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WO2020157841A1 - Compresseur à spirale à rotation bidirectionnelle - Google Patents

Compresseur à spirale à rotation bidirectionnelle Download PDF

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Publication number
WO2020157841A1
WO2020157841A1 PCT/JP2019/003047 JP2019003047W WO2020157841A1 WO 2020157841 A1 WO2020157841 A1 WO 2020157841A1 JP 2019003047 W JP2019003047 W JP 2019003047W WO 2020157841 A1 WO2020157841 A1 WO 2020157841A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive
scroll member
driven
wall body
scroll
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/003047
Other languages
English (en)
Japanese (ja)
Inventor
拓馬 山下
弘文 平田
隆英 伊藤
恵太 北口
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to DE112019006759.1T priority Critical patent/DE112019006759T5/de
Priority to PCT/JP2019/003047 priority patent/WO2020157841A1/fr
Priority to JP2020568927A priority patent/JP7143450B2/ja
Publication of WO2020157841A1 publication Critical patent/WO2020157841A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C18/023—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 both members are moving
    • F04C18/0238—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 both members are moving with symmetrical double wraps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2240/80—Other components
    • F04C2240/809—Lubricant sump

Definitions

  • the present disclosure relates to a dual rotation scroll compressor.
  • a double rotation scroll type compressor is known. This is provided with a driving side scroll and a driven side scroll that rotates in synchronization with the driving side scroll, and a driven shaft that supports the rotation of the driven side scroll with respect to the drive shaft that rotates the driving side scroll is equivalent to a turning radius. Only by offsetting, the drive shaft and the driven shaft are rotated in the same direction at the same angular velocity.
  • Patent Document 1 by providing wrap portions on both sides of the end plate of the driven scroll portion, a compression space is formed on both sides of the end plate. This is because the compression space can be formed on both sides of the end plate, and thus the flow rate can be doubled as compared with the case where the compression space is formed only on one side of the end plate.
  • it is necessary to enlarge the scroll portion in the radial direction.
  • the scroll portion is expanded in the radial direction, the amount of deformation and stress of the wrap portion increases, so there is a limit to increasing the flow rate. Therefore, an object of the present disclosure is to provide a double-rotating scroll compressor that can realize a large flow rate.
  • the compression unit side space is provided with the suction unit for sucking the gas before compression, so that the inside pressure is higher than the atmospheric pressure. It may be low. Therefore, a pressure difference may occur between the drive unit side space and the compression unit side space, which are at atmospheric pressure. When such a pressure difference occurs, the lubricant used for the drive side bearing that supports the drive shaft with respect to the partition wall body may leak into the compression portion space on the low pressure side, causing poor lubrication. Therefore, it is an object of the present disclosure to provide a double-rotating scroll compressor that can suppress poor lubrication of a drive-side bearing.
  • the second side plate spaced apart and substantially parallel to the first side plate, and the center plate connected to the drive unit.
  • a conceivable configuration is one in which a sealed internal space is formed and a synchronous drive unit that synchronizes the drive side scroll member and the driven side scroll member is installed in this internal space.
  • the center plate and the first side plate are in contact with each other in a sliding state, the lubricant is supplied.
  • the lubricant may leak due to centrifugal force and become insufficient. Therefore, it is an object of the present disclosure to provide a double-rotating scroll compressor that can suppress a shortage of lubricant between the first side plate and the center plate.
  • a tip seal is provided in the tip seal groove at the height direction tip of the wall portion (wrap) of each scroll member.
  • the tip seal is sealed by floating on the end plate side by the pressure of the fluid that has entered the back surface of the tip seal.
  • the pressure ratio is low, the tip seal may not be sufficiently floated, and the desired sealing performance may not be obtained. Therefore, an object of the present disclosure is to provide a double-rotating scroll compressor that can improve the sealing performance of the tip seal.
  • an object of the present disclosure is to provide a double-rotating scroll compressor including a scroll member having good workability.
  • an end plate extension portion that projects radially outward from the wall body is provided on the circumferentially inner side portion of the wall body that is located radially inward with respect to the winding end position in the circumferential direction of the wall body. It is conceivable to make the scroll member smaller. However, if the end plate extension is provided with a small projecting portion having a radial dimension smaller than the thickness of the wall body, the height direction tip of the wall body will protrude from the small projecting portion. A tip seal cannot be provided at the tip in the height direction. In this case, the desired sealing performance cannot be obtained in the gap between the small protruding portion and the tip of the wall in the height direction. Therefore, an object of the present disclosure is to provide a double-rotating scroll compressor that can obtain a desired sealing performance in the gap between the small protruding portion and the height direction tip of the wall body.
  • an object of the present disclosure is to provide a double-rotating scroll compressor that can reduce the processing time of a scroll member including a wall body having a fastening portion.
  • a double rotary scroll compressor is driven to rotate about a rotation axis by a drive unit, and a spiral first drive side wall body is disposed on each side of a first drive side end plate.
  • a first drive side scroll member and a spiral first driven side wall body are arranged on both sides of the first driven side end plate, and one of the first driven side wall bodies is opposed to one of the first drive side wall bodies.
  • the second drive side scroll member in which the spiral second drive side wall body that forms the second compression space is disposed on the second drive side end plate, and the spiral second driven side wall body is the second driven side end plate.
  • a second driven side scroll member that forms a third compression space by meshing the second driven side wall body with the other of the first drive side wall bodies, and the first drive side scroll member, The second driven scroll member, the first driven scroll member, and the second driven scroll member rotate from the drive unit side to the first driven scroll member and the first driven scroll member so that the second driven scroll member and the second driven scroll member rotate in the same direction at the same angular velocity.
  • a synchronous drive mechanism that transmits a driving force to the driven scroll member.
  • the first driving side scroll member is a so-called double-toothed scroll member having first driving side wall bodies on both sides of the first driving side end plate.
  • the first driven side scroll member is also a double-toothed scroll member having first driven side walls on both sides of the first driven side end plate. Then, the first compression side wall body of the first drive side scroll member having both teeth is meshed with the one first drive side wall body of the first driven side scroll member having both teeth, so that a first compression is achieved. A space is formed.
  • the other first driven side wall body of the first driven side scroll member having both teeth meshes with the second drive side wall body of the second drive side scroll member to form a second compression space.
  • the other first driving side wall body of the first driving side scroll member having both teeth is meshed with the second driven side wall body of the second driven side scroll member to form a third compression space.
  • the number of scroll members having both teeth is not limited to two and may be three or more. That is, the second driving side scroll member and the second driven side scroll member may have two teeth instead of one tooth.
  • a final discharge port through which the fluids compressed in the compression spaces merge and is discharged is provided, and the central portion of the first drive side end plate is provided.
  • the flow passage cross-sectional areas of the first drive side discharge port and the first driven side discharge port are smaller on the upstream side than on the downstream side with respect to the final discharge port.
  • the fluids compressed in the respective compression spaces are merged and then discharged from the final discharge port to the outside of the rotary scroll compressor. Since the flow rate of the upstream discharge port is smaller than that of the downstream discharge port after the fluids have merged, the possibility of choking is low, so the flow path cross-sectional area of the upstream discharge port is smaller than that of the downstream side. can do. Therefore, of the first drive side discharge port and the first driven side discharge port, the upstream side with respect to the final discharge port has a smaller flow passage cross-sectional area than the downstream side. Further, by making the flow passage cross-sectional area of the discharge port on the upstream side small, the wall body can be formed closer to the discharge port as compared with the case where the flow passage cross-sectional area is large, so that the pressure ratio can be increased.
  • a drive unit side space that accommodates the drive unit, the first drive side scroll member, the second drive side scroll member, and the first driven side.
  • a compression part side space that accommodates the scroll member, the second driven side scroll member, and the synchronous drive mechanism, a suction part that is connected to the compression part space and that sucks gas before compression, and the drive part side space.
  • a partition wall portion that separates the compression side space, a drive shaft that is rotatably driven by the drive portion and penetrates the partition wall portion, and a drive that rotatably supports the drive shaft with respect to the partition wall portion.
  • a side bearing, and a pressure equalizing hole for equalizing the pressure of the drive unit side space and the compression unit side space is formed in the partition wall portion.
  • the drive side space and the compression side space are separated by a partition wall. Since the compression unit side space is provided with the suction unit that sucks the gas before compression, the inside may be lower than the ambient pressure (for example, atmospheric pressure). Therefore, a pressure difference may occur between the drive unit side space and the compression unit side space, which are at ambient pressure. When such a pressure difference occurs, the lubricant used for the drive-side bearing that supports the drive shaft may leak into the compression portion space on the low-pressure side, resulting in poor lubrication. Therefore, a pressure equalizing hole for equalizing the pressure of the driving side space and the pressure of the compression portion side is formed in the partition wall portion. Thereby, the pressure difference between the drive unit side space and the compression unit side space can be reduced, and the lubrication failure of the drive side bearing can be suppressed.
  • the ambient pressure for example, atmospheric pressure
  • a first side plate arranged on the rotation axis direction side with respect to each scroll member, and the rotation axis line with respect to the first side plate.
  • a second side plate fixed at a predetermined interval in a direction, and an inside that is disposed between the first side plate and the second side plate and is sealed together with the first side plate and the second side plate.
  • a center plate forming a space, the first side plate is fixed to the first driven scroll member or the second driven scroll member, and the center plate is fixed to the drive unit.
  • the synchronous drive mechanism is provided in the internal space, and a lubricant space for containing a lubricant is provided in a region between the first side plate and the center plate and on the rotation axis side. ..
  • the center plate is in sliding contact with the first side plate to form a closed space, so that the lubricant is supplied.
  • a lubricant space for containing a lubricant is provided between the first side plate and the center plate and in a region on the rotation axis side. Accordingly, even if the center plate rotates around the rotation axis and the lubricant flows radially outward due to the centrifugal force, it is possible to prevent the lubricant from becoming insufficient.
  • lubrication is performed between the first side plate and the center plate by using relative movement between the first side plate and the center plate.
  • a lubricant introduction flow path is provided for guiding the agent to the lubricant space.
  • the lubricant introduced between the first side plate and the center plate is guided to the lubricant space by the lubricant introduction flow path, it is possible to further prevent the lubricant from becoming insufficient.
  • the lubricant introducing passage is formed as a groove in the first side plate or the center plate, for example.
  • a tip seal that seals with the corresponding end plate is provided at a tip end in the height direction of the wall body, and the height of the wall body is increased.
  • a tip seal groove for accommodating the tip seal is formed at a tip end in the depth direction, and a tip seal groove for accommodating the tip seal is formed at an outer side of the tip seal groove in a radial direction with the rotation axis as a center.
  • a first inclined wall portion that is inclined outward in the radial direction is provided.
  • the tip seal that receives the centrifugal force moves to the end plate side facing the first inclined wall portion.
  • the sealing performance of the tip seal can be improved.
  • the radial direction inner side of the tip seal groove around the rotation axis is the radial direction toward the tip end side in the height direction of the wall body.
  • a second inclined wall portion that is inclined symmetrically with the first inclined wall portion is provided inside.
  • the second inclined wall is provided symmetrically with the first inclined wall, the workability of the tip seal groove is improved.
  • a tip seal that seals with the corresponding end plate is provided at a tip end in the height direction of the wall body, and the height of the wall body is increased.
  • a tip seal groove for accommodating the tip seal is formed at the tip in the depth direction, and a tip at the outer side in the circumferential direction of the tip seal groove is provided at the tip in the circumferential direction toward the tip side in the height direction of the wall body.
  • a third sloped portion that slopes toward the tip is provided.
  • the tip seal moves outward in the circumferential direction.
  • the tip seal can be moved to the end plate side along the third inclined portion. As a result, the sealing performance of the tip seal can be improved.
  • the wall body protrudes radially outward from the wall body and has a center at a center position of the end plate.
  • An arc portion is provided.
  • the arc part has an arc shape centered on the center position of the end plate, it can be easily and accurately positioned when gripped by the chuck of the machine tool when processing the scroll member, and the workability is improved. Can be improved.
  • the winding end portion is provided with a protrusion having a hole for positioning or fixing and protruding radially outward from the wall body,
  • the arc portion is provided on the outer side in the circumferential direction or the inner side in the circumferential direction of the projecting portion.
  • the protrusion has a hole for positioning or fixing. Using this hole, the scroll members facing each other are positioned or fixed.
  • the projecting portion can be provided on the outer side in the circumferential direction as much as possible, and can be easily gripped by the chuck of the machine tool. Further, by providing the circular arc portion on the inner side in the circumferential direction of the projecting portion, the inertial force when the scroll member rotates can be reduced as much as possible.
  • the wall body is provided at a circumferentially outer side portion of the wall body located radially inward with respect to a winding end position in the circumferential direction of the wall body.
  • a circular arc portion is provided which protrudes outward in the radial direction from and is centered at the center position of the end plate.
  • ⁇ It has been decided to provide the circular arc portion on the outer side in the circumferential direction of the wall located radially inward of the winding end position in the circumferential direction of the wall.
  • the wall body is provided at a circumferentially outer side portion of the wall body located radially inward with respect to a winding end position in the circumferential direction of the wall body.
  • the abradable coating is applied to the surface facing the body or the tip in the height direction of the wall facing the small protruding portion.
  • the end plate extension part faces the height direction tip of the facing wall body.
  • the end plate extension is provided with a small projecting portion having a radial dimension smaller than the thickness of the wall body, the tip in the height direction of the wall body will protrude from the small projecting portion.
  • the tip seal cannot be provided at the tip in the height direction of. Therefore, the abradable coating is applied to the surface of the small protruding portion facing the wall or the tip of the wall facing the small protruding portion in the height direction.
  • the size of the gap between the small protruding portion and the height direction tip of the wall can be reduced as much as possible, and the sealing performance can be improved.
  • the first drive-side scroll member and the second drive-side scroll member are in a state in which the height direction tips of the wall bodies face each other.
  • Fastening portions to be fastened are provided on each of the first driving side scroll member and the second driving side scroll member, and one end of the driving side scroll member in the height direction of the wall body and the fastening direction of the fastening portion.
  • a tip end has the same height, or a fastening portion that fastens the first driven side scroll member and the second driven side scroll member in a state where the height direction tips of the wall bodies face each other. It is provided in each of the first driven side scroll member and the second driven side scroll member, and one end of the driven side scroll member in the height direction of the wall body and the other end in the height direction of the fastening portion have the same height. ing.
  • the fastening portion of the other scroll member has a shape different in height from the wall body so as to come into contact with the fastening member of the one scroll member.
  • the double-rotating scroll compressor of the present disclosure it is possible to suppress the lack of lubricant in the first side plate and the center plate.
  • the sealing performance of the tip seal can be improved.
  • the workability of the scroll member can be improved.
  • desired sealing performance can be obtained in the gap between the small protruding portion and the height direction tip of the wall body.
  • the dual rotation scroll compressor of the present disclosure it is possible to shorten the processing time of the scroll member including the wall body having the fastening portion.
  • FIG. 1 is a vertical cross-sectional view showing a dual rotation scroll compressor according to a first embodiment of the present disclosure.
  • FIG. 3 is a plan view showing a first driving side wall body of FIG. 1.
  • FIG. 3 is a plan view showing a first driven side wall body of FIG. 1.
  • It is a longitudinal cross-sectional view showing a modified example of FIG.
  • It is a longitudinal section showing a double rotation scroll type compressor concerning a 2nd embodiment of this indication.
  • It is a longitudinal section showing a double rotation scroll type compressor concerning a 3rd embodiment of this indication.
  • FIG. 7 is a plan view showing a modified example of the center plate of FIG. 6.
  • FIG. 9 is a cross-sectional view taken along the section line AA of FIG. 2 showing the fourth embodiment of the present disclosure.
  • FIG. 9 is a cross-sectional view taken along the line BB in FIG. 2 showing the fourth embodiment of the present disclosure. It is a top view showing the 1st drive side scroll member concerning a 5th embodiment of this indication.
  • FIG. 11 is a plan view showing a modified example of FIG. 10.
  • FIG. 11 is a plan view showing a modified example of FIG. 10.
  • FIG. 14 is a cross-sectional view taken along the section line CC of FIG. 13.
  • FIG. 16 is a vertical cross-sectional view showing a main part of a connecting portion of a drive side scroll member according to a seventh embodiment of the present disclosure.
  • FIG. 1 shows a double rotary scroll compressor 1.
  • the double rotary scroll compressor 1 is, for example, a supercharger for compressing combustion air (fluid) supplied to an internal combustion engine such as a vehicle engine, a compressor for supplying compressed air to electrodes of a fuel cell, or a railway. It can be used as a compressor for supplying compressed air for use in a vehicle braking device such as the above, or as a refrigerant compressor used in an air conditioning machine.
  • the rotary scroll type compressor 1 includes a housing 3, a motor (drive unit) 5 housed on one end side of the housing 3, a drive side scroll member 70 and a driven side scroll member housed on the other end side of the housing 3. 90 and.
  • the housing 3 has a substantially cylindrical shape, and includes a motor housing portion 3a that forms a drive portion side space that houses the motor 5, and a scroll housing portion 3b that forms a compression portion side space that houses the scroll members 70, 90 and the like. It has and.
  • the motor housing portion 3a and the scroll housing portion 3b are partitioned by a partition wall portion 3e.
  • An external discharge port 3d for discharging compressed air to the outside is formed at an end portion (left end in FIG. 1) of the scroll housing portion 3b.
  • an air suction port (suction part) for sucking air is provided in the scroll housing part 3b.
  • the motor 5 is driven by power supplied from a power supply source (not shown).
  • the rotation control of the motor 5 is performed by a command from a control unit (not shown).
  • the stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3.
  • the rotor 5b of the motor 5 rotates around the drive-side rotation axis CL1.
  • a drive shaft 6 extending on the drive side rotation axis CL1 is connected to the rotor 5b.
  • the drive shaft 6 is connected to a drive shaft portion 72d fixed to the first drive side scroll member 71 of the drive side scroll member 70.
  • a drive-side bearing 11 that rotatably supports the drive shaft 6 is provided at the front end (left end in FIG. 1) of the drive shaft 6.
  • the drive shaft 6 is rotatably supported between the drive shaft 6 and the housing 3 at the rear end (the right end in FIG. 1), that is, at the end of the drive shaft 6 opposite to the drive side scroll member 70.
  • a rear bearing 17 is provided.
  • the drive side scroll member 70 includes three drive side scroll members 71, 72, 73.
  • the drive side scroll members 71, 72, 73 are arranged and connected in the drive side rotation axis CL1 direction.
  • the first drive side scroll member 71 includes a first drive side end plate 71a and a first drive side wall body 71b.
  • the first drive side end plate 71a extends in a direction orthogonal to the drive side rotation axis CL1.
  • the first drive side end plate 71a has a substantially disc shape when seen in a plan view.
  • a first drive side discharge port 71d is formed in the center of the first drive side end plate 71a along the drive side rotation axis CL1.
  • first driving side wall bodies 71b that is, three strips, are provided on the first driving side end plate 71a.
  • the first drive side wall body 71b which has three rows, is arranged at equal intervals around the drive side rotation axis CL1.
  • the number of threads of the first driving side wall body 71b may be one, two, or four or more.
  • the first drive side wall body 71b is provided on both sides of the first drive side end plate 71a. Therefore, the first drive side scroll member 71 has so-called double teeth.
  • a second drive side scroll member 72 is provided on the motor 5 side of the first drive side scroll member 71 (right side in FIG. 1).
  • the second drive side scroll member 72 includes a second drive side end plate 72a and a second drive side wall body 72b.
  • the second drive side wall body 72b has three strips, like the first drive side wall body 71b (see FIG. 2) described above.
  • the number of threads of the second drive side wall body 72b may be one, two, or four or more.
  • the second drive side wall body 72b is provided only on one side of the second drive side end plate 72a. That is, the second drive side wall body 72b is provided toward the first drive side scroll member 71 side. Therefore, the second drive side scroll member 72 is a so-called single tooth.
  • a drive shaft portion 72d extending along the drive side rotation axis CL1 is fixed to the rotation center of the second drive side end plate 72a.
  • the center plate 20 is integrally provided on the drive shaft portion 72d.
  • the center plate 20 extends parallel to the second drive side end plate 72a.
  • a third drive-side scroll member 73 is provided on the external discharge port 3d side (left side in FIG. 1) of the first drive-side scroll member 71.
  • the third drive side scroll member 73 includes a third drive side end plate 73a and a third drive side wall body 73b.
  • the third drive side wall body 73b has three threads, like the first drive side wall body 71b (see FIG. 2) described above.
  • the number of threads of the third driving side wall body 73b may be one, two, or four or more.
  • the third drive side wall body 73b is provided only on one side of the third drive side end plate 73a. That is, the third drive side wall body 73b is provided toward the first drive side scroll member 71 side. Therefore, the third drive side scroll member 73 is a so-called single tooth.
  • a third drive side shaft portion 73c extending in the drive side rotation axis CL1 direction is connected to the third drive side end plate 73a.
  • the third drive side shaft portion 73c is rotatably provided with respect to the housing 3 via the third drive side bearing 14 which is a ball bearing.
  • a third drive side discharge port 73d is formed in the third drive side end plate 73a along the drive side rotation axis CL1.
  • Two seal members 26 are provided between the third drive side shaft portion 73c and the housing 3 on the tip side (left side in FIG. 1) of the third drive side shaft portion 73cc with respect to the third drive side bearing 14. ing.
  • the two seal members 26 and the third drive side bearing 14 are arranged at a predetermined interval in the drive side rotation axis CL1 direction.
  • a lubricant such as grease, which is a semi-solid lubricant, is enclosed between the two seal members 26.
  • the number of seal members 26 may be one. In this case, the lubricant is sealed between the seal member 26 and the third drive side bearing 14.
  • the first drive side scroll member 71 and the second drive side scroll member 72, and the first drive side scroll member 71 and the third drive side scroll member 73 are the tip ends (free ends) of the walls 71b, 72b, 73b. Are fixed facing each other.
  • the first driving side scroll member 71 and the second driving side scroll member 72, and the first driving side scroll member 71 and the third driving side scroll member 73 are fixed in the circumferential direction so as to project outward in the radial direction. It is performed by the bolts 31 fastened to the flange portions 74 provided at a plurality of locations.
  • the driven scroll member 90 includes two driven scroll members 91 and 92.
  • the first driven scroll member 91 is arranged on the motor 5 side (right side in FIG. 1) with respect to the second driven scroll member 92.
  • the first driven-side scroll member has a first driven-side end plate 91a located substantially at the center in the axial direction (horizontal direction in the drawing).
  • a first driven-side discharge port 91d is formed at the center of the driven-side end plate 90a so that compressed air can flow to the first drive-side discharge port 71d.
  • First driven side wall bodies 91b are provided on both sides of the first driven side end plate 91a, respectively. Therefore, the first driven scroll member 91 has so-called both teeth.
  • the first driven side wall body 91b installed on the motor 5 side from the first driven side end plate 91a is meshed with the second driving side wall body 72b of the second driving side scroll member 72, and the first driven side end plate 91a is externally connected.
  • the first driven side wall body 91b installed on the discharge port 3d side is meshed with the first drive side wall body 71b of the first drive side scroll member 71.
  • the first driven side wall body 91b is provided in three pieces, that is, in three rows.
  • the first driven side wall body 91b which has three rows, is arranged at equal intervals around the driven side rotation axis CL2.
  • the number of threads of the first driven side wall body 91b may be one, two, or four or more.
  • a first side plate 27 is provided on the motor 5 side (right side in FIG. 1) of the first driven scroll member 91.
  • the first side plate 27 is fixed to the tip (free end) of the first driven side wall body 91b by a bolt 28.
  • a first side plate hole 27h for allowing the drive shaft 72d to pass therethrough is formed.
  • the second side plate 30 is provided on the motor 5 side of the first side plate 27 at a predetermined interval.
  • the second side plate 30 is fixed to the first side plate 27 by bolts 34.
  • a second side plate hole 30h for allowing the drive shaft 72d to pass therethrough is formed.
  • a second side plate shaft portion 30a is provided on the center axis side of the second side plate 30, and a second side plate bearing 32, which is an angular ball bearing, is mounted on the second side plate shaft portion 30a. It is fixed to the housing 3 via the. Thereby, the driven side scroll member 90 is configured to rotate around the driven side rotation axis CL2 via the second side plate 30 and the first side plate 27.
  • the first side plate 27, the second side plate 30, and the center plate 20 form a liquid-tight sealed space.
  • the pin 15 and the pin bearing 18 are housed in this closed space.
  • Both ends of the pin 15 are fixed to the first side plate 27 and the second side plate 30.
  • the pin 15 is inserted into an inner peripheral side of a pin bearing 18 which is a rolling bearing (for example, a needle bearing) provided on the center plate 20.
  • the pin bearing 18 is filled with a lubricant such as grease.
  • the pin bearing 18 may be omitted and the pin 15 may be inserted into the through hole formed in the center plate 20.
  • the pin 15 and the pin bearing 18 serve as a synchronous drive mechanism that transmits a driving force from the drive shaft 72d to the driven scroll member 90 so that the driving scroll member 70 and the driven scroll member 90 revolve in a revolving orbit in synchronization.
  • a plurality of synchronous drive mechanisms including the pin 15 are preferably provided, and for example, three synchronous drive mechanisms are provided around the drive side rotation axis CL1 at equal angular intervals.
  • the second driven-side scroll member 92 is arranged on the external discharge port 3d side (left side in FIG. 1) with respect to the first driven-side scroll member 91.
  • the first driven scroll member 91 and the second driven scroll member 92 are fixed to each other by a bolt or the like (not shown) while facing each other in the driven rotation axis CL2 direction.
  • the second driven-side scroll member 92 has a second driven-side end plate 92a located substantially at the center in the axial direction (horizontal direction in the drawing).
  • a second driven-side discharge port 92d is formed in the center of the second driven-side end plate 92a so that compressed air can flow to the third drive-side discharge port 73d.
  • Second driven side wall bodies 92b are provided on both sides of the second driven side end plate 92a, respectively. Therefore, the second driven scroll member 92 has so-called both teeth.
  • the second driven side wall body 92b installed on the motor 5 side from the second driven side end plate 92a is meshed with the first driving side wall body 71b of the first driving side scroll member 71, and externally from the second driven side end plate 92a.
  • the second driven side wall body 92b installed on the discharge port 3d side is meshed with the third drive side wall body 73b of the third drive side scroll member 73.
  • the second driven side wall members 92b which are formed of three threads, are arranged at equal intervals around the driven-side rotation axis CL2.
  • the number of threads of the second driven side wall body 92b may be one or two, or may be four or more.
  • a support member 33 is provided on the external discharge port 3d side (left side in FIG. 1) of the second driven scroll member 92.
  • the support member 33 is fixed to the tip of the second driven side wall body 92b by the bolt 25.
  • a support member shaft portion 35a is provided on the center axis side of the support member 33, and the support member shaft portion 35a is attached to the housing 3 via a second support member bearing 38 that is a ball bearing. It is fixed. As a result, the driven scroll member 90 rotates around the driven rotation axis CL2 via the support member 33.
  • the double-rotating scroll compressor 1 having the above-described configuration operates as follows.
  • the center plate 20 is also rotated about the drive side axis CL1 together with the drive side scroll member 70 via the drive shaft portion 72d connected to the drive shaft 6.
  • the driving force transmitted to the center plate 20 by the rotation of the center plate 20 is transmitted from the first side plate 27 and the second side plate 30 to the driven scroll member 90 via the pin 15 as a synchronous drive mechanism.
  • the driven scroll member 90 rotates around the driven rotation axis CL2. As a result, the scroll members 70 and 90 relatively perform the orbiting motion.
  • both scroll members 70, 90 make an orbiting motion
  • the air sucked from the suction port of the housing 3 is sucked from the outer peripheral sides of the scroll members 70, 90, and the compression chamber formed by the scroll members 70, 90 is formed. Is taken into.
  • the compression chambers formed on both sides of the first driven scroll member 91 and the compression chambers formed on both sides of the second driven scroll member 92 are separately compressed.
  • the volume of each compression chamber decreases as it moves toward the center, and air is compressed accordingly.
  • the air compressed by the first driven side wall body 91b and the second drive side wall body 72b passes through the first driven side discharge port 91d and is compressed by the first driven side wall body 91b and the first drive side wall body 71b.
  • the combined air moves toward the first drive-side discharge port 71d. After that, it merges with the air compressed by the first driving side wall body 71b and the second driven side wall body 92b, moves toward the second driven side discharge port 92d, and becomes the second driven side wall body 92b and the third driving side wall body 73b.
  • the air is combined with the air compressed by, flows into the third drive side discharge port 73d, and is finally discharged from the external discharge port 3d to the outside of the rotary scroll type compressor 1.
  • the flow passage cross-sectional areas of the first driven-side discharge port 91d, the first drive-side discharge port 71d, and the second driven-side discharge port 92d may be changed.
  • the upstream side of the external outlet 3d which is the final outlet, has a smaller cross-sectional area than the downstream side.
  • the diameter of the first driven side discharge port 91d is d3
  • the diameter of the first drive side discharge port 71d is d2
  • the diameter of the second driven side discharge port 92d is d1.
  • d3 ⁇ d3 ⁇ d1 The flow channel cross-sectional area is determined so as to have the relationship of
  • the wall body 91b closer to the first driven-side discharge outlet 91d up to the inner peripheral side than when the flow passage cross-sectional area is large, The pressure ratio can be increased.
  • the partition wall portion 3e of the housing 3 is formed with a pressure equalizing hole 3h which is a through hole.
  • the number of pressure equalizing holes 3h may be one or two or more.
  • the pressure equalizing hole 3h equalizes pressure in the drive unit side space in the motor housing 3a and the compression unit side space in the scroll housing 3b. No through hole is formed in the partition wall portion 3e other than the hole in which the drive-side bearing 11 is installed.
  • the drive unit side space and the compression unit side space are partitioned by a partition wall 3e. Since the motor housing portion 3a forming the compression portion side space is provided with a suction portion (not shown) for sucking the gas before compression, the inside may be lower than the ambient pressure (for example, atmospheric pressure). Therefore, a pressure difference may occur between the drive unit side space and the compression unit side space in the scroll housing portion 3b, which are at the ambient pressure. When such a pressure difference occurs, the lubricant used for the drive-side bearing 11 that supports the drive shaft 72d may leak into the compression portion space on the low-pressure side, resulting in poor lubrication.
  • the pressure equalizing hole 3h is formed in the partition wall portion 3e, the pressure difference between the drive unit side space and the compression unit side space is reduced, and the lubrication failure of the drive side bearing 11 is suppressed. be able to.
  • the structure in which the pressure equalizing hole 3h is formed in the partition wall portion 3e can be used only in the double-rotating scroll compressor 1 having three double-toothed scroll members 71, 91, and 92 as in the present embodiment.
  • the invention can also be applied to a double-rotating scroll compressor composed only of a single-tooth scroll member or a double-rotating scroll compressor composed of a single double-tooth scroll member and two single-tooth scroll members. it can. That is, the present invention can be applied to both rotary scroll compressors including a drive side scroll member and a driven side scroll member.
  • a third embodiment of the present disclosure will be described.
  • the present embodiment is different in that the first embodiment has three scroll members 71, 91, 92 having two teeth, whereas the scroll member having two teeth has one scroll member. Further, the mechanism for transmitting power from the drive shaft 72d to each scroll member is different. Since the other points are the same, the same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. Further, the present embodiment can also be applied to the double rotary scroll compressor 1 shown in FIG.
  • the first driving side scroll member 71 of the first embodiment is omitted, and the second driving side scroll member 72 of one tooth and the one tooth.
  • the drive side scroll member 70 is configured by the third drive side scroll member 73.
  • the driven scroll member 90 is composed of only one first driven scroll member 91 having two teeth.
  • the drive side plate 37 is connected to the second drive side end plate 72a.
  • the drive side plate 37 extends in parallel with the second drive side end plate 72a.
  • the drive side plate 37 is connected to the outer peripheral portion of the third drive side end plate 73a by a fixing portion 37a provided at the outer peripheral end.
  • the fixed portion 37a has a tubular shape extending in parallel with the drive-side rotation axis CL1.
  • a through hole is formed in the fixing portion 37a, and the fixing portion 37a is fixed to the second drive side end plate 72a by inserting a bolt 37b into the through hole.
  • a shaft portion 37c is provided at the center of the drive side plate 37.
  • the shaft portion 37c has a cylindrical shape, and the inner peripheral side thereof is fixed to the outer peripheral side of the drive shaft portion 72d of the center plate 20.
  • the central axis of the shaft portion 37c is the drive side rotation axis CL1.
  • the shaft portion 37c of the drive side plate 37 is fixed to the drive shaft portion 72d.
  • the shaft portion 37c and the drive shaft portion 72d are connected by serration, shrink fitting, bolts, keys or the like.
  • the center plate 20 is housed in a space surrounded by the first side plate 27 and the second side plate 30.
  • An O-ring 36 is provided as a seal member on the center side of the second side plate 30.
  • the O-ring 36 is provided so as to seal with the end surface of the center plate 20.
  • the lubricant of the pin bearing 18 is enclosed in the accommodation space formed between the first side plate 27 and the second side plate 30.
  • a split shaft portion 30e is provided at the center of the second side plate 30 so as to project in parallel with the driven-side rotation axis CL2 toward the motor 5 side.
  • the tip end of the split shaft portion 30e is pivotally supported by the side plate bearing 39 provided in the housing 3.
  • the driven side scroll member 90 is configured to rotate around the driven side rotation axis CL2 via the second side plate 30 and the first side plate 27.
  • the split shaft portion 30e is a shaft portion that is split in the circumferential direction, and for example, three split shaft portions are provided at equal intervals in the circumferential direction.
  • a lubricant space for containing a lubricant is provided between the first side plate 27 and the center plate 20 and in the central region where the rotation axes CL1 and CL2 are located.
  • the first side plate groove portion 27c is formed in the central portion of the first side plate 27 to be a recess.
  • a center plate groove 20c is formed in the center of the center plate 20 so as to be a recess. These groove portions 27c and 20c are formed so that their opening sides face each other. Note that only one of the groove portions 27c and 20c may be adopted.
  • the effects of the present embodiment are as follows.
  • An internal space sealed by the first side plate 27, the second side plate 30, and the center plate 20 is formed, and a synchronous drive unit for the pin 15 and the pin bearing 18 is provided in the internal space. Since the center plate 20 is in sliding contact with the first side plate 27 to form a closed space, the lubricant is supplied.
  • Grooves 27c, 20c are provided between the first side plate 27 and the center plate 20 and in the regions on the rotation axis lines CL1, CL2 side as lubricant space portions for containing a lubricant.
  • FIG. 7 is a plan view of the center plate 20 from the center plate groove portion 20c side.
  • a plurality of radial groove portions (lubricant introduction flow paths) 20d are formed radially outward from the center plate groove portion 20c formed in the center.
  • Each radial groove portion 20d is provided so as to be inclined so as to have an attack angle with respect to the rotation direction. As a result, the lubricant is guided from the outer peripheral side to the central side by utilizing the rotation.
  • the radial groove 20d guides the lubricant existing between the first side plate 27 and the center plate 20 to the center center plate groove 20c, it is possible to further prevent the lubricant from becoming insufficient on the center side. it can.
  • the same configuration as the radial groove portion 20d may be provided in the first side plate 27, and the radial groove portions may be provided in the plates 27 and 20 on both sides. Alternatively, only one of the plates 27, 20 may be provided with the radial groove portion.
  • FIG. 8 shows a cross section taken along the section line AA of FIG.
  • FIG. 8 is an enlarged view of the first driving side wall body 71b at the tip in the height direction.
  • a tip seal groove 72c for accommodating a tip seal is formed at the tip in the height direction of the first driving side wall body 71b.
  • the cross section of the tip seal groove 72c has a shape in which the bottom is narrow and the opening side is wide.
  • the first inclined wall portion 71c1 is provided so that the radially outer wall surface centering on the drive side rotation axis CL1 is inclined radially outward toward the distal end side, and the radially inner wall surface is toward the distal end side.
  • the second inclined wall portion 71c2 is provided so as to incline radially inward.
  • the inclination angles of the first inclined wall portion 71c1 and the second inclined wall portion 71c2 are symmetrical.
  • the tip seal that has been subjected to the centrifugal force moves to the tip side, that is, the end plate side that faces the tip inclined side along the first inclined wall portion 71c1.
  • the sealing performance of the tip seal can be improved.
  • the pressure ratio of both rotary scroll compressors 1 is small, it is effective because a sufficient force for floating the tip seal cannot be obtained.
  • the second inclined wall portion 71c2 is provided symmetrically with the first inclined wall portion 71c1, the workability of the chip seal groove is improved.
  • the second inclined wall portion 71c2 may be a wall portion that is erected substantially vertically without being inclined.
  • FIG. 9 shows a cross section taken along the line BB in FIG.
  • FIG. 9 is an enlarged view of the top end of the first drive sidewall body 71b in the height direction.
  • the third tip inclined toward the tip on the outer side in the circumferential direction toward the tip side in the height direction of the first drive side wall body 71b.
  • An inclined wall portion 71c3 is provided.
  • the tip seal moves outward in the circumferential direction.
  • the tip seal can be moved to the end plate side along the third inclined wall portion 71c3. As a result, the sealing performance of the tip seal can be improved.
  • the inclined wall portions 71c1, 71c2, 71c3 are provided on the first drive side wall body 71b, but other drive side scroll members 72, 73 and driven side scroll members 91, 92 are provided. It may be provided in. Further, the inclined wall portions 71c1, 71c2, 71c3 can be used not only in the double-rotation scroll compressor 1 having three double-teeth scroll members 71, 91, 92 as in the present embodiment, but also in the single-teeth
  • the present invention can be applied to both rotary scroll compressors that are configured only with the above scroll members, and to both rotary scroll compressors that combine one double-toothed scroll member and two single-toothed scroll members. That is, the present invention can be applied to both rotary scroll compressors including a drive side scroll member and a driven side scroll member.
  • FIG. 10 shows a plan view of the first drive side scroll member 71.
  • a flange portion (projection portion) 74 that projects radially outward from the outer peripheral surface is provided at the winding end portion of the first drive sidewall body 71b.
  • the flange portion 74 is used when fastening the drive side scroll members 71, 72, 73 to each other. Therefore, the hole portion 74a for fastening the bolt is provided. Further, the flange portion 74 may include a hole portion for positioning.
  • An arc portion 75a which projects outward in the radial direction and has its center on the drive-side rotation axis CL1, is provided on the outer side in the circumferential direction of the flange portion 74.
  • the arc portion 75a has a shape formed by extending the first drive side end plate 71a in the outer peripheral direction.
  • the arc portion 75a is provided at the winding end portion of each wall 71b. That is, in the present embodiment, three are provided with an angular interval of 120°.
  • the arc portion 75a has an arc shape having a center on the drive-side rotation axis CL1 which is the center position of the end plate, when the first drive-side scroll member 71 is processed by a chuck of a machine tool. It can be positioned easily and accurately, and the workability can be improved.
  • an arc portion 75b may be provided on the inner side in the circumferential direction of the flange portion 74.
  • the inner wall of the arc portion 75b in the circumferential direction is not provided with a protrusion corresponding to the end plate 71a up to the wall bodies 71b adjacent in the circumferential direction. Therefore, in this region, the outer peripheral surface of the wall body 71b constitutes the outer shape of the scroll member 71. As a result, the scroll member 71 is downsized.
  • an arcuate portion 75c is formed on the circumferentially outer side portion of the first drive side wall body 71b located radially inward of the winding end position of the first drive side wall body 71b in the circumferential direction. It may be provided.
  • a projecting portion corresponding to the end plate 71a does not exist outside the arc portion 75c in the circumferential direction, and the outer peripheral surface of the first drive sidewall body 71b constitutes the outer shape of the scroll member 71. Since the arc portion 75c is provided at the position of FIG. 12, the distance from the end plate center of the arc portion 75c can be made smaller than that of the arc portion 75a of FIG. 10 and the arc portion 75b of FIG. Power can be reduced.
  • the above-described arc portions 75a, 75b, 75c may be applied not only to the first drive side scroll member 71 but also to the other scroll members 72, 73, 91, 92. Further, the arcuate portions 75a, 75b, 75c can be used not only in the double-rotating scroll compressor 1 having three double-teeth scroll members 71, 91, 92 as in the present embodiment, but also in the single-teeth
  • the present invention can be applied to both the rotary scroll type compressor configured only with the scroll member and the double rotary scroll type compressor in which the scroll member having one both teeth and the scroll member having two single teeth are combined. That is, the present invention can be applied to both rotary scroll compressors including a drive side scroll member and a driven side scroll member.
  • FIG. 13 shows the first drive side scroll member 71.
  • An end plate extension portion 76 protruding outward in the radial direction is provided at a circumferentially outer side portion of the first drive sidewall body 71b located radially inward with respect to a winding end position in the circumferential direction of the first drive sidewall body 71b.
  • the end plate extension portion 76 is used as the outermost end plate portion when the suction is cut off.
  • the end plate extension portion 76 has a small protruding portion 76a having a radial dimension smaller than the thickness of the opposing wall bodies 72b and 73b.
  • a protrusion corresponding to the end plate 71a is not provided between the end plate extension 76 and the flange 74. Therefore, in this region, the outer peripheral surface of the wall body 71b constitutes the outer shape of the scroll member 71.
  • abradable coating is applied to the facing surface 76b of the small projecting portion 76a that faces the tips in the height direction of the walls 72b and 73b.
  • a resin such as epoxy type or Teflon (registered trademark) is used.
  • the end plate extension portion 76 faces the height-direction tips of the walls 72b and 73b.
  • the tip ends in the height direction of the wall bodies 72b and 73b facing each other. Since it protrudes from the small protruding portion 76a (see FIG. 14), the tip seal cannot be provided at the tips in the height direction of the opposing wall bodies 72b and 73b. Therefore, the abradable coating is applied to the facing surface 76b of the small protruding portion 76a facing the walls 72b and 73b.
  • the size of the gap between the small projecting portion 76a and the heightwise ends of the walls 72b, 73b can be made as small as possible, and the sealing performance can be improved.
  • abradable coating may be applied to the surface of the first drive sidewall body 71b facing the small protruding portion 76a at the tip in the height direction.
  • the abradable coating described above may be applied not only to the first drive side scroll member 71 but also to the other scroll members 72, 73, 91 and 92.
  • the abradable coating can be used not only in the double-rotating scroll type compressor 1 having three double-teeth scroll members 71, 91, 92 as in the present embodiment, but also in the single-teeth scroll member.
  • the double rotary scroll type compressor configured as described above or a double rotary scroll type compressor in which a scroll member having one double tooth and a scroll member having two single teeth are combined can be applied. That is, the present invention can be applied to both rotary scroll compressors including a drive side scroll member and a driven side scroll member.
  • a seventh embodiment of the present disclosure will be described.
  • the same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.
  • a (fastening portion) 74 is provided.
  • FIG. 15 shows an enlarged connection structure of the first drive side scroll member 71 and the second drive side scroll member 72.
  • the height direction tip of the first drive side wall body 71b of the first drive side scroll member 71 and the height direction tip of the flange portion 74 are at the same height H.
  • the flange portion 74 of the second driving side scroll member 72 has a height higher than that of the second driving side wall body 72b so as to come into contact with the flange portion 74 of the first driving side scroll member 71. There is.
  • the first drive-side scroll member 71 Since the first drive-side scroll member 71 has both teeth, the first drive-side scroll member 71 also has a flange 74 (left-hand flange 74 in FIG. 15) facing the third drive-side scroll member 73 (see FIG. 1).
  • the height is preferably the same as the height of the driving side wall body 71b.
  • the height direction tip of the first drive side wall body 71b and the height direction tip of the flange portion 74 are at the same height H, it is not necessary to change the position in the height direction at the time of machining. The time can be shortened.
  • the fastening structure of the driving side scroll members 71, 72, 73 has been described, but it can also be used for the flange portion for fastening the driven side scroll members 91, 92.

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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)

Abstract

L'invention concerne un compresseur à spirale à rotation bidirectionnelle étant pourvu : d'un premier élément en spirale côté entraînement (71) à double denture ; d'un premier élément en spirale côté entraîné (91) à double denture qui s'engrène avec le premier élément en spirale côté entraînement (71) ; d'un second élément en spirale côté entraînement (72) qui s'engrène avec le premier élément en spirale côté entraîné (91) ; d'un second élément en spirale côté entraîné (92) qui s'engrène avec le premier élément en spirale côté entraînement (71) ; et d'un mécanisme d'entraînement synchrone comprenant un axe (15) et un palier d'axe (18) pour transmettre une force d'entraînement d'un côté partie d'entraînement vers le premier élément en spirale côté entraîné (91) et vers le second élément en spirale côté entraîné (92) de telle sorte que le premier élément en spirale côté entraînement (71), le second élément en spirale côté entraînement (72), le premier élément en spirale côté entraîné (91) et le second élément en spirale côté entraîné (92) tournent dans la même direction avec la même vitesse angulaire.
PCT/JP2019/003047 2019-01-30 2019-01-30 Compresseur à spirale à rotation bidirectionnelle Ceased WO2020157841A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE112019006759.1T DE112019006759T5 (de) 2019-01-30 2019-01-30 Korotierender Scroll-Verdichter
PCT/JP2019/003047 WO2020157841A1 (fr) 2019-01-30 2019-01-30 Compresseur à spirale à rotation bidirectionnelle
JP2020568927A JP7143450B2 (ja) 2019-01-30 2019-01-30 両回転スクロール型圧縮機

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PCT/JP2019/003047 WO2020157841A1 (fr) 2019-01-30 2019-01-30 Compresseur à spirale à rotation bidirectionnelle

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WO2024202334A1 (fr) * 2023-03-24 2024-10-03 株式会社豊田自動織機 Compresseur à spirales corotatives

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JPH07301101A (ja) * 1994-05-06 1995-11-14 Daikin Ind Ltd スクロール形流体機械
JPH07324688A (ja) * 1994-05-30 1995-12-12 Daikin Ind Ltd 共回り型スクロール流体機械
JPH0988851A (ja) * 1995-09-29 1997-03-31 Ntn Corp 容積形圧縮機のスクロール部材の製造方法
JPH09195958A (ja) * 1996-01-16 1997-07-29 Nippon Soken Inc スクロール型圧縮機
JP2002371978A (ja) * 2001-06-12 2002-12-26 Anest Iwata Corp スクロール流体機械
JP2013174241A (ja) * 2013-04-10 2013-09-05 Ricchisutoon:Kk スクロール流体機械
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WO2024202334A1 (fr) * 2023-03-24 2024-10-03 株式会社豊田自動織機 Compresseur à spirales corotatives

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