced as much as possible, thereby increasing the intake efficiency.
  • the inner circumference side of the radially extending slit 58 provided in the bearing bracket 11 is closed by the bearing case 31 to form the wiring channel 59 through which the motor lead wire 19 passes on the outer circumference side thereof.
  • the wiring channel 59 having a minimum channel area and capable of minimizing bypassing of the intake gas can be easily formed without providing a through-hole. Accordingly, there is no need to allow the motor lead wire 19 to pass through a small through-hole, simplifying wiring and leading out of the motor lead wire 19 to be connected to the electric motor 4.
  • gas-channel grooves 56, the slit 58, etc. are processed in the bearing bracket 11, they do not penetrate through to the extreme outer circumferential surface of the bearing bracket 11, so that no portion penetrates through to the outer circumferential surface.
  • strength against deformation during welding or the like can be ensured as much as possible. Accordingly, deformation during welding is reduced as much as possible, whereby high assembly precision can be maintained.
  • FIG. 7 a second embodiment of the present invention will be described using FIG. 7 .
  • This embodiment differs from the above-described first embodiment in the inside diameter ⁇ 3 of the center housing 10A and the inside diameter ⁇ 4 of the upper housing 10C. Because the other structures are the same as those in the first embodiment, descriptions thereof will be omitted.
  • the inside diameter ⁇ 4 of the upper housing 10C accommodating the scroll compressor 3 is slightly smaller than the inside diameter ⁇ 3 of the center housing 10A accommodating the electric motor 4 ( ⁇ 3 > ⁇ 4), and the diameters of the first welded portion 54 and the second welded portion 55 provided on the bearing bracket 11 have the same relationship.
  • the relationship between the inside diameter ⁇ 3 of the center housing 10A accommodating the electric motor 4 and the inside diameter ⁇ 4 of the upper housing 10C accommodating the scroll compressor 3 can be made ⁇ 3 > ⁇ 4 to make the inside diameter ⁇ 3 of the center housing 10A larger, in contrast to the first embodiment.
  • the other configurations are the same as those in the first embodiment.
  • FIG. 8 Next, a third embodiment of the present invention will be described using FIG. 8 .
  • This embodiment differs from the above-described first and second embodiments in that the ratio of the difference in diameter between an inside diameter ⁇ 5 of the center housing 10A and an inside diameter ⁇ 6 of the upper housing 10C is further increased. Because other configurations are the same as those in the first and second embodiments, descriptions thereof will be omitted.
  • the inside diameter ⁇ 5 of the center housing 10A accommodating the electric motor 4 is much larger than the inside diameter ⁇ 6 of the upper housing 10C accommodating the scroll compressor 3 ( ⁇ 5 >> ⁇ 6).
  • the diameters of the first welded portion 54 and the second welded portion 55 provided on the bearing bracket 11A have the same relationship.
  • the flange portion 50B of the bearing bracket 11A extending in the radial direction corresponding to the size of the inside diameter ⁇ 5 of the center housing 10A is formed in a shape smoothly protruding toward the upper housing 10C having a smaller diameter.
  • the invention can reduce the capacity of the compressor by using high-pressure, high-density refrigerant, it can be effectively applied to a hermetic scroll compressor that requires a high-output electric motor.
  • the present invention is not limited to the invention according to the above-described embodiments but may be appropriately modified within a scope not departing from the spirit thereof.
  • the hermetic scroll compressors 3 according to the above-described embodiments are applicable to refrigeration cycle compressors that use any type of refrigerant (working gas), including R410A refrigerant and CO2 refrigerant
  • the hermetic scroll compressor 3 according to the third embodiment is particularly suited for use with CO2 refrigerant, which is a high-pressure refrigerant. That is, because the CO2 refrigerant has a high pressure and a high density, it can reduce the capacity of the scroll compressor 3.
  • the diameter of the housing accommodating the electric motor 4 increases.
  • the present invention is effective.
  • the bearing bracket 11 may be formed in a shape smoothly protruding toward the housing accommodating the electric motor.
  • the first and second welded portions 54 and 55 provided on the bearing bracket 11 they may be configured such that the end of the upper housing 10C is fitted to the first welded portion 54 from the inside, and the center housing 10A is fitted to the second welded portion 55 from the outside. This configuration is also encompassed by the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP09705815.0A 2008-01-29 2009-01-21 Versiegelungs-spiralverdichter Active EP2236829B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008018203A JP5244407B2 (ja) 2008-01-29 2008-01-29 密閉型スクロール圧縮機及びその製造方法
PCT/JP2009/050861 WO2009096288A1 (ja) 2008-01-29 2009-01-21 密閉型スクロール圧縮機

Publications (3)

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EP2236829A1 true EP2236829A1 (de) 2010-10-06
EP2236829A4 EP2236829A4 (de) 2015-06-24
EP2236829B1 EP2236829B1 (de) 2018-10-10

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102010053915B4 (de) * 2009-12-09 2019-04-25 Danfoss Scroll Technologies, Llc Verformter Mantel zum Halten des Motorstators in einem Kompressormantel

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011089507A (ja) * 2009-10-26 2011-05-06 Sanden Corp スクロール型流体機械
JP2012117380A (ja) * 2010-11-29 2012-06-21 Daikin Industries Ltd 圧縮機用ケーシング
JP6680594B2 (ja) 2016-03-30 2020-04-15 三菱重工サーマルシステムズ株式会社 密閉型二段圧縮機、及び圧縮機システム
CN106762657A (zh) * 2017-01-25 2017-05-31 珠海凌达压缩机有限公司 压缩机支架、压缩机及电动汽车

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Publication number Priority date Publication date Assignee Title
JP2979777B2 (ja) 1991-10-01 1999-11-15 ダイキン工業株式会社 スクロール形流体機械
JP2000213472A (ja) * 1999-01-21 2000-08-02 Matsushita Electric Ind Co Ltd 自動車用横型スクロ―ル圧縮機
JP3683760B2 (ja) * 1999-11-01 2005-08-17 ダイキン工業株式会社 スクロール圧縮機
JP2001263273A (ja) * 2000-03-17 2001-09-26 Fujitsu General Ltd スクロール圧縮機
US6884046B2 (en) * 2002-03-04 2005-04-26 Daiken Industries, Ltd. Scroll compressor
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Publication number Priority date Publication date Assignee Title
DE102010053915B4 (de) * 2009-12-09 2019-04-25 Danfoss Scroll Technologies, Llc Verformter Mantel zum Halten des Motorstators in einem Kompressormantel

Also Published As

Publication number Publication date
EP2236829A4 (de) 2015-06-24
JP2009180107A (ja) 2009-08-13
JP5244407B2 (ja) 2013-07-24
WO2009096288A1 (ja) 2009-08-06
EP2236829B1 (de) 2018-10-10

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