EP3318759A1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

Info

Publication number
EP3318759A1
EP3318759A1 EP16866107.2A EP16866107A EP3318759A1 EP 3318759 A1 EP3318759 A1 EP 3318759A1 EP 16866107 A EP16866107 A EP 16866107A EP 3318759 A1 EP3318759 A1 EP 3318759A1
Authority
EP
European Patent Office
Prior art keywords
lubricant oil
oil
scroll
rotational frequency
compression mechanism
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.)
Withdrawn
Application number
EP16866107.2A
Other languages
English (en)
French (fr)
Other versions
EP3318759A4 (de
Inventor
Masahiro Taniguchi
Yoshiyuki Kimata
Hajime Sato
Yogo Takasu
Youhei Hotta
Taichi Tateishi
Takuma YAMASHITA
Akihiro KANAI
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
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 Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3318759A1 publication Critical patent/EP3318759A1/de
Publication of EP3318759A4 publication Critical patent/EP3318759A4/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • 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
    • F04C29/028—Means for improving or restricting lubricant flow

Definitions

  • the present invention relates to a scroll compressor which is used in a refrigerator, an air-conditioning device, or the like.
  • a scroll compressor which includes a scroll compression mechanism which is accommodated in a housing and a drive motor which drives the scroll compression mechanism.
  • the scroll compression mechanism is configured to include a fixed scroll member and an orbiting scroll member on which spiral wraps are provided on a surface of a disk-shaped end plate, and in the scroll compression mechanism, a fixed scroll and an orbiting scroll face each other in a state where the spiral wraps mesh with each other and the orbiting scroll revolves around the fixed scroll.
  • a fluid (gas refrigerant) in the space is compressed by decreasing a volume of a compression space formed between wraps of both scrolls according to orbiting of the orbiting scroll.
  • the lubricant oil drawn by the lubricant oil pump After the lubricant oil drawn by the lubricant oil pump is supplied to each sliding portion, the lubricant oil falls and is returned to the bottom portion of the housing to circulate through the housing.
  • the fluid introduced into the housing is suctioned into a portion between a fixed scroll and an orbiting scroll while winding up the lubricant oil, and thus, the lubricant oil is mixed in the fluid. Accordingly, the lubricant oil mixed in the fluid seals a minute gap between the wraps of the fixed scroll and the orbiting scroll, and thus, a decrease in an operation efficiency of the compressor is prevented.
  • (A) For example, in order to prevent a decrease in an operation efficiency by sealing a gap between wraps during a low speed operation of approximately 50 rps, it is necessary to supply a sufficient amount of lubricant oil to each sliding portion.
  • (B) Meanwhile, for example, in a case where the amount of the lubricant oil discharged to the outside of the housing along with the fluid increases during a high speed operation of 150 rps or higher, there is a concern that the lubricant oil stored in the housing is insufficient, and thus, it is necessary to decrease the amount of the discharged lubricant oil. However, in a case where the amount supplied to each sliding portion increases, in general, the amount of the discharged lubricant oil also increases, and thus, it is difficult to satisfy both of the conditions (A) and (B).
  • the present invention is made in consideration of the above-described circumstances, and an object thereof is to provide a scroll compressor capable of preventing a decrease in an operation efficiency of the compressor during a low speed operation and decreasing an amount of lubricant oil discharged from the compressor during a high speed operation.
  • a scroll compressor including: a housing into which a low-pressure gas flows; a scroll compression mechanism which is accommodated in the housing and compresses the low-pressure gas; a drive motor which is connected to the scroll compression mechanism by a drive shaft to drive the scroll compression mechanism; a bearing portion which supports the drive shaft in a rotatable manner; and a lubricant oil pump which draws a lubricant oil stored in a bottom portion of the housing by a rotation of the drive shaft to supply the lubricant oil to each sliding portion of the scroll compression mechanism and the bearing portion, in which the lubricant oil pump is a positive-displacement pump which is operable in an operation region in which a rotational frequency of the drive motor is at least 150 rps or higher and an inclination indicating a rate of increase of an amount of oil supplied per unit time with respect to the rotational frequency decreases as the rotational frequency increases.
  • the scroll compressor may include an oil supply passage through which the lubricant oil supplied to the sliding portion flows and a return oil passage through which excess lubricant oil supplied to the sliding portion is returned into the housing, in which in a case where a minimum diameter in the oil supply passage is defined as d1, an equivalent diameter of the return oil passage is defined as d2, and an inner diameter of a suction port of the lubricant oil pump is defined as D, the inner diameter of the suction port of the lubricant oil pump may satisfy d1 ⁇ D s d2.
  • the minimum diameter d1 in the oil supply passage is equal to or less than the inner diameter D of the suction port, and thus, it is possible to reliably supply the lubricant oil drawn by the lubricant oil pump to the sliding portion.
  • the equivalent diameter d2 of the return oil passage is equal to or more than the inner diameter D of the suction port, and thus, an excess lubricant oil is prevented from staying in the return oil passage, and it is possible to prevent the lubricant oil stored in the bottom portion of the housing from being insufficient.
  • the lubricant oil pump may be a rolling piston type lubricant oil pump. According to this configuration, in the rolling piston type lubricant oil pump, a suction loss is generated during a high speed rotation, and thus, an amount of the supplied oil during a high speed operation of the compressor can be effectively suppressed.
  • the lubricant oil pump is the positive-displacement pump which is operable in the operation region in which the rotational frequency of the drive motor is at least 150 rps or higher and the inclination indicating the rate of increase of the amount of oil supplied per unit time with respect to the rotational frequency decreases as the rotational frequency increases. Accordingly, it is possible to prevent an operation efficiency of the compressor from decreasing during a low speed operation and decrease an amount of the lubricant oil discharged from the compressor during a high speed operation, and the operation can be performed in a wider rotational frequency region.
  • Fig. 1 is an overall sectional view of a scroll compressor according to the present embodiment.
  • a scroll compressor 1 compresses a suctioned fluid (for example, refrigerant) and discharges the compressed fluid, and in the present embodiment, the scroll compressor 1 is interposed between refrigerant flow paths through which the refrigerant circulates in an air-conditioning device, a refrigerator, or the like.
  • a suctioned fluid for example, refrigerant
  • the scroll compressor 1 includes a motor (drive motor) 5 which is driving means and a scroll compression mechanism 7 which is driven by the motor 5 in an interior space of a housing 3.
  • motor drive motor
  • scroll compression mechanism 7 which is driven by the motor 5 in an interior space of a housing 3.
  • the housing 3 includes a tubular housing main body 3a which vertically extends, a bottom portion 3b which closes a lower end of the housing main body 3a, and a cover portion 3c which closes an upper end of the housing main body 3a, and is a pressure container that is sealed in its entirety.
  • a suction pipe 9 through which the refrigerant (low-pressure gas) is introduced into the housing 3 is provided on the side portion of the housing main body 3a.
  • a discharge pipe 11 through which the refrigerant (high-pressure gas) compressed by the scroll compression mechanism 7 is discharged is provided on the upper portion of the cover portion 3c.
  • a discharge cover 13 is provided between the housing main body 3a and the cover portion 3c, and the interior space of the housing 3 is divided into a low-pressure chamber 3A positioned below the discharge cover 13 and a high-pressure chamber 3B positioned above the discharge cover 13.
  • a discharge cover 13 which communicates with the low-pressure chamber 3A and the high-pressure chamber 3B is formed and a discharge reed valve 13b which opens and closes the opening hole 13a is provided.
  • a bottom inside the housing 3 (low-pressure chamber 3A) is configured as an oil reservoir 41 in which a lubricant oil 40 is stored.
  • the motor 5 includes a stator 15, a rotor 17, and a rotary shaft (drive shaft) 19.
  • the stator 15 is fixed to an inner wall surface of the housing main body 3a at an approximately intermediate portion in a vertical direction of the housing main body 3a.
  • the rotor 17 is rotatably provided to the stator 15.
  • a rotary shaft 19 is disposed above and below the rotor 17 in the longitudinal direction. Power is supplied to the motor 5 from the outside of the housing 3 to rotate the rotor 17, and thus, the rotor 17 and the rotary shaft 19 are rotated.
  • the motor 5 is configured such that an operation frequency can be controlled by an inverter (not shown) and the motor 5 can be operated in a wide range from a low rotational frequency region to a high rotational frequency region.
  • the rotary shaft 19 is provided such that end portions protrude upward and downward from the rotor 17, and an upper end portion of the rotary shaft 19 is rotatably supported on the housing main body 3a by an upper bearing (bearing portion) 21 and a lower end portion thereof is rotatably supported on the housing main body 3a by a lower bearing (bearing portion) 23 about an axis CE extending in the vertical direction.
  • an eccentric pin 25 which protrudes upward along an eccentricity LE eccentric to the axis CE is formed on an upper end of the rotary shaft 19.
  • the scroll compression mechanism 7 is connected to the upper end of the rotary shaft 19 having the eccentric pin 25.
  • the rotary shaft 19 and the eccentric pin 25 have an oil supply hole (oil supply passage) 27, which vertically penetrates the rotary shaft 19 and the eccentric pin 25, inside the rotary shaft 19 and the eccentric pin 25.
  • the oil supply hole 27 includes an upper oil supply hole (oil supply passage) 27a and a lower oil supply hole (oil supply passage) 27b, which communicate with the oil supply hole 27 and penetrate the rotary shaft 19 in a radial direction, at height positions corresponding to heights of the upper bearing 21 and the lower bearing 23.
  • an oil supply pump (lubricant oil pump) 29 in which the oil reservoir 41 is disposed is provided on the upper end of the rotary shaft 19.
  • the oil supply pump 29 draws the lubricant oil 40 stored in the oil reservoir 41 according to a rotation of the rotary shaft 19.
  • the drawn lubricant oil is supplied to the sliding portions between the upper bearing 21 and the lower bearing 23 and the rotary shaft 19, and the scroll compression mechanism 7 through the oil supply hole 27, the upper oil supply hole 27a, and the lower oil supply hole 27b of the rotary shaft 19.
  • the upper end portion of the rotary shaft 19 penetrates the upper bearing 21, and thus, the upper bearing rotatably supports the rotary shaft 19.
  • a recessed portion 21a is formed on an upper surface of the upper bearing 21 to surround an upper end portion of the rotary shaft 19 penetrating the upper bearing 21.
  • a slide bush 37 described later is accommodated in the recessed portion 21a, and the lubricant oil 40 fed via the oil supply hole 27 by the oil supply pump 29 is stored in the recessed portion 21a.
  • the stored lubricant oil 40 is supplied to the scroll compression mechanism 7.
  • a notch 21b is formed on a portion of an outer periphery to have a gap between an inner wall surface of the housing main body 3a of the housing 3 and the upper bearing 21, and the oil drain hole (return oil passage) 21c which communicates with the notch 21b and the recessed portion 21a is formed.
  • a cover plate 31 is provided below the notch 21b of the upper bearing 21.
  • the cover plate 31 is provided to extend in the vertical direction.
  • the cover plate 31 is formed such that both side ends are curved toward the inner wall surface of the housing main body 3a so as to cover the vicinity of the notch 21b, and is formed such that a lower end of the cover plate 31 is gradually curved toward the inner wall surface of the housing main body 3a.
  • the lubricant oil 40 excessively stored in the recessed portion 21a is discharged from the notch 21b to the outer periphery of the upper bearing 21 through the oil drain hole 21c.
  • the cover plate 31 receives the lubricant oil 40 discharged from the notch 21b and guides the lubricant oil 40 toward the inner wall surface of the housing main body 3a.
  • the lubricant oil 40 guided toward the inner wall surface by the cover plate 31 is returned to the oil reservoir 41 on the bottom inside the housing 3 along the inner wall surface by the cover plate 31.
  • the scroll compression mechanism 7 is disposed above the upper bearing 21 in the low-pressure chamber 3A below the discharge cover 13, and includes a fixed scroll 33, an orbiting scroll 35, and a slide bush 37.
  • a spiral fixed wrap 33b is formed on an inner surface (lower surface in Fig. 1 ) of the fixed end plate 33a fixed to the interior space of the housing 3.
  • a discharge hole 33c is formed at the center portion of the fixed end plate 33a.
  • a spiral movable wrap 35b is formed on an inner surface (upper surface in Fig. 1 ) of a movable end plate 35a facing the inner surface of the fixed end plate 33a in the fixed scroll 33.
  • the movable wrap 35b of the orbiting scroll 35 and the fixed wrap 33b of the fixed scroll 33 mesh with each other with their phases shifted from each other, and thus, a compression chamber which is partitioned by the end plates 33a and 35a and the wraps 33b and 35b is formed.
  • a cylindrical boss 35c to which the eccentric pin 25 of the rotary shaft 19 is connected and an eccentric rotation of the eccentric pin 25 is transmitted is formed on the outer surface (lower surface in Fig.
  • the orbiting scroll 35 is revolved while being prevented from rotating on the basis of the eccentric rotation of the eccentric pin 25 by a rotation prevention mechanism 39 such as a well-known Oldham link disposed between the outer surface of the movable end plate 35a and the upper bearing 21.
  • the slide bush 37 is accommodated in the recessed portion 21a of the above-described upper bearing 21, is interposed between the eccentric pin 25 of the rotary shaft 19 and the boss 35c of the orbiting scroll 35, and transmits the rotation of the eccentric pin 25 as an orbiting movement of the orbiting scroll 35.
  • the slide bush 37 is provided to be slidable in a radial direction of the eccentric pin 25 to maintain meshing between the movable wrap 35b of the orbiting scroll 35 and the fixed wrap 33b of the fixed scroll 33.
  • the lubricant oil 40 mixed in the refrigerant seals a minute gap between the wraps 33b and 35b, and thus, the refrigerant is prevented from leaking from the gap, and the operation efficiency of the scroll compressor 1 is prevented from decreasing.
  • the compressed high-pressure refrigerant is discharged from the discharge hole 33c of the fixed scroll 33 to the outer surface side of the fixed end plate 33a, and the discharge reed valve 13b of the discharge cover 13 is opened by the pressure of the refrigerant. Accordingly, the refrigerant flows from the opening hole 13a into the high-pressure chamber 3B and is discharged to the outside of the housing 3 via the discharge pipe 11.
  • an upper limit value of the rotational frequency (operation frequency) is set to 100 to 140 rps.
  • the upper limit value increases to be a larger value (for example, 150 rps or higher) than the value of the related art such that the scroll compressor is operated at a wider rotational frequency region.
  • Fig. 2 is a cross sectional view of the oil supply pump.
  • the oil supply pump 29 is a so-called rolling piston (positive-displacement) oil supply pump, and as shown in Fig. 1 , the oil supply pump 29 is provided in the lower bearing 23.
  • the oil supply pump 29 includes a cylinder chamber 45 of which a lower opening portion is closed by a cover body 44 attached to the lower surface portion of the lower bearing 23.
  • the cover body 44 integrally includes a suction nozzle 43 extending downward, and a suction port 43A communicating with the cylinder chamber 45 is formed in the suction nozzle 43. As shown in Figs.
  • a rotor 47 fitted to an eccentric shaft portion 46 formed on the lower end of the rotary shaft 19 is accommodated in the cylinder chamber 45, and the rotor 47 revolves while sliding on the inner peripheral surface of the cylinder chamber 45 according to the rotation of the rotary shaft 19.
  • a plate 47A which divides the interior space of the cylinder chamber 45 into an oil supply chamber 45A and an oil discharge chamber 45B is integrally provided in the rotor 47.
  • the lubricant oil 40 stored in the oil reservoir 41 is suctioned to the oil supply chamber 45A through the suction port 43A of the suction nozzle 43 and an oil supply port 48, is discharged from the oil discharge chamber 45B to the oil discharge port 49, and is fed to the oil supply hole 27 of the rotary shaft 19 via a communication passage 50 (refer to Fig. 1 ).
  • a suction loss is generated during the high speed rotation, and thus, it is possible to effectively suppress the amount of the supplied oil during the high speed operation of the motor 5 (compressor 1).
  • the above-described rolling piston oil supply pump 29 is only an example, and oil supply pump having other configurations may be adopted as long as they are positive-displacement oil supply pumps.
  • the lubricant oil 40 drawn by the oil supply pump 29 through the suction port 43A flows to the oil supply hole 27 of the rotary shaft 19, and a portion of the lubricant oil 40 is supplied to the sliding portions between the upper bearing 21 and the lower bearing 23 and the rotary shaft 19 through the upper oil supply hole 27a and the lower oil supply hole 27b.
  • a portion of the lubricant oil 40 is stored in the recessed portion 21a of the upper bearing 21 to be supplied to the sliding portion between the recessed portion 21a and the orbiting scroll 35, and excess lubricant oil 40 is returned to the oil reservoir 41 through the oil drain hole 21c.
  • a relationship among an inner diameter D of the suction port 43A of the oil supply pump 29, the minimum diameter d1 of the oil supply hole 27 including the upper oil supply hole 27a and the lower oil supply hole 27b, and an equivalent diameter d2 of the oil drain hole 21c satisfies d1 ⁇ D s d2.
  • the minimum diameter d1 of the oil supply hole 27 indicates a diameter of a portion of the oil supply hole 27 having the narrowest inner diameter for supplying the oil from the oil supply pump 29 to each sliding portion (upper bearing 21, recessed portion 21a, and lower bearing 23), and in the present embodiment, the inner diameter of each of the upper oil supply hole 27a and the lower oil supply hole 27b becomes the minimum diameter d1.
  • the minimum diameter d1 (the inner diameter of each of the upper oil supply hole 27a and the lower oil supply hole 27b) of the oil supply hole 27 is equal to or less than the inner diameter D of the suction port 43A, and thus, the lubricant oil 40 drawn by the oil supply pump 29 can be reliably supplied to the sliding portions between the upper bearing 21 and the lower bearing 23 and the rotary shaft 19.
  • the equivalent diameter d2 of the oil drain hole 21c is equal to or more than the inner diameter D of the suction port 43A, the excess lubricant oil 40 is prevented from staying in the recessed portion 21a and the oil drain hole 21c, and the lubricant oil stored in the oil reservoir 41 of the bottom portion of the housing 3 from being insufficient.
  • the inner diameter D of the suction port 43A of the oil supply pump 29 is set to satisfy d1 ⁇ D ⁇ d2, and thus, it is possible to further increase the pressure loss.
  • Fig. 3 is a graph showing a relationship between an amount Q of oil supplied by a pump with respect to scroll displacement Vs and the rotational frequency of the motor.
  • Fig. 4 is a graph showing a relationship between an amount of oil supplied per unit time of a pump and the rotational frequency of the motor.
  • the amount Q (cc / rev) of oil supplied by a pump is a value indicating an amount of oil supplied (discharged) per revolution of the oil supply pump 29, and the scroll displacement Vs (cc / rev) is a value indicating an amount of displacement (discharge) per revolution of the scroll compression mechanism 7.
  • a theoretical value of the amount Q of oil supplied by a pump / the scroll displacement Vs in the oil supply pump 29 becomes 0.008.
  • Fig. 3 shows that the amount Q (cc / rev) of oil supplied by a pump of the oil supply pump 29 having the above-described performance is measured in a state where the rotational frequency is changed.
  • an actual measurement value of the amount Q of oil supplied by a pump / the scroll displacement Vs tends to decrease as the rotational frequency of the motor 5 increases.
  • Q / Vs > 0.006 is satisfied during the low speed operation (low rotation region) in which the rotational frequency of the motor 5 is 0 rps to 60 rps.
  • the actual measurement value decreases to a range satisfying 0.003 ⁇ Q / Vs ⁇ 0.006 during the high speed operation (high rotation region) in which the rotational frequency of the motor 5 is at least 150 rps to 200 rps.
  • OCR a ratio of an amount of discharged oil to an amount of a circulating refrigerant
  • the OCR decreases, and the amount of the oil supplied by the oil supply pump 29 greatly affects the efficiency.
  • the amount Q of oil supplied by a pump / the scroll displacement Vs satisfies Q / Vs > 0.006 during the low speed operation, and thus, as shown in Fig. 4 , the actual measurement value of the amount V (cc / s) of the oil supplied per unit time during the low speed operation can keep a deviation from the theoretical value small. Accordingly, it is possible to sufficiently secure the amount of the lubricant oil mixed in the refrigerant, and this lubricant oil seals the minute gap between wraps 33b and 35b. Therefore, the refrigerant is prevented from leaking from the gap, and it is possible to prevent the operation efficiency of the scroll compressor 1 from decreasing.
  • the amount Q of oil supplied by a pump / the scroll displacement Vs satisfies 0.003 ⁇ Q / Vs ⁇ 0.006 during the high speed operation, and thus, as shown in Fig. 4 , the actual measurement value of the amount V (cc / s) of the oil supplied per unit time during the high speed operation can increase the deviation from the theoretical value compared to the low speed operation. Accordingly, the amount V (cc / s) of the oil supplied per unit time during the high speed operation can decrease, and thus, it is possible to decrease the amount of the lubricant oil discharged from the scroll compressor 1 by the decreased amount.
  • the present embodiment is configured such that the amount Q of oil supplied by a pump / the scroll displacement Vs satisfies 0.003 ⁇ Q / Vs ⁇ 0.006 during the high speed operation.
  • the amount of the lubricant oil supplied to each sliding portion decreases, a cooling failure of the scroll compression mechanism 7, the upper bearing 21, or the lower bearing 23 occurs, and there is a concern that seizing of the scroll compression mechanism 7, the upper bearing 21, or the lower bearing 23 may occur.
  • the amount of the lubricant oil discharged from the scroll compressor 1 is increased by increasing the amount of the lubricant oil supplied from the oil supply pump 29, and as a result, the amount of the lubricant oil stored in the housing 3 decreases, the cooling failure of the scroll compression mechanism 7, the upper bearing 21, or the lower bearing 23 occurs, and there is a concern that seizing of the scroll compression mechanism 7, the upper bearing 21, or the lower bearing 23 may occur.
  • an inclination 0 indicating a rate of increase in the amount of the supplied oil decreases as the rotational frequency increases. Accordingly, it is possible to decrease the supply amount of the lubricant oil during the high speed operation and it is possible to sufficiently secure the supply amount of the lubricant oil to each sliding portion during the low speed operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP16866107.2A 2015-11-20 2016-10-25 Spiralverdichter Withdrawn EP3318759A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015227877A JP2017096145A (ja) 2015-11-20 2015-11-20 スクロール圧縮機
PCT/JP2016/081635 WO2017086105A1 (ja) 2015-11-20 2016-10-25 スクロール圧縮機

Publications (2)

Publication Number Publication Date
EP3318759A1 true EP3318759A1 (de) 2018-05-09
EP3318759A4 EP3318759A4 (de) 2018-10-31

Family

ID=58718700

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16866107.2A Withdrawn EP3318759A4 (de) 2015-11-20 2016-10-25 Spiralverdichter

Country Status (4)

Country Link
EP (1) EP3318759A4 (de)
JP (1) JP2017096145A (de)
CN (1) CN107850069B (de)
WO (1) WO2017086105A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020115376B4 (de) 2019-06-28 2024-03-21 Danfoss Commercial Compressors Scroll-Verdichter mit Orbitalscheiben-Schmiersystem

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7281017B2 (ja) * 2020-07-20 2023-05-24 株式会社日立産機システム スクロール圧縮機
CN113482932B (zh) * 2021-08-23 2023-09-01 广东美芝制冷设备有限公司 旋转式压缩机及制冷设备

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06137292A (ja) * 1992-10-23 1994-05-17 Daikin Ind Ltd ローリングピストン型圧縮機
JP3274900B2 (ja) * 1993-03-16 2002-04-15 東芝キヤリア株式会社 圧縮機における給油ポンプ装置
JPH08177773A (ja) * 1994-12-27 1996-07-12 Toshiba Corp 圧縮機における給油ポンプ装置
JPH0921391A (ja) * 1995-07-05 1997-01-21 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
JPH0942181A (ja) * 1995-08-04 1997-02-10 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
JP2003184776A (ja) * 2001-12-18 2003-07-03 Mitsubishi Heavy Ind Ltd 圧縮機
CN103492719B (zh) * 2011-04-25 2016-08-17 日立空调·家用电器株式会社 冷媒压缩机以及使用其的冷冻循环装置
US9562530B2 (en) * 2012-04-12 2017-02-07 Emerson Climate Technologies (Suzhou) Co., Ltd. Rotor pump and rotary machinery comprising the same, the rotor pump including a pump body forming an accommodation cavity, a pump wheel rotating in the accommodation cavity and a sealing plate having an eccentric hole that is eccentric relative to a rotation axis of the pump wheel, where a shaft portion of the pump wheel is rotatably fitted in the eccentric hole
JP5999974B2 (ja) * 2012-05-14 2016-09-28 三菱電機株式会社 スクロール圧縮機
CN203476700U (zh) * 2013-09-12 2014-03-12 南京奥特佳冷机有限公司 卧式全封闭涡旋压缩机

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020115376B4 (de) 2019-06-28 2024-03-21 Danfoss Commercial Compressors Scroll-Verdichter mit Orbitalscheiben-Schmiersystem

Also Published As

Publication number Publication date
CN107850069A (zh) 2018-03-27
JP2017096145A (ja) 2017-06-01
CN107850069B (zh) 2019-04-12
EP3318759A4 (de) 2018-10-31
WO2017086105A1 (ja) 2017-05-26

Similar Documents

Publication Publication Date Title
US9316225B2 (en) Scroll compressor with thrust sliding surface oiling groove
US8834139B2 (en) Lubrication of a scroll compressor
WO2016052503A1 (ja) スクロール圧縮機及びこれを用いた冷凍サイクル装置
US8888475B2 (en) Scroll compressor with oil supply across a sealing part
JP5433604B2 (ja) スクロール圧縮機
EP3318759A1 (de) Spiralverdichter
EP3418569B1 (de) Offener kältemittelverdichter
JP2018021493A (ja) スクロール圧縮機
EP2581603A1 (de) Spiralverdichter
US7458789B2 (en) Scroll compressor
CN108496008B (zh) 涡旋压缩机以及具备该涡旋压缩机的空调装置
KR102392655B1 (ko) 냉매의 토출 유로와 오일 회수 유로를 분리한 압축기
EP2905469A1 (de) Hermetischer spiralverdichter
JPWO2019240134A1 (ja) スクロール圧縮機
EP3339647A1 (de) Verdichter
EP3524819A2 (de) Verdichter
JP5114708B2 (ja) 密閉形スクロール圧縮機
WO2018198811A1 (ja) ローリングシリンダ式容積型圧縮機
JP2000179472A (ja) ロータリ圧縮機
JP2009062858A (ja) 横形圧縮機
EP4098877A1 (de) Spiralverdichter
EP4102074A1 (de) Spiralverdichter
JP7139718B2 (ja) 圧縮機
JP2023000564A (ja) スクロール圧縮機
JP2006070711A (ja) スクロール圧縮機

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20180130

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 29/02 20060101ALI20180917BHEP

Ipc: F04C 23/00 20060101ALI20180917BHEP

Ipc: F04C 18/02 20060101AFI20180917BHEP

A4 Supplementary search report drawn up and despatched

Effective date: 20180927

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 23/00 20060101ALI20190314BHEP

Ipc: F04C 18/02 20060101AFI20190314BHEP

Ipc: F04C 29/02 20060101ALI20190314BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20190509

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20190920