JP5402889B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor that compresses and discharges a fluid.

  2. Description of the Related Art Conventionally, a compressor includes a compression mechanism that compresses and discharges a fluid mixed with lubricating oil, and a lubricating oil reservoir that separates and stores the lubricating oil out of the fluid discharged from the compression mechanism. It is known that the lubricating oil in the lubricating oil reservoir is supplied to a lubrication target portion (for example, a bearing portion) in the housing through an oil supply passage. In addition, since the lubricating oil mixed with the fluid discharged from the compression mechanism is stored in the lubricating oil reservoir of the compressor, the inside of the lubricating oil reservoir is the discharge pressure of the compressor. For this reason, it becomes possible to supply the lubricating oil to the lubrication target portion existing in the medium to low pressure space that is lower than the discharge pressure of the compressor in the housing due to the differential pressure between the inside of the lubricating oil reservoir and the low pressure space in the housing. .

  However, in such a configuration, when the operation of the compressor is stopped, the lubricating oil may suddenly flow out of the lubricating oil reservoir due to a differential pressure between the inside of the lubricating oil reservoir and the low pressure space in the housing. is there. In this case, when the compressor is restarted, there may be a shortage of lubricating oil in the lubricating oil reservoir of the compressor.

  Therefore, for example, in the compressor described in Patent Document 1, a bypass hole (radial through hole) is provided in the oil supply passage that guides the lubricating oil from the lubricating oil reservoir to each sliding portion, and the inside of the housing is provided via the bypass hole. The high-pressure fluid is configured to be able to flow into the oil supply passage. Furthermore, a lid with a weight body that uses the rotational driving force of the drive shaft to close the bypass hole of the oil supply passage during operation of the compressor and open the bypass hole of the oil supply passage when the compressor is stopped. It has.

  According to such a configuration, when stopping the operation of the compressor, not the lubricating oil inside the lubricating oil reservoir but the high-pressure fluid flows into the oil supply passage from the bypass hole, so that the lubricating oil is introduced from the inside of the lubricating oil reservoir. Can be prevented from suddenly flowing out.

Japanese Patent No. 43222349

  However, in the compressor described in Patent Document 1, it is necessary to use a new member such as a lid with a weight as a configuration for opening and closing the bypass hole of the oil supply passage. For this reason, the number of parts of a compressor increases and there exists a problem that the cost of a compressor will increase.

  The present invention has been made in view of the above points, and an object of the present invention is to prevent the lubricating oil from flowing out of the lubricating oil reservoir when stopping the operation of the compressor without increasing the number of parts of the compressor.

  In order to achieve the above object, according to the first aspect of the present invention, the housing (30) and the fluid contained in the housing (30) and mixed with the lubricating oil are sucked from the fluid suction portion (114) and compressed. A compression mechanism section (10) for discharging and an oil separation section (40) for separating and storing lubricating oil from the fluid discharged from the compression mechanism section (10), the compression mechanism section (10) being a housing A fixed member (12) fixed to (30), and a movable member (11) that is rotationally displaced with respect to the fixed member (12) when a rotational driving force is transmitted to the movable member (11). The compressor changes the volume of the compression chamber (15) sealed by the fixed member (12) and the movable member (11) according to the rotational displacement, and the fixed member (12) includes an oil separator ( 40) the lubricating oil stored in the housing (30) A fixed-side oil guide passage (127) is provided that leads to a lubrication target site in a medium-low pressure space that is lower than the pressure of the fluid discharged from the compression mechanism (10) in the part, and the movable member (11) In accordance with the rotational displacement, a movable side oil guide passage (115) that connects the medium-low pressure space and the fixed side oil guide passage (127) a predetermined number of times per rotation is provided, and the fixed side oil guide passage (127) is provided. ) When the transmission of the rotational driving force to the movable member (11) is interrupted and the movable member (11) rotates in reverse due to the pressure of the fluid pressurized in the compression chamber (15). (115) is formed at a position that is not in communication.

  In this way, the fixed-side oil guide passage (127) and the movable-side oil guide passage (115) are intermittently communicated with the rotational displacement of the movable member (11), and are rotated with respect to the movable member (11). When the transmission of the driving force is interrupted and the movable member (11) rotates in the reverse direction, the fixed oil guide passage (127) and the movable oil guide passage (115) do not communicate with each other. Without adding, when the compression of the fluid in the compression mechanism section (10) is stopped, it is possible to prevent the lubricating oil in the oil separation section (40) from flowing out into the medium-low pressure space.

  Therefore, it is possible to suppress a shortage of lubricating oil inside the oil separation section (40) when the compressor is restarted without increasing the number of parts.

  Here, according to the study by the present inventors, when the transmission of the rotational driving force to the movable member (11) is interrupted, the pressure of the pressurized fluid remaining in the compression chamber (15), and the movable member Due to the inertial force acting on (11), the movable member (11) is at a reference angle, that is, the rotation angle when the suction of the fluid from the fluid suction portion (114) into the compression chamber (15) is completed. It has been found that there is a tendency for the movable member (11) to reversely rotate to an angle advanced to a range of 190 ° to 310 °.

Therefore, in the invention according to claim 1, variable dynamic side oil guide passage (115) only once per revolution in accordance with the rotational displacement of the movable member (11), the fixed oil guide passage and the intermediate and low pressure space (127) is configured to communicate with the fixed side oil guide passage (127), and the movable member (11) rotates and displaces in the compression chamber (15) from the fluid suction portion (114). When the rotation angle when the fluid suction is completed is set as a reference angle, the movable member (11) is guided to the movable side at an angle advanced to a range of −45 ° or more and 180 ° or less with respect to the reference angle. It is configured to communicate with the oil passage (115).

  According to this, when the transmission of the rotational driving force to the movable member (11) is interrupted and the movable member (11) rotates in the reverse direction, the reference angle when the suction of the fluid is completed inside the compression chamber (15). If the angle is not advanced to a range of −45 ° or more and 180 ° or less, the fixed-side oil guide passage (127) and the movable-side oil guide passage (115) do not communicate with each other in the compression mechanism section (10). When the compression of the fluid is stopped, it is possible to suppress the lubricating oil in the oil separation part (40) from flowing out into the medium / low pressure space.

According to a second aspect of the present invention, in the compressor according to the first aspect, the electric motor unit (20) for supplying a rotational driving force to the movable member (11) is provided, and the electric motor unit (20) After the supply of the rotational driving force to the movable member (11) is shut off and the movable member (11) rotates reversely by the pressure of the fluid boosted in the compression chamber (15), the fixed-side oil guide passage (127) The movable member (11) is rotationally displaced to a position where the movable oil guide passage (115) is not in communication.

  According to this, even after the supply of the rotational driving force to the movable member (11) is cut off, even if the movable member (11) rotates in the reverse direction, the movable member (11) is fixed to the fixed oil guide passage (127) and the movable side. The oil guide passage (115) stops at a position where it does not communicate.

  Therefore, when the compression of the fluid in the compression mechanism section (10) is stopped, it is possible to more reliably suppress the lubricating oil in the oil separation section (40) from flowing out into the intermediate / low pressure space.

Specifically, as in the invention described in claim 3 , in the compressor described in claim 2 , the electric motor section (20) is a three-phase motor having winding coils of U phase, V phase, and W phase. The fixed-side oil guide passage (127) and the movable-side oil guide passage (115) are not communicated by applying a voltage to only one of the U-phase, V-phase, and W-phase winding coils. It can be set as the structure which rotationally displaces a movable member (11) to the position which becomes.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is an axial sectional view of the compressor concerning a 1st embodiment. It is explanatory drawing for demonstrating the locus | trajectory of a movable side opening hole when a movable scroll revolves once with respect to a fixed scroll. FIG. 2 is an axial sectional view of a compressor in which a flow of lubricating oil is added to FIG. 1. It is a schematic diagram of the rotor and stator of the electric motor part which concerns on 2nd Embodiment. It is explanatory drawing explaining the flow of the electric current of each phase in a stator coil. It is explanatory drawing explaining the stop position of a movable scroll at the time of applying a voltage only to the U phase of a stator coil.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. The compressor 1 of this embodiment is applied to a heat pump hot water supply machine. This heat pump type hot water heater heats hot water by a heat pump cycle, and the compressor 1 functions to compress and discharge the refrigerant in the heat pump cycle.

  The heat pump cycle is variable as a water-refrigerant heat exchanger for exchanging heat between the refrigerant discharged from the compressor 1 and hot water and heating the hot water, and a decompressing means for decompressing and expanding the refrigerant flowing out of the water-refrigerant heat exchanger. They are a throttle mechanism, an outdoor evaporator that heats and evaporates the refrigerant expanded under reduced pressure by the variable throttle mechanism, and the vapor compression refrigeration cycle in which the compressor 1 is annularly connected.

  Furthermore, in the heat pump cycle of the present embodiment, carbon dioxide is adopted as the refrigerant, and a supercritical refrigeration cycle in which the high-pressure refrigerant discharged from the compressor 1 is equal to or higher than the critical pressure of the refrigerant is configured. Further, the refrigerant is mixed with lubricating oil (refrigeration oil) that lubricates each sliding portion inside the compressor 1, and a part of this lubricating oil circulates in the cycle together with the refrigerant.

  Of course, in the heat pump cycle, a gas-liquid separator is arranged between the outdoor evaporator and the compressor 1 to separate the gas-liquid refrigerant and store surplus refrigerant and to let the gas-phase refrigerant flow out to the compressor 1 side. May be. Furthermore, in addition to the heat pump cycle, the heat pump type hot water heater circulates hot water between a hot water storage tank for storing hot water heated by a water-refrigerant heat exchanger, and between the hot water storage tank and the water-refrigerant heat exchanger. It has a hot water circulation circuit and the like.

  Next, the detailed configuration of the compressor 1 of the present embodiment will be described with reference to FIG. FIG. 1 is a schematic axial sectional view of the compressor 1. In addition, the up and down arrows in FIG. 1 indicate the up and down directions when the compressor 1 is mounted on the heat pump water heater.

  The compressor 1 sucks a refrigerant that is a fluid, compresses and discharges the refrigerant, a motor unit 20 that drives the compressor unit 10, and a rotational driving force from the motor unit 20 to the compressor unit 10. This is an electric compressor in which a shaft 25 or the like, which is a drive shaft for transmission, is housed in a housing 30.

  Furthermore, as shown in FIG. 1, the compressor 1 has a so-called vertical structure in which the rotation axis of the shaft 25 extends in the vertical direction (vertical direction), and the compression mechanism unit 10 and the motor unit 20 are arranged in the vertical direction. It is configured as a stand type. More specifically, in this embodiment, the compression mechanism unit 10 is disposed below the electric motor unit 20.

  First, the housing 30 has a cylindrical member 31 extending in the vertical direction, an upper lid member 32 that closes the upper end portion of the cylindrical member 31, and a lower lid member 33 that closes the lower end portion of the cylindrical member 31, and these are joined together. Thus, a sealed container structure is obtained. The cylindrical member 31, the upper lid member 32, and the lower lid member 33 are all made of iron, and these are joined by welding.

  Further, an oil separator 40 to be described later is joined to the side of the cylindrical member 31 of the housing 30 via a bracket 44. Both the housing 30 and the oil separator 40 are formed in a vertically long shape extending in the vertical direction.

  Next, the electric motor unit 20 is a three-phase brushless DC motor (three-phase motor) having U-phase, V-phase, and W-phase winding coils. A stator 21 forming a stator in the electric motor unit 20 includes a stator core 211 made of a magnetic material and a stator coil (winding coil) 212 wound around the stator core 211. More specifically, a winding coil corresponding to each of the U phase, V phase, and W phase of the stator coil 212 is wound around the stator 21 in each slot provided in the stator core 211.

  The stator 21 generates a rotating magnetic field that rotates the rotor 22 by supplying electric power to a winding coil of each phase in the stator coil 212 via an inverter circuit (not shown). Note that power is supplied to the stator coil 212 through the power supply terminal 23 arranged at the upper end of the housing 30. The power supply terminal 23 is disposed so as to penetrate the front and back of the power supply terminal fixing plate 24 fixed so as to close a through hole formed in the central portion of the upper cover member 32 of the housing 30.

  On the other hand, the rotor 22 constituting the rotor in the electric motor unit 20 is configured to have a permanent magnet, and is disposed on the inner peripheral side of the stator 21. The rotor 22 is formed in a cylindrical shape extending in the rotation axis direction, and a substantially cylindrical shaft 25 extending in the rotation axis direction is fixed to the axial center hole of the rotor 22 by press-fitting. Therefore, when electric power is supplied to the stator coil 212 and a rotating magnetic field is generated, the rotor 22 and the shaft 25 rotate together.

  The shaft 25 is formed in a substantially cylindrical shape, and has a main oil supply passage 25a through which the above-mentioned lubricating oil is circulated, and a sliding portion (lubricating portion between the main oil supply passage 25a and the shaft 25 and a first bearing portion 29 described later. A first sub oil supply passage 25b that guides the lubricating oil to the target portion), and a second sub oil passage that guides the lubricating oil from the main oil supply passage 25a to the sliding portion (lubrication target portion) between the shaft 25 and the second bearing portion 27 described later. An oil supply passage 25c is formed.

  The main oil supply passage 25 a formed inside the shaft 25 extends in the axial direction of the shaft 25 and opens at the lower end surface of the shaft 25, and the upper end surface of the shaft 25 is closed by the closing member 26. Then, the lubricating oil flowing out from the movable oil guide passage 115 described later flows into the main oil supply passage 25a from the lower end side that is one end side of the shaft 25 in the axial direction.

  The first sub oil supply passage 25b and the second sub oil supply passage 25c are formed as communication holes that extend in the radial direction of the shaft 25 and allow the main oil supply passage 25a and the outer surface of the shaft 25 to communicate with each other. Further, the second sub oil supply passage 25c is arranged on the upper side in the vertical direction than the first sub oil supply passage 25b.

  In addition, as a guide member that guides the oil flowing in from the lower end side of the shaft 25 to the vicinity of the inlet of the second sub oil supply passage 25c disposed above the first sub oil supply passage 25b in the main oil supply passage 25a. The tubular pipe member 50 is arranged.

  The pipe member 50 extends in the axial direction of the shaft 25 and is formed of a pipe having a lower end portion whose diameter is larger than that of the remaining portion. The outer peripheral surface of the expanded lower end portion is an inner wall surface of the main oil supply passage. It is press-fitted and fixed. As the pipe member 50, a pipe having a circular cross section, a polygonal cross section, an elliptical cross section, or the like can be used.

  Accordingly, a part of the oil guided by the pipe member 50 is first supplied to the second sub oil supply passage 25c through the oil outlet hole 501 provided in the upper end portion of the pipe member 50, and the remaining oil is mainly supplied. It flows between the oil supply passage 25a and the pipe member 50 and is supplied to the first sub oil supply passage 25b.

  The shaft 25 is longer in the axial direction than the rotor 22, and the lower end side (on the compression mechanism unit 10 side), which is one end side in the axial direction, extends below the lowermost end portion of the rotor 22. The other end side in the axial direction (the side opposite to the compression mechanism portion 10) extends upward from the uppermost end portion of the rotor 22. A flange portion 251 that protrudes in the horizontal direction perpendicular to the axial direction is formed in a portion of the shaft 25 below the rotor 22.

  A balance weight 254 that suppresses eccentric rotation of the rotor 22 and the shaft 25 is disposed on the flange portion 251. In addition, balance weights 221 and 222 that exhibit the same function are also arranged on both sides of the rotor 22 in the vertical direction. Further, a portion between the rotor 22 and the flange portion 251 in a portion below the rotor 22 of the shaft 25 is rotatably supported by a first bearing portion 29 formed in the middle housing 36.

  That is, the first bearing portion 29 supports the lower end side that is one axial end side of the shaft 25. Furthermore, the 1st bearing part 29 is comprised as a slide bearing which receives the outer peripheral surface of the shaft 25 by the circular inner peripheral surface when it sees from the axial direction of the shaft 25. As shown in FIG.

  The middle housing 36 has a cylindrical shape whose outer diameter and inner diameter increase stepwise from the upper side to the lower side, and the first bearing portion 29 is formed in the upper side portion where the outer diameter and inner diameter are the smallest. Has been. Further, the outer peripheral surface of the lower side portion having the largest outer diameter and inner diameter is fixed in a state of being in contact with the cylindrical member 31 of the housing 30.

  On the other hand, the part above the rotor 22 of the shaft 25 is rotatably supported by the second bearing portion 27. That is, the second bearing portion 27 supports the upper end side that is the other axial end side of the shaft 25. Further, the second bearing portion 27 is configured as a slide bearing having an inner peripheral shape that is similar to the outer peripheral shape of the shaft 25 when viewed from the axial direction of the shaft 25.

  Further, the second bearing portion 27 is fixed to the cylindrical member 31 of the housing 30 via the interposition member 28. The interposition member 28 is formed in a shape in which the outer peripheral portion of the annular plate extending in the horizontal direction is bent downward, and the outer peripheral portion is fixed in a state where the outer peripheral portion is in contact with the cylindrical member 31 of the housing 30. Further, a flange portion 271 protruding in the horizontal direction is formed at the upper end portion of the second bearing portion 27, and the flange portion 271 is fixed on the interposed member 28.

  More specifically, the flange portion 271 of the second bearing portion 27 is fastened and fixed to the interposition member 28 by a bolt (not shown). Accordingly, the horizontal position of the second bearing portion 27 with respect to the interposition member 28 can be adjusted, and the shaft 25 can be easily aligned (centered).

  Next, the compression mechanism unit 10 is a scroll type compression mechanism including a movable scroll 11 and a fixed scroll 12 each having a tooth portion formed in a spiral shape. The movable scroll 11 is disposed on the inner peripheral side of the lower portion having the largest inner diameter in the middle housing 36 described above, and the fixed scroll 12 is disposed on the lower side of the movable scroll 11.

  The movable scroll 11 and the fixed scroll 12 have disk-shaped substrate portions 111 and 121, respectively, and both the substrate portions 111 and 121 are arranged to face each other in the vertical direction. The outer peripheral side of the substrate portion (fixed side substrate portion) 121 of the fixed scroll 12 is fixed to the cylindrical member 31 of the housing 30. Note that the fixed scroll 12 of the present embodiment constitutes a fixed member that is fixed inside the housing 30.

  A cylindrical boss portion 113 into which the lower end portion of the shaft 25 is inserted is formed at the center portion on the upper surface side of the substrate portion (movable side substrate portion) 111 in the movable scroll 11. The lower end portion of the shaft 25 is an eccentric portion 253 that is eccentric with respect to the rotation center of the shaft 25. Therefore, the eccentric part 253 of the shaft 25 is inserted into the movable scroll 11.

  Further, a rotation prevention mechanism that prevents the movable scroll 11 from rotating about the eccentric portion 253 is provided between the movable scroll 11 and the middle housing 36. For this reason, when the shaft 25 rotates, the movable scroll 11 revolves while turning around the center of rotation of the shaft 25 without rotating around the eccentric portion 253. That is, when the rotational driving force is supplied from the electric motor unit 20 via the shaft 25, the movable scroll 11 revolves while turning around the rotation center of the shaft 25 as the revolution center. Note that the movable scroll 11 of this embodiment constitutes a movable member that is rotationally displaced with respect to the fixed scroll 12 fixed to the housing 30.

  The movable scroll 11 is formed with spiral tooth portions (movable side tooth portions) 112 protruding from the substrate portion 111 toward the fixed scroll 12 side. On the other hand, the fixed scroll has a spiral tooth portion (fixed side tooth portion) 122 that protrudes from the substrate portion 121 toward the movable scroll 11 side and meshes with the tooth portion 112 of the movable scroll 11.

  Then, the tooth portions 112 and 122 of the scrolls 11 and 12 mesh with each other and come into contact with each other at a plurality of locations, thereby forming a sealed working chamber formed in a crescent shape when viewed from the rotation axis direction (hereinafter referred to as compression). A plurality of 15 are formed. In FIG. 1, for clarity of illustration, only one working chamber among the plurality of working chambers 15 is denoted by reference numerals, and the other working chambers are not denoted by reference numerals.

  The working chamber 15 moves while changing (decreasing) the volume from the outer peripheral side to the central side in the circumferential direction of the rotation axis by the revolving motion of the movable scroll 11. Furthermore, the refrigerant is supplied to the working chamber 15 through the refrigerant supply passages 37 and 114, and the refrigerant in the working chamber 15 is compressed by reducing the volume of the working chamber 15.

  Specifically, the refrigerant supply passages 37 and 114 for supplying the refrigerant to the working chamber 15 include the refrigerant inlet 37 formed in the cylindrical member 31 of the housing 30 and the refrigerant suction formed in the middle housing 36. It is constituted by a passage 114. A pipe connection member 38 is connected to the refrigerant suction port 37. The refrigerant suction passage 114 constitutes a fluid suction portion that communicates with the compression chamber 15 formed on the outermost peripheral side of the tooth portions 112 and 122 of the scrolls 11 and 12.

  In addition, tip seals 16 and 17 for securing the airtightness of the working chamber 15 are mounted on the tip portions in the axial direction of the tooth portion 112 on the movable scroll 11 side and the tooth portion 122 on the fixed scroll 12 side. The chip seals 16 and 17 are formed in a prismatic shape extending along the spiral direction of the tooth portions 112 and 122 with a resin material such as polyether ether ketone ketone (PEEK).

  The tip seal 16 on the movable scroll 11 side is fitted and fixed in the tip seal groove formed on the tip surface of the tooth portion 112 on the movable scroll 11 side facing the substrate portion 121 on the fixed scroll 12 side. The tip seal 17 on the 12th side is fitted and fixed in a tip seal groove formed on the tip surface of the tooth portion 122 on the fixed scroll 12 side facing the substrate portion 111 on the movable scroll 11 side.

  In addition, a discharge hole 123 through which the refrigerant compressed in the working chamber 15 is discharged is formed in the central portion of the substrate portion 121 on the fixed scroll 12 side. Further, a discharge chamber 124 communicating with the discharge hole 123 is formed below the discharge hole 123. The discharge chamber 124 is defined by a recess 125 formed on the lower surface of the substrate portion 121 of the fixed scroll 12 and a partition member 18 fixed on the lower surface of the fixed scroll 12.

  Further, a reed valve 19 serving as a check valve for preventing the refrigerant from flowing back to the working chamber 15 is disposed in the discharge chamber 124. The refrigerant that has flowed into the discharge chamber 124 includes a refrigerant discharge passage formed in the substrate portion 121 on the fixed scroll 12 side and a refrigerant discharge port formed in the cylindrical member 31 of the housing 30 (both not shown). ) To the outside of the housing 30. A refrigerant inlet of the oil separator 40 is connected to the refrigerant outlet through a refrigerant pipe.

  The oil separator 40 functions as an oil separator that separates the lubricating oil from the compressed refrigerant discharged from the housing 30 and returns the separated lubricating oil into the housing 30. Specifically, the oil separator 40 includes a cylindrical member 41 extending in the vertical direction, an upper lid member 42 that closes the upper end portion of the cylindrical member 41, and a lower lid member 43 that closes the lower end portion of the cylindrical member 41, These are integrally joined to form a sealed container structure. The oil separator 40 separates the lubricating oil from the high-pressure refrigerant discharged from the compression mechanism unit 10, and therefore the inside of the oil separator 40 is equivalent to the high-pressure refrigerant discharged from the compression mechanism unit 10. High pressure.

  The cylindrical member 41, the upper lid member 42, and the lower lid member 43 are all made of iron, and these are joined by welding. Furthermore, the cylindrical member 41 of the oil separator 40 is joined to the cylindrical member 31 of the housing 30 by welding via a bracket 44 formed of iron. Thereby, as described above, the oil separator 40 is fixed to the side of the housing 30.

  The upper lid member 42 has a double cylinder structure constituted by an outer cylinder member 421 and an inner cylinder member 422. The outer cylinder member 421 and the inner cylinder member 422 are cylindrical members extending in the vertical direction, and the inner cylinder member 422 is inserted in the upper side of the inside of the outer cylinder member 421.

  The refrigerant flowing from the refrigerant inlet of the oil separator 40 (not shown) is introduced into the cylindrical space 42a formed between the inner peripheral side of the outer cylindrical member 421 and the outer peripheral side of the inner cylindrical member 422. . Accordingly, the refrigerant inlet of the oil separator 40 is formed in a side portion of the cylindrical space 42 a in the outer cylinder member 421.

  Further, the upper end portion of the cylindrical space 42 a is closed by the inner cylinder member 422. Specifically, the upper end portion of the inner cylinder member 422 has a larger diameter than the remaining portion, and closes the upper end opening 421a of the outer cylinder member 421. Furthermore, the upper end opening 45 of the inner cylinder member 422 is a refrigerant outlet that discharges the refrigerant from which the lubricating oil has been separated to the outside of the oil separator 40, that is, to the inlet side of the water-refrigerant heat exchanger outside the compressor 1. Is configured.

  A lower side portion formed by the cylindrical member 41 and the lower lid member 43 in the oil separator 40 serves as an oil storage tank that stores lubricating oil separated from the refrigerant. An oil outlet 431 for allowing the stored lubricating oil to flow out of the oil separator 40 is formed in the lower lid member 43 of the oil separator 40.

  An oil pipe 46 is connected to the oil outlet 431, and the oil pipe 46 is connected to a pipe connecting member 34 fixed to the tubular member 31 of the housing 30. The pipe connecting member 34 passes through a through hole formed in the tubular member 31 of the housing 30 and is inserted into an insertion hole 126 formed on the side surface of the substrate portion 121 on the fixed scroll 12 side.

  Further, a fixed-side oil guide passage 127 that communicates with the insertion hole 126 is formed inside the substrate portion 121 on the fixed scroll 12 side. The fixed-side oil guide passage 127 opens the lubricating oil flowing through the pipe connecting member 34 and the insertion hole 126 to the upper surface of the substrate portion 121 on the fixed scroll 12 side (surface on the substrate portion 111 side on the movable scroll 11 side). To the fixed side opening hole 127a. The fixed-side opening hole 127a is formed so as to open to the outer peripheral side from the tooth portion 122 on the fixed scroll 12 side so that the fixed-side oil guide passage 127 and the compression chamber 15 do not communicate with each other.

  Furthermore, a movable oil guide passage 115 is formed in the substrate portion 111 on the movable scroll 11 side so as to intermittently communicate with one passage of the fixed oil guide passage 127. More specifically, one end side of the movable oil guide passage 115 is arranged on the lower surface of the substrate portion 111 on the movable scroll 11 side (the surface of the substrate portion 121 on the fixed scroll 12 side) of the substrate portion 121 on the fixed scroll 12 side. It opens so as to face the fixed side opening hole 127a formed on the upper surface. Note that the movable side opening hole 115a formed in the lower surface of the substrate portion 111 on the movable scroll 11 side in the movable side oil guide passage 115 has a movable scroll 11 so that the movable side oil guide passage 115 and the compression chamber 15 do not communicate with each other. It forms so that it may open to an outer peripheral side rather than the tooth | gear part 112 of the side.

  Accordingly, the movable side opening hole 115a of the movable side oil guide passage 115 overlaps or shifts with the fixed side opening hole 127a of the fixed side oil guide passage 127 as the movable scroll 11 revolves. The oil guide passage 115 communicates intermittently with the fixed side oil guide passage 127. The other end side of the movable oil guide passage 115 is open inside the boss 113 of the movable scroll 11.

  Specifically, in the compression mechanism portion 10 of the present embodiment, one fixed-side oil guide passage 127 is formed in the substrate portion 121 on the fixed scroll 12 side, and one in the substrate portion 111 on the movable scroll 11 side. A movable oil guide passage 115 is formed. For this reason, the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 are configured to communicate only once per revolution of the movable scroll 11.

  Note that the fixed-side oil guide passage 127 is a sliding part (the object to be lubricated) in which the lubricating oil of the oil separator 40 is present in an intermediate / low pressure space that is lower in pressure than the high-pressure refrigerant discharged from the compression mechanism unit 10 inside the housing 30. It functions as a passage for guiding to the site. In addition, the movable oil guide passage 115 functions as a passage that connects the fixed oil guide passage 127 and the medium / low pressure space inside the housing 30 only once per revolution when revolving.

  Here, in the compressor 1 of the present embodiment, the inside of the oil separator 40 has a high pressure equal to that of the high-pressure refrigerant discharged from the compression mechanism unit 10. On the other hand, the sliding portion between the shaft 25 and the first bearing portion 29 and the sliding portion between the shaft 25 and the second bearing portion 27 exist in the medium / low pressure space inside the housing 30.

  For this reason, when the movable-side oil guide passage 115 and the fixed-side oil guide passage 127 are intermittently communicated, the oil separator 40 and the fixed-side oil guide due to the differential pressure between the inside of the oil separator 40 and the medium-low pressure space. Lubricating oil that has flowed into the passage 127 is introduced into the gap between the boss portion 113 and the eccentric portion 253 of the shaft 25 through the movable oil guide passage 115, and then from the lower end side of the shaft 25 to the inside of the shaft 25. Into the main oil supply passage 25a.

  Then, the sliding portion between the shaft 25 and the first bearing portion 29 from the main oil supply passage 25a through the first sub oil supply passage 25b, and the shaft 25 and the second bearing portion 27 through the second sub oil supply passage 25c. Lubricant flows to the sliding part.

  The lubricating oil supplied to the first sliding portion via the first sub oil supply passage 25b lubricates the first sliding portion and then flows downward in the housing 30 due to gravity, so that the lowermost portion of the housing 30 Return to the oil storage chamber 35 formed in The lubricating oil supplied to the second sliding portion lubricates the second sliding portion, then flows downward in the housing 30 by gravity and returns to the oil storage chamber 35.

  The oil storage chamber 35 is a space for storing lubricating oil formed below the partition member 18 disposed below the fixed scroll 12. The partition member 18 is formed with a through hole 181 penetrating in the vertical direction. This through hole 181 is provided on the outermost peripheral side of the tooth portions 112 and 122 of both scrolls 11 and 12 through a passage formed inside the substrate portion 121 on the fixed scroll 12 side, similarly to the refrigerant suction passage 114 described above. It communicates with the compression chamber 15 formed in the above.

  Therefore, the flow rate of the lubricating oil flowing into the compression chamber 15 can be adjusted by the passage cross-sectional area (pressure loss) of the throttle passage formed inside the substrate portion 121 on the fixed scroll 12 side. A pipe 182 that sucks up the lubricating oil stored in the oil storage chamber 35 is inserted into the through hole 181 from below.

  By the way, when the operation of the compressor 1 is stopped, if the supply of the rotational driving force from the electric motor unit 20 to the movable scroll 11 is interrupted, the pressurized high-pressure refrigerant in the compression chamber 15 and the suction refrigerant passage The movable scroll 11 rotates reversely due to the differential pressure with the low-pressure refrigerant and the movable scroll 11 due to the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant. According to the experiments and examinations by the present inventors, after the operation of the compressor 1 is stopped, the movable scroll 11 is rotated at the reference angle (the rotation angle when the suction of the refrigerant from the refrigerant supply passage 114 into the compression chamber 15 is completed). ), The pressure difference between the refrigerant in the compression chamber 15 and the refrigerant in the refrigerant suction passage 114 is reduced to equalize the pressure, and the movable scroll 11 It turns out that there is a tendency to stop. Since the inertial force acts on the movable scroll 11 during reverse rotation, the movable scroll 11 stops at a position advanced from the rotation angle when the suction of the refrigerant from the refrigerant supply passage 114 is completed inside the compression chamber 15 in the movable scroll 11. To do.

  At this time, if the fixed side oil guide passage 127 and the movable side oil guide passage 115 communicate with each other, the oil pressure is increased by the differential pressure between the high pressure space inside the oil separator 40 and the medium / low pressure space inside the housing 30. Lubricating oil in the separator 40 suddenly flows out from the fixed side oil guide passage 127 to the movable side oil guide passage 115. In this case, the lubricating oil inside the oil separator 40 is suddenly decreased, and when the compressor 1 is restarted, the oil separator 40 becomes insufficient in lubricating oil, causing a delay in oil supply to each sliding portion. End up.

  Therefore, in the present embodiment, when the transmission of the rotational driving force to the movable scroll 11 is interrupted and the movable scroll 11 stops by rotating in the reverse direction, the stationary oil guide passage 127 is not in communication with the movable oil guide passage 115. It is formed in the position. In other words, when the transmission of the rotational driving force to the movable scroll 11 is interrupted and the movable scroll member 11 rotates in the reverse direction, the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 are configured not to communicate with each other. Has been. That is, the movable side oil guide passage 115 and the fixed side oil guide passage 127 do not communicate with each other in the vicinity of the position where the movable scroll 11 rotates in the reverse direction and stops.

  Specifically, the fixed-side oil guide passage 127 of the present embodiment uses the rotation angle of the movable scroll 11 at the suction completion position where the suction of the refrigerant into the compression chamber 15 is completed as a reference angle (θ = 0 °). When this is done, the movable scroll 11 is configured to communicate with the movable-side oil guide passage 115 at a rotation angle advanced from the reference angle to a range of −45 ° or more and 180 ° or less. For this reason, the angle at which the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 communicate with each other is a rotation angle advanced from the reference angle to a range of −45 ° or more and 180 ° or less. The suction completion position is also the compression start position in the compression chamber 15.

  Here, as an example, a configuration in which the fixed-side oil guiding passage 127 and the movable-side oil guiding passage 115 communicate with each other at a position where the rotation angle of the movable scroll 11 is advanced by 180 ° from the reference angle is based on FIG. I will explain. FIG. 2 is an explanatory diagram for explaining the trajectory of the movable-side opening hole 115a when the movable scroll 11 revolves once with respect to the fixed scroll 12. FIG. FIG. 2A shows the position (reference angle: θ = 0 °) of the movable side opening hole 115a at the suction completion position where the refrigerant has been sucked into the compression chamber 15, from the state of FIG. The positions of the movable side opening holes 115a when the movable scroll 11 is advanced by 90 °, 180 °, and 270 ° are shown in FIGS. 2B, 2C, and 2D. In FIG. 2, the configuration on the fixed scroll 12 side is indicated by a dotted line, and the locus of the movable side opening hole 115 a when the movable scroll 11 is revolved is indicated by a dashed line.

  First, as shown in FIG. 2A, when the refrigerant is completely sucked, the movable side opening hole 115a of the movable side oil guide passage 115 is the most fixed side opening of the fixed side oil guide passage 127 on the locus indicated by the chain line. It is away from the hole 127a, and the communication between the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 is cut off, resulting in a non-communication state.

  From the state of FIG. 2A, the movable scroll 11 is advanced by 90 ° (see FIG. 2B), and then the state of FIG. 2C is reached (the state advanced 180 ° from the reference angle). When the movable scroll 11 is advanced to the fixed angle, the fixed-side opening hole 127a and the movable-side opening hole 115a are overlapped, and the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 communicate with each other.

  Then, when the angle is further advanced from the state of FIG. 2C, the communication between the fixed side oil guide passage 127 and the movable side oil guide passage 115 is cut off again, and the movable scroll 11 goes through the state shown in FIG. It returns to the state of FIG. 2A (inhalation completion position).

  When the compressor 1 is stopped, for example, in the state of FIG. 2 (d), the state of FIG. 2 (c) → the state of FIG. 2 (b) → the state of FIG. 2 (a). The movable scroll 11 rotates in the reverse direction, and the movable scroll 11 stops at a rotation angle of 310 ° to 190 ° with respect to the reference angle.

  In FIG. 2, as an example, the fixed side oil guide passage 127 and the movable side oil guide passage 115 communicate with each other at an angle where the rotation angle of the movable scroll 11 is advanced by 180 ° from the reference angle. The fixed-side oil guide passage 127 and the movable-side oil guide passage 115 may communicate with each other at an angle advanced to a range of −45 ° or more and 180 ° or less.

  Next, the operation of the compressor 1 of the present embodiment having the above configuration will be described. When electric power is supplied to the stator coil 212 of the electric motor unit 20 and the rotor 22 and the shaft 25 rotate, a rotational driving force is supplied to the movable scroll 11 through the shaft 25, and the movable scroll 11 revolves with respect to the shaft 25 ( Swivel).

  As a result, the refrigerant and the lubricating oil are placed in the working chamber 15 positioned on the outermost periphery of the crescent-shaped working chamber 15 formed between the tooth portion 112 on the movable scroll 11 side and the tooth portion 122 on the fixed scroll 12 side. Inhaled. Specifically, the refrigerant that has flowed out of the outdoor evaporator is supplied to the working chamber 15 through the refrigerant supply passages 37 and 114, and the lubricating oil in the oil storage chamber 35 is supplied to the working chamber 15 through the pipe 182.

  The refrigerant supplied to the working chamber 15 is compressed as the volume of the working chamber 15 decreases. At this time, the sliding parts of the movable scroll 11 and the fixed scroll 12 are lubricated by the lubricating oil sucked into the working chamber 15. The refrigerant compressed in the working chamber 15 is discharged together with the lubricating oil to the outside of the housing 30 through the discharge hole 123 of the fixed scroll 12, the discharge chamber 124, and the refrigerant discharge port of the housing 30. Flows into the inlet.

  The refrigerant that has flowed into the refrigerant inlet of the oil separator 40 is introduced into the cylindrical space 42a in the oil separator 40 as indicated by the thick arrows in FIG. Note that FIG. 3 is obtained by adding the flow of lubricating oil to the axial cross-sectional view of the compressor 1 of FIG. 1 with a thick arrow. In FIG. 3, reference numerals of some components are omitted for clarity of illustration.

  Then, a swirling flow is generated in the refrigerant in the cylindrical space 42a, and the lubricating oil is separated from the refrigerant by the action of the centrifugal force generated by the swirling flow of the refrigerant. The refrigerant from which the lubricating oil has been separated is discharged from the refrigerant discharge port (upper end opening 45) of the oil separator 40 to the refrigerant inlet side of the water-refrigerant heat exchanger as the discharge refrigerant of the compressor 1.

  The lubricating oil separated from the refrigerant flows down the oil separator 40 due to gravity and is stored in the lower part of the oil separator 40. The lubricating oil stored in the oil separator 40 is intermittently supplied to the shaft via the oil outlet 431, the oil pipe 46, the insertion hole 126, the fixed side oil guide passage 127, and the movable side oil guide passage 115. 25 flows into the main oil supply passage 25a formed in the shaft 25 from the lower end side of the shaft 25.

  The lubricating oil that has flowed into the main oil supply passage 25a of the shaft 25 is guided to the vicinity of the inlet of the second sub oil supply passage 25c by the pipe member 50, and a part thereof flows into the second sub oil supply passage 25c. The lubricating oil that has flowed into the second auxiliary oil supply passage 25c is supplied to the sliding portion between the shaft 25 and the second bearing portion 27, and after lubricating the sliding portion, the inside of the housing 30 is moved downward by the action of gravity. It flows and returns to the oil storage chamber 35 again.

  Of the lubricating oil that has flowed out of the pipe member 50, the remaining lubricating oil that has not flowed into the second auxiliary oil supply passage 25c passes between the main oil supply passage 25a and the pipe member 50 due to the action of gravity. It flows toward the side and flows into the first sub oil supply passage 25b. The lubricating oil that has flowed into the first sub oil supply passage 25b is supplied to the sliding portion between the shaft 25 and the first bearing portion 29, lubricates the sliding portion, and then flows out into the housing 30 and is again stored in the oil storage chamber. Return to 35.

  On the other hand, the lubricating oil stored in the oil storage chamber 35 passes through the pipe 182, the through hole 181, and the passage formed in the substrate portion 121 on the fixed scroll 12 side, and the tooth portions 112 and 122 of the scrolls 11 and 12. Flows into the compression chamber 15 formed on the outermost peripheral side.

  Further, when the power supply to the stator coil 212 of the electric motor unit 20 is cut off and the rotor 22 and the shaft 25 stop rotating, the supply of the rotational driving force to the movable scroll 11 is cut off. The movable scroll 11 rotates reversely with respect to the advance direction by the pressurized high-pressure refrigerant remaining in the compression chamber 15, and the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 are disconnected. In this state, the movable scroll 11 stops.

  The compressor 1 of the present embodiment operates as described above, and exhibits a function of sucking, compressing and discharging the refrigerant in the heat pump cycle.

  Further, in the compressor 1 of the present embodiment, the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 are configured to intermittently communicate with the revolution rotation of the movable scroll 11 so as to rotate the movable scroll 11. When the transmission of force is interrupted and the movable scroll 11 rotates backward to the position where the compression chamber 15 and the refrigerant suction passage 114 communicate with each other, the fixed-side oil guide passage 127 and the movable-side oil guide passage 115 do not communicate with each other. ing.

  For this reason, when the compression of the refrigerant in the compression mechanism unit 10 is stopped without adding new parts, the lubricating oil inside the oil separator 40 is moved to the movable side oil guide passage 115 and the fixed side oil guide passage 127. It can suppress flowing out to each sliding site | part inside the housing 30 via.

  Accordingly, it is possible to suppress a shortage of lubricating oil in the oil separator 40 when the compressor 1 is restarted without increasing the number of parts of the compressor 1, and lubricating oil to each sliding portion in the housing 30. Supply delay can be suppressed.

  Further, in the conventional technique, when the operation of the compressor 1 is stopped, the rotational driving force of the compressor 1 is reduced in order to prevent the lubricating oil from flowing out from the oil separator 40 to each sliding portion. Since it is set as the structure utilized, the increase in the power consumption of the compressor 1 will be caused.

  On the other hand, in the configuration of the present embodiment, the lubricant oil is prevented from flowing out from the oil separator 40 when the operation of the compressor 1 is stopped without using the rotational driving force of the compressor 1. Therefore, the consumption power of the compressor 1 is not increased.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. In the present embodiment, after the operation of the compressor 1 is stopped (energization to the stator coil 212 is stopped) and the movable scroll 11 is stopped, the movable scroll 11 is fixed to the movable oil guide passage 115 by the electric motor unit 20. The side oil guide passage 127 is rotated to a position where it does not communicate with the side oil guide passage 127 and stopped at the position.

  Specifically, in this embodiment, after the operation of the compressor 1 is stopped, a voltage is applied to only one phase of the three-phase winding coils in the stator coil 212 of the electric motor unit 20 by an inverter circuit (not shown). Thus, the movable scroll 11 is stopped at a position where the movable oil guide passage 115 and the fixed oil guide passage 127 do not communicate with each other.

  Here, operation | movement of the rotor 22 of the electric motor part 20 when a voltage is applied only to U phase among the three-phase winding coils of the stator coil 212 is demonstrated based on FIG. 4, FIG. FIG. 4 is a schematic diagram of the rotor 22 and the stator 21 of the electric motor unit 20 of the present embodiment, and FIG. 5 is an explanatory diagram for explaining the flow of current in each phase in the stator coil 212. In the present embodiment, a case where a brushless DC motor having three phases, four poles and six slots is employed will be described as an example.

  As shown in FIG. 4, when a voltage is applied to the U phase of the stator coil 212 in the electric motor unit 20 via an inverter circuit, the U phase of the stator coil 212 is magnetized to the N pole as shown in FIG. And the W phase is magnetized to the south pole. Current flows from the U phase of stator coil 212 to the V phase and the W phase.

  For this reason, the S pole of the rotor 22 is at an angular position facing the U phase (N pole) of the stator coil 212, and the N pole of the rotor 22 faces the V phase (S pole) and the W phase (S pole). Stop at the angular position you want. And with the movement of the rotor 22, the movable scroll 11 also revolves and stops at a predetermined position.

  Therefore, if the predetermined position where the movable scroll 11 stops when a voltage is applied only to the U phase is set to a position where the movable side oil guide passage 115 and the fixed side oil guide passage 127 do not communicate with each other, the operation of the compressor 1 is performed. At the time of stop, the movable scroll 11 can be stopped at a position where the movable oil guide passage 115 and the fixed oil guide passage 127 do not communicate with each other.

  The angular position at which the rotor 22 stops when a voltage is applied only to the U phase is an angular position where one S pole of the rotor 22 faces one U phase (N pole) and 180 ° from the angular position. It rotates and becomes one of the angular positions where one S pole of the rotor 22 and the other U phase (N pole) face each other.

  For this reason, in this embodiment, when a voltage is applied only to the U phase, the movable-side oil guide passage 115 and the fixed side at any of the two angular positions where the rotor 22 may stop. The movable scroll 11 is stopped at a position where it does not communicate with the oil guide passage 127.

  This point will be described with reference to FIG. FIG. 6 is an explanatory diagram illustrating the stop position of the movable scroll 11 when a voltage is applied only to the U phase. Here, FIG. 6A is a diagram corresponding to the positional relationship between the movable side opening hole 115a and the fixed side opening hole 127a shown on the lower left side of FIG. 2A. 6B is a diagram corresponding to FIG. 2A, and FIG. 6C shows the correspondence between the positional relationship between the fixed scroll 12 and the stator 21 shown in FIG. 6B. FIG. In addition, the one-dot chain line in Fig.6 (a) has shown the locus | trajectory of the movable side opening hole 115a when the movable scroll 11 revolves once. Moreover, the X-axis and the Y-axis shown in FIGS. 6A to 6C indicate a common direction in each drawing.

  For example, when the fixed scroll 12 and the stator 21 are in the positional relationship shown in FIGS. 6A and 6C and the rotation angle of the movable scroll 11 is advanced by 180 ° from the reference angle, the movable side oil guide When the passage 115 and the fixed-side oil guide passage 127 are configured to communicate with each other, the movable scroll 11 can be moved to the U-phase provided at the position shown in FIG. As shown in FIG. 5, the configuration may be such that the vehicle is stopped at an angle advanced from the reference angle θ = 0 ° (inhalation completion position) to 45 ° or more and 135 ° or less, or 225 ° or more and 315 ° or less. .

  According to this, the angular position at which the rotor 22 stops when a voltage is applied only to the U phase, the angular position at which one S pole of the rotor 22 faces one U phase (N pole), and the angular position The movable scroll 11 can be stopped at a position where the movable side oil guide passage 115 and the fixed side oil guide passage 127 do not communicate with each other at any angular position rotated 180 ° from the first position.

  As described above, according to the configuration of the present embodiment that has been described, the lubricating oil inside the oil separator 40 is transferred to the movable oil guide passage 115 and the fixed side without adding any new parts, as in the first embodiment. It is possible to prevent the oil from flowing out to each sliding portion inside the housing 30 through the oil guide passage 127.

  Further, in the present embodiment, after the operation of the compressor 1 is stopped, the movable scroll 11 is stopped at the position where the movable oil guide passage 115 and the fixed oil guide passage 127 do not communicate with each other in the electric motor unit 20. Even when the movable scroll 11 is reversely rotated substantially beyond the suction completion position due to an inertia force or the like when the compressor 1 is stopped, the movable scroll 11 is moved through the movable oil guide passage 115 and the fixed oil guide passage 127. It is possible to stop at a position that does not communicate with each other.

  Therefore, according to the present embodiment, when the operation of the compressor 1 is stopped, the lubricating oil inside the oil separator 40 flows through the movable oil guide passage 115 and the fixed oil guide passage 127 in the housing 30. It can suppress more reliably that it flows out into each sliding part inside.

  In the configuration of the present embodiment, the operation of the compressor 1 is stopped, and the movable side oil guide passage 115 and the fixed side oil guide passage 127 when the movable scroll 11 stops by rotating backward to the vicinity of the suction completion position are Even when applied to a configuration that communicates, it is possible to sufficiently prevent the lubricating oil inside the oil separator 40 from flowing out to each sliding portion inside the housing 30 when the operation of the compressor 1 is stopped. It is.

(Other embodiments)
As mentioned above, although embodiment of this invention was described, this invention is not limited to this, Unless it deviates from the range described in each claim, it is not limited to the wording of each claim, and those skilled in the art Improvements based on the knowledge that a person skilled in the art normally has can be added as appropriate to the extent that they can be easily replaced. For example, various modifications are possible as follows.

  (1) In each of the above-described embodiments, the movable-side oil guide passage 115 and the fixed-side oil guide passage 127 are configured to communicate once per rotation of the movable scroll 11, but the present invention is not limited to this. That is, when the operation of the compressor 1 is stopped, the movable side oil guide passage 115 and the fixed side oil guide passage 127 may be configured to communicate with each other a predetermined number of times per rotation of the movable scroll 11 as long as the movable side oil guide passage 115 and the fixed side oil guide passage 127 are not in communication.

  (2) In the second embodiment described above, the case where the voltage is applied only to the U phase among the U-phase, V-phase, and W-phase winding coils of the stator coil 212 has been described. As long as the position where the movable scroll 11 stops is a position where the movable oil guide passage 115 and the fixed oil guide passage 127 do not communicate with each other, the voltage is applied not only to the U phase but also to the V phase and the W phase. Also good.

  (3) In the second embodiment described above, a three-phase motor composed of a six-slot stator 21 and a four-pole rotor 22 is adopted as the electric motor unit 20, but one phase of a three-phase winding coil is used. If the predetermined position where the movable scroll 11 stops when a voltage is applied can be set to a position where the movable-side oil guide passage 115 and the fixed-side oil guide passage 127 do not communicate with each other, three other configurations are possible. A phase motor can be employed.

  (4) In each of the embodiments described above, the oil separator 40 is disposed outside the housing 30, but the oil separator 40 may be housed inside the housing 30.

  (5) In each of the above-described embodiments, the heat pump cycle constitutes a supercritical refrigeration cycle, and carbon dioxide is used as the refrigerant. However, the subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure. Or a refrigerant such as a chlorofluorocarbon refrigerant or a hydrocarbon refrigerant may be employed.

  (6) In each of the above-described embodiments, the vertical type compressor 1 has been described. However, the vertical type compressor 1 may be applied to a horizontal type compressor in which the rotation axis of the shaft 25 extends in the horizontal direction.

  (7) In each of the above-described embodiments, an example in which the present invention is applied to a scroll type compressor has been described. However, the present invention is not limited to this, and for example, a rotor (rotating and displacing in a cylinder (fixed member) The present invention is applicable to a compressor that compresses a fluid, such as a rotary compressor having a movable member.

DESCRIPTION OF SYMBOLS 10 Compression mechanism part 11 Movable scroll (movable member)
111 Substrate (movable side substrate)
112 tooth (movable side tooth)
114 Refrigerant suction passage (fluid suction part)
115 Movable oil guide passage 12 Fixed scroll (fixed member)
121 Substrate (fixed side substrate)
122 teeth (fixed side teeth)
127 Fixed side oil guide passage 15 Compression chamber (working chamber)
20 Electric motor part 30 Housing 40 Oil separator (oil separation part)

Claims (3)

A housing (30);
A compression mechanism (10) for receiving a fluid contained in the housing (30) and mixed with lubricating oil from the fluid suction part (114), compressing and discharging the fluid;
An oil separation part (40) for separating and storing the lubricating oil from the fluid discharged from the compression mechanism part (10),
The compression mechanism section (10) includes a fixed member (12) fixed to the housing (30) and a movable member (11) that is rotationally displaced with respect to the fixed member (12) when a rotational driving force is transmitted. )
A compressor for changing a volume of a compression chamber (15) sealed between the fixed member (12) and the movable member (11) in accordance with the rotational displacement of the movable member (11),
In the fixing member (12), the lubricating oil stored in the oil separation part (40) has a pressure lower than the pressure of the fluid discharged from the compression mechanism part (10) inside the housing (30). A fixed-side oil guide passage (127) that leads to a lubrication target portion existing in the medium-low pressure space,
The movable member (11) has a movable oil guide passage (115) that connects the medium-low pressure space and the fixed oil guide passage (127) only once per rotation in accordance with the rotational displacement. Provided,
The fixed-side oil guide passage (127) is
When the transmission of the rotational driving force to the movable member (11) is cut off and the movable member (11) rotates in the reverse direction due to the pressure of the fluid boosted in the compression chamber (15), the movable side guide is provided. Formed in a position not communicating with the oil passage (115) ,
Furthermore, when the movable member (11) is rotationally displaced and the rotation angle when the suction of the fluid from the fluid suction part (114) is completed inside the compression chamber (15) is set as a reference angle, The movable member (11) is configured to communicate with the movable-side oil guide passage (115) at an angle advanced to a range of −45 ° or more and 180 ° or less with respect to the reference angle. Compressor characterized by. An electric motor section (20) for supplying the rotational driving force to the movable member (11);
The electric motor section (20) shuts off the supply of the rotational driving force to the movable member (11), and the movable member (11) is reversed by the pressure of the fluid boosted in the compression chamber (15). after rotation, according to claim 1, characterized in that rotationally displacing said movable member to a position where the fixed-side oil guiding path (127) and said movable-side oil guiding path (115) are non-communicating (11) Compressor. The electric motor section (20) is composed of a three-phase motor having U-phase, V-phase, and W-phase winding coils, and only one phase among the U-phase, V-phase, and W-phase winding coils. The movable member (11) is rotationally displaced by applying a voltage to the position until the fixed-side oil guide passage (127) and the movable-side oil guide passage (115) are not in communication. Item 3. The compressor according to Item 2 .

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