EP3499042A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- EP3499042A1 EP3499042A1 EP17897200.6A EP17897200A EP3499042A1 EP 3499042 A1 EP3499042 A1 EP 3499042A1 EP 17897200 A EP17897200 A EP 17897200A EP 3499042 A1 EP3499042 A1 EP 3499042A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- detection means
- lubricating oil
- scroll
- compressor according
- 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- Withdrawn
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
- 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 which includes a mechanism for reducing a mechanical loss during an operation.
- a compressor such as a scroll compressor or a rotary compressor is used in a refrigerating cycle.
- a scroll compressor disclosed in PTL 1 includes a fixed scroll which is fixed to an inside of a casing and an orbiting scroll which meshes with the fixed scroll and of which a drive shaft is connected to a rear surface side of the scroll compressor.
- the scroll compressor if the drive shaft rotates, the orbiting scroll orbits.
- a fluid is sucked into a compression chamber formed between the two scrolls, and the fluid in the compression chamber is compressed.
- the operating condition of the scroll compressor is restricted. Accordingly, higher ability can be exerted if the operating condition is not restricted. But, the ability cannot be sufficiently exerted due to the restriction of the operating condition.
- an object of the present invention is to provide a compressor capable of exerting an appropriate compressor capacity according to an operating condition by controlling the operating condition during an operation of the compressor without restricting the operating condition in advance.
- a compressor which compresses a refrigerant by a transmitted driving force, including: a movement element which is moved by a driving force; a support element which supports the movement element; and detection means which is provided in association with the movement element, in which the detection means detects a change in a state around the detection means.
- the detection means of the present invention is a sensor having a thickness of 10 ⁇ m or less.
- the detection means of the present invention is provided on a sliding surface of the support element with respect to the movement element.
- the detection means of the present invention is provided in the movement element.
- the change in the state around the detection means is at least one of a change in a pressure of a lubricating oil, a change in a temperature of the lubricating oil, and a change in capacitance.
- the compressor of the present invention is a scroll compressor which includes a fixed scroll, an orbiting scroll which revolves and orbits with respect to the fixed scroll, a thrust bearing which supports the orbiting scroll in a revolvable manner, and a back pressure chamber into which the lubricating oil flows.
- the detection means is provided on a sliding surface of the thrust bearing, which is connected to the back pressure chamber, with respect to the orbiting scroll.
- the detection means is provided inside an accommodation chamber recessed from the sliding surface of the thrust bearing.
- the detection means has a measurement region which measures a pressure of the lubricating oil between the thrust bearing and the orbiting scroll, and the measurement region is provided inside a disposition region of the thrust bearing.
- a pressure of the lubricating oil inside the back pressure chamber is adjusted by a detection value of the detection means.
- the detection means can detect a change in a state between a key of an Oldham ring which restricts a rotation of the orbiting scroll and a key groove into which the key is inserted.
- the detection means can detect a change in a state of a compression chamber between a tooth surface of a wrap of the fixed scroll, the fixed scroll, and the orbiting scroll.
- the compressor of the present invention is a rotary compressor which includes a cylinder, a piston rotor which slides inside the cylinder, an upper bearing which is disposed on upper-side end surfaces of the cylinder and the piston rotor, a lower bearing which is disposed on lower-side end surfaces of the cylinder and the piston rotor, a compression chamber which is formed by the cylinder, the piston rotor, the upper bearing, and the lower bearing, a blade which partitions the compression chamber, and a blade groove into which the blade is inserted.
- the detection means can detect a change in a state between the blade and the blade groove.
- an appropriate compressor capacity can be exerted according to an operating condition by controlling a operating condition by a detection result without restricting the operating condition in advance.
- a physical quantity at a predetermined place is measured when the compressor is operated, and the compressor is operated under an appropriate condition based on a measurement result.
- the compressor of the present invention is applied to a scroll compressor 1
- the compressor of the present invention is applied to a rotary compressor 8.
- the scroll compressor 1 of the present embodiment includes a fixed scroll 3, an orbiting scroll 4 which is a movement element revolved and orbited with respect to the fixed scroll 3, a motor 6 which drives the orbiting scroll 4, a rotary shaft 5 which transmits the power of the motor 6 to the orbiting scroll 4, and a housing 2 which accommodates the above-described components.
- the orbiting scroll 4 is supported by a thrust bearing 22 which is a support element such that the orbiting scroll 4 can be revolved and orbited. However, a rotation of the orbiting scroll 4 is restricted by an Oldham ring 23.
- the rotary 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 which stores a lubricating oil O in a bottom portion of the housing 2.
- the lubricating oil O is pumped through an oil supply path 53 inside the rotary shaft 5 by a pump 54 provided on a lower end of the rotary shaft 5, and is supplied to locations at which the upper bearing 21, the lower bearing 24, a bearing 52 provided in an eccentric pin 51 of the rotary shaft 5, the orbiting scroll 4, the Oldham ring 23, and the thrust bearing 22 and other parts slide on each other.
- the supplied lubricating oil O is returned to the storage region 26 through a circulation passage 25.
- a suction pipe 28 and a discharge pipe 29 provided in the housing 2 is connected to a refrigerant circuit of a refrigerator (not shown) or an air conditioner (not shown).
- a drive current is supplied to a stator 61 of the motor 6 by a power supply (not shown), a rotor 62 of the motor 6 rotates, and a driving force is output to the rotary shaft 5.
- the driving force is transmitted to the orbiting scroll 4 via the eccentric pin 51 eccentrically provided in one direction (eccentric direction) radially outward from a center axis of the rotary shaft 5 on an upper end of the rotary shaft 5, and the orbiting scroll 4 is revolved and orbited with respect to the fixed scroll 3 fixed to the housing 2.
- a refrigerant which has flowed into the housing 2 from the suction pipe 28 is sucked to between the orbiting scroll 4 and the fixed scroll 3 by the orbiting of the orbiting scroll 4.
- a volume of a compression chamber R1 between the orbiting scroll 4 and the fixed scroll 3 is decreased by the orbiting of the orbiting scroll 4, and thus, the refrigerant in the compression chamber R1 is compressed.
- a thrust load generated by a pressure of the compressed refrigerant is born by the upper bearing 21 supporting an end plate 41 of the orbiting scroll 4 via the thrust bearing 22.
- the compressed refrigerant is discharged to the refrigerant circuit through the discharge pipe 29 via a discharge port 32 of the fixed scroll 3 and a discharge port 38 of a discharge cover 37.
- a reed valve 36 attached to an end plate 31 of the fixed scroll 3 via a retainer 35 is provided in the discharge port 32
- a reed valve 37B attached to the discharge cover 37 via a retainer 37A is provided in the discharge port 38 of the discharge cover 37. If the pressure of the compressed refrigerant reaches a predetermined value, the refrigerant which pushes and opens the reed valves 36 and 37B is discharged to the refrigerant circuit.
- the scroll compressor 1 of the first embodiment includes a pressure adjustment mechanism which adjusts a pressure of the lubricating oil O inside a back pressure chamber 27.
- the orbiting scroll 4 is pressed to the fixed scroll 3 side by the pressure of the lubricating oil O inside the back pressure chamber 27.
- the pressure adjustment mechanism includes the back pressure chamber 27, an accommodation chamber 22B which is formed on a surface of the thrust bearing 22 facing the orbiting scroll 4, a thin film sensor 7 which is provided inside the accommodation chamber 22B, and a control valve V which is provided in a circulation passage 25.
- the pressure of the lubricating oil O supplied into the back pressure chamber 27 is measured by the thin film sensor 7, and opening and closing of the control valve V of the circulation passage 25 are adjusted by a measurement result such that the pressure of the back pressure chamber 27 reaches a predetermined pressure.
- the back pressure chamber 27 is partitioned by the orbiting scroll 4, the upper bearing 21, and the thrust bearing 22 and is a space inside the thrust bearing 22.
- the back pressure chamber 27 is formed in an annular shape.
- the lubricating oil O supplied into the back pressure chamber 27 from the storage region 26 is returned to the storage region 26 of the housing 2 from the back pressure chamber 27 through the circulation passage 25.
- the circulation passage 25 is connected to the storage region 26 in which the lubricating oil O of the housing 2 is stored.
- the circulation passage 25 includes the control valve V which controls a circulation flow rate of the lubricating oil O.
- the control valve V is used as a generic name for control valves V1, V2, V3, and V4.
- control valve V an electromagnetic valve whose flow path is opened or closed according to an instruction can be exemplified as the control valve V.
- An amount of the lubricating oil O inside the back pressure chamber 27 is controlled by the control valve V as follows.
- the lubricating oil O is supplied to the back pressure chamber 27 during the operation of the scroll compressor 1. If the control valve V is closed, the lubricating oil O, which is no longer inside the back pressure chamber 27, is introduced to a thrust surface 22A side of the thrust bearing 22 and enters a gap C between the thrust bearing 22 and the orbiting scroll 4.
- the circulation passage 25 of the present embodiment branches into four passages 25A, 25B, 25C, and 25D in the middle of the circulation passage 25, and the control valves V1, V2, V3, and V4 are respectively provided in the passages 25A to 25D.
- the circulation passage 25 it is possible to adjust the amount of the lubricating oil O returned from the back pressure chamber 27 to the storage region 26 can be adjusted according to the number of the control valves V1 to V4 which are opened and closed.
- the thrust bearing 22 includes the accommodation chamber 22B which is recessed backward from the thrust surface 22A coming into contact with the orbiting scroll 4.
- the accommodation chamber 22B is provided such that a measurement region 74 which is a detection unit of the thin film sensor 7 described later does not come into contact with the orbiting scroll 4.
- the accommodation chamber 22B is connected to the back pressure chamber 27 via the gap C between the thrust bearing 22 and the orbiting scroll 4.
- the accommodation chamber 22B is formed of a linear groove which is provided on the thrust surface 22A and extends in a radial direction.
- a depth D of the accommodation chamber 22B is deeper than a thickness T of the measurement region 74 of the thin film sensor 7 which is provided inside the accommodation 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 an electric resistance value.
- the thin film sensor 7 includes a linear portion which extends radially inward from an outer peripheral edge 22D of the thrust surface 22A, a curved portion which is connected to the linear portion, and a linear portion which is connected to the curved portion and extends the outer peripheral edge 22D of the thrust surface 22A. That is, the thin film sensor 7 is formed in an approximately 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 respective 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 laminated in order from the thrust bearing 22 side.
- the sensor layer 71 has a characteristic that the electric resistance value is changed if the pressure of the lubricating oil O inside the back pressure chamber 27 is changed.
- the insulating layer 72 electrically insulates a portion between the thrust bearing 22 and the sensor layer 71.
- the protective layer 73 protects the sensor layer 71 such that the sensor layer 71 is not damaged by foreign matters such as metal powder entering the accommodation chamber 22B.
- a thickness of the sensor layer 71 is 1 ⁇ m or less, preferably, the entire thickness T of the thin film sensor 7 including the insulating layer 72 and the protective layer 73 is selected from a range of 10 ⁇ m or less, more preferably is approximately 5 ⁇ m or less, and particularly preferably is approximately 3 ⁇ m or less.
- the sensor layer 71 is formed of a material having a characteristic that the electric resistance value is changed according to the change in the pressure.
- a material having a characteristic that the electric resistance value is changed according to the change in the pressure For example, Manganin (registered trademark) which is a Cu-Mn-Ni based alloy can be used. Typically, the Manganin has a chemical composition of 84% of Cu, 12% of Mn, and 4% of Ni in mass%.
- the insulating layer 72 is formed of a material having electric insulation properties.
- 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
- aluminum oxide or the like
- the thin film sensor 7 has the measurement region 74 which is used as a detection unit which measures the pressure of the lubricating oil O inside the back pressure chamber 27.
- the measurement region 74 is set to a width which is so small that the electric resistance value of the other regions 79 can be ignored, as compared with the electric resistance value of the measurement region 74.
- an electric resistance value between terminals provided on both ends of the thin film sensor 7 is substantially the same as the electric resistance value of the measurement region 74.
- the change in the pressure by the lubricating oil O acting on the measurement region 74 of the thin film sensor 7 inside the accommodation chamber 22B is detected as a change in an electric resistance between the terminals.
- the width of the measurement region 74 is narrow, and thus, sensitivity of the measurement region 74 with respect to the change in the electric resistance is higher than those of the other regions 79.
- a width W of the measurement region 74 can be 20 to 30 ⁇ m.
- the entire thin film sensor 7 including the measurement region 74 is a three-layer structure including the insulating layer 72, the sensor layer 71, and the protective layer 73.
- the measurement region 74 is provided in a disposition region 22C of the thrust surface 22A of the thrust bearing 22.
- annular region 22E radially inside the outer peripheral edge 22D strongly abuts against the end plate 41 of the orbiting scroll 4 which revolves and orbits.
- annular region 22G radially outside an inner peripheral edge 22F strongly abuts against the end plate 41 if the end plate 41 of the orbiting scroll 4 is deformed.
- the disposition region 22C is an annular region except for the regions 22E and 22G in the thrust surface 22A of the thrust bearing 22.
- a width of each of the regions 22E and 22G is approximately 1 mm.
- the measurement region 74 is provided in the disposition region 22C which has a weaker abutment against the end plate 41 compared to the regions 22E and 22G, the thin film sensor 7 can stably measure the pressure of the lubricating oil O inside the back pressure chamber 27.
- the thrust bearing 22 is in contact with the orbiting scroll 4, and thus, in a boundary lubrication state I where the lubricating oil O is insufficient or does not exist in the gap C between the thrust surface 22A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4, an oil pressure measured by the thin film sensor 7 is low.
- the measured oil pressure further increases. Moreover, in a fluid lubrication state III where the thrust bearing 22 and the orbiting scroll 4 do not come into contact with each other and is completely separated from each other, the oil pressure measured by the thin film sensor 7 is higher than that in the mixed lubrication state II.
- a dynamic frictional coefficient between the thrust surface 22A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4 decreases if the state is transferred from the boundary lubrication state I to the mixed lubrication state II.
- the dynamic frictional coefficient increases if the state is transferred from the mixed lubrication state II to the fluid lubrication state III.
- the gap C between the thrust surface 22A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4 is in the mixed lubrication state II.
- the pressure adjustment mechanism In the pressure adjustment mechanism, the gap C between the thrust surface 22A and the end plate 41 maintains the mixed lubrication state II in which an oil film is formed by the lubricating oil O. Accordingly, the pressure adjustment mechanism changes the number of the control valves V to be closed for each threshold value.
- the lubricating oil O is supplied to the back pressure chamber 27.
- four threshold values such as threshold values P1, P2, P3, and P4 are set in order to control opening and closing of the control valve V (V1 to V4).
- the threshold values P1, P2, P3, and P4 are set to determine the number of the control valves V1 to V4 to be opened and closed by the oil pressure measured 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 mixed lubrication state II in which the oil film is formed by the lubricating oil O.
- the state is not transferred from the state II to the fluid lubrication state III in which much lubricating oil O enters the gap C and the thrust bearing 22 and the orbiting scroll 4 are separated from each other without coming into contact with each other.
- the gap C between the thrust surface 22A and the end plate 41 is in the state III. Accordingly, all the control valves V1 to V4 are opened such that the gap C between the thrust surface 22A and the end plate 41 is transferred from the state III to the state II.
- the pressure of the lubricating oil O inside the back pressure chamber 27 measured by the thin film sensor 7 does not reach the threshold value P1
- the gap C between the thrust surface 22A of the thrust bearing 22 and the end plate 41 of the orbiting scroll 4 is in the boundary lubrication state I in which the lubricating oil O is insufficient or does not exist. Therefore, all the control valves V1 to V4 are closed. Accordingly, the amount of the lubricating oil O inside the back pressure chamber 27 increases, and thus, the state can be transferred to the mixed lubrication state II in which the oil film is formed between the thrust surface 22A and the end plate 41 by the lubricating oil O.
- the scroll compressor 1 includes the pressure adjustment mechanism which adjusts the pressure of the back pressure chamber 27 to a desired pressure by controlling opening and closing of the control valve V (V1 to V4) of the circulation passage 25 based on the pressure of the lubricating oil O inside the back pressure chamber 27 measured by the thin film sensor 7 which is the detection means.
- the scroll compressor 1 it is possible to appropriately control the pressure of the lubricating oil O inside the back pressure chamber 27 while lubricating a location at which the orbiting scroll 4, the thrust bearing 22, or the like and other parts slide on each other, and thus, an appropriate compressor capacity can be exerted according to the operating condition.
- the pressure of the lubricating oil O inside the back pressure chamber 27 required to obtain a desired compressor capacity during the operation of the scroll compressor 1 is changed by influences of a thrust load of the orbiting scroll 4 changed by the operating condition, wedge effects of the lubricating oil on a sliding surface, or the like. Accordingly, it is difficult to calculate the appropriate pressure of the lubricating oil O inside the back pressure chamber 27 during the operation of the scroll compressor 1.
- the pressure of the lubricating oil O inside the back pressure chamber 27 may not be the value required to obtain a desired compressor capacity due to the operating condition of the scroll compressor 1.
- the pressure can be appropriately controlled, and thus, an appropriate compressor capacity can be exerted according to the operating condition.
- the thin film sensor 7 is provided in the accommodation chamber 22B provided on the thrust surface 22A coming into contact with the orbiting scroll 4, and a portion between the thin film sensor 7 and the orbiting scroll 4 is filled with the lubricating oil O. Accordingly, the thin film sensor 7 can detect the pressure of the lubricating oil O inside the back pressure chamber 27 without coming into contact with the orbiting scroll 4.
- the measurement region 74 is disposed within the range of the disposition region 22C having a relatively weak abutment, and thus, it is possible to stably measure the pressure of the lubricating oil O inside the back pressure chamber 27.
- the thin film sensor 7 in association with the orbiting scroll 4 which is a movement element. That is, the thin film sensor 7 can be provided in the orbiting scroll 4. However, the thin film sensor 7 is provided in the stationary thrust bearing 22, and thus, compared to a case where the thin film sensor 7 is provided in the orbiting scroll 4 which performs the orbiting movement, a terminal of the thin film sensor 7 can be easily wired.
- the scroll compressor 1 of the second embodiment suggests that the thin film sensor 7 for measuring the pressure or the temperature of the lubricating oil O between a key and a key groove is provided in the key groove of the upper bearing 21 on which the key of the Oldham ring 23 (not shown) slides.
- thermocouple which can measure a temperature by a thermoelectromotive force or a resistance temperature sensor in which a resistance value is changed by a temperature so as to measure the temperature
- a platinum thin film temperature sensor can be used as the thin film sensor which detects the temperature.
- the thin film sensor is provided in an accommodation chamber which is formed in the key groove similarly to the accommodation chamber 22B of the first embodiment. This also applies to the third and subsequent embodiments.
- the amount of the lubricating oil O to be supplied to a portion between the key and the key groove is increased by temporarily increasing a rotating speed of the orbiting scroll 4.
- the same reference numerals as those of the first embodiment are assigned to components similar to those of the first embodiment, and descriptions thereof are omitted.
- the thin film sensor 7 can be provided on a tooth surface 34 of a wrap 33 of the fixed scroll 3. Although not shown, the thin film sensor 7 is provided inside an accommodation chamber formed on the tooth surface 34. In the third embodiment, the thin film sensor 7 is provided so as to detect occurrence of so-called liquid compression inside the compression chamber R1 in advance.
- the thin film sensor 7 is provided on the tooth surface 34, the thin film sensor 7 is extremely thin, and thus, it is possible to minimize a dead volume which a factor of lowering compression efficiency of the refrigerant.
- the scroll compressor 1 if a liquid refrigerant is sucked and liquid compression is generated, the pressure inside the compression chamber R1 significantly increases. Therefore, in the scroll compressor 1, if the thin film sensor 7 measures a pressure having a predetermined value at which the liquid compression may be generated, the rotating speed of the orbiting scroll 4 decreases.
- the thin film sensor 7 which measures a pressure of the lubricating oil O between the upper bearing 21 and the rotary shaft 5
- a sensor which measures capacitance between the upper bearing 21 and the rotary shaft 5 is provided in a portion of the upper bearing 21 facing the rotary shaft 5.
- the above-described sensors can be used.
- the thin film sensor detects that the temperature between the upper bearing 21 and the rotary shaft 5 or the load obtained from the pressure of the lubricating oil O is a predetermined value or more. Then, the load between the upper bearing 21 and the rotary shaft 5 is decreased or the operation of the scroll compressor 1 is stopped by decreasing the rotating speed of the rotary shaft 5.
- a dilution rate of the lubricating oil O by the refrigerant is calculated from a relationship between temperature and the pressure measured by the thin film sensor or the capacitance and the dilution rate is a predetermined value or more, an operation of decreasing the load between the upper bearing 21 and the rotary shaft 5 can be performed by decreasing the rotating speed of the rotary shaft 5 or the pressure of the lubricating oil O until the dilution rate decreases.
- the dilution rate from the relationship between the temperature and the pressure is calculated from a relationship expression previously obtained according to a type of the compressed refrigerant or the used lubricating oil O.
- the dilution rate from the capacitance is calculated by a correlation between the capacitance and the dilution rate obtained in advance.
- the gap means not only a presence or absence of a gap but also a dimension of the gap. This is also applied to a fifth embodiment described next.
- the above-described sensor for measuring the capacitance can be used.
- a capacitance sensor is provided on the upper bearing 21 so as to measure the capacitance between the upper bearing 21 and the rotary shaft 5. If a gap between the capacitance sensor and the rotary shaft 5 is changed, the capacitance generated between the capacitance sensor and the rotary shaft 5 is changed, and thus, it is possible to detect the gap between the upper bearing 21 and the rotary shaft 5 from the measured capacitance.
- an outer peripheral surface of the rotary shaft 5 strongly abuts against the upper bearing 21 a position which is deviated by a predetermined angle in a rotation direction of the rotary shaft 5 in an eccentric direction of the provided eccentric pin 51.
- this position varies depending on an element such as a centrifugal force generated by the orbiting of the orbiting scroll 4, typically, the position is a position deviated by 90°. Accordingly, if the scroll compressor 1 is continuously used, abrasion of the strongly abutting portion of the rotary shaft 5 preferentially increases, and thus, a radial gap between the strongly abutting portion of the rotary shaft 5 and the upper bearing 21 increases.
- the scroll compressor 1 of the fourth embodiment if the capacitance sensor provided in the upper bearing 21 detects that the radial gap between the upper bearing 21 and the rotary shaft 5 increases to be a predetermined value or more, the operation is stopped. In the scroll compressor 1, an error signal for informing that the operation has been stopped can be output according to the stopping of the operation.
- the fifth embodiment relates to the rotary compressor 8.
- the rotary compressor 8 includes a cylinder 83, a piston rotor 82 which slides inside the cylinder 83, a motor 89 which drives the piston rotor 82, a rotary shaft 87 which transmits power of the motor 89 to the piston rotor 82, and a housing 81 which accommodates the above-described components.
- An upper bearing 84 is disposed on upper-side end surfaces of the cylinder 83 and the piston rotor 82, and a lower bearing 85 is disposed on lower-side end surfaces thereof.
- the piston rotor 82 is inserted into an eccentric shaft portion 87A of the rotary shaft 87 along a center axis of the housing 81 and is fixed to the eccentric shaft portion 87A.
- the rotary shaft 87 is rotatably supported by the upper bearing 84 and the lower bearing 85.
- a 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 includes a blade groove 83B which is connected to the compression chamber R2 and into which a blade 86 is inserted and an accommodation groove 83D which is connected to the blade groove 83B and in which a coil spring 83C is accommodated.
- the cylinder 83 penetrates in a radial direction by the blade groove 83B and the accommodation groove 83D.
- the compression chamber R2 is partitioned by the plate-shaped blade 86 which is formed to have a height similar to an axial dimension of the piston rotor 82.
- the blade 86 is inserted into the blade groove 83B and is circumferentially supported. In addition, a distal end of the blade 86 is always pressed to an outer peripheral surface of the piston rotor 82 by a pressing force generated by the coil spring 83C disposed inside the accommodation groove 83D and a pressure generated by a high-pressure portion. The blade 86 protrudes or retracts with respect to the compression chamber R2 inside the cylinder 83 according to a rotation angle of the piston rotor 82.
- the refrigerant sucked into the cylinder 83 from a suction port 83A is compressed by being pushed by the piston rotor 82 in the cylinder 83.
- the compressed refrigerant is discharged from a discharge port 84A formed in the upper bearing 84.
- a reed valve (not shown) is provided in the discharge port 84A. If the pressure of the compressed refrigerant reaches a predetermined value, the reed valve is pushed and opened, and thus, the refrigerant is discharged to the outside of the cylinder 83.
- the discharged refrigerant is supplied to a system side such as a refrigerator (not shown) or an air conditioner (not shown) connected to the rotary compressor 8.
- the thin film sensor 7 which measures a circumferential contact pressure between the blade 86 and the blade groove 83B is provided in the blade 86 or the blade groove 83B.
- the thin film sensor 7 is not shown.
- the rotary compressor 8 includes a thin film sensor which detects a circumferential gap between the blade 86 and the blade groove 83B. This thin film sensor is not shown.
- the thin film sensor 7 detects that the contact pressure between the blade 86 and the blade groove 83B is a predetermined value or more. Then, a rotating speed of the piston rotor 82 is limited so as to decrease a sliding speed between the blade 86 and the blade groove 83B or change an opening degree of an expansion valve on the system side. In this way, in the rotary compressor 8, a 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 is decreased so as to decrease a load between the blade 86 and the blade groove 83B. Alternatively, the operation of the rotary compressor 8 may be stopped.
- the above-described capacitance sensor can be used.
- the capacitance sensor is provided in the blade 86 or the blade groove 83B in order to measure the capacitance between the blade 86 and the blade groove 83B.
- the gap between the blade 86 and the blade groove 83B is detected from the measured capacitance.
- the capacitance sensor provided in the blade 86 or the blade groove 83B detects that the circumferential gap between the blade 86 and the blade groove 83B increase to reach the predetermined value or more. Then, the rotating speed of the piston rotor 82 is limited so as to decrease the sliding speed between the blade 86 and the blade groove 83B or change the opening degree of the expansion valve on the system side. In this way, in the rotary compressor 8, a 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 is decreased so as to decrease a load between the blade 86 and the blade groove 83B.
- an error signal may be output to the outside.
- the present invention is not limited to this, and the thin film sensor 7 may be formed in any shape.
- the thin film sensor 7 has a three-layer structure including the insulating layer 72, the sensor layer 71, and the protective layer 73 is described.
- the present invention is not limited to this.
- the thin film sensor 7 may have any layer structure as long as it has at least the sensor layer 71.
- the signal of the thin film sensor 7 may be used to determine an error. For example, if the thin film sensor 7 outputs a signal having an abnormal value, an error signal indicating that the thrust surface 22A of the thrust bearing 22 may be damaged may be output to the outside.
- the thin film sensor 7 is provided in the upper bearing 21 of the scroll compressor 1 in the fourth embodiment.
- the thin film sensor 7 may be provided in other journal bearings, for example, the lower bearing 24 of the scroll compressor 1, the upper bearing 84 and the lower bearing 85 of the rotary compressor 8, or the like.
- the thin film sensor is used.
- the present invention is not limited to this.
- a wire formed of a thin film may be provided on the surface of the reed valve 36 so as to detect the damage of the reed valve 36 such that the wire is cut off and an electric connection is cut off if damage such as defect or crack occurs in the reed valve 36 of the scroll compressor 1.
- an error signal may be output to the outside, and the operation of the scroll compressor 1 may be stopped such that a reverse rotation is not generated in the orbiting scroll 4.
- the wire formed of a thin film can be applied to a reed valve (not shown) of the rotary compressor 8.
- the type of the compressor to which the present invention is applied is not limited to the scroll compressor or the rotary compressor, and can be widely applied to a screw compressor, a reciprocating compressor, or the like.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Provided is a compressor with which the operating conditions can be controlled during operation of the compressor and suitable compressor performance in response to the operating conditions can be exhibited, with no prior restrictions on the operating conditions. This compressor, which compresses a refrigerant by transmitted driving force, is characterized by being equipped with a moving element moved by driving force, a support element supporting the moving element, and a detection means provided accompanying the moving element, said detection means detecting a change in the state in the vicinity of the detection means.
Description
- The present invention relates to a compressor which includes a mechanism for reducing a mechanical loss during an operation.
- In the related art, a compressor such as a scroll compressor or a rotary compressor is used in a refrigerating cycle. For example, a scroll compressor disclosed in
PTL 1 includes a fixed scroll which is fixed to an inside of a casing and an orbiting scroll which meshes with the fixed scroll and of which a drive shaft is connected to a rear surface side of the scroll compressor. In the scroll compressor, if the drive shaft rotates, the orbiting scroll orbits. In addition, during the orbiting, a fluid is sucked into a compression chamber formed between the two scrolls, and the fluid in the compression chamber is compressed. - In addition, in the scroll compressor, during a compression operation, a pressure of a back pressure space formed between the orbiting scroll and a housing on a rear surface side of the orbiting scroll increases, and thus, the orbiting scroll is pressed to the fixed scroll, a sliding loss of thrust bearing decreases, and it is possible to improve efficiency of the compression.
- [PTL 1] Japanese Unexamined Patent Application Publication No.
5-187369 - However, in a scroll compressor, a state of an orbiting scroll depends on an operating condition. In addition, it is difficult to ascertain the state of the orbiting scroll with respect to the operating condition.
- Therefore, in order to secure ability of the orbiting scroll capable of performing a required function during a given period under a given condition, that is, in order to secure reliability performance thereof, the operating condition of the scroll compressor is restricted. Accordingly, higher ability can be exerted if the operating condition is not restricted. But, the ability cannot be sufficiently exerted due to the restriction of the operating condition.
- Therefore, an object of the present invention is to provide a compressor capable of exerting an appropriate compressor capacity according to an operating condition by controlling the operating condition during an operation of the compressor without restricting the operating condition in advance.
- According to an aspect of the present invention, there is provided a compressor which compresses a refrigerant by a transmitted driving force, including: a movement element which is moved by a driving force; a support element which supports the movement element; and detection means which is provided in association with the movement element, in which the detection means detects a change in a state around the detection means.
- Preferably, the detection means of the present invention is a sensor having a thickness of 10 µm or less.
- Preferably, the detection means of the present invention is provided on a sliding surface of the support element with respect to the movement element.
- Preferably, the detection means of the present invention is provided in the movement element.
- Preferably, the change in the state around the detection means is at least one of a change in a pressure of a lubricating oil, a change in a temperature of the lubricating oil, and a change in capacitance.
- Preferably, the compressor of the present invention is a scroll compressor which includes a fixed scroll, an orbiting scroll which revolves and orbits with respect to the fixed scroll, a thrust bearing which supports the orbiting scroll in a revolvable manner, and a back pressure chamber into which the lubricating oil flows.
- Preferably, in a case where the compressor of the present invention is a scroll compressor, the detection means is provided on a sliding surface of the thrust bearing, which is connected to the back pressure chamber, with respect to the orbiting scroll.
- In this case, preferably, the detection means is provided inside an accommodation chamber recessed from the sliding surface of the thrust bearing.
- Moreover, preferably, the detection means has a measurement region which measures a pressure of the lubricating oil between the thrust bearing and the orbiting scroll, and the measurement region is provided inside a disposition region of the thrust bearing.
- Preferably, in the compressor of the present invention, a pressure of the lubricating oil inside the back pressure chamber is adjusted by a detection value of the detection means.
- In the case where the compressor of the present invention is the scroll compressor, the detection means can detect a change in a state between a key of an Oldham ring which restricts a rotation of the orbiting scroll and a key groove into which the key is inserted.
- Moreover, the detection means can detect a change in a state of a compression chamber between a tooth surface of a wrap of the fixed scroll, the fixed scroll, and the orbiting scroll.
- Preferably, the compressor of the present invention is a rotary compressor which includes a cylinder, a piston rotor which slides inside the cylinder, an upper bearing which is disposed on upper-side end surfaces of the cylinder and the piston rotor, a lower bearing which is disposed on lower-side end surfaces of the cylinder and the piston rotor, a compression chamber which is formed by the cylinder, the piston rotor, the upper bearing, and the lower bearing, a blade which partitions the compression chamber, and a blade groove into which the blade is inserted.
- In a case where the compressor of the present invention is the rotary compressor, the detection means can detect a change in a state between the blade and the blade groove.
- According to the present invention, by measuring a physical quantity at a predetermined place when the compressor is operated, an appropriate compressor capacity can be exerted according to an operating condition by controlling a operating condition by a detection result without restricting the operating condition in advance.
-
-
Fig. 1 is a sectional view schematically showing the entire view of a scroll compressor of a first embodiment. -
Fig. 2 is a partially enlarged view ofFig. 1 . -
Fig. 3 is a plan view of a characteristic portion of the scroll compressor of the first embodiment. -
Fig. 4A is a plan view of the characteristic portion of the scroll compressor of the first embodiment,Fig. 4B is a sectional view taken along line b-b ofFig. 4A, and Fig. 4C is a partially enlarged view ofFig. 4A . -
Fig. 5A is a graph showing a relationship between a sensor output of a thin film sensor and a pressure of a lubricating oil inside a back pressure chamber andFig. 5B is a graph (Stribeck curve) showing a relationship between a frictional coefficient between an orbiting scroll and a thrust bearing and a bearing characteristic number of the orbiting scroll. -
Fig. 6A is a sectional view schematically showing the entire view of a rotary compressor of another embodiment andFig. 6B is a sectional view taken along line b-b ofFig. 4A . - In a compressor of the present invention, a physical quantity at a predetermined place is measured when the compressor is operated, and the compressor is operated under an appropriate condition based on a measurement result.
- Hereinafter, in the compressor of the present invention, first to fifth embodiments will be described.
- In the first to fourth embodiments, the compressor of the present invention is applied to a
scroll compressor 1, and in the fifth embodiment, the compressor of the present invention is applied to a rotary compressor 8. - First, configurations and operations common to the first to fourth embodiments described later will be described with reference to
Fig. 1 . - As shown in
Fig. 1 , thescroll compressor 1 of the present embodiment includes afixed scroll 3, anorbiting scroll 4 which is a movement element revolved and orbited with respect to thefixed scroll 3, amotor 6 which drives theorbiting scroll 4, arotary shaft 5 which transmits the power of themotor 6 to theorbiting scroll 4, and ahousing 2 which accommodates the above-described components. - The orbiting
scroll 4 is supported by a thrust bearing 22 which is a support element such that the orbitingscroll 4 can be revolved and orbited. However, a rotation of the orbitingscroll 4 is restricted by an Oldhamring 23. - The
rotary shaft 5 is rotatably supported by an upper bearing 21 and a lower bearing 24 fixed to thehousing 2. - As shown in
Fig. 1 , thehousing 2 includes astorage region 26 which stores a lubricating oil O in a bottom portion of thehousing 2. The lubricating oil O is pumped through anoil supply path 53 inside therotary shaft 5 by apump 54 provided on a lower end of therotary shaft 5, and is supplied to locations at which the upper bearing 21, thelower bearing 24, abearing 52 provided in aneccentric pin 51 of therotary shaft 5, the orbitingscroll 4, the Oldhamring 23, and the thrust bearing 22 and other parts slide on each other. The supplied lubricating oil O is returned to thestorage region 26 through acirculation passage 25. - A
suction pipe 28 and adischarge pipe 29 provided in thehousing 2 is connected to a refrigerant circuit of a refrigerator (not shown) or an air conditioner (not shown). - In the
scroll compressor 1, if a drive current is supplied to astator 61 of themotor 6 by a power supply (not shown), a rotor 62 of themotor 6 rotates, and a driving force is output to therotary shaft 5. - If the
rotary shaft 5 rotates, the driving force is transmitted to theorbiting scroll 4 via theeccentric pin 51 eccentrically provided in one direction (eccentric direction) radially outward from a center axis of therotary shaft 5 on an upper end of therotary shaft 5, and theorbiting scroll 4 is revolved and orbited with respect to the fixedscroll 3 fixed to thehousing 2. - A refrigerant which has flowed into the
housing 2 from thesuction pipe 28 is sucked to between the orbitingscroll 4 and the fixedscroll 3 by the orbiting of theorbiting scroll 4. In addition, a volume of a compression chamber R1 between the orbitingscroll 4 and the fixedscroll 3 is decreased by the orbiting of theorbiting scroll 4, and thus, the refrigerant in the compression chamber R1 is compressed. A thrust load generated by a pressure of the compressed refrigerant is born by theupper bearing 21 supporting anend plate 41 of theorbiting scroll 4 via thethrust bearing 22. - The compressed refrigerant is discharged to the refrigerant circuit through the
discharge pipe 29 via adischarge port 32 of the fixedscroll 3 and adischarge port 38 of adischarge cover 37. Areed valve 36 attached to anend plate 31 of the fixedscroll 3 via aretainer 35 is provided in thedischarge port 32, and areed valve 37B attached to thedischarge cover 37 via aretainer 37A is provided in thedischarge port 38 of thedischarge cover 37. If the pressure of the compressed refrigerant reaches a predetermined value, the refrigerant which pushes and opens thereed valves - The
scroll compressor 1 of the first embodiment includes a pressure adjustment mechanism which adjusts a pressure of the lubricating oil O inside aback pressure chamber 27. - In the
scroll compressor 1, theorbiting scroll 4 is pressed to the fixedscroll 3 side by the pressure of the lubricating oil O inside theback pressure chamber 27. - As shown in
Figs. 2 and3 , the pressure adjustment mechanism includes theback pressure chamber 27, anaccommodation chamber 22B which is formed on a surface of the thrust bearing 22 facing theorbiting scroll 4, athin film sensor 7 which is provided inside theaccommodation chamber 22B, and a control valve V which is provided in acirculation passage 25. - In the pressure adjustment mechanism, the pressure of the lubricating oil O supplied into the
back pressure chamber 27 is measured by thethin film sensor 7, and opening and closing of the control valve V of thecirculation passage 25 are adjusted by a measurement result such that the pressure of theback pressure chamber 27 reaches a predetermined pressure. - Hereinafter, each configuration of the pressure adjustment mechanism will be described.
- As shown in
Fig. 2 , theback pressure chamber 27 is partitioned by theorbiting scroll 4, theupper bearing 21, and thethrust bearing 22 and is a space inside thethrust bearing 22. Theback pressure chamber 27 is formed in an annular shape. - The lubricating oil O supplied into the
back pressure chamber 27 from thestorage region 26 is returned to thestorage region 26 of thehousing 2 from theback pressure chamber 27 through thecirculation passage 25. - As shown in
Fig. 1 , thecirculation passage 25 is connected to thestorage region 26 in which the lubricating oil O of thehousing 2 is stored. Thecirculation passage 25 includes the control valve V which controls a circulation flow rate of the lubricating oil O. In the present embodiment, the control valve V is used as a generic name for control valves V1, V2, V3, and V4. - In the present embodiment, an electromagnetic valve whose flow path is opened or closed according to an instruction can be exemplified as the control valve V.
- An amount of the lubricating oil O inside the
back pressure chamber 27 is controlled by the control valve V as follows. - In the
scroll compressor 1, the lubricating oil O is supplied to theback pressure chamber 27 during the operation of thescroll compressor 1. If the control valve V is closed, the lubricating oil O, which is no longer inside theback pressure chamber 27, is introduced to athrust surface 22A side of thethrust bearing 22 and enters a gap C between thethrust bearing 22 and theorbiting scroll 4. - Meanwhile, if the control valve V is opened in a state where the lubricating oil O enters the gap C, the lubricating oil O flows from the gap C toward the
circulation passage 25. - The
circulation passage 25 of the present embodiment branches into fourpassages 25A, 25B, 25C, and 25D in the middle of thecirculation passage 25, and the control valves V1, V2, V3, and V4 are respectively provided in the passages 25A to 25D. In thecirculation passage 25, it is possible to adjust the amount of the lubricating oil O returned from theback pressure chamber 27 to thestorage region 26 can be adjusted according to the number of the control valves V1 to V4 which are opened and closed. - In addition, it is possible to adjust the amount of the lubricating oil O returned from the
back pressure chamber 27 to thestorage region 26 using a flow rate adjustment valve instated of the plurality of control valves V1 to V4. - As shown in
Fig. 3 , thethrust bearing 22 includes theaccommodation chamber 22B which is recessed backward from thethrust surface 22A coming into contact with theorbiting scroll 4. - The
accommodation chamber 22B is provided such that ameasurement region 74 which is a detection unit of thethin film sensor 7 described later does not come into contact with theorbiting scroll 4. - As shown in
Fig. 2 , theaccommodation chamber 22B is connected to theback pressure chamber 27 via the gap C between thethrust bearing 22 and theorbiting scroll 4. - As shown in
Figs. 4A and 4C , theaccommodation chamber 22B is formed of a linear groove which is provided on thethrust surface 22A and extends in a radial direction. - As shown in
Figs. 4B and 4C , a depth D of theaccommodation chamber 22B is deeper than a thickness T of themeasurement region 74 of thethin film sensor 7 which is provided inside theaccommodation chamber 22B. - The
thin film sensor 7 detects a change in the pressure of the lubricating oil O inside theback pressure chamber 27 as a change in an electric resistance value. - As shown in
Fig. 4A , thethin film sensor 7 includes a linear portion which extends radially inward from an outerperipheral edge 22D of thethrust surface 22A, a curved portion which is connected to the linear portion, and a linear portion which is connected to the curved portion and extends the outerperipheral edge 22D of thethrust surface 22A. That is, thethin film sensor 7 is formed in an approximately U shape on thethrust surface 22A. Thethin film sensor 7 is connected to a terminal (not shown) at theperipheral edge 22D of thethrust 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 respective terminals. - As shown in
Fig. 4B , thethin film sensor 7 has a three-layer structure in which an insulatinglayer 72, asensor layer 71, and aprotective layer 73 are laminated in order from the thrust bearing 22 side. - The
sensor layer 71 has a characteristic that the electric resistance value is changed if the pressure of the lubricating oil O inside theback pressure chamber 27 is changed. The insulatinglayer 72 electrically insulates a portion between thethrust bearing 22 and thesensor layer 71. Theprotective layer 73 protects thesensor layer 71 such that thesensor layer 71 is not damaged by foreign matters such as metal powder entering theaccommodation chamber 22B. - A thickness of the
sensor layer 71 is 1 µm or less, preferably, the entire thickness T of thethin film sensor 7 including the insulatinglayer 72 and theprotective layer 73 is selected from a range of 10 µm or less, more preferably is approximately 5 µm or less, and particularly preferably is approximately 3 µm or less. - The
sensor layer 71 is formed of a material having a characteristic that the electric resistance value is changed according to the change in the pressure. For example, Manganin (registered trademark) which is a Cu-Mn-Ni based alloy can be used. Typically, the Manganin has a chemical composition of 84% of Cu, 12% of Mn, and 4% of Ni in mass%. - The insulating
layer 72 is formed of a material having electric insulation properties. For example, silicon oxide (SiO2), aluminum oxide (Al2O3), or the like can be used. - For example, DLC (Diamond-Like Carbon), PTFE (Poly Tetra Fluoro Ethylene), silicon oxide, aluminum oxide, or the like can be used for the
protective layer 73. - As shown in
Fig. 4C , thethin film sensor 7 has themeasurement region 74 which is used as a detection unit which measures the pressure of the lubricating oil O inside theback pressure chamber 27. Themeasurement region 74 is set to a width which is so small that the electric resistance value of theother regions 79 can be ignored, as compared with the electric resistance value of themeasurement region 74. - Accordingly, an electric resistance value between terminals provided on both ends of the
thin film sensor 7 is substantially the same as the electric resistance value of themeasurement region 74. In addition, the change in the pressure by the lubricating oil O acting on themeasurement region 74 of thethin film sensor 7 inside theaccommodation chamber 22B is detected as a change in an electric resistance between the terminals. - The width of the
measurement region 74 is narrow, and thus, sensitivity of themeasurement region 74 with respect to the change in the electric resistance is higher than those of theother regions 79. - For example, a width W of the
measurement region 74 can be 20 to 30 µm. - In addition, the entire
thin film sensor 7 including themeasurement region 74 is a three-layer structure including the insulatinglayer 72, thesensor layer 71, and theprotective layer 73. - As shown in
Fig. 3 , in thethin film sensor 7, themeasurement region 74 is provided in adisposition region 22C of thethrust surface 22A of thethrust bearing 22. - As shown in
Fig. 4A , in thethrust surface 22A, there is a concern that anannular region 22E radially inside the outerperipheral edge 22D strongly abuts against theend plate 41 of theorbiting scroll 4 which revolves and orbits. In addition, there is a concern that anannular region 22G radially outside an innerperipheral edge 22F strongly abuts against theend plate 41 if theend plate 41 of theorbiting scroll 4 is deformed. - As shown in
Fig. 4A , thedisposition region 22C is an annular region except for theregions thrust surface 22A of thethrust bearing 22. A width of each of theregions - The
measurement region 74 is provided in thedisposition region 22C which has a weaker abutment against theend plate 41 compared to theregions thin film sensor 7 can stably measure the pressure of the lubricating oil O inside theback pressure chamber 27. - As shown in
Fig. 5A , thethrust bearing 22 is in contact with theorbiting scroll 4, and thus, in a boundary lubrication state I where the lubricating oil O is insufficient or does not exist in the gap C between thethrust surface 22A of thethrust bearing 22 and theend plate 41 of theorbiting scroll 4, an oil pressure measured by thethin film sensor 7 is low. - However, in a mixed lubrication state II in which the lubricating oil O enters the gap C between the
thrust surface 22A of thethrust bearing 22 and theend plate 41 of theorbiting scroll 4 and an oil film is formed in the gap C by the lubricating oil O, the oil pressure measured by thethin film sensor 7 gradually increases. - If the amount of the lubricating oil O which enters the gap C between the
thrust surface 22A of thethrust bearing 22 and theend plate 41 of theorbiting scroll 4 increases, the measured oil pressure further increases. Moreover, in a fluid lubrication state III where thethrust bearing 22 and theorbiting scroll 4 do not come into contact with each other and is completely separated from each other, the oil pressure measured by thethin film sensor 7 is higher than that in the mixed lubrication state II. - In addition, as shown in
Fig. 5B , a dynamic frictional coefficient between thethrust surface 22A of thethrust bearing 22 and theend plate 41 of theorbiting scroll 4 decreases if the state is transferred from the boundary lubrication state I to the mixed lubrication state II. However, the dynamic frictional coefficient increases if the state is transferred from the mixed lubrication state II to the fluid lubrication state III. - That is, during the operation of the
scroll compressor 1, it is preferable that the gap C between thethrust surface 22A of thethrust bearing 22 and theend plate 41 of theorbiting scroll 4 is in the mixed lubrication state II. - During the operation of the
scroll compressor 1, an operation of the pressure adjustment mechanism for adjusting the pressure of the lubricating oil O inside theback pressure chamber 27 will be described with reference toFig. 1 . - In the pressure adjustment mechanism, the gap C between the
thrust surface 22A and theend plate 41 maintains the mixed lubrication state II in which an oil film is formed by the lubricating oil O. Accordingly, the pressure adjustment mechanism changes the number of the control valves V to be closed for each threshold value. - In addition, during the operation of the
scroll compressor 1, the lubricating oil O is supplied to theback pressure chamber 27. Moreover, in thescroll compressor 1, four threshold values such as threshold values P1, P2, P3, and P4 are set in order to control opening and closing of the control valve V (V1 to V4). The threshold values P1, P2, P3, and P4 are set to determine the number of the control valves V1 to V4 to be opened and closed by the oil pressure measured by thethin film sensor 7. Moreover, in the present embodiment, the threshold value P2 is larger than the threshold value P1, the threshold value P3 is larger than the threshold value P2, and the threshold value P4 is larger than the threshold value P3. - When the pressure of the lubricating oil O inside the
back pressure chamber 27 measured by thethin film sensor 7 is in a range of the threshold values P1, P2, and P3, the gap C between thethrust surface 22A and theend plate 41 is in the mixed lubrication state II in which the oil film is formed by the lubricating oil O. By increasing the number of the control valves V opened as the pressure reaches the threshold value P3 from the threshold value P1, the state is not transferred from the state II to the fluid lubrication state III in which much lubricating oil O enters the gap C and thethrust bearing 22 and theorbiting scroll 4 are separated from each other without coming into contact with each other. - If the measured oil pressure reaches the threshold value P4, the gap C between the
thrust surface 22A and theend plate 41 is in the state III. Accordingly, all the control valves V1 to V4 are opened such that the gap C between thethrust surface 22A and theend plate 41 is transferred from the state III to the state II. - Moreover, if the pressure of the lubricating oil O inside the
back pressure chamber 27 measured by thethin film sensor 7 does not reach the threshold value P1, the gap C between thethrust surface 22A of thethrust bearing 22 and theend plate 41 of theorbiting scroll 4 is in the boundary lubrication state I in which the lubricating oil O is insufficient or does not exist. Therefore, all the control valves V1 to V4 are closed. Accordingly, the amount of the lubricating oil O inside theback pressure chamber 27 increases, and thus, the state can be transferred to the mixed lubrication state II in which the oil film is formed between thethrust surface 22A and theend plate 41 by the lubricating oil O. - Hereinafter, effects exerted by the
scroll compressor 1 will be described. - The
scroll compressor 1 includes the pressure adjustment mechanism which adjusts the pressure of theback pressure chamber 27 to a desired pressure by controlling opening and closing of the control valve V (V1 to V4) of thecirculation passage 25 based on the pressure of the lubricating oil O inside theback pressure chamber 27 measured by thethin film sensor 7 which is the detection means. - Accordingly, in the
scroll compressor 1, it is possible to appropriately control the pressure of the lubricating oil O inside theback pressure chamber 27 while lubricating a location at which theorbiting scroll 4, thethrust bearing 22, or the like and other parts slide on each other, and thus, an appropriate compressor capacity can be exerted according to the operating condition. - Hereinafter, with comparison with the pressure of the lubricating oil O inside the
back pressure chamber 27 is set in advance so as to be within a predetermined defined value, descriptions will be given. - The pressure of the lubricating oil O inside the
back pressure chamber 27 required to obtain a desired compressor capacity during the operation of thescroll compressor 1 is changed by influences of a thrust load of theorbiting scroll 4 changed by the operating condition, wedge effects of the lubricating oil on a sliding surface, or the like. Accordingly, it is difficult to calculate the appropriate pressure of the lubricating oil O inside theback pressure chamber 27 during the operation of thescroll compressor 1. - Therefore, even when the pressure of the lubricating oil O inside the
back pressure chamber 27 is within the predetermined defined value, the pressure of the lubricating oil O inside theback pressure chamber 27 may not be the value required to obtain a desired compressor capacity due to the operating condition of thescroll compressor 1. - Meanwhile, in the
scroll compressor 1, the change in the state around thethin film sensor 7, that is, the change in the pressure of the lubricating oil O inside theback pressure chamber 27 during the operation is detected, the pressure can be appropriately controlled, and thus, an appropriate compressor capacity can be exerted according to the operating condition. - Next, in the
scroll compressor 1, thethin film sensor 7 is provided in theaccommodation chamber 22B provided on thethrust surface 22A coming into contact with theorbiting scroll 4, and a portion between thethin film sensor 7 and theorbiting scroll 4 is filled with the lubricating oil O. Accordingly, thethin film sensor 7 can detect the pressure of the lubricating oil O inside theback pressure chamber 27 without coming into contact with theorbiting scroll 4. - Moreover, in the
thin film sensor 7, themeasurement region 74 is disposed within the range of thedisposition region 22C having a relatively weak abutment, and thus, it is possible to stably measure the pressure of the lubricating oil O inside theback pressure chamber 27. - In addition, in the
scroll compressor 1, it is sufficient for thethin film sensor 7 to be provided in association with theorbiting scroll 4 which is a movement element. That is, thethin film sensor 7 can be provided in theorbiting scroll 4. However, thethin film sensor 7 is provided in thestationary thrust bearing 22, and thus, compared to a case where thethin film sensor 7 is provided in theorbiting scroll 4 which performs the orbiting movement, a terminal of thethin film sensor 7 can be easily wired. - Next, a second embodiment of the present invention will be described with reference to
Figs. 1 and2 . - Moreover, in the second embodiment, the same reference numerals as those of the first embodiment are assigned to components similar to those of the first embodiment, and descriptions thereof are omitted.
- The
scroll compressor 1 of the second embodiment suggests that thethin film sensor 7 for measuring the pressure or the temperature of the lubricating oil O between a key and a key groove is provided in the key groove of theupper bearing 21 on which the key of the Oldham ring 23 (not shown) slides. - As the thin film sensor which detects the temperature, a thermocouple which can measure a temperature by a thermoelectromotive force or a resistance temperature sensor in which a resistance value is changed by a temperature so as to measure the temperature, for example, a platinum thin film temperature sensor can be used.
- In the second embodiment, the thin film sensor is provided in an accommodation chamber which is formed in the key groove similarly to the
accommodation chamber 22B of the first embodiment. This also applies to the third and subsequent embodiments. - In the
scroll compressor 1 during the operation thereof, if the pressure or temperature of the lubricating oil O between the key of theOldham ring 23 and the key groove of theupper bearing 21 increases and the lubricating oil O inside the key groove decreases, an abrasion amount between theupper bearing 21 and theOldham ring 23 increases. - Accordingly, in the
scroll compressor 1 of the second embodiment, if a predetermined pressure or temperature is measured by the thin film sensor, the amount of the lubricating oil O to be supplied to a portion between the key and the key groove is increased by temporarily increasing a rotating speed of theorbiting scroll 4. - Accordingly, it is possible to prevent the abrasion amount between the
upper bearing 21 and theOldham ring 23 from increasing. - Next, a third embodiment of the present invention will be described with reference to
Figs. 1 and2 . - Moreover, in the third embodiment, the same reference numerals as those of the first embodiment are assigned to components similar to those of the first embodiment, and descriptions thereof are omitted.
- In the
scroll compressor 1 of the third embodiment, thethin film sensor 7 can be provided on atooth surface 34 of awrap 33 of the fixedscroll 3. Although not shown, thethin film sensor 7 is provided inside an accommodation chamber formed on thetooth surface 34. In the third embodiment, thethin film sensor 7 is provided so as to detect occurrence of so-called liquid compression inside the compression chamber R1 in advance. - Even when the
thin film sensor 7 is provided on thetooth surface 34, thethin film sensor 7 is extremely thin, and thus, it is possible to minimize a dead volume which a factor of lowering compression efficiency of the refrigerant. - In the
scroll compressor 1, if a liquid refrigerant is sucked and liquid compression is generated, the pressure inside the compression chamber R1 significantly increases. Therefore, in thescroll compressor 1, if thethin film sensor 7 measures a pressure having a predetermined value at which the liquid compression may be generated, the rotating speed of theorbiting scroll 4 decreases. - Accordingly, the liquid compression is avoided, and thus, it is possible to the pressure inside the compression chamber R1 from abnormally increasing.
- Next, a fourth embodiment of the present invention will be described with reference to
Fig. 1 . - Moreover, in the fourth embodiment, the same reference numerals as those of the first embodiment are assigned to components similar to those of the first embodiment, and descriptions thereof are omitted.
- In the
scroll compressor 1 of the fourth embodiment, thethin film sensor 7 which measures a pressure of the lubricating oil O between theupper bearing 21 and therotary shaft 5, the thin film sensor which measures a temperature between theupper bearing 21 and therotary shaft 5, or a sensor which measures capacitance between theupper bearing 21 and therotary shaft 5 is provided in a portion of theupper bearing 21 facing therotary shaft 5. - Moreover, as the sensor to measure the pressure of the lubricating oil O and measure the temperature of the lubricating oil O, the above-described sensors can be used.
- In the
scroll compressor 1, if the temperature or a load between theupper bearing 21 and therotary shaft 5 abnormally increases, there is a concern that a so-called lock state in which thescroll compressor 1 is not operated may occur. - Accordingly, in the
scroll compressor 1 of the fourth embodiment, the thin film sensor detects that the temperature between theupper bearing 21 and therotary shaft 5 or the load obtained from the pressure of the lubricating oil O is a predetermined value or more. Then, the load between theupper bearing 21 and therotary shaft 5 is decreased or the operation of thescroll compressor 1 is stopped by decreasing the rotating speed of therotary shaft 5. - Accordingly, it is possible to prevent the
scroll compressor 1 from entering the lock state. - Moreover, if a dilution rate of the lubricating oil O by the refrigerant is calculated from a relationship between temperature and the pressure measured by the thin film sensor or the capacitance and the dilution rate is a predetermined value or more, an operation of decreasing the load between the
upper bearing 21 and therotary shaft 5 can be performed by decreasing the rotating speed of therotary shaft 5 or the pressure of the lubricating oil O until the dilution rate decreases. - The dilution rate from the relationship between the temperature and the pressure is calculated from a relationship expression previously obtained according to a type of the compressed refrigerant or the used lubricating oil O. In addition, the dilution rate from the capacitance is calculated by a correlation between the capacitance and the dilution rate obtained in advance.
- Next, an example in which a thin film sensor for detecting a radial gap between the
upper bearing 21 and therotary shaft 5 is provided will be described. In addition, here, it should be noted that the gap means not only a presence or absence of a gap but also a dimension of the gap. This is also applied to a fifth embodiment described next. - As this thin film sensor, the above-described sensor for measuring the capacitance can be used.
- In the fourth embodiment, a capacitance sensor is provided on the
upper bearing 21 so as to measure the capacitance between theupper bearing 21 and therotary shaft 5. If a gap between the capacitance sensor and therotary shaft 5 is changed, the capacitance generated between the capacitance sensor and therotary shaft 5 is changed, and thus, it is possible to detect the gap between theupper bearing 21 and therotary shaft 5 from the measured capacitance. - Meanwhile, an outer peripheral surface of the
rotary shaft 5 strongly abuts against the upper bearing 21 a position which is deviated by a predetermined angle in a rotation direction of therotary shaft 5 in an eccentric direction of the providedeccentric pin 51. Although this position varies depending on an element such as a centrifugal force generated by the orbiting of theorbiting scroll 4, typically, the position is a position deviated by 90°. Accordingly, if thescroll compressor 1 is continuously used, abrasion of the strongly abutting portion of therotary shaft 5 preferentially increases, and thus, a radial gap between the strongly abutting portion of therotary shaft 5 and theupper bearing 21 increases. - Accordingly, in the
scroll compressor 1 of the fourth embodiment, if the capacitance sensor provided in theupper bearing 21 detects that the radial gap between theupper bearing 21 and therotary shaft 5 increases to be a predetermined value or more, the operation is stopped. In thescroll compressor 1, an error signal for informing that the operation has been stopped can be output according to the stopping of the operation. - Next, a fifth embodiment of the present invention will be described with reference to
Fig. 6 . - Moreover, the fifth embodiment relates to the rotary compressor 8. As shown in
Fig. 6A , the rotary compressor 8 includes acylinder 83, apiston rotor 82 which slides inside thecylinder 83, amotor 89 which drives thepiston rotor 82, arotary shaft 87 which transmits power of themotor 89 to thepiston rotor 82, and ahousing 81 which accommodates the above-described components. - An
upper bearing 84 is disposed on upper-side end surfaces of thecylinder 83 and thepiston rotor 82, and alower bearing 85 is disposed on lower-side end surfaces thereof. - The
piston rotor 82 is inserted into aneccentric shaft portion 87A of therotary shaft 87 along a center axis of thehousing 81 and is fixed to theeccentric shaft portion 87A. Therotary shaft 87 is rotatably supported by theupper bearing 84 and thelower bearing 85. - As shown in
Fig. 6B , a compression chamber R2 is formed by thecylinder 83, thepiston rotor 82, theupper bearing 84, and thelower bearing 85. - The
cylinder 83 includes ablade groove 83B which is connected to the compression chamber R2 and into which ablade 86 is inserted and anaccommodation groove 83D which is connected to theblade groove 83B and in which acoil spring 83C is accommodated. - The
cylinder 83 penetrates in a radial direction by theblade groove 83B and theaccommodation groove 83D. - The compression chamber R2 is partitioned by the plate-shaped
blade 86 which is formed to have a height similar to an axial dimension of thepiston rotor 82. - The
blade 86 is inserted into theblade groove 83B and is circumferentially supported. In addition, a distal end of theblade 86 is always pressed to an outer peripheral surface of thepiston rotor 82 by a pressing force generated by thecoil spring 83C disposed inside theaccommodation groove 83D and a pressure generated by a high-pressure portion. Theblade 86 protrudes or retracts with respect to the compression chamber R2 inside thecylinder 83 according to a rotation angle of thepiston rotor 82. - The refrigerant sucked into the
cylinder 83 from asuction port 83A is compressed by being pushed by thepiston rotor 82 in thecylinder 83. The compressed refrigerant is discharged from adischarge port 84A formed in theupper bearing 84. - A reed valve (not shown) is provided in the
discharge port 84A. If the pressure of the compressed refrigerant reaches a predetermined value, the reed valve is pushed and opened, and thus, the refrigerant is discharged to the outside of thecylinder 83. The discharged refrigerant is supplied to a system side such as a refrigerator (not shown) or an air conditioner (not shown) connected to the rotary compressor 8. - In the rotary compressor 8 of the fifth embodiment, the
thin film sensor 7 which measures a circumferential contact pressure between theblade 86 and theblade groove 83B is provided in theblade 86 or theblade groove 83B. In addition, inFigs. 6A and 6B , thethin film sensor 7 is not shown. Alternatively, the rotary compressor 8 includes a thin film sensor which detects a circumferential gap between theblade 86 and theblade groove 83B. This thin film sensor is not shown. - First, an example in which the
thin film sensor 7 is provided will be described. - In the rotary compressor 8 during the operation thereof, if the contact pressure between the
blade 86 and theblade groove 83B increases, there is a concern that a so-called lock state in which the rotary compressor 8 is not operated may occur. - Accordingly, in the rotary compressor 8 of the fifth embodiment, the
thin film sensor 7 detects that the contact pressure between theblade 86 and theblade groove 83B is a predetermined value or more. Then, a rotating speed of thepiston rotor 82 is limited so as to decrease a sliding speed between theblade 86 and theblade groove 83B or change an opening degree of an expansion valve on the system side. In this way, in the rotary compressor 8, a differential pressure between the compression chamber R2 on thesuction port 83A side and the compression chamber R2 on thedischarge port 84A side separated by theblade 86 is decreased so as to decrease a load between theblade 86 and theblade groove 83B. Alternatively, the operation of the rotary compressor 8 may be stopped. - As described above, it is possible to prevent the rotary compressor 8 from entering the lock state.
- Next, an example in which the thin film sensor which detects the circumferential gap between the
blade 86 and theblade groove 83B is provided will be described. - As the thin film sensor which detects the gap, the above-described capacitance sensor can be used.
- In the fifth embodiment, the capacitance sensor is provided in the
blade 86 or theblade groove 83B in order to measure the capacitance between theblade 86 and theblade groove 83B. The gap between theblade 86 and theblade groove 83B is detected from the measured capacitance. - In the rotary compressor 8, if the
blade 86 and theblade groove 83B wear, the circumferential gap between theblade 86 and theblade groove 83B gradually increases. - Accordingly, in the rotary compressor 8 of the fifth embodiment, the capacitance sensor provided in the
blade 86 or theblade groove 83B detects that the circumferential gap between theblade 86 and theblade groove 83B increase to reach the predetermined value or more. Then, the rotating speed of thepiston rotor 82 is limited so as to decrease the sliding speed between theblade 86 and theblade groove 83B or change the opening degree of the expansion valve on the system side. In this way, in the rotary compressor 8, a differential pressure between the compression chamber R2 on thesuction port 83A side and the compression chamber R2 on thedischarge port 84A side separated by theblade 86 is decreased so as to decrease a load between theblade 86 and theblade groove 83B. - In addition, if the circumferential gap between the
blade 86 and theblade groove 83B reaches the predetermined value or more, in addition to stopping the operation of the above-described rotary compressor 8 and reducing the load, an error signal may be output to the outside. - Hereinbefore, preferred embodiments of the present invention are described. However, in addition to this, the configurations described in the above embodiments can be selected or appropriately changed to other configurations within a scope which does not depart from the gist of the present invention.
- For example, in the
scroll compressor 1 of the present embodiment, the example in which thethin film sensor 7 is formed in an approximately U shape is described. However, the present invention is not limited to this, and thethin film sensor 7 may be formed in any shape. - Moreover, in the
scroll compressor 1 of the present embodiment, the example in which thethin film sensor 7 has a three-layer structure including the insulatinglayer 72, thesensor layer 71, and theprotective layer 73 is described. However, the present invention is not limited to this. Thethin film sensor 7 may have any layer structure as long as it has at least thesensor layer 71. - Moreover, in the first embodiment, the signal of the
thin film sensor 7 may be used to determine an error. For example, if thethin film sensor 7 outputs a signal having an abnormal value, an error signal indicating that thethrust surface 22A of thethrust bearing 22 may be damaged may be output to the outside. - In addition, in the fourth embodiment, the example in which the
thin film sensor 7 is provided in theupper bearing 21 of thescroll compressor 1 is described. However, thethin film sensor 7 may be provided in other journal bearings, for example, thelower bearing 24 of thescroll compressor 1, theupper bearing 84 and thelower bearing 85 of the rotary compressor 8, or the like. - Moreover, in the first to fifth embodiments, the thin film sensor is used. However, the present invention is not limited to this.
- For example, a wire formed of a thin film may be provided on the surface of the
reed valve 36 so as to detect the damage of thereed valve 36 such that the wire is cut off and an electric connection is cut off if damage such as defect or crack occurs in thereed valve 36 of thescroll compressor 1. - When the damage of the
reed valve 36 is detected, an error signal may be output to the outside, and the operation of thescroll compressor 1 may be stopped such that a reverse rotation is not generated in theorbiting scroll 4. - Moreover, similarly, the wire formed of a thin film can be applied to a reed valve (not shown) of the rotary compressor 8.
- Moreover, the type of the compressor to which the present invention is applied is not limited to the scroll compressor or the rotary compressor, and can be widely applied to a screw compressor, a reciprocating compressor, or the like.
- Moreover, as the portion of the compressor to which the present invention is applied, in addition to the above-described portions, there are the
retainer 35 of the fixedscroll 3, theretainer 37A of thedischarge cover 37, and the shaft thrustsurface 24A of thelower bearing 24 of thescroll compressor 1, the shaft thrustsurface 85A of thelower bearing 85 of the rotary compressor 8, or the like. -
- 1:
- scroll compressor
- 2:
- housing
- 21:
- upper bearing
- 22:
- thrust bearing
- 22A:
- thrust surface
- 22B:
- accommodation chamber
- 22C:
- disposition region
- 22D:
- peripheral edge
- 22E:
- region
- 22F:
- peripheral edge
- 22G:
- region
- 23:
- Oldham ring
- 24:
- lower bearing
- 24A:
- shaft thrust surface
- 25:
- circulation passage
- 26:
- storage region
- 27:
- back pressure chamber
- 28:
- suction pipe
- 29:
- discharge pipe
- 3:
- fixed scroll
- 31:
- end plate
- 32:
- discharge port
- 33:
- wrap
- 34:
- tooth surface
- 35:
- retainer
- 36:
- reed valve
- 37:
- discharge cover
- 37A:
- retainer
- 37B:
- reed valve
- 38:
- discharge port
- 4:
- orbiting scroll
- 41:
- end plate
- 5:
- rotary shaft
- 51:
- eccentric pin
- 52:
- bearing
- 53:
- oil supply path
- 54:
- pump
- 6:
- motor
- 61:
- stator
- 62:
- rotor
- 7:
- thin film sensor
- 71:
- sensor layer
- 72:
- insulating layer
- 73:
- protective layer
- 74:
- measurement region
- 8:
- rotary compressor
- 81:
- housing
- 82:
- piston rotor
- 83:
- cylinder
- 83A:
- suction port
- 83B:
- blade groove
- 83C:
- coil spring
- 84:
- upper bearing
- 84A:
- discharge port
- 85:
- lower bearing
- 85A:
- shaft thrust surface
- 86:
- blade
- 87:
- rotary shaft
- 89:
- motor
- C:
- gap
- O:
- lubricating oil
- V1, V2, V3, V4:
- control valve
Claims (14)
- A compressor which compresses a refrigerant by a transmitted driving force, comprising:a movement element which is moved by a driving force;a support element which supports the movement element; anddetection means which is provided in association with the movement element,wherein the detection means detects a change in a state around the detection means.
- The compressor according to claim 1,
wherein the detection means is a sensor having a thickness of 10 µm or less. - The compressor according to claim 1 or 2,
wherein the detection means is provided on a sliding surface of the support element with respect to the movement element. - The compressor according to claim 1 or 2,
wherein the detection means is provided in the movement element. - The compressor according to any one of claims 1 to 4,
wherein the change in the state around the detection means is at least one of a change in a pressure of a lubricating oil, a change in a temperature of the lubricating oil, and a change in capacitance. - The compressor according to any one of claims 1 to 5,
wherein the compressor is a scroll compressor which includes
a fixed scroll,
an orbiting scroll which revolves and orbits with respect to the fixed scroll,
a thrust bearing which supports the orbiting scroll in a revolvable manner, and
a back pressure chamber into which the lubricating oil flows. - The compressor according to claim 6,
wherein the detection means is provided on a sliding surface of the thrust bearing, which is connected to the back pressure chamber, with respect to the orbiting scroll. - The compressor according to claim 7,
wherein the detection means is provided inside an accommodation chamber recessed from the sliding surface of the thrust bearing. - The compressor according to claim 8,
wherein the detection means has a measurement region which measures a pressure of the lubricating oil between the thrust bearing and the orbiting scroll, and
wherein the measurement region is provided inside a disposition region of the thrust bearing. - The compressor according to any one of claims 6 to 9,
wherein a pressure of the lubricating oil inside the back pressure chamber is adjusted by a detection value of the detection means. - The compressor according to claim 6,
wherein the detection means detects a change in a state between a key of an Oldham ring which restricts a rotation of the orbiting scroll and a key groove into which the key is inserted. - The compressor according to claim 6,
wherein the detection means detects a change in a state of a compression chamber between a tooth surface of a wrap of the fixed scroll, the fixed scroll, and the orbiting scroll. - The compressor according to any one of claims 1 to 5,
wherein the compressor is a rotary compressor which includes
a cylinder,
a piston rotor which slides inside the cylinder,
an upper bearing which is disposed on upper-side end surfaces of the cylinder and the piston rotor,
a lower bearing which is disposed on lower-side end surfaces of the cylinder and the piston rotor,
a compression chamber which is formed by the cylinder, the piston rotor, the upper bearing, and the lower bearing,
a blade which partitions the compression chamber, and
a blade groove into which the blade is inserted. - The compressor according to claim 13,
wherein the detection means detects a change in a state between the blade and the blade groove.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2017027428A JP2018132020A (en) | 2017-02-17 | 2017-02-17 | Compressor |
PCT/JP2017/044982 WO2018150706A1 (en) | 2017-02-17 | 2017-12-14 | Compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3499042A1 true EP3499042A1 (en) | 2019-06-19 |
Family
ID=63169427
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17897200.6A Withdrawn EP3499042A1 (en) | 2017-02-17 | 2017-12-14 | Compressor |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3499042A1 (en) |
JP (1) | JP2018132020A (en) |
WO (1) | WO2018150706A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2021171347A1 (en) * | 2020-02-25 | 2021-09-02 | 三菱電機株式会社 | Compressor, air conditioner, refrigerator, and compressor control method |
JP2024010832A (en) * | 2022-07-13 | 2024-01-25 | 三菱重工業株式会社 | Control device, compression system, and control method |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0733829B2 (en) * | 1986-02-03 | 1995-04-12 | 松下電器産業株式会社 | Scroll compressor |
JP3864264B2 (en) * | 1999-09-30 | 2006-12-27 | 株式会社日立製作所 | Refrigeration air conditioning compressor |
JP6567352B2 (en) * | 2015-07-28 | 2019-08-28 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
-
2017
- 2017-02-17 JP JP2017027428A patent/JP2018132020A/en active Pending
- 2017-12-14 WO PCT/JP2017/044982 patent/WO2018150706A1/en unknown
- 2017-12-14 EP EP17897200.6A patent/EP3499042A1/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
WO2018150706A1 (en) | 2018-08-23 |
JP2018132020A (en) | 2018-08-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7789640B2 (en) | Scroll fluid machine with a pin shaft and groove for restricting rotation | |
KR101529415B1 (en) | Scroll-type compressor | |
US9316225B2 (en) | Scroll compressor with thrust sliding surface oiling groove | |
US9816553B2 (en) | Compressor having balance mechanism for a thrust bearing | |
US20140017108A1 (en) | Scroll compressor | |
WO2011099308A1 (en) | Scroll compressor | |
EP3499042A1 (en) | Compressor | |
EP2484909B1 (en) | Scroll fluid machine | |
WO2016107601A1 (en) | Vortex compressor | |
US8568119B2 (en) | Single screw compressor | |
JP2007204602A (en) | Composition for sliding member, and fluid machine | |
CN108496008B (en) | Scroll compressor and air conditioner provided with same | |
JP2002227789A (en) | Rotary compressor | |
US10670015B2 (en) | Screw Compressor | |
US10100833B2 (en) | Scroll compressor | |
JP5034975B2 (en) | Scroll compressor | |
US20150118089A1 (en) | Compressor with unloader counterweight assembly | |
US20050207926A1 (en) | Scroll compressor | |
EP3751143B1 (en) | Scroll fluid machine | |
WO2017130321A1 (en) | Compressor | |
CN114787577A (en) | Compressor system, compressor, and refrigeration cycle device | |
JPWO2004029461A1 (en) | Scroll compressor | |
EP3546758B1 (en) | Single-screw compressor | |
CN110100137B (en) | Vortex unloading detection system | |
JP5361682B2 (en) | Compressor |
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: 20190315 |
|
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 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN |
|
18W | Application withdrawn |
Effective date: 20191029 |