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WO2018150706A1 - Compresseur - Google Patents

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Publication number
WO2018150706A1
WO2018150706A1 PCT/JP2017/044982 JP2017044982W WO2018150706A1 WO 2018150706 A1 WO2018150706 A1 WO 2018150706A1 JP 2017044982 W JP2017044982 W JP 2017044982W WO 2018150706 A1 WO2018150706 A1 WO 2018150706A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
detection means
lubricating oil
scroll
compressor according
Prior art date
Application number
PCT/JP2017/044982
Other languages
English (en)
Japanese (ja)
Inventor
太一 舘石
拓馬 山下
暉裕 金井
創 佐藤
央幸 木全
洋悟 高須
一樹 高橋
Original Assignee
三菱重工サーマルシステムズ株式会社
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 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to EP17897200.6A priority Critical patent/EP3499042A1/fr
Publication of WO2018150706A1 publication Critical patent/WO2018150706A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/28—Safety arrangements; Monitoring
    • 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
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • 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

Definitions

  • the present invention relates to a compressor having a mechanism for reducing mechanical loss during operation.
  • a compressor such as a scroll compressor or a rotary compressor is used in the refrigeration cycle.
  • a scroll compressor disclosed in Patent Document 1 includes a fixed scroll fixed inside a casing, and a turning scroll that meshes with the fixed scroll and has a drive shaft connected to the back side.
  • the orbiting scroll revolves. And at the time of the turning, the fluid is sucked into the compression chamber formed between the two scrolls, and the fluid is compressed in the compression chamber.
  • the scroll compressor presses the orbiting scroll against the fixed scroll by increasing the back pressure space formed between the orbiting scroll and the housing on the rear side during the compression operation, and the sliding loss of the thrust bearing is reduced. And the compression efficiency can be improved.
  • the state of the orbiting scroll depends on the operating conditions. It is difficult to grasp the state of the orbiting scroll with respect to the driving conditions. Therefore, the operating conditions of the scroll compressor are limited in order to ensure the ability to perform the required function, that is, the reliability performance, for the given period under the given conditions. For this reason, although there is no limitation on the operating conditions, it may not be possible to fully exhibit the ability even though the higher ability can be exhibited.
  • an object of the present invention is to provide a compressor capable of controlling the motion condition during operation of the compressor and exhibiting an appropriate compression function force according to the operation condition without restricting the motion condition in advance.
  • the present invention is a compressor that compresses a refrigerant by a transmitted driving force, a moving element that is moved by the driving force, a support element that supports the moving element, and a detection means provided in association with the moving element.
  • the detection means detects a change in the state around the detection means.
  • the detection means of the present invention is preferably a sensor having a thickness of 10 ⁇ m or less.
  • the detection means of the present invention is preferably provided on a sliding surface of the support element with the motion element.
  • the detection means of the present invention is preferably provided on the movement element itself.
  • the change in the state around the detecting means is preferably at least one of a change in the pressure of the lubricating oil, a change in the temperature of the lubricating oil, and a change in the capacitance.
  • the compressor of the present invention preferably includes a fixed scroll, an orbiting scroll that revolves around the fixed scroll, a thrust bearing that supports the orbiting scroll so as to revolve, and a back pressure chamber into which lubricating oil flows. It is a scroll compressor.
  • the detecting means is preferably provided on a sliding surface with the orbiting scroll of the thrust bearing connected to the back pressure chamber.
  • the detection means is preferably provided inside the storage chamber that retreats from the sliding surface of the thrust bearing.
  • the detection means preferably has a measurement area for detecting the pressure of the lubricating oil between the thrust bearing and the orbiting scroll, and the measurement area is provided inside the arrangement area of the thrust bearing.
  • the pressure of the lubricating oil inside the back pressure chamber is preferably adjusted by the value detected by the detecting means.
  • the detecting means can detect a change in state between an Oldham ring key that restricts rotation of the orbiting scroll and a key groove into which the key is inserted.
  • the detection means can detect a change in the state of the compression chamber between the tooth surface of the wrap of the fixed scroll and the fixed scroll and the orbiting scroll.
  • the compressor of the present invention is preferably arranged on a cylinder, a piston rotor sliding inside the cylinder, an upper bearing disposed on the cylinder and the upper end surface of the piston rotor, and an end surface on the lower side of the cylinder and the piston rotor.
  • the rotary compressor includes a lower bearing, a cylinder, a piston rotor, a compression chamber formed by the upper bearing and the lower bearing, a blade that divides the compression chamber, and a blade groove into which the blade is inserted.
  • the detection means can detect a change in state between the blade and the blade groove.
  • the exercise condition is controlled based on the detection result without restricting the exercise condition in advance. Can exert appropriate compression function.
  • FIG. 2 is a partially enlarged view of FIG. 1. It is a top view of the characteristic part of the scroll compressor of a 1st embodiment.
  • (A) is a top view of the characteristic part of the scroll compressor of 1st Embodiment,
  • (b) is the bb sectional view taken on the line of (a),
  • (c) is (a).
  • FIG. (A) is a graph which shows the relationship between the sensor output of a thin film sensor, and the pressure of the lubricating oil inside a back pressure chamber,
  • (b) is the friction coefficient between a turning scroll and a thrust bearing, and the bearing characteristic of a turning scroll. It is a graph which shows the relationship of a number (Stribeck curve).
  • (A) is sectional drawing which simplifies and shows the whole view of the rotary compressor of other embodiment,
  • (b) is the bb sectional view taken on the line of (a).
  • the compressor of the present invention detects a physical quantity at a predetermined place when the compressor is operated, and is operated under appropriate conditions based on the detection result.
  • the compressor of the present invention will be described with reference to the first to fifth embodiments.
  • the compressor of the present invention is applied to the scroll compressor 1, and in the fifth embodiment, the compressor of the present invention is applied to the rotary compressor 8.
  • the scroll compressor 1 includes a fixed scroll 3, a turning scroll 4 that is an orbital element that revolves around the fixed scroll 3, and a motor 6 that drives the turning scroll 4.
  • the rotating shaft 5 that transmits the power of the motor 6 to the orbiting scroll 4 and the housing 2 that houses them are provided.
  • the orbiting scroll 4 is supported by a thrust bearing 22 as a support element so as to be capable of revolution orbit, but its rotation is restricted by the Oldham ring 23.
  • the rotating shaft 5 is rotatably supported by an upper bearing 21 and a lower bearing 24 fixed to the housing 2.
  • the housing 2 includes a storage region 26 that stores the lubricating oil O at the bottom.
  • the lubricating oil O is pumped up through an oil supply path 53 inside the rotating shaft 5 by a pump 54 provided at the lower end of the rotating shaft 5, and a bearing 52 provided in the upper bearing 21, the lower bearing 24, and the eccentric pin 51 of the rotating shaft 5.
  • Orbiting scroll 4, Oldham ring 23, and the parts that slide with other parts of thrust bearing 22 are supplied.
  • the supplied lubricating oil O is returned to the storage area 26 through the circulation passage 25.
  • a suction pipe 28 and a discharge pipe 29 provided in the housing 2 are connected to a refrigerant circuit of a refrigerator or an air conditioner (not shown).
  • the scroll compressor 1 when a driving current is supplied from a power source (not shown) to the stator 61 of the motor 6, the rotor 62 of the motor 6 rotates and the driving force is output to the rotating shaft 5.
  • a driving force is transmitted to an upper end of the rotating shaft 5 via an eccentric pin 51 provided eccentrically in one direction (eccentric direction) radially outward from the central axis of the rotating shaft 5.
  • the orbiting scroll 4 is revolved with respect to the fixed scroll 3 fixed to the housing 2. Due to the turning of the orbiting scroll 4, the refrigerant inside the housing 2 flowing in from the suction pipe 28 is sucked between the orbiting scroll 4 and the fixed scroll 3.
  • the volume of the compression chamber R1 between the orbiting scroll 4 and the fixed scroll 3 decreases, so that the refrigerant is compressed in the compression chamber R1.
  • the thrust bearing due to the pressure of the compressed refrigerant is handled by the upper bearing 21 that supports the end plate 41 of the orbiting scroll 4 via the thrust bearing 22.
  • the compressed refrigerant is discharged to the refrigerant circuit by the discharge pipe 29 through the discharge port 32 of the fixed scroll 3 and the discharge port 38 of the discharge cover 37.
  • the discharge port 32 is provided with a reed valve 36 attached to the end plate 31 of the fixed scroll 3 via a retainer 35.
  • the discharge port 38 of the discharge cover 37 is also connected to the discharge cover 37 via a retainer 37A.
  • An attached reed valve 37B is provided.
  • the scroll compressor 1 includes a pressure adjustment mechanism that adjusts the pressure of the lubricating oil O inside the back pressure chamber 27.
  • the orbiting scroll 4 is pressed toward the fixed scroll 3 by the pressure of the lubricating oil O inside the back pressure chamber 27.
  • the pressure adjustment mechanism includes a back pressure chamber 27, a storage chamber 22B formed on the surface of the thrust bearing 22 facing the orbiting scroll 4, and a thin film provided inside the storage chamber 22B.
  • the sensor 7 and the control valve V provided in the circulation passage 25 are included.
  • the pressure adjusting mechanism detects the pressure of the lubricating oil O supplied to the inside of the back pressure chamber 27 by the thin film sensor 7 and adjusts the opening / closing of the control valve V of the circulation passage 25 based on the detection result.
  • the chamber 27 is adjusted so as to have a desired pressure.
  • the back pressure chamber 27 is a space inside the thrust bearing 22 that is partitioned by the orbiting scroll 4, the upper bearing 21, and the thrust bearing 22.
  • the back pressure chamber 27 is formed in an annular shape.
  • the circulation passage 25 is for returning the lubricating oil O supplied from the storage region 26 to the inside of the back pressure chamber 27 from the back pressure chamber 27 to the storage region 26 of the housing 2. As shown in FIG. 1, the circulation passage 25 is connected to a storage area 26 in which the lubricating oil O of the housing 2 is stored.
  • the circulation passage 25 includes a control valve V that controls the circulation flow rate of the lubricating oil O.
  • the control valve V is used as a general term for the control valves V1, V2, V3, and V4.
  • an electromagnetic valve whose flow path is opened and closed according to a command can be exemplified.
  • the amount of the lubricating oil O inside the back pressure chamber 27 is controlled by the control valve V as follows.
  • the scroll compressor 1 is supplied with lubricating oil O to the back pressure chamber 27 during operation.
  • the control valve V is closed, the lubricating oil O that has lost its place in the back pressure chamber 27 is guided to the thrust surface 22 ⁇ / b> A side of the thrust bearing 22, and enters the gap C between the thrust bearing 22 and the orbiting scroll 4. Enter.
  • the control valve V is opened with the lubricating oil O in the gap C, the lubricating oil O flows out from the gap C toward the circulation passage 25.
  • the circulation passage 25 of the present embodiment is branched into four passages 25A, 25B, 25C, and 25D along the way, and control valves V1, V2, V3, and V4 are provided in the passages 25A to 25D, respectively.
  • the circulation passage 25 can adjust the amount of the lubricating oil O returned from the back pressure chamber 27 to the storage region 26 by the number of opening and closing the control valves V1 to V4. Note that the amount of the lubricating oil O returned from the back pressure chamber 27 to the storage region 26 can be adjusted by using a flow rate adjusting valve instead of the plurality of control valves V1 to V4.
  • the thrust bearing 22 includes an accommodation chamber 22 ⁇ / b> B that is recessed from the thrust surface 22 ⁇ / b> A that contacts the orbiting scroll 4 and retracts.
  • a measurement region 74 that is a detection unit of the thin film sensor 7 to be described later is provided so as not to contact the orbiting scroll 4.
  • the accommodation chamber 22 ⁇ / b> B is connected to the back pressure chamber 27 through a gap C between the thrust bearing 22 and the orbiting scroll 4.
  • the storage chamber 22B is composed of a linear groove extending in the radial direction provided on the thrust surface 22A.
  • the depth D of the storage chamber 22B is formed deeper than the thickness T of the measurement region 74 of the thin film sensor 7 provided inside the storage chamber 22B.
  • the thin film sensor 7 detects a change in the pressure of the lubricating oil O inside the back pressure chamber 27 as a change in electric resistance value.
  • the thin film sensor 7 includes a straight portion extending radially inward from a peripheral edge 22D of the thrust surface 22A, a curved portion connected to the straight portion, and a thrust surface connected to the curved portion. It consists of a straight line portion extending to the outer peripheral edge 22D of 22A. That is, the thin film sensor 7 is formed in a substantially U shape on the thrust surface 22A.
  • the thin film sensor 7 is connected to a terminal (not shown) at the peripheral edge 22D of the thrust surface 22A.
  • a detection signal from the thin film sensor 7 is input to a control unit (not shown) via lead wires connected to the terminals.
  • the thin film sensor 7 has a three-layer structure in which an insulating layer 72, a sensor layer 71, and a protective layer 73 are stacked in this order from the thrust bearing 22 side.
  • the sensor layer 71 has a characteristic that the electric resistance value changes when the pressure of the lubricating oil O inside the back pressure chamber 27 changes.
  • the insulating layer 72 electrically insulates between the thrust bearing 22 and the sensor layer 71.
  • the protective layer 73 protects the sensor layer 71 from being damaged by foreign matter such as metal powder that has entered the storage chamber 22B.
  • the thickness of the sensor layer 71 is 1 ⁇ m or less, and the total thickness T of the thin film sensor 7 including the insulating layer 72 and the protective layer 73 is preferably selected within a range of 10 ⁇ m or less, 5 ⁇ m or less, and further 3 ⁇ m. It is particularly preferable that it is about the following.
  • the sensor layer 71 is formed of a material having a characteristic that an electric resistance value changes according to a change in pressure.
  • Manganin registered trademark which is a Cu—Mn—Ni alloy can be used. Manganin is typically in weight percent and has a chemical composition of Cu: 84%, Mn: 12%, Ni: 4%.
  • the insulating layer 72 is formed of a material having electrical insulation.
  • silicon oxide (SiO 2 ), aluminum oxide (Al 2 O 3 ), or the like can be used.
  • DLC Diamond-Like Carbon
  • PTFE Poly Tetra Fluoro Ethylene
  • silicon oxide, aluminum oxide, or the like can be used for the protective layer 73.
  • the thin film sensor 7 includes a measurement region 74 that is used as a detection unit that measures the pressure of the lubricating oil O inside the back pressure chamber 27.
  • the measurement region 74 is set to have a width that is smaller than the electrical resistance values of the other regions 79 as compared with the electrical resistance values of the measurement region 74.
  • the electrical resistance value between the terminals provided at both ends of the thin film sensor 7 becomes substantially the same as the electrical resistance value of the measurement region 74.
  • region 74 of the thin film sensor 7 inside the storage chamber 22B is detected as a change of the electrical resistance between terminals.
  • the measurement region 74 Since the measurement region 74 has a narrow width, it has a higher sensitivity to changes in electrical resistance than the other regions 79.
  • the width W of the measurement region 74 can be set to 20 to 30 ⁇ m, for example.
  • the thin film sensor 7 including the measurement region 74 has a three-layer structure including an insulating layer 72, a sensor layer 71, and a protective layer 73 as a whole.
  • the measurement region 74 is provided in the arrangement region 22 ⁇ / b> C of the thrust surface 22 ⁇ / b> A of the thrust bearing 22.
  • the thrust surface 22A has a possibility that an annular region 22E radially inward from the outer peripheral edge 22D may strongly hit the end plate 41 of the orbiting scroll 4 that makes a revolving orbit. Further, when the end plate 41 of the orbiting scroll 4 is deformed, the annular region 22G in the radial direction from the inner peripheral edge 22F may hit the end plate 41 strongly.
  • the arrangement region 22C is an annular region excluding the regions 22E and 22G in the thrust surface 22A of the thrust bearing 22.
  • the widths of the regions 22E and 22G are about 1 mm.
  • the lubricating oil O is sufficient in the gap C between the thrust surface 22 ⁇ / b> A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4.
  • boundary lubrication state I which does not exist or does not exist
  • the oil pressure detected by the thin film sensor 7 is low.
  • the lubricant oil O enters the gap C between the thrust surface 22A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4, and the mixed lubrication state II in which an oil film is formed in the gap C, The oil pressure detected by the thin film sensor 7 gradually increases.
  • the dynamic friction coefficient between the thrust surface 22A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4 is lowered when the boundary lubrication state I is shifted to the mixed lubrication state II as shown in FIG. 5B.
  • the threshold values P1, P2, P3, and P4 are set to determine the number of control valves V1 to V4 that are opened and closed based on the hydraulic pressure detected by the thin film sensor 7.
  • the threshold value P2 is larger than the threshold value P1
  • the threshold value P3 is larger than the threshold value P2
  • the threshold value P4 is larger than the threshold value P3.
  • the gap C between the thrust surface 22A and the end plate 41 is in the state III. Therefore, all of the control valves V1 to V4 are opened, and the thrust surface 22A and the end plate are The gap C between 41 is shifted from the state III to the state II. If the pressure of the lubricating oil O inside the back pressure chamber 27 detected by the thin film sensor 7 does not reach the threshold value P1, the clearance C between the thrust surface 22A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4 is set. This is a boundary lubrication state I where the lubricating oil O is insufficient or absent. Therefore, all the control valves V1 to V4 are closed. As a result, the amount of the lubricating oil O inside the back pressure chamber 27 can be increased to shift to the mixed lubrication state II in which an oil film is formed by the lubricating oil O between the thrust surface 22A and the end plate 41.
  • the scroll compressor 1 adjusts the opening and closing of the control valves V (V1 to V4) of the circulation passage 25 based on the pressure of the lubricating oil O inside the back pressure chamber 27 detected by the thin film sensor 7 which is a detecting means. And a pressure adjusting mechanism for adjusting the back pressure chamber 27 to a desired pressure.
  • the scroll compressor 1 appropriately controls the pressure of the lubricating oil O inside the back pressure chamber 27 while performing lubrication of a portion that slides with other components such as the orbiting scroll 4 and the thrust bearing 22. Therefore, an appropriate compression function can be exhibited according to the operating conditions.
  • the pressure of the lubricating oil O in the back pressure chamber 27 necessary for the scroll compressor 1 to obtain a desired compression function force during operation depends on the thrust load of the orbiting scroll 4 and the sliding surface depending on the operating conditions. It depends on the influence of the wedge effect of the lubricating oil. For this reason, it is difficult to calculate the pressure of the lubricating oil O inside the back pressure chamber 27 suitable for the operation of the scroll compressor 1.
  • the pressure of the lubricating oil O inside the back pressure chamber 27 depends on the operating conditions of the scroll compressor 1. It may not be a value necessary to obtain a desired compression function.
  • the scroll compressor 1 detects a change in the state around the thin film sensor 7, that is, a change in the pressure of the lubricating oil O inside the back pressure chamber 27 during operation, and appropriately controls this pressure. Therefore, an appropriate compression function can be exhibited according to the operating conditions.
  • the thin film sensor 7 is provided in a storage chamber 22 ⁇ / b> B provided on the thrust surface 22 ⁇ / b> A that contacts the orbiting scroll 4, and the lubricant O fills between the orbiting scroll 4.
  • the thin film sensor 7 can detect the pressure of the lubricating oil O inside the back pressure chamber 27 without contacting the orbiting scroll 4.
  • the thin film sensor 7 is arranged within the range of the arrangement area 22C where the measurement area 74 is relatively weak, it can stably detect the pressure of the lubricating oil O inside the back pressure chamber 27. it can.
  • the scroll compressor 1 is sufficient if the thin film sensor 7 is provided along with the orbiting scroll 4 which is a motion element.
  • the thin film sensor 7 can be provided on the orbiting scroll 4, but the thin film sensor 7 is provided on the stationary thrust bearing 22. Easy to wire.
  • the scroll compressor 1 of the second embodiment detects the pressure or temperature of the lubricating oil O between the key and the key groove in the key groove of the upper bearing 21 on which the key of the Oldham ring 23 (not shown) slides. It is proposed to provide a thin film sensor 7 to be used.
  • thermocouple capable of measuring the temperature by thermoelectromotive force or a resistance temperature sensor capable of measuring the temperature by changing the resistance value depending on the temperature, for example, a platinum thin film temperature sensor can be used.
  • the thin film sensor is provided in a storage chamber formed in a keyway, similar to the storage chamber 22B of the first embodiment. The same applies to the third and subsequent embodiments.
  • the scroll compressor 1 in operation, when the pressure or temperature of the lubricating oil O between the key of the Oldham ring 23 and the key groove of the upper bearing 21 increases and the lubricating oil O inside the key groove decreases, the upper bearing 21 and Oldham ring 23 wear increases. Therefore, the scroll compressor 1 according to the second embodiment, when a predetermined value of pressure or temperature is detected by the thin film sensor, temporarily increases the rotational speed of the orbiting scroll 4 and lubricates between the key and the key groove. Increase the amount of oil O supplied. Thereby, it can prevent that the abrasion loss of the upper bearing 21 and the Oldham ring 23 increases.
  • the thin film sensor 7 can be provided on the tooth surface 34 of the wrap 33 of the fixed scroll 3. Although not shown, the thin film sensor 7 is provided inside a storage chamber formed on the tooth surface 34.
  • the thin film sensor 7 according to the third embodiment is provided to detect in advance that so-called liquid compression occurs in the compression chamber R1. Even if the thin film sensor 7 is provided on the tooth surface 34, since the thin film sensor 7 is extremely thin, it is possible to minimize the dead volume that causes a reduction in the efficiency of refrigerant compression.
  • the scroll compressor 1 When the scroll compressor 1 sucks a liquid refrigerant and causes liquid compression, the pressure inside the compression chamber R1 becomes very large. Therefore, the scroll compressor 1 reduces the rotational speed of the orbiting scroll 4 when the thin film sensor 7 detects a predetermined pressure that may cause liquid compression. Thereby, liquid compression can be avoided and it can prevent that the pressure inside compression chamber R1 becomes abnormally large.
  • the scroll compressor 1 according to the fourth embodiment includes a thin film sensor 7 that detects the pressure of the lubricating oil O between the upper bearing 21 and the rotary shaft 5, the upper bearing 21, and a portion facing the rotary shaft 5 of the upper bearing 21.
  • a thin film sensor that detects the temperature between the rotating shafts 5 or a sensor that detects the capacitance between the upper bearing 21 and the rotating shaft 5 is provided. The sensor described above can be used as a sensor for detecting the pressure of the lubricating oil O and detecting the temperature.
  • the scroll compressor 1 may be in a so-called locked state in which the scroll compressor 1 does not operate. Therefore, in the scroll compressor 1 according to the fourth embodiment, the thin film sensor detects that the load obtained from the temperature between the upper bearing 21 and the rotating shaft 5 or the pressure of the lubricating oil O has become a predetermined value or more. To do. Then, the load between the upper bearing 21 and the rotary shaft 5 is reduced by reducing the rotational speed of the rotary shaft 5 or the operation of the scroll compressor 1 is stopped. This can prevent the scroll compressor 1 from being locked.
  • the dilution rate of the lubricating oil O by the refrigerant is calculated from the relationship between the temperature and pressure detected by the thin film sensor, or the electrostatic capacity. If the dilution rate is equal to or greater than a certain value, the rotation shaft 5 It is also possible to perform an operation in which the load between the upper bearing 21 and the rotary shaft 5 is reduced by reducing the rotational speed and the pressure of the lubricating oil O. From the relationship between temperature and pressure, the dilution rate is calculated by a relational expression obtained in advance according to the type of refrigerant to be compressed and the type of lubricating oil O to be used. Further, the dilution rate is calculated from the electrostatic capacitance based on the correlation between the previously obtained capacitance and the dilution rate.
  • the clearance gap here means not only the presence or absence of a clearance gap but the dimension.
  • the clearance gap here means not only the presence or absence of a clearance gap but the dimension.
  • the above-described sensor for detecting the capacitance can be used.
  • the upper bearing 21 is provided with a capacitance sensor so as to detect the capacitance between the upper bearing 21 and the rotary shaft 5. If the gap between the capacitance sensor and the rotating shaft 5 changes, the capacitance generated between the capacitance sensor and the rotating shaft 5 changes, so that the upper bearing 21 and the rotating shaft are detected from the detected capacitance. 5 can be detected.
  • the outer peripheral surface of the rotating shaft 5 strongly contacts the upper bearing 21 at a position shifted from the eccentric direction of the provided eccentric pin 51 by a predetermined angle in the rotating direction of the rotating shaft 5.
  • This position varies depending on factors such as centrifugal force caused by the turning of the orbiting scroll 4, but is typically a position shifted by 90 degrees. For this reason, if the use of the scroll compressor 1 is continued, the wear of the portion of the rotating shaft 5 that is strongly contacted increases preferentially, so that the radial gap between the portion of the rotating shaft 5 that is strongly contacted and the upper bearing 21 increases.
  • the scroll compressor 1 when the scroll compressor 1 according to the fourth embodiment detects that the radial gap between the upper bearing 21 and the rotary shaft 5 becomes larger than a predetermined value by a capacitance sensor provided in the upper bearing 21. Stop driving.
  • the scroll compressor 1 can also output an error signal notifying that the operation has been stopped along with the operation stop.
  • the rotary compressor 8 includes a cylinder 83, a piston rotor 82 that slides inside the cylinder 83, a motor 89 that drives the piston rotor 82, and the power of the motor 89 as a piston rotor.
  • Rotating shaft 87 that transmits to 82, and housing 81 that accommodates these.
  • An upper bearing 84 is disposed on the upper end surfaces of the cylinder 83 and the piston rotor 82, and a lower bearing 85 is disposed on the lower end surface.
  • the piston rotor 82 is inserted and fixed to an eccentric shaft portion 87 ⁇ / b> A of the rotation shaft 87 along the central axis of the housing 81.
  • the rotating shaft 87 is rotatably supported by the upper bearing 84 and the lower bearing 85.
  • the compression chamber R2 is formed by the cylinder 83, the piston rotor 82, the upper bearing 84, and the lower bearing 85.
  • the cylinder 83 has a blade groove 83B connected to the compression chamber R2 and into which the blade 86 is inserted, and a storage groove 83D connected to the blade groove 83B and storing the coil spring 83C.
  • the blade groove 83B and the storage groove 83D penetrate the cylinder 83 in the radial direction.
  • the compression chamber R ⁇ b> 2 is divided by a plate-like blade 86 formed at a height similar to the axial dimension of the piston rotor 82.
  • the blade 86 is inserted into the blade groove 83B and supported in the circumferential direction.
  • the tip of the blade 86 is always pressed against the outer peripheral surface of the piston rotor 82 by the pressing force of the coil spring 83C disposed inside the housing groove 83D and the pressure of the high pressure portion.
  • the blade 86 moves in and out of the compression chamber R ⁇ b> 2 inside the cylinder 83 according to the rotation angle of the piston rotor 82.
  • the refrigerant sucked into the cylinder 83 from the suction port 83 ⁇ / b> A is compressed by the displacement by the piston rotor 82 in the cylinder 83.
  • the compressed refrigerant is discharged from a discharge port 84 ⁇ / b> A formed in the upper bearing 84.
  • the discharge port 84A is provided with a reed valve (not shown). When the pressure of the compressed refrigerant reaches a predetermined value, the reed valve is pushed open, so that the refrigerant is discharged to the outside of the cylinder 83.
  • the discharged refrigerant is supplied to a system side such as a refrigerator or an air conditioner (not shown) connected to the rotary compressor 8.
  • the thin film sensor 7 that detects the contact pressure in the circumferential direction between the blade 86 and the blade groove 83B is provided on the blade 86 or the blade groove 83B.
  • the description of the thin film sensor 7 is omitted.
  • the rotary compressor 8 is provided with a thin film sensor that detects a circumferential gap between the blade 86 and the blade groove 83B. Illustration of this thin film sensor is also omitted.
  • the rotary compressor 8 of the fifth embodiment detects that the contact pressure between the blade 86 and the blade groove 83B has become a predetermined value or more by the thin film sensor 7. Then, the rotational speed of the piston rotor 82 is limited, the sliding speed between the blade 86 and the blade groove 83B is lowered, or the opening degree of the expansion valve on the system side is changed. Thus, the rotary compressor 8 reduces the differential pressure between the compression chamber R2 on the suction port 83A side and the compression chamber R2 on the discharge port 84A side separated by the blade 86, and reduces the load between the blade 86 and the blade groove 83B. Alternatively, the rotary compressor 8 may stop operating. As described above, the rotary compressor 8 can be prevented from being locked.
  • a thin film sensor that detects a circumferential gap between the blade 86 and the blade groove 83B As the thin film sensor for detecting the gap, the above-described capacitance sensor can be used.
  • a capacitance sensor is provided on the blade 86 or the blade groove 83B so as to detect the capacitance between the blade 86 and the blade groove 83B. A gap between the blade 86 and the blade groove 83B is detected from the detected capacitance.
  • the rotary compressor 8 when wear of the blade 86 and the blade groove 83B progresses, a circumferential clearance between the blade 86 and the blade groove 83B gradually increases. Therefore, the rotary compressor 8 according to the fifth embodiment has a capacitance sensor provided in the blade 86 or the blade groove 83B that the circumferential clearance between the blade 86 and the blade groove 83B becomes larger than a predetermined value. Detect by. Then, the rotational speed of the piston rotor 82 is limited to reduce the sliding speed between the blade 86 and the blade groove 83B, or the opening degree of the expansion valve on the system side is changed.
  • the rotary compressor 8 reduces the differential pressure between the compression chamber R2 on the suction port 83A side and the compression chamber R2 on the discharge port 84A side separated by the blade 86, and reduces the load between the blade 86 and the blade groove 83B.
  • the error signal may be output to the outside. Good.
  • the scroll compressor 1 of this embodiment showed the example in which the thin film sensor 7 was formed in the substantially U shape, this invention is not limited to this,
  • the shape of the thin film sensor 7 is arbitrary.
  • the thin film sensor 7 has an example of a three-layer structure including the insulating layer 72, the sensor layer 71, and the protective layer 73. It is not limited to this.
  • the thin film sensor 7 only needs to include at least the sensor layer 71.
  • the signal of the thin film sensor 7 may be used for error determination. For example, when the thin film sensor 7 outputs an abnormal value signal, an error signal indicating that the thrust surface 22A of the thrust bearing 22 may be damaged may be output to the outside.
  • the first to fifth embodiments use a thin film sensor, but the present invention is not limited to this.
  • a wire made of a thin film is provided on the surface of the reed valve 36 so that the wire is disconnected and the electrical connection is cut off. You may detect damage. When damage to the reed valve 36 is detected, an error signal may be output to the outside, and the operation of the scroll compressor 1 may be stopped so that the revolving scroll 4 does not reverse.
  • the wiring which consists of a thin film is applicable to the reed valve which abbreviate
  • the types of compressors to which the present invention is applied are not limited to scroll compressors and rotary compressors, but can be widely applied to screw compressors, reciprocating compressors, and the like.
  • the parts of the compressor to which the present invention is applied include the retainer 35 of the fixed scroll 3 of the scroll compressor 1, the retainer 37A of the discharge cover 37, the shaft thrust surface 24A of the lower bearing 24, and The shaft thrust surface 85A of the lower bearing 85 of the rotary compressor 8 is listed.

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

Abstract

L'invention concerne un compresseur avec lequel les conditions de fonctionnement peuvent être commandées pendant le fonctionnement du compresseur et des performances de compresseur appropriées en réponse aux conditions de fonctionnement peuvent être présentées, sans restrictions préalables sur les conditions de fonctionnement. Ce compresseur, qui comprime un fluide frigorigène par une force d'entraînement transmise, est caractérisé en ce qu'il est équipé d'un élément mobile déplacé par la force d'entraînement, d'un élément de support supportant l'élément mobile, et d'un moyen de détection disposé sur l'élément mobile, ledit moyen de détection détectant un changement de l'état au voisinage du moyen de détection.
PCT/JP2017/044982 2017-02-17 2017-12-14 Compresseur WO2018150706A1 (fr)

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JP2017-027428 2017-02-17
JP2017027428A JP2018132020A (ja) 2017-02-17 2017-02-17 圧縮機

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6879434B1 (ja) * 2020-02-25 2021-06-02 三菱電機株式会社 圧縮機、空気調和機、冷凍機および圧縮機制御方法
WO2024014025A1 (fr) * 2022-07-13 2024-01-18 三菱重工業株式会社 Dispositif de commande, système de compression et procédé de commande

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62178791A (ja) * 1986-02-03 1987-08-05 Matsushita Electric Ind Co Ltd スクロ−ル圧縮機
JP2001099070A (ja) * 1999-09-30 2001-04-10 Hitachi Ltd 冷凍空調圧縮機
JP2017031810A (ja) * 2015-07-28 2017-02-09 東芝キヤリア株式会社 回転式圧縮機及び冷凍サイクル装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62178791A (ja) * 1986-02-03 1987-08-05 Matsushita Electric Ind Co Ltd スクロ−ル圧縮機
JP2001099070A (ja) * 1999-09-30 2001-04-10 Hitachi Ltd 冷凍空調圧縮機
JP2017031810A (ja) * 2015-07-28 2017-02-09 東芝キヤリア株式会社 回転式圧縮機及び冷凍サイクル装置

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6879434B1 (ja) * 2020-02-25 2021-06-02 三菱電機株式会社 圧縮機、空気調和機、冷凍機および圧縮機制御方法
WO2021171347A1 (fr) * 2020-02-25 2021-09-02 三菱電機株式会社 Compresseur, climatiseur, réfrigérateur et procédé de commande de compresseur
JP2021134791A (ja) * 2020-02-25 2021-09-13 三菱電機株式会社 圧縮機、空気調和機、冷凍機、圧縮機制御方法、圧縮機制御学習用データ作成方法および圧縮機制御学習済みモデル作成方法
CN115135890A (zh) * 2020-02-25 2022-09-30 三菱电机株式会社 压缩机、空调机、制冷机以及压缩机控制方法
CN115135890B (zh) * 2020-02-25 2023-08-15 三菱电机株式会社 压缩机、空调机、制冷机、压缩机控制方法、压缩机控制学习完毕模型创建方法以及压缩机控制学习用数据创建方法
WO2024014025A1 (fr) * 2022-07-13 2024-01-18 三菱重工業株式会社 Dispositif de commande, système de compression et procédé de commande

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