EP3418569B1 - Offener kältemittelverdichter - Google Patents

Offener kältemittelverdichter Download PDF

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Publication number
EP3418569B1
EP3418569B1 EP17827539.2A EP17827539A EP3418569B1 EP 3418569 B1 EP3418569 B1 EP 3418569B1 EP 17827539 A EP17827539 A EP 17827539A EP 3418569 B1 EP3418569 B1 EP 3418569B1
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EP
European Patent Office
Prior art keywords
refrigerant
refrigerant gas
housing
compression mechanism
open
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.)
Active
Application number
EP17827539.2A
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English (en)
French (fr)
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EP3418569A1 (de
EP3418569A4 (de
Inventor
Hajime Sato
Yoshiaki Miyamoto
Hisao Mizuno
Akihiro Noguchi
Takashi Goto
Toshiyuki Shikanai
Syusaku Goto
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 Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
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Publication date
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Publication of EP3418569A1 publication Critical patent/EP3418569A1/de
Publication of EP3418569A4 publication Critical patent/EP3418569A4/de
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Publication of EP3418569B1 publication Critical patent/EP3418569B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • 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
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0028—Internal leakage control
    • 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
    • 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

Definitions

  • the present invention relates to an open-type refrigerant compressor which compresses a refrigerant gas, and more specifically, relates to an open-type refrigerant compressor which prevents wear of a seal member provided in a portion where a drive shaft protrudes from a housing.
  • a compression mechanism which compresses refrigerant gas in a car air conditioner or the like
  • a compression mechanism is accommodated inside a housing formed of an aluminum alloy or the like
  • a drive shaft driving the compression mechanism protrudes from one side of the housing
  • a pulley having an electromagnetic clutch provided on the protrusion portion is driven by an engine or the like via a belt.
  • a shaft hole through which the drive shaft protrudes is formed in the housing, and thus, the refrigerant compressor is referred to as an open-type refrigerant compressor.
  • a refrigerant compressor in which a compression mechanism and a drive motor are housed inside a sealed pressure container is referred to as a closed-type refrigerant compressor.
  • a lip seal (an oil seal having a lip) is provided in the protrusion portion of the drive shaft, that is, the shaft hole of the housing, and thus, a refrigerant gas inside the housing is prevented from leaking to the outside.
  • the lip seal is lubricated by a lubricant mixed with the refrigerant gas.
  • oil supplied to the lip seal is insufficient at a low load operation where a circulation amount of the refrigerant gas decreases or the like. In this case, a tip end of the lip wears, and there is a concern that the refrigerant gas and the oil leak.
  • PTL 1 discloses an open-type refrigerant compressor in which a guide groove or a communication hole communicating with a lip seal and a bearing member around the lip seal is formed on an inner wall surface of a housing, and a refrigerant gas and a lubricant flowing through an inside of the housing are supplied to the lip seal and the bearing member via the oil passage during an operation.
  • the present invention is made in order to solve the problems, and an object thereof is to provide an open-type refrigerant compressor capable of reliably lubricating the seal member provided in a portion where the drive shaft protrudes from the housing by the lubricant contained in the refrigerant gas and preventing wear of the seal member.
  • an open-type refrigerant compressor including: a housing; a suction port which is formed in the housing; a compression mechanism which is provided inside the housing and compresses a refrigerant gas containing a lubricant; a drive shaft which drives the compression mechanism; a seal member which is provided in a shaft hole through which the drive shaft protrudes from the housing to an outside so as to prevent the refrigerant gas from leaking from an inside of the housing to the outside thereof; a refrigerant supply passage which is continuous from the inside of the housing to the seal member; and a refrigerant gas distribution portion which distributes the refrigerant gas introduced from the suction port to the inside of the housing to the refrigerant supply passage side and the compression mechanism side, in which a distribution ratio of the refrigerant gas distributed by the refrigerant gas distribution portion is set such that an amount distributed to the refrigerant supply passage side is greater than an amount distributed to the compression mechanism side.
  • the refrigerant gas introduced from the suction port to the inside of the housing is distributed to the refrigerant supply passage side and the compression mechanism side by the refrigerant gas distribution portion.
  • the refrigerant gas distributed to the refrigerant supply passage side flows to the seal member, and the seal member is lubricated by the lubricant contained in the refrigerant gas.
  • the refrigerant gas distributed to the compression mechanism side is compressed by the compression mechanism, becomes a compressed refrigerant gas, and is discharged from the discharge port formed in the housing.
  • the distribution ratio of the refrigerant gas by the refrigerant gas distribution portion is set such that the distribution amount to the refrigerant supply passage side is greater than the distribution amount to the compression mechanism side, and thus, a sufficient amount of refrigerant gas can be supplied to the seal member. Accordingly, the seal member is preferentially lubricated by the lubricant contained in the refrigerant gas, a lubrication state of the seal member is improved, and thus, it is possible to prevent wear of the seal member. Thereafter, the refrigerant gas supplied to the seal member flows to the compression mechanism side, lubricates other mechanisms or the like, and is compressed by the compression mechanism so as to be a compressed refrigerant gas.
  • the distribution ratio of the refrigerant gas distributed by the refrigerant gas distribution portion may be set such that an entire amount of the refrigerant gas introduced from the suction port to the inside of the housing flows to the refrigerant supply passage side. Accordingly, the entire amount of the refrigerant gas sucked from the suction port initially flows to the seal member, and thus, the amount of the lubricant supplied to the seal member becomes the maximum amount. Therefore, a lubrication state of the seal member is maximally improved.
  • the refrigerant gas distribution portion may be attached to the inside of the housing as a separate part. Accordingly, it is possible to freely set the distribution amount of the refrigerant gas by appropriately setting the shape of the refrigerant gas distribution portion.
  • the refrigerant supply passage may be formed by covering a refrigerant supply groove formed on an inner surface of the housing with the refrigerant gas distribution portion.
  • the shape of the refrigerant gas distribution portion may have any shape as long as it has a shape capable of covering the refrigerant supply groove formed on the inner surface of the housing, and thus, it is possible to simplify the shape of the refrigerant gas distribution portion.
  • a terminal portion of the refrigerant supply passage may communicate with a seal space which is formed between the seal member and a bearing member disposed on the compression mechanism side of the seal member. Accordingly, the refrigerant gas supplied to the seal space passes through a gap with the bearing member and flows to compression mechanism side, and thus, the bearing member can be favorably lubricated, and even when the amount of the refrigerant supplied to the seal member is excessive, it is possible to prevent a pressure of the refrigerant gas applied to the seal member from excessively increasing, and it is possible to prevent the refrigerant from leaking to the outside.
  • a refrigerant discharge passage through which the refrigerant gas is introduced from the seal member to the compression mechanism side may be provided. Accordingly, the refrigerant gas and the lubricant supplied to the seal member are introduced to the compression mechanism side by the refrigerant discharge passage so as to form steady flows of the refrigerant gas and the lubricant, and thus, it is possible to favorably lubricate the respective portions of the open-type refrigerant compressor.
  • a seal member provided in a portion where a drive shaft protrudes from a housing can be reliably lubricated by a lubricant contained in a refrigerant gas, and it is possible to prevent wear of the seal member.
  • Fig. 1 is a partially longitudinal sectional view of an open-type scroll compressor (open-type refrigerant compressor) showing an embodiment of the present invention.
  • an open-type scroll compressor 1 according to the present embodiment is used for a car air conditioner which is installed in an engine room of an automobile, is driven by engine power, and is configured to compress a refrigerant gas.
  • the present invention is not limited to this, and the present invention may be applied to an open-type compressor used for living space air conditioning, a refrigeration system, a heat pump type hot water supply system, or the like.
  • the open-type scroll compressor 1 includes an approximately cylindrical housing 2 formed of an aluminum alloy or the like.
  • the housing 2 includes a housing main body 2A constituting a main body, and a housing cover 2B which is fixed by a bolt or the like so as to airtightly close an opening portion provided on one end of the housing main body 2A. The other end (not shown) of the housing main body 2A is closed.
  • a scroll compression mechanism 4 compression mechanism and a drive shaft 5 are accommodated in an internal space S1 of the housing 2.
  • a drive shaft 5 is rotatably supported by the housing cover 2B via a main bearing 6 and a sub bearing 7 (bearing member).
  • a main bearing 6 For example, a single row deep groove ball bearing is used as the main bearing 6 and a needle bearing is used as the sub bearing 7.
  • One end of the drive shaft 5 protrudes to the outside through a shaft hole 8 which is formed in the housing cover 2B.
  • the sub bearing 7 is press-fitted to the inside of the shaft hole 8, and a lip seal 9 (seal member) is press-fitted to the outer side of the sub bearing 7.
  • the lip seal 9 is inclined toward the sub bearing 7 and includes a lip 9a lightly pressed against an outer peripheral surface of the drive shaft 5.
  • a pulley 12 is rotatably installed on a tip outer peripheral portion of the housing cover 2B via a pulley bearing 11, and a belt (not shown) is wound between the pulley 12 and a drive pulley provided in a driving source such as an engine (not shown).
  • a clutch plate 13 fixed to a tip end portion of the drive shaft 5 faces an outer end surface of the pulley 12 to be close to the outer end surface, and if an electromagnetic clutch 14 fixed to the housing cover 2B so as to be positioned inside the pulley 12 is excited, the clutch plate 13 is pulled toward the pulley 12 side to frictionally engage with the outer end surface of the pulley 12, a rotation of the pulley 12 is transmitted to the drive shaft 5, and the drive shaft 5 rotates.
  • a crank pin 5a which is eccentric by a predetermined dimension with respect to a center axis of the drive shaft 5 is integrally formed on a rear end of the drive shaft 5, and the crank pin 5a is fitted to a boss 18a, which is formed on a rear surface of an orbiting scroll 18 of the scroll compression mechanism 4, via a drive bush 16 and a drive bearing 17.
  • the scroll compression mechanism 4 has a known configuration in which the orbiting scroll 18 and a fixed scroll (not shown) engage with each other to be shifted by a phase of 180°, and if the drive shaft 5 rotates, the orbiting scroll 18 is driven so as to revolve with respect to the fixed scroll by an operation of a rotation prevention mechanism 19, a pair of compression chambers (not shown) formed between both scrolls is moved from an outer peripheral position to a center position, and thus, a volume gradually decreases.
  • the refrigerant gas sucked from the suction port 3 into the internal space S1 of the housing 2 is sucked and compressed by the scroll compression mechanism 4, is discharged from the discharge port, and is supplied to a condenser (not shown) or the like.
  • a member 20 is a balancer weight.
  • the refrigerant gas contains a lubricant (refrigerating machine oil) at a predetermined ratio, and respective internal mechanism portions such as the main bearing 6, the sub bearing 7, the lip seal 9, the crank pin 5a, the drive bush 16, the drive bearing 17, the rotation prevention mechanism 19, or the scroll compression mechanism 4 is lubricated by a mist of the lubricant.
  • the lip seal 9 is a seal member which prevents the refrigerant gas and the lubricant from leaking from the inside of the housing 2 to the outside thereof, and the lip 9a is lubricated by oil contained in the refrigerant gas so as to prevent wear of the lip 9a.
  • the oil supplied to the lip seal 9 is insufficient and a tip of the lip 9a wears.
  • the open-type scroll compressor 1 is configured such that the refrigerant gas sucked from the suction port 3 preferentially flows to the lip seal 9 side rather than to the internal space S1 side of housing 2. This configured is as follows.
  • a refrigerant introduction space S2 is defined inside the suction port 3.
  • the refrigerant introduction space S2 is formed as a room having a predetermined volume (approximately several cubic centimeters) by closing a bottom portion of a refrigerant passage hole 2Bb (existing hole in the related art) penetrating an insertion flange 2Ba of the housing cover 2B inserted into the opening portion of the housing main body 2A using a partition plate 22 (refrigerant gas distribution portion) shown in Fig. 2 .
  • the suction port 3 and the refrigerant introduction space S2 are positioned on a top portion of the housing 2.
  • the partition plate 22 does not exist, and thus, the suction port 3 communicates with the internal space S1 as it is via the refrigerant passage hole 2Bb.
  • the partition plate 22 is attached to the inside of the housing 2 (2B) by two bolts 23 as separate parts.
  • the partition plate 22 has a shape formed by bending a sheet metal material in a stepwise manner, and as shown in Figs. 1 and 2 , includes, in order from a center side of the housing 2, a first vertical surface 22a, a first horizontal surface 22b, a second vertical surface 22c, and a second horizontal surface 22d.
  • the second horizontal surface 22d is a surface which is a bottom portion of the refrigerant introduction space S2, and bolt holes 22e are drilled on both horizontal end portions of the first vertical surface 22a.
  • refrigerant guide grooves 25 are formed on an inner peripheral surface of the shaft hole 8, to which the sub bearing 7 is press-fitted, at regular intervals in a circumferential direction.
  • the refrigerant guide grooves 25 are respectively disposed at 12 o'clock, 3 o'clock, 6 o'clock, 9 o'clock positions (see Fig. 3 ) in a dial of a timepiece, tips of the refrigerant guide grooves 25 communicate with a seal space S3 formed between the lip seal 9 and the sub bearing 7, and rear ends thereof communicate with the internal space S1 of the housing 2.
  • Fig. 1 and 3 four refrigerant guide grooves 25 are formed on an inner peripheral surface of the shaft hole 8, to which the sub bearing 7 is press-fitted, at regular intervals in a circumferential direction.
  • the refrigerant guide grooves 25 are respectively disposed at 12 o'clock, 3 o'clock, 6 o'clock, 9 o'clock positions (see Fig. 3 ) in a dial of
  • the sub bearing 7 includes an outer ring member 7a, an inner ring member 7b, a plurality of roller-shaped rolling members 7c disposed between the inner and outer ring members 7a and 7b, and a retainer 7d which holds the plurality of rolling members 7c at regular intervals.
  • oil supply holes 7e are formed at positions aligned with the refrigerant guide grooves 25.
  • refrigerant discharge passages 27 which extends in a radial direction from an axial line of the drive shaft 5 and communicate with the internal space S1 of the housing 2 are formed from the refrigerant guide grooves 25 positioned at the 3 o'clock, 6 o'clock, and 9 o'clock positions.
  • three refrigerant discharge passages 28 penetrating the insertion flange 2Ba of the housing cover 2B are formed in accordance with the positions of the three refrigerant discharge passage 27.
  • the refrigerant discharge passages 27 and 28 are passages through which the refrigerant gas supplied to the lip seal 9 is introduced to the scroll compression mechanism 4 side.
  • a cladding portion 31 having a height of several millimeters is formed on an upper inner wall surface of a portion where the shaft hole 8 is open toward the internal space S1 side, a refrigerant supply groove 32a extending in a vertical direction shown in Fig. 1 is formed at a center portion of the cladding portion 31 in a width direction, and bolt holes 33 are formed on both sides of the refrigerant supply groove 32a. It is not essential to form the cladding portion 31, and the cladding portion 31 may be omitted as long as the refrigerant supply groove 32a can be formed.
  • a refrigerant supply groove 32b which extends horizontally from an upper end portion of the refrigerant supply groove 32a toward the main bearing 6 side is formed (refer to Figs. 1 and 2 ).
  • One refrigerant guide passage 29 which is formed similarly to the above-described three refrigerant discharge passages 28 communicates with the refrigerant supply groove 32b, and the other end of the refrigerant guide passage 29 communicates with the refrigerant introduction space S2.
  • the first vertical surface 22a abuts against the cladding portion 31 and is fastened to the bolt holes 33 by two bolts 23. Accordingly, as described above, the bottom portion of the refrigerant introduction space S2 is closed by the second horizontal surface 22d of the partition plate 22.
  • the refrigerant supply grooves 32a and 32b are respectively covered with the first vertical surface 22a and the first horizontal surface 22b of the partition plate 22, and the refrigerant supply grooves 32a and 32b are passages which are separated from the internal space S1, respectively.
  • the second horizontal surface 22d of the partition plate 22 is interposed between the outer peripheral surface of the main bearing 6 and the housing cover 2B.
  • the partition plate 22 may be divided into two portions with the main bearing 6 as a boundary, and the divided portions may be individually fixed to the inner surface of the housing 2.
  • the refrigerant supply passage 35 which is continuous from the refrigerant introduction space S2 to the lip seal 9 is formed by the uppermost refrigerant guide groove 25 (positioned at the 12 o'clock position shown in Fig. 3 ), the refrigerant supply groove 32a, the refrigerant supply groove 32b, and the refrigerant guide passage 29.
  • a terminal portion of the refrigerant supply passage 35 is the refrigerant guide groove 25 which is formed on the inner peripheral surface of the shaft hole 8, and thus, the terminal portion communicates with the seal space S3 between the lip seal 9 and the sub bearing 7.
  • the partition plate 22 functions as a refrigerant gas distribution portion which distributes the refrigerant gas introduced from the suction port 3 into the refrigerant introduction space S2 to the refrigerant supply passage 35 side and the scroll compression mechanism 4 side.
  • a distribution ratio of the refrigerant gas distributed by the partition plate 22 is set such that an amount of the refrigerant gas distributed to the refrigerant supply passage 35 side is significantly greater than an amount of the refrigerant gas distributed to the scroll compression mechanism 4 side. That is, a shape of the partition plate 22 is determined such that a flow resistance of the refrigerant gas from the refrigerant introduction space S2 to the refrigerant supply passage 35 side is significantly smaller than a flow resistance of the refrigerant gas from the refrigerant introduction space S2 to the scroll compression mechanism 4 side.
  • the bottom portion of the refrigerant introduction space S2 is completely closed by the second horizontal surface 22d of the partition plate 22, and thus, the distribution ratio of the refrigerant gas is set such that substantially the entire amount of the refrigerant gas introduced into the refrigerant introduction space S2 flows to the refrigerant supply passage 35 side.
  • no sealing means is provided between the respective surfaces 22a to 22d of the partition plate 22 and the refrigerant introduction space S2 (housing cover 2B), there is a gap between the two sides 22 and 2B, and thus, a small amount of the refrigerant gas flowing into the refrigerant introduction space S2 leaks from the gap to the scroll compression mechanism 4 side (internal space S1 side).
  • the scroll compression mechanism 4 sucks the refrigerant gas, and thus, a negative pressure is generated in the internal space S1 of the housing 2, and the refrigerant gas is introduced from the suction port 3 to the refrigerant introduction space S2 by the negative pressure.
  • the introduced refrigerant gas is distributed into the refrigerant supply passage 35 side and the scroll compression mechanism 4 side (internal space S1 side) by the partition plate 22.
  • the present embodiment is set such that substantially the entire amount of the refrigerant gas introduced into the refrigerant introduction space S2 is distributed to the refrigerant supply passage 35 side.
  • the refrigerant gas distributed from the refrigerant introduction space S2 to the refrigerant supply passage 35 side flows from the refrigerant guide passage 29 which is a starting point of the refrigerant supply passage 35, flows to the seal space S3 via the refrigerant supply grooves 32 and 32b and the upper refrigerant guide groove 25 (the refrigerant guide groove 25 positioned at the 12 o'clock position shown in Fig. 3 ) which is the terminal portion of the refrigerant supply passage 35, and lubricates the lip seal 9 and the sub bearing 7 by a misty lubricant contained in the refrigerant gas.
  • the refrigerant gas passes through the upper refrigerant guide groove 25, the refrigerant gas flows to the inside of the sub bearing 7 from the oil supply holes 7e formed on the outer ring member 7a of the sub bearing 7 to lubricate the sub bearing 7.
  • the refrigerant gas (lubricant) which has lubricated the sub bearing 7 is discharged to the internal space S1 side through the refrigerant guide grooves 25 positioned at the 3 o'clock, 6 o'clock, 9 o'clock positions shown in Fig. 3 , the three refrigerant discharge passage 27 extending from the three refrigerant guide grooves 25, and the refrigerant discharge passages 28 aligned therewith, and joins with the refrigerant gas which has passed through the gap between the refrigerant introduction space S2 and the partition plate 22.
  • the refrigerant gas After the refrigerant gas passes through the main bearing 6 and lubricates the main bearing, the refrigerant gas is supplied to the crank pin 5a, the drive bush 16, the drive bearing 17, the rotation prevention mechanism 19, the scroll compression mechanism 4, or the like so as to lubricate these. Thereafter, the refrigerant gas is sucked into the scroll compression mechanism 4 so as to be compressed, becomes a compressed refrigerant gas, and is discharged from the discharge port formed in the housing 2 so as to be supplied to a demand unit such as a condenser.
  • the distribution amount of the refrigerant gas flowing from the refrigerant introduction space S2 to the refrigerant supply passage 35 side is set to be greater than the distribution amount of the refrigerant gas flowing from the refrigerant introduction space S2 to the scroll compression mechanism 4 side (internal space S1) by the partition plate 22, and thus, a sufficient amount of refrigerant gas can be supplied to the lip seal 9. Accordingly, even at the time of the low load operation in which the circulation amount of the refrigerant gas decreases, the lip seal 9 is preferentially lubricated by the lubricant contained in the refrigerant gas, a lubrication state of the lip seal 9 is improved, and thus, it is possible to prevent wear of the lip 9a.
  • the distribution ratio of the refrigerant gas by the partition plate 22 is set such that substantially the entire amount of the refrigerant gas introduced into the refrigerant introduction space S2 flows to the refrigerant supply passage 35 side, substantially the entire amount of the refrigerant gas sucked from the suction port 3 initially flows to the lip seal 9. Accordingly, the amount of the lubricant supplied to the lip seal 9 becomes the maximum amount, the lubrication state of the lip seal 9 is maximally improved, and it is possible to prevent the wear of the lip 9a.
  • the partition plate 22 is attached to the inside of the housing 2 as a separate part, and thus, it is possible to freely set the distribution amount of the refrigerant gas by appropriately setting the shape of the partition plate. For example, it is possible to easily change the refrigerant gas distribution ratio by drilling a hole in the second horizontal surface 22d or the like of the partition plate 22 or bending (deforming) the partition plate 22 (22a to 22d) so as to widen a gap between the partition plate 22 and the refrigerant introduction space S2 or the housing cover 2B (cladding portion 31).
  • a portion of the refrigerant supply passage 35 is formed by covering the refrigerant supply grooves 32a and 32b formed on the inner surface of the housing 2 with the first vertical surface 22a and the first horizontal surface 22b of the partition plate 22.
  • the shape of the partition plate 22 may have any shape as long as it has a flat shape capable of covering the refrigerant supply grooves 32a and 32b, and thus, it is possible to simplify the shape of the partition plate 22.
  • the partition plate 22 is formed of a sheet metal material, respective surfaces 22a to 22d have flat shapes so as to be simplified, and the partition plate 22 is easily manufactured.
  • the refrigerant guide groove 25 which is the terminal portion of the refrigerant supply passage 35 communicates with the seal space S3 which is formed between the lip seal 9 and the sub bearing 7, and thus, the refrigerant gas supplied to the lip seal 9 passes through the gap with the sub bearing 7 and flows to the scroll compression mechanism 4 side. Accordingly, the sub bearing 7 is favorably lubricated, and even when the amount of the refrigerant supplied to the lip seal 9 is excessive, it is possible to prevent a pressure of the refrigerant gas applied to the lip seal 9 from excessively increasing, and it is possible to prevent the refrigerant from leaking to the outside.
  • the refrigerant discharge passages 27 and 28 through which the refrigerant gas is introduced from the lip seal 9 to the scroll compression mechanism 4 side are provided. Accordingly, the refrigerant gas and the lubricant supplied to the lip seal 9 are introduced to the scroll compression mechanism 4 side by the refrigerant discharge passages 27 and 28 so as to form steady flows of the refrigerant gas and the lubricant, and thus, it is possible to favorably lubricate the respective portions of the open-type scroll compressor 1.
  • the lip seal 9 provided in the portion (shaft hole 8) where the drive shaft 5 protrudes from the housing 2 can be reliably lubricated by the lubricant contained in the refrigerant gas, and it is possible to prevent the wear of the lip seal 9 (lip 9a).
  • the refrigerant introduction space S2 formed inside the suction port 3 is configured by closing the bottom portion of the refrigerant passage hole 2Bb drilled in the insertion flange 2Ba of the housing cover 2B by the second horizontal surface 22d of the partition plate 22.
  • the refrigerant introduction space S2 may be formed by only the shape of the partition plate 22.
  • scroll type refrigerant compression mechanism instead of the scroll type refrigerant compression mechanism, another type refrigerant compression mechanism such as a rotary type compression mechanism, a vane type compression mechanism, or a swash plate type compression mechanism may be adopted.
  • a rotary type compression mechanism instead of the scroll type refrigerant compression mechanism, another type refrigerant compression mechanism such as a rotary type compression mechanism, a vane type compression mechanism, or a swash plate type compression mechanism may be adopted.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Rotary Pumps (AREA)

Claims (4)

  1. Offener Kältemittelverdichter, der Folgendes umfasst:
    ein Gehäuse (2);
    einen Ansauganschluss (3), der im Gehäuse (2) gebildet ist;
    einen Verdichtungsmechanismus (4), der im Gehäuse (2) bereitgestellt und dazu ausgelegt ist, ein Kältemittelgas, das ein Schmiermittel enthält, zu verdichten;
    eine Antriebswelle (5), die dazu ausgelegt ist, den Verdichtungsmechanismus (4) anzutreiben;
    ein Dichtungselement (9), das in einem Wellenloch (8), durch das die Antriebswelle (5) aus dem Gehäuse (2) zu einer Außenseite ragt, bereitgestellt ist, um zu verhindern, dass das Kältemittelgas von einer Innenseite des Gehäuses (2) zur Außenseite davon leckt;
    einen Kältemittelzuführungskanal (35), der von der Innenseite des Gehäuses (2) zum Dichtungselement (9) durchgehend ist; und
    einen Kältemittelgasverteilungsabschnitt (22), der dazu ausgelegt ist, das Kältemittelgas, das vom Ansauganschluss (3) in den Innenraum des Gehäuses (2) eingeleitet wird, auf die Seite des Kältemittelzuführungskanals (35) und die Seite des Verdichtungsmechanismus (4) zu verteilen,
    wobei ein Verteilungsverhältnis des Kältemittelgases, das vom Kältemittelgasverteilungsabschnitt (22) verteilt wird, derart eingestellt ist, dass eine Menge, die auf die Seite des Kältemittelzuführungskanals (35) verteilt wird, größer ist als eine Menge, die auf die Seite des Verdichtungsmechanismus (4) verteilt wird,
    wobei der offene Kältemittelverdichter dadurch gekennzeichnet ist, dass
    der Kältemittelgasverteilungsabschnitt (22) als ein separates Teil im Innenraum des Gehäuses (2) befestigt ist und
    mindestens ein Abschnitt des Kältemittelzuführungskanals (35) durch Abdecken einer Kältemittelzuführungsrinne (32a, 32b), die auf einer Innenfläche des Gehäuses (2) gebildet ist, mit dem Kältemittelgasverteilungsabschnitt (22) gebildet ist.
  2. Offener Kältemittelverdichter nach Anspruch 1,
    wobei das Verteilungsverhältnis des Kältemittelgases, das vom Kältemittelgasverteilungsabschnitt (22) verteilt wird, derart eingestellt ist, dass eine Gesamtmenge des Kältemittelgases, das vom Ansauganschluss (3) in den Innenraum des Gehäuses (2) eingeleitet wird, zur Seite des Kältemittelzuführungskanals (35) strömt.
  3. Offener Kältemittelverdichter nach Anspruch 1 oder 2,
    wobei ein Endabschnitt des Kältemittelzuführungskanals (35) mit einem Dichtungsraum (53) kommuniziert, der zwischen dem Dichtungselement (9) und einem Lagerelement (7), das auf der Verdichtungsmechanismusseite des Dichtungselements (9) angeordnet ist, gebildet ist.
  4. Offener Kältemittelverdichter nach einem der Ansprüche 1 bis 3,
    wobei ein Kältemittelabführungskanal (27, 28), durch den das Kältemittelgas vom Dichtungselement (9) zur Seite des Verdichtungsmechanismus (4) eingeleitet wird, bereitgestellt ist.
EP17827539.2A 2016-07-11 2017-07-06 Offener kältemittelverdichter Active EP3418569B1 (de)

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JP2016136771A JP6762785B2 (ja) 2016-07-11 2016-07-11 開放型冷媒圧縮機
PCT/JP2017/024878 WO2018012411A1 (ja) 2016-07-11 2017-07-06 開放型冷媒圧縮機

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CN112020633B (zh) * 2018-04-24 2024-06-18 安捷伦科技有限公司 分光光度计校准方法和系统
US11879464B1 (en) 2022-09-13 2024-01-23 Mahle International Gmbh Electric compressor having a swing link and integrated limit pin and swing link and integrated limit pin for use in an electric compressor
US11994130B2 (en) 2022-09-13 2024-05-28 Mahle International Gmbh Electric compressor bearing oil communication aperture
JP2024060884A (ja) * 2022-10-20 2024-05-07 三菱重工サーマルシステムズ株式会社 スクロール圧縮機

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JP3207308B2 (ja) * 1993-12-16 2001-09-10 株式会社デンソー スクロール型圧縮機
JPH0932745A (ja) * 1995-07-17 1997-02-04 Matsushita Electric Ind Co Ltd 開放型スクロール圧縮機
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EP3418569A4 (de) 2019-04-17
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JP2018009457A (ja) 2018-01-18
JP6762785B2 (ja) 2020-09-30

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