JP2014129757A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor capable of promptly supplying oil to the bearing of a crankshaft even at a time of starting.SOLUTION: A scroll compressor 1 includes: a casing 10; a compression mechanism unit 15; a crankshaft 17; a motor 16; and a lower oil reservoir P, and is configured as follows. The lower oil reservoir P is provided in a space below a coupling portion between a movable scroll 26 and the crankshaft 17 in the casing 10, and stores lubrication oil for supplying the lubrication oil to at least the coupling portion. The crankshaft 17 includes an oil supply path 17a formed therein to extend axially. A check structure 5 opens the oil supply path 17a in a state in which the crankshaft 17 is driven to rotate, and shuts off a flow of the lubrication oil from upward to downward within the oil supply path 17a in a state in which the crankshaft 17 is stopped.

Description

  The present invention relates to a scroll compressor.

  Conventionally, for example, as described in Patent Document 1 (Japanese Patent Application Laid-Open No. 2011-1854), a crankshaft extending in the vertical direction is used, and lubricating oil (refrigerator oil) is stored in the bottom portion in the casing. There is a scroll compressor.

  In this scroll compressor, by providing a positive displacement pump, from an opening formed at the lower end of the crankshaft, from an opening formed at the upper end of the crankshaft through an oil supply passage extending vertically inside the crankshaft, The structure which supplies oil with respect to an upper bearing and its periphery is employ | adopted.

  However, in the scroll compressor described in the above-mentioned Patent Document 1 (Japanese Patent Application Laid-Open No. 2011-1854), refueling is continuously performed during the operation of the positive displacement pump being driven, but the operation is stopped. At the time of subsequent activation, in order to supply oil to the sliding portion above the crankshaft and its periphery, the lubricating oil must be moved from the lower end to the upper end in the oil supply passage in the crankshaft extending in the vertical direction.

  For this reason, at the time of start-up, for a while after the start of start-up, a state in which oil is not supplied to the sliding portion above the crankshaft, the upper bearing, and the periphery thereof tends to continue. In this case, seizure and abnormal friction may occur in the sliding portion above the crankshaft, the upper bearing, and the periphery thereof, and the portion may be damaged.

  The present invention has been made in view of the above-described points, and an object of the present invention is to provide a scroll compressor capable of quickly supplying oil to a crankshaft bearing even at the time of startup.

  A scroll compressor according to a first aspect of the present invention includes a casing, a compression mechanism portion, a crankshaft, a motor, a lower oil sump portion, and a check structure. The compression mechanism unit is housed in the casing, and includes a fixed scroll and a movable scroll that forms a compression chamber between the fixed scroll and the fixed scroll. The crankshaft is rotatably connected to the upper bearing portion and the lower bearing portion. The motor rotates the crankshaft. The lower oil reservoir is provided in a space below the lower bearing portion in the casing, and accumulates lubricating oil. The crankshaft has an oil supply passage formed therein so as to extend in the axial direction. The check structure communicates the oil supply passage when the crankshaft is rotationally driven, and blocks the flow of lubricating oil from the top to the bottom when the crankshaft is stopped.

  In this scroll compressor, when the motor is driven and the crankshaft is driven to rotate, the check structure allows the crankshaft oil passage to communicate with the crankshaft. And its surroundings can be refueled. When the operation is stopped when the motor is stopped, the check structure cuts off the flow of lubricating oil from the top to the bottom in the oil supply passage. The lubricating oil that has been supplied to the upper part through the passage does not fall to the lower oil reservoir, but is held by the check structure at an upper position closer to the lower bearing than the lower oil reservoir. For this reason, the lubricating oil held in the check structure can be supplied to the lower bearing portion and the upper bearing portion in a short time from the start-up when the operation of the motor is resumed. Thereby, it is possible to quickly supply oil to the lower bearing portion and the upper bearing portion even at the time of starting, and it becomes possible to solve the shortage of oil around the lower bearing portion and the upper bearing portion at the time of starting. .

  A scroll compressor according to a second aspect of the present invention is the scroll compressor according to the first aspect, wherein the check structure is located above the lower oil reservoir and closer to the lower bearing than the lower oil reservoir. Alternatively, at a position close to the upper bearing portion, a check member provided separately from the crankshaft is provided inside the crankshaft radially inside the outer periphery of the crankshaft. In the state where the crankshaft is rotationally driven, the check member moves by the centrifugal force to connect the oil supply passage extending in the axial direction. When the crankshaft is stopped, the check member closes the middle of the oil supply passage extending in the axial direction by releasing the centrifugal force.

  In this scroll compressor, the centrifugal force acting on the check member can be released and the middle of the oil supply passage can be closed only by stopping the crankshaft from the rotationally driven state. Accordingly, it is possible to solve the shortage of oil around the lower bearing portion and the upper bearing portion at the time of starting without performing control for opening and closing the oil supply passage.

  The scroll compressor according to a third aspect of the present invention is the scroll compressor according to the second aspect, wherein the check member is such that the centrifugal force is released and the pressure of the upper lubricating oil when the crankshaft is stopped. By both, it moves to the position which closes the middle of the oil supply channel | path currently extended in the axial direction.

  In this scroll compressor, the centrifugal force acting on the check member can be released and the pressure of the upper lubricating oil can be applied to the check member simply by stopping the crankshaft from the rotationally driven state. For this reason, when the drive of the crankshaft is stopped, the check member can be moved to a position where the middle of the oil supply passage is closed more quickly. Thereby, when the drive of the crankshaft is stopped, the check structure can hold the lubricating oil more reliably.

  A scroll compressor according to a fourth aspect of the present invention is the scroll compressor according to any one of the first to third aspects, wherein the axis of the oil supply passage of the crankshaft is relative to the axis of the crankshaft with respect to the outer periphery. Eccentric.

  In this scroll compressor, since the shaft center of the oil supply passage of the crankshaft is eccentric with respect to the shaft center with respect to the outer periphery of the crankshaft, centrifugal force acts on the lubricating oil flowing through the oil supply passage of the crankshaft. Therefore, the lubricating oil can be easily pulled upward by the centrifugal force only by rotating the crankshaft.

  In the scroll compressor according to the first aspect of the present invention, it is possible to solve the shortage of oil around the lower bearing portion and the upper bearing portion at the time of startup.

  In the scroll compressor according to the second aspect of the present invention, it is possible to solve the shortage of oil around the lower bearing portion and the upper bearing portion at the time of starting without performing control for opening and closing the oil supply passage. .

  In the scroll compressor according to the third aspect of the present invention, the check structure can hold the lubricating oil more reliably when the drive of the crankshaft is stopped.

  In the scroll compressor according to the fourth aspect of the present invention, the lubricating oil can be easily pulled upward by the centrifugal force only by rotating the crankshaft.

It is a longitudinal section of the scroll compressor concerning a 1st embodiment of the present invention. It is the elements on larger scale of the X section of Drawing 1 showing the state at the time of stop of the non-return structure of a 1st embodiment. It is the elements on larger scale of the X section of Drawing 1 showing the state at the time of the drive of the non-return structure of a 1st embodiment. It is a top view schematic diagram which shows the state at the time of the stop of the non-return structure of 1st Embodiment. It is a top view schematic diagram which shows the state at the time of the drive of the non-return structure of 1st Embodiment. It is a longitudinal cross-sectional view which shows the state at the time of the stop of the non-return structure of other embodiment (5-1). It is a longitudinal cross-sectional view which shows the state at the time of the drive of the non-return structure of other embodiment (5-1). It is a longitudinal cross-sectional view which shows the state at the time of the stop of the non-return structure of other embodiment (5-2). It is a longitudinal cross-sectional view which shows the state at the time of the drive of the non-return structure of other embodiment (5-2). It is a longitudinal cross-sectional view which shows the state at the time of the stop of the non-return structure of other embodiment (5-3). It is a longitudinal cross-sectional view which shows the state at the time of the drive of the non-return structure of other embodiment (5-3). It is a longitudinal cross-sectional view of the scroll compressor which concerns on other embodiment (5-4). It is a longitudinal cross-sectional view which shows the state at the time of the stop of the non-return structure of other embodiment (5-4). It is a longitudinal cross-sectional view which shows the state at the time of the drive of the non-return structure of other embodiment (5-4). It is a longitudinal cross-sectional view of the scroll compressor which concerns on other embodiment (5-5) of this invention.

  Hereinafter, a scroll compressor according to an embodiment of the present invention will be described with reference to the drawings.

(1) 1st Embodiment The scroll compressor 1 shown in FIG. 1 is a high-low pressure dome type scroll compressor, and comprises a refrigerant circuit with an evaporator, a condenser, an expansion mechanism, etc. FIG. The scroll compressor 1 plays a role of compressing the refrigerant gas in the refrigerant circuit.

  The scroll compressor 1 mainly includes a vertically long cylindrical closed dome-shaped casing 10, a pin bearing portion 22, an upper bearing portion 32, a lower bearing portion 27, a motor 16, a positive displacement pump 79, a suction pipe 19, and a discharge pipe 20. , The compression mechanism 15, the upper bearing housing 23, the crankshaft 17 that is a drive shaft, the gas guide 71, and the like. Hereinafter, the components of the scroll compressor 1 will be described in detail.

(1-1) Casing The casing 10 is a vertically long sealed container, and has a substantially cylindrical body casing part 11 and a bowl-shaped upper wall part 12 welded in an airtight manner to the upper end part of the body casing part 11. And a bowl-shaped bottom wall portion 13 that is welded to the lower end portion of the body casing portion 11 in an airtight manner. And this casing 10 mainly accommodates the compression mechanism part 15 which compresses refrigerant gas, and the motor 16 arrange | positioned under the compression mechanism part 15. FIG. The compression mechanism portion 15 and the motor 16 are connected by a crankshaft 17 that is disposed so as to extend vertically in the casing 10. A high-pressure space 18 is provided between the compression mechanism unit 15 and the motor 16.

(1-2) Pin Bearing Part The pin bearing part 22 is a so-called slide bearing, and supports the pin shaft part 17b at the upper end of the crankshaft 17 from the outside in the radial direction. The pin bearing portion 22 includes a boss portion 26c that extends in a cylindrical shape from the vicinity of the center of a movable scroll 26, which will be described later, and a pin shaft bearing that is fitted to the inner peripheral surface of the boss portion 26c in the radial direction. The pin 87 is provided so that the inner peripheral surface of the pin shaft bearing metal 87 is in contact with the outer peripheral surface of the pin shaft portion 17 b of the crank shaft 17.

(1-3) Upper bearing portion The upper bearing portion 32 is a so-called slide bearing, and is positioned slightly above the center in the casing 10, and the portion below the pin shaft portion 17 b of the crankshaft 17 is radially outward. I support from. The upper bearing portion 32 is configured by an upper inner peripheral portion 23a on the radially inner side of the upper bearing housing 23, which will be described later, and an upper bearing metal 88 fitted on the inner peripheral surface on the radially inner side of the upper inner peripheral portion 23a. Yes. An inner peripheral surface of the upper bearing metal 88 is provided so as to contact an outer peripheral surface of a portion of the crankshaft 17 below the pin shaft portion 17b. The relationship between the upper bearing portion 32 and the upper bearing housing 23 will be described later.

(1-4) Lower bearing portion The lower bearing portion 27 is a so-called slide bearing, is located below the casing 10 and supports the lower portion of the crankshaft 17 from the radially outer side. The lower bearing portion 27 includes a lower inner peripheral portion 28a radially inward of the lower bearing housing 28, and a lower bearing metal 89 fitted on the inner peripheral surface of the lower inner peripheral portion 28a in the radial direction. The inner peripheral surface of the lower bearing metal 89 is provided so as to contact the outer peripheral surface of the lower portion of the crankshaft 17. The lower bearing housing 28 is disposed in a lower space below the motor 16. The lower bearing housing 28 has its radially outer end fixed to the inner peripheral portion of the body casing portion 11.

(1-5) Motor The motor 16 is mainly rotatably accommodated with an annular stator 51 fixed to the inner wall surface of the casing 10 and a slight gap (air gap passage) inside the stator 51. And a rotor 52.

  A copper wire is wound on the stator 51 upward and downward, and a coil end 53 is formed. The upper end of the coil end 53 of the stator 51 is disposed so as to be substantially at the same height as the lower end of the upper bearing portion 32 of the upper bearing housing 23 described later. On the outer peripheral surface of the stator 51, groove-shaped core cut portions 51 a extending in the vertical direction from the upper end surface to the lower end surface of the stator 51 are provided at a plurality of locations at predetermined intervals in the circumferential direction. The core cut portion 51a constitutes a motor cooling passage extending in the vertical direction between the inner peripheral side of the body casing portion 11 and the outer peripheral side of the stator 51.

  The rotor 52 is drivably coupled to the movable scroll 26 of the compression mechanism unit 15 via the crankshaft 17 disposed at the shaft center of the body casing unit 11 so as to extend in the vertical direction.

(1-6) Positive displacement pump At the lower end of the crankshaft 17, a positive displacement pump 79 that sucks the lubricating oil in the lower oil reservoir P into the oil supply passage 17 a of the crankshaft 17 is provided. In the first embodiment, a so-called trochoid pump is employed as the positive displacement pump 79. In the trochoid pump, the volume of the lubricating oil in the lower oil reservoir P is changed by the rotational movement of the rotor and gears, and suction and discharge are performed to suck up the lubricating oil.

(1-7) Suction Pipe The suction pipe 19 is a pipe for guiding the refrigerant of the refrigerant circuit to the compression mechanism section 15 and is fitted into the upper wall section 12 of the casing 10 in an airtight manner. The suction pipe 19 penetrates a low pressure space 29 that is an upper space inside the casing 10 in the vertical direction, and a lower end portion is fitted into the fixed scroll 24.

(1-8) Discharge Pipe The discharge pipe 20 is a pipe for discharging the refrigerant in the casing 10 to the outside of the casing 10, and is fitted in the body casing portion 11 of the casing 10 in an airtight manner. And the edge part of this discharge pipe 20 is provided so that it may become the position which protruded further inward from the internal peripheral surface of the trunk | drum casing part 11. FIG.

(1-9) Compression Mechanism Unit As shown in FIG. 1, the compression mechanism unit 15 mainly meshes with the fixed scroll 24 and the fixed scroll 24 disposed in close contact with the upper bearing housing 23 described later. The movable scroll 26 is constituted.

  Hereinafter, the components of the compression mechanism section 15 will be described in detail.

(1-9-1) Fixed Scroll As shown in FIG. 1, the fixed scroll 24 has a flat end plate 24a and a bottom view formed by extending downward from the lower surface of the end plate 24a in a spiral shape (involute shape). The wrap 24b is provided.

  The end plate 24a has a discharge port 41 penetrating in the axial direction at a substantially axial center on the upper surface side. The discharge port 41 communicates with a compression chamber 40 described later. The discharge port 41 is formed to extend in the vertical direction.

  On the upper surface side of the end plate 24a, on the upper part of the discharge port 41, there is formed an enlarged recess 42 that extends upward by further expanding the upper end opening of the discharge port 41 in the horizontal direction. A lid 44 is fixed to the enlarged recess 42 so as to be closed from above. A space surrounded by the enlarged recess 42 and the lid body 44 in the vertical direction forms a muffler space 45. The muffler space 45 functions as an expansion chamber that silences the operation sound of the compression mechanism unit 15. A sealing structure is employed between the fixed scroll 24 and the lid 44 by being in close contact with each other via a gasket (not shown).

  Note that the refrigerant discharged from the discharge port 41 of the compression mechanism portion 15 passes through the muffler space 45 and passes through the communication passage 25 formed so as to penetrate in the vertical direction formed near the outer periphery of the upper bearing housing 23. To the gas guide 71, a part of the flow is diverted, passes through a specific core cut portion 51a downward, reaches the space around the lower side of the motor 16, and then another core cut. By passing upward through a passage such as the part 51 a, it is sent to the high-pressure space 18. The other part is separated from the lubricating oil by centrifugal force and sent to the high-pressure space 18 through a hole provided in the gas guide 71.

(1-9-2) Movable Scroll As shown in FIG. 1, the movable scroll 26 includes an end plate 26a, and a wrap 26b having a spiral view (involute shape) formed so as to extend toward the upper surface side of the end plate 26a. And a boss portion 26c constituting a pin bearing portion 22 that is formed on the lower surface side of the end plate 26a so as to extend in a cylindrical shape and receives the upper end of the crankshaft 17.

  The movable scroll 26 is not particularly limited, but an inner drive movable scroll is adopted in the present embodiment. The boss portion 26c of the movable scroll 26 covers the pin shaft portion 17b constituting the vicinity of the upper end of the crankshaft 17 from the outside in the radial direction. In this manner, the movable scroll 26 and the crankshaft 17 are rotatably connected.

  The wrap 26b extending above the movable scroll 26 is meshed with the wrap 24b extending below the fixed scroll 24 from above and below so as to overlap in the radial direction. Here, the wrap 24b of the fixed scroll 24 and the wrap 26b of the movable scroll 26 are meshed so that the compression chamber 40 is formed between the contact portions.

  The movable scroll 26 is supported by the upper surface of the upper bearing housing 23 so as to prevent rotation. As described above, the pin shaft portion 17b at the upper end of the crankshaft 17 is inserted into the boss portion 26c on the radially inner side.

  When the crankshaft 17 is rotationally driven, the boss portion 26c connected so as to transmit the rotational driving force to the pin shaft portion 17b receives the action of the force from the crankshaft 17, so that the movable scroll 26 rotates. Without rotating, the inside of the upper bearing housing 23 is revolved. At that time, as the movable scroll 26 revolves, the compression chamber 40 formed by the wrap 24b of the fixed scroll 24 and the wrap 26b of the movable scroll 26 moves in the radial direction with respect to the discharge port 41 while proceeding in the rotational traveling direction. As the distance becomes shorter, the volume shrinks toward the center. In the scroll compressor 1 according to the present embodiment, the refrigerant gas is compressed in this way.

  Further, as shown in FIG. 1, the thickness portion of the end plate 26 a of the movable scroll 26 extends radially outward, the inner end communicates with the inside of the boss portion 26 c, and is more radial than the compression chamber 40. An oil supply minute passage 81 is formed in which an outer end extending to the vicinity of the outer side communicates with the upper surface side of the end plate 26a.

  With the above structure, the lubricating oil pressurized by the positive displacement pump 79 rises through the oil supply passage 17a penetrating the inside of the crankshaft 17 in the axial direction, and is inside the inner peripheral surface of the boss portion 26c of the movable scroll 26. It is supplied to the sliding portion of the pin bearing portion 22 via the pin shaft upper space 37 at the upper end of the crankshaft 17 that is a part of the connection space. Specifically, the sliding between the inner peripheral surface of the pin shaft bearing metal 87 fitted to the inner peripheral surface of the boss portion 26 c of the movable scroll 26 and the outer peripheral surface of the pin shaft portion 17 b of the crankshaft 17. Lubricating oil is supplied to the part. Also, the lubricating oil sent to the pin shaft upper space 37 is supplied between the end plate 26 a of the movable scroll 26 and the end plate 24 a of the fixed scroll 24 via the oil supply micro-passage 81 of the end plate 26 a of the movable scroll 26. .

(1-10) Upper Bearing Housing The upper bearing housing 23 is press-fitted and fixed to the inner peripheral surface of the body casing portion 11 over the entire outer circumferential surface in the circumferential direction. Thereby, the radial direction inner side of the trunk | drum casing part 11 and the radial direction outer side of the upper bearing housing 23 are closely_contact | adhered airtightly over the perimeter. For this reason, the inside of the casing 10 is partitioned into a high pressure space 18 below the upper bearing housing 23 and a low pressure space 29 above the upper bearing housing 23. In addition, the fixed scroll 24 is fastened and fixed to the upper bearing housing 23 with bolts (not shown) so that the upper end surface is in close contact with the lower end surface of the fixed scroll 24.

  The upper bearing housing 23 has a crank chamber 31 that is recessed downward in the center of the upper surface. In addition, the lower part of the upper bearing housing 23 is formed such that the outer circumference thereof increases in the radial direction from the lower end toward the upper side, and the inner circumference thereof has a cylindrical shape in which the axial direction is the vertical direction. It is formed to become. The cylindrical portion is an upper inner peripheral portion 23 a that constitutes the upper bearing portion 32. The upper inner peripheral portion 23a constitutes the upper bearing portion 32 together with a cylindrical upper bearing metal 88 having a common axial direction that is fitted radially inward. The inner peripheral surface of the upper bearing metal 88 supports a portion below the pin shaft portion 17b of the crankshaft 17 so as to be rotatable from the outside in the radial direction.

  The upper bearing housing 23 is formed with a radial oil passage (not shown) extending radially outward from the vicinity of the lower end of the crank chamber 31 to the outer peripheral surface. The lubricating oil supplied to the inside of the crank chamber 31 passes through this radial oil passage, descends the gap between the trunk casing portion 11 and the stator 51, and enters the lower oil sump portion P at the lower portion of the casing 10. Returned.

  Furthermore, on the portion of the upper surface of the upper bearing housing 23 that is radially outward from the crank chamber 31, there is a portion where the inner pressure is high below the movable scroll 26 and the pressure outside the movable scroll 26 is outside. An annular seal member 86 is provided to seal between the lower portion and maintain the high pressure inside the crank chamber 31.

(1-11) Others As described above, the refrigerant discharged from the discharge port 41 of the compression mechanism unit 15 passes through the muffler space 45 and a part thereof faces the specific core cut part 51a downward. After passing through and reaching the space around the lower part of the motor 16, it is sent to the high-pressure space 18 by passing upward through a passage such as another core cut part 51a. Another part passes through the hole of the gas guide 71 and is sent to the high-pressure space 18. Then, the refrigerant gas sent to the high-pressure space 18 is discharged from the discharge pipe 20 to the outside of the casing 10.

(1-12) Crankshaft The crankshaft 17 is a drive shaft that transmits the driving force of the motor 16 to the compression mechanism portion 15, and the crankshaft 17 penetrates in the axial direction of the crankshaft 17 and is an oil supply passage. 17a is formed. The axis of the oil supply passage 17a and the axis on the outer peripheral surface of the crankshaft 17 are formed at different positions. That is, the axis of the oil supply passage 17 a is eccentric with respect to the axis with respect to the outer periphery of the crankshaft 17. Thereby, when the crankshaft 17 rotates, centrifugal force acts on the lubricating oil in the oil supply passage 17a, so that it is supplied upward.

  The crankshaft 17 is rotatably supported inside the casing 10 by a pin bearing portion 22, an upper bearing portion 32 of the upper bearing housing 23, and a lower bearing portion 27 of the lower bearing housing 28. An intermediate portion of the crankshaft 17 is concentrically connected to the rotor 52 of the motor 16.

  Further, the pin shaft portion 17 b at the upper end of the crankshaft 17 is provided so as to be eccentric from the intermediate portion of the crankshaft 17. Since the pin shaft portion 17b is inserted into the inner peripheral space of the boss portion 26c of the movable scroll 26, the movable scroll 26 can revolve by rotating the crankshaft 17 by the driving force of the motor 16. It is.

  Further, the pin shaft portion 17b of the crankshaft 17 branches out and extends radially outward from the middle of the oil supply passage 17a and communicates to the front of the inner peripheral surface of the external pin shaft bearing metal 87. A pin bearing oil supply lateral hole 17c is formed. The lubricating oil slides between the inner peripheral surface of the pin shaft bearing metal 87 and the outer peripheral surface of the pin shaft portion 17b provided inside the boss portion 26c of the movable scroll 26 through the pin bearing oil supply lateral hole 17c. Supplied to the part.

  A portion of the crankshaft 17 that is supported by the lower bearing portion 27 branches and extends from the middle of the oil supply passage 17a toward the radially outer side, and is in front of the inner peripheral surface of the outer lower bearing metal 89. A lower bearing oil supply lateral hole 17d is formed extending so as to penetrate to the end. The sliding portion between the inner peripheral surface of the lower bearing metal 89 of the lower bearing portion 27 and the outer peripheral surface near the lower end of the crankshaft 17 is supplied with oil through the lower bearing oil supply lateral hole 17d.

  Further, a portion of the crankshaft 17 supported by the upper bearing portion 32 extends and diverges from the middle of the oil supply passage 17a toward the radially outer side, and is in front of the inner peripheral surface of the outer upper bearing metal 88. An upper bearing oil supply lateral hole 17e extending so as to penetrate through is formed. The sliding portion between the inner peripheral surface of the upper bearing metal 88 of the upper bearing portion 32 and the outer peripheral surface below the pin shaft portion 17b of the crankshaft 17 is supplied with oil through the upper bearing oil supply lateral hole 17e. .

  Below the pin shaft portion 17b, there is a check structure 5 that allows only the upward flow of the lubricating oil during operation and closes the oil supply passage 17a to hold the lubricating oil upward when the operation is stopped. It has been adopted (see FIG. 2). The check structure 5 includes a check space 60 and a check member 90. The detailed configuration of the check structure 5 will be described later.

  As shown in FIG. 1, inside the boss portion 26c of the movable scroll 26, the space above the pin shaft, which is the space between the upper end surface of the pin shaft portion 17b at the tip of the crankshaft 17 and the lower surface of the end plate 26a of the movable scroll 26. 37 and a pin shaft circumferential space which is a space between the outer peripheral surface of the pin shaft portion 17b at the tip of the crankshaft 17 and the inner peripheral surface of the pin shaft bearing metal 87 provided inside the boss portion 26c of the movable scroll 26. 38 (a part of the crank chamber 31) are formed. A part of the lubricating oil supplied via the oil supply passage 17 a inside the crankshaft 17 is interposed between the movable scroll 26 and the fixed scroll 24 via the pin shaft upper space 37 and the above-described oil supply fine passage 81. Supplied. The pin shaft circumferential direction space 38 is formed so that a width of about several tens of microns in the radial direction extends in the vertical direction.

(1-13) Gas Guide As shown in FIG. 1, the gas guide 71 is disposed in the space below the upper bearing housing 23 in the radial direction and above the motor 16, and is located in the body casing portion 11. It is a metal thin plate-like member that is fixed and forms a flow path with the inner peripheral surface of the trunk casing portion 11.

  The gas guide 71 separates a part of the gas refrigerant that has passed through the connecting passage 25 formed in the upper bearing housing 23 and penetrating in the vertical direction, so that the outer peripheral surface of the stator 51 and the inner peripheral surface of the body casing portion 11 are separated. Guide to pass between. Another part of the refrigerant passes through a hole (not shown) of the gas guide 71 and is sent to the high-pressure space 18.

(2) Detailed Configuration of Check Structure As shown in FIG. 2 which is a partially enlarged cross-sectional view of a portion X in FIG. A check space 60 formed below the pin bearing oil supply lateral hole 17c of 17b and at a height above the upper bearing portion 32, and a check member 90 disposed in the check space 60. It is configured.

  As shown in FIG. 2 and FIG. 4 which is a schematic view in a top view, the check space 60 is located below the pin bearing oil supply lateral hole 17c of the pin shaft portion 17b and at a height position above the upper bearing portion 32. It is a space formed by a groove recessed from the side surface of the oil supply passage 17a toward the radially outer side. The check space 60 has an inclined surface 61 that is a surface extending radially outward as it goes upward from the lower end, and a groove bottom 62 that is a surface extending upward from the upper end portion of the inclined surface 61. It has a flat surface 63 extending horizontally at the upper end of the groove bottom 62. The groove bottom 62 is located radially outside the oil supply passage 17a of the crankshaft 17 and inside the outer periphery of the crankshaft 17.

  The check member 90 is disposed in the check space 60 and moves with the rotation of the crankshaft 17 to open the oil supply passage 17a, and when the crankshaft 17 is stopped, the oil supply passage 17a. It is the member which closes. The check member 90 includes a slide surface 91 that is in surface contact with the inclined surface 61 of the check space 60, an outer end surface 92 that extends upward from the upper end of the slide surface 91, and a horizontal direction at the upper end of the outer end surface 92. The upper surface 93 extends, the inner end surface 94 is parallel to the outer end surface 92 and forms the inner end portion, and the lower surface 95 is parallel to the upper surface 93 and forms the lower end portion.

  When the crankshaft 17 is stopped, the check member 90 is positioned so that the center of gravity is lowest due to its own weight, as shown in FIGS. In the state where the crankshaft 17 is stopped, the center of gravity of the check member 90 is located outside the center of rotation of the crankshaft 17. When the crankshaft 17 is stopped, the inner end surface 94 of the check member 90 is in contact with the side surface of the opposing oil supply passage 17a.

  Further, when the crankshaft 17 is driven, the check member 90 slides the slide surface 91 against the inclined surface 61 of the check space 60 due to the centrifugal force acting as shown in FIGS. 3 and 5. The groove bottom 62 and the outer end surface 92 of the check space 60 are slid upward toward the radially outer side so as to approach each other. The check member 90 rises while the center of gravity moves radially outward as the rotational speed of the crankshaft 17 increases. However, when the rotational speed exceeds the predetermined rotational speed, the check member 90 and the groove bottom 62 of the check space 60 The outer end surface 92 stays in a contact state. In this state, since the oil supply passage 17a is opened up and down, the lubricating oil pumped up by the positive displacement pump 79 from the lower oil reservoir P passes through the check structure 5 and is supplied further upward. Is done. As a result, when the crankshaft 17 is driven, the lubricating oil is supplied to the pin bearing portion 22 and the sliding portion around the pin bearing oil supply lateral hole 17c, and scroll compression is performed via the pin shaft upper space 37. It is supplied to the sliding part of the machine 15.

  Further, the check structure 5 is released in the state where the centrifugal shaft 17 is stopped in the state where the drive of the crankshaft 17 is stopped, and is pushed downward by the pressure of the lubricating oil above the oil supply passage 17a. The member 90 closes the oil supply passage 17a. For this reason, the lubricating oil existing above the oil supply passage 17a and between the check member 90 and the check space 60 does not drop to the lower oil sump portion P and is held in the middle. For this reason, at the time of start-up when the crankshaft 17 starts to drive again, it is not necessary to wait for the lubricating oil pumped up from the lower oil sump portion P to reach the upper side of the check member 90 and the check member 90. By using the lubricating oil held between the space 60 and the sliding portion of the scroll compressor 15, the pin bearing portion 22 and the surrounding sliding portion can be supplied more quickly.

(3) Operation Operation of Scroll Compressor Next, operation operation of the scroll compressor 1 will be briefly described with reference to FIGS.

  First, when the drive of the motor 16 is started, the crankshaft 17 rotates and the revolving operation is performed without the movable scroll 26 rotating. At this time, the check member 90 of the check structure 5 moves in the check space 60 radially outward and upward, and opens the oil supply passage 17a in the up-down direction due to the centrifugal force.

  In the compression mechanism unit 15 that receives the rotational force from the crankshaft 17, low-pressure refrigerant gas is sucked into the compression chamber 40 from the peripheral side of the compression chamber 40 through the suction pipe 19, and the volume change of the compression chamber 40 is changed. As a result, it is compressed and becomes a high-pressure refrigerant gas.

  The high-pressure refrigerant gas is discharged from the central portion of the compression chamber 40 through the discharge port 41 to the muffler space 45, and then flows downward through the communication passage 25 of the upper bearing housing 23, and a part of the refrigerant gas is separated. It flows in the circumferential direction along the inner peripheral surface of the partial casing portion 11 and is sent to the high-pressure space 18 through the hole of the gas guide 71. At this time, the lubricating oil mixed in the refrigerant gas is separated and stored in the lower oil reservoir P. Further, another part of the refrigerant gas that has been diverted passes downward through a specific core cut portion 51a formed in the stator 51, reaches the space around the lower side of the motor 16, and then reverses. By passing upward through the core cut portion 51 a and the air gap passage between the stator 51 and the rotor 52, it is sent to the high-pressure space 18. The refrigerant gas sent to the high-pressure space 18 and merged is discharged outside the casing 10 through the discharge pipe 20.

  The refrigerant gas discharged to the outside of the casing 10 circulates through the refrigerant circuit, and is again sucked into the compression mechanism portion 15 through the suction pipe 19 and compressed.

  Further, when the scroll compressor 1 is driven, the lubricating oil in the lower oil reservoir P is sucked up by the pumping action of the positive displacement pump 79 inside the casing 10, so that the oil supply passage 17 a of the crankshaft 17 is opened as described above. Oil supply to the sliding portion of the pin bearing portion 22 is performed through the non-return structure 5 and the pin bearing oil supply lateral hole 17c. At the same time, oil can be supplied between the fixed scroll 24 and the end plate 26 a of the movable scroll 26 via the pin shaft upper space 37 and the oil supply minute passage 81 in the plate thickness portion of the movable scroll 26.

  The oil supply to the sliding portion of the lower bearing portion 27 of the crankshaft 17 is appropriately supplied through the lower bearing oil supply lateral hole 17d branched from the oil supply passage 17a inside the crankshaft 17, and the sliding of the upper bearing portion 32 of the crankshaft 17 is performed. The oil supply to the moving part is appropriately supplied through the upper bearing oil supply lateral hole 17e branched from the oil supply passage 17a inside the crankshaft 17.

(4) Features of the First Embodiment In the scroll compressor 1 according to the first embodiment, when the motor 16 is driven and the crankshaft 17 is rotationally driven, the positive displacement pump 79 is driven to move downward. The lubricating oil stored in the oil reservoir P passes through the oil supply passage 17a and the open check structure 5 and is fed upward, so that the periphery of the upper compression mechanism 15 and the boss 26c It is supplied to the sliding portion such as between the pin shaft portion 17b and the periphery of the upper bearing portion 32, and the sliding portion can be prevented from being burned.

  Further, in the scroll compressor 1 of the first embodiment, the check structure 5 is employed, and when the drive of the motor 16 is stopped and the rotation drive of the crankshaft 17 is also stopped, it acts on the check member 90. The centrifugal force that has been released is released, the check member 90 closes the oil supply passage 17a, and the lubricating oil is retained above the check member 90 and between the check member 90 and the check space 60. It becomes the state of. For this reason, even after the motor 16 is driven again and the rotation of the crankshaft 17 is started, the lubricating oil stored in the lower oil reservoir P is not yet supplied. The lubricating oil held above the stop member 90 and between the check member 90 and the check space 60 is used to remove the lubricating oil around the surrounding compression mechanism 15, between the boss portion 26 c and the pin shaft portion 17 b, or at the upper bearing portion. 32 can be quickly supplied to sliding parts such as the periphery. For this reason, about the sliding part located in the place far away from the lower oil sump part P, it is possible to eliminate the shortage of lubricating oil at the time of start-up and suppress problems such as seizing.

(5) Other Embodiments In the first embodiment, one embodiment of the present invention has been described as an example.

  However, the present invention is not limited to these, and naturally includes embodiments obtained by appropriately changing without departing from the spirit of the present invention.

(5-1)
In the said 1st Embodiment, the case where the non-return member 90 which moves by centrifugal force acting was one member was demonstrated as an example.

  However, the present invention is not limited to this. For example, as shown in FIGS. 6 and 7, a first check member 290 a and a second check member 290 b are provided in the check space 260. The scroll compressor 201 provided with the non-return structure 205 may be used.

  In the scroll compressor 201, during operation of the crankshaft 17, as shown in FIG. 7, the two first check members 290a and the second check members 290b are separated from each other by the action of centrifugal force. However, the oil supply passage 17a is opened by moving upward.

  In addition, when the crankshaft 17 is stopped, the scroll compressor 201 abuts the two first check members 290a and 290b with each other in a state of being lowered by its own weight, as shown in FIG. In this state, the oil supply passage 17a is closed.

  Even with the above configuration, the same effects as those of the first embodiment can be obtained.

  Moreover, in this scroll compressor 201, since the check member is divided into a plurality of parts, the movement distance per check member for reducing the oil supply passage 17a from the closed state is shortened. Is able to. Thereby, even if it is difficult to secure an installation space, for example, the crankshaft 17 has a thin shape, the check structure 205 is easily adopted.

(5-2)
In the first and second embodiments described above, a structure in which the oil supply passage 17a is opened by moving the check member 90, the first check member 290a, the second check member 290b, and the like by centrifugal force will be described as an example. did.

  However, the present invention is not limited to this. For example, as shown in FIGS. 8 and 9, a check member 390 is provided in the check space 360, and the positive displacement pump 79 is used from below. The scroll compressor 301 may be provided with a check structure 305 that operates under the pressure of

  The check space 360 is formed in the middle of the oil supply passage 17a so as to expand the oil supply passage 17a in the radial direction so as to be an axial object of the oil supply passage 17a.

  The check member 390 is formed so that the lower edge corresponds to the shape of the check space 360 below.

  When the scroll compressor 301 is in operation, the motor 16 is driven to rotate the crankshaft 17 and the positive displacement pump 79 is also driven. When the positive displacement pump 79 is driven, the lubricating oil stored in the lower oil reservoir P is supplied to the check structure 305 via the oil supply passage 17a. At this time, the check member 390 of the check structure 305 is pushed up by the flow of lubricating oil supplied from below by the positive displacement pump 79, and as shown in FIG. 9, the outer periphery of the check member 390 and the check space 360 A gap is formed between the two. Then, the lubricating oil pushed up by the positive displacement pump 79 passes through a gap formed between the outer periphery of the check member 390 and the check space 360 and is sent upward, and around the upper compression mechanism portion 15 and the like. Lubricating oil can be supplied to the sliding portions such as between the boss portion 26c and the pin shaft portion 17b and around the upper bearing portion 32.

  On the other hand, when the crankshaft 17 is stopped, the scroll compressor 301 closes the oil supply passage 17a with the check member 390 descending by its own weight as shown in FIG. The oil is held without descending to the lower oil sump portion P.

  For this reason, also by the above structure, the effect similar to the said 1st Embodiment has been able to be show | played.

(5-3)
In the first and second embodiments, the structure in which the check members 90, 290a, and 290b are lowered by their own weight to stop the oil supply passage 17a when stopped is described as an example.

  However, the present invention is not limited to this. For example, as shown in FIGS. 10 and 11, the check member 490 is fixed while being accommodated in the check space 460 via the elastic support body 465. The scroll compressor 401 provided with the check structure 405 may be used.

  The check space 460 is formed in the middle of the oil supply passage 17a so as to expand the oil supply passage 17a in the radial direction.

  The check member 490 is formed in a shape that can be slid in the horizontal direction in the check space 460 corresponding to the vertical width of the check space 460 in the vertical direction. The check member 490 is formed with a through hole 417a penetrating in the vertical direction. The through hole 417a has a size corresponding to the inner diameter of the oil supply passage 17a. Further, the center of gravity of the check member 490 is located radially outward from the axis of the crankshaft 17 even when the crankshaft 17 is not driven, and the crankshaft 17 is driven. Thus, the centrifugal force directed radially outward is arranged to act.

  One end of the elastic support 465 is joined to a radial end on the direction of centrifugal force acting on the check member 490 when the crankshaft 17 is driven. Further, the other end of the elastic support 465 is joined to a surface of the check space 460 that faces the surface where the check member 490 and the elastic support 465 are joined.

  As a result, when the crankshaft 17 is driven and a centrifugal force acts on the check member 490 and the check member 490 tries to slide outward in the radial direction, the elastic support 465 is elastically deformed so as to contract, and the elastic reaction force Acts on the check member 490. As a result, as shown in FIG. 11, the check member 490 can be slid by an amount corresponding to the rotational speed of the crankshaft 17, so the degree of opening of the oil supply passage 17 a depends on the rotational speed of the crankshaft 17. Can be adjusted.

  When the crankshaft 17 is stopped and not rotating, there is no centrifugal force acting on the check member 490, so that the elastic support 465 and the check space 460 are joined as shown in FIG. The check member 490 is pushed away by the elastic support member 465 in a direction away from the portion. In this state, the check member 490 completely closes the oil supply passage 17a. Therefore, when the operation is stopped, the lubricating oil that has existed at the upper side does not fall to the lower oil sump portion P without being lowered. It is held in the oil supply passage 17 a above the stop member 490.

  For this reason, also by the above structure, the effect similar to the said 1st Embodiment has been able to be show | played.

(5-4)
In the first embodiment, the case where the check structure 5 is provided at the height position between the pin bearing portion 22 and the upper bearing portion 32 has been described as an example.

  However, the present invention is not limited to this. For example, as shown in FIGS. 13 and 14 which are partial enlarged sectional views of the Y portion in FIGS. 12 and 12, the upper pin bearing portion 22 and the upper bearing Instead of having the check structure 5 at the height position between the parts 32, the scroll compressor 501 having the check structure 505 at the height position of the lower bearing part 27 may be used. In this check structure 505, the check member 590 is accommodated in a check space 560 configured such that a portion of the lower bearing portion 27 in the oil supply passage 17 a of the crankshaft 17 is widened. It is composed of that. Specifically, the check structure 505 is a height position of the lower bearing portion 27 and extends downward from the side surface of the oil supply passage 17a of the crankshaft 17 so as to penetrate radially outward. It is formed at a position further below the hole 17d.

  As shown in FIG. 14, the check structure 505 of the scroll compressor 501 is configured such that when the crankshaft 17 is driven, centrifugal force acts on the check member 590 so that the check member 590 is not checked. The inside of the space 560 moves upward in the radial direction and opens the oil supply passage 17a in the vertical direction. As a result, the lubricating oil stored in the lower oil reservoir P and pumped up by the positive displacement pump 79 is supplied to the sliding portion of the lower bearing portion 27 via the lower bearing oil supply lateral hole 17d and further upward. Also supplied to the sliding part.

  Further, in the check structure 505 of the scroll compressor 501, when the crankshaft 17 is stopped, the centrifugal force acting on the check member 590 is released as shown in FIG. Drops due to its own weight and closes the oil supply passage 17a. As a result, the lubricating oil existing above the check member 590 and between the check member 590 and the check space 560 can be retained.

  For this reason, also by the above structure, the effect similar to the said 1st Embodiment has been able to be show | played. Moreover, in the example of this other embodiment (5-4), when the drive of the motor 16 is stopped and the rotational drive of the crankshaft 17 is also stopped, the check member 590 and the check member 590 are not checked. Lubricating oil can be kept between the space 560. Here, in the example of the other embodiment (5-4), the check member 590 of the check structure 505 in the oil supply passage 17a of the crankshaft 17 is compared with the example of the first embodiment. The upper volume can be secured more widely. For this reason, it becomes possible to hold more lubricating oil in a state where the rotational drive of the crankshaft 17 is stopped. Therefore, even after the motor 16 is driven again and the rotation of the crankshaft 17 is started, even if the lubricating oil stored in the lower oil reservoir P is not yet supplied, the check is not performed. A sufficient amount of lubricating oil retained above the member 590 and between the check member 590 and the check space 560 is removed between the periphery of the compression mechanism portion 15 and between the boss portion 26c and the pin shaft portion 17b. It is possible to quickly and effectively supply the sliding portion around the upper bearing portion 32 and the like.

  In this other embodiment (5-4), unlike the first embodiment having the check structure 5 at the height position between the upper pin bearing portion 22 and the upper bearing portion 32, the check structure 5 is provided. The scroll compressor 501 having the check structure 505 at the height position of the lower bearing portion 27 is described as an example. However, the present invention is not limited to this, for example, a scroll having both the check structure 5 of the first embodiment and the check structure 505 of the other embodiment (5-4). Of course, the compressor is also included in the present invention.

(5-5)
In the said 1st Embodiment and each other embodiment, the case where the means for sending lubricating oil upward was a positive displacement pump was mentioned as an example, and was demonstrated.

  However, the present invention is not limited to this. For example, as shown in FIG. 15, a scroll compressor 601 that employs a differential pressure pump 679 instead of a positive displacement pump may be used.

  In the differential pressure pump 679, when the crankshaft 17 rotates during driving, the pressure near the upper end of the oil supply passage 17 a of the crankshaft 17 is near the lower end inlet of the differential pressure pump 679 connected to the lower end of the crankshaft 17. The lubricating oil stored in the lower oil reservoir P is sucked up by utilizing the fact that the pressure becomes lower than the pressure of the oil.

  Specifically, with respect to the oil level, the crankshaft 17 rotates during driving, and the compression mechanism unit 15 performs a compression operation, whereby the discharged high-pressure refrigerant is sent to the high-pressure space 18, and the high-pressure space 18 The high pressure acts to push the oil level of the lower oil sump P downward. On the other hand, the vicinity of the upper end of the oil supply passage 17a of the crankshaft 17 is affected by the pressure of the low pressure space 29 via the pin shaft upper space 37 and the oil supply minute passage 81 of the movable scroll 26. Lower than the pressure near the inlet. The differential pressure pump 679 supplies the lubricating oil in the lower oil sump P upward using the pressure difference thus generated.

  In the scroll compressor 601 provided with the differential pressure pump 679, the lubricating oil in the lower oil sump portion P cannot be supplied upward unless the above-described differential pressure is sufficiently ensured at the time of activation. On the other hand, the lubricating oil retained above the check structure 5 can be quickly applied to the sliding portion of the pin bearing portion 22 without waiting until the differential pressure is sufficiently secured at the time of startup. It is possible to supply.

(5-6)
In the first embodiment, the case where the oil supply passage 17a of the crankshaft 17 is provided eccentrically has been described as an example.

  However, the present invention is not limited to this, and may have an oil supply passage concentric with the outer periphery of the crankshaft 17.

(5-7)
In the above-described embodiment and each of the other embodiments, the case where a slide bearing is employed as the bearing that receives the crankshaft 17 has been described as an example.

  However, the bearing that receives the crankshaft 17 is not particularly limited. For example, another type of bearing such as a rolling bearing may be employed as the bearing.

  The scroll compressor of the present invention is particularly useful in, for example, a scroll compressor in which a crankshaft extends in the vertical direction and lubricating oil is stored at the lower end.

1, 201, 301, 401, 501, 601 Scroll compressor 5, 205, 305, 405, 505 Check structure 15 Compression mechanism 16 Motor 17 Crankshaft 17a Oil supply passage 17b Pin shaft 17c Pin bearing oil supply side hole (oil supply side hole )
18 High pressure space 22 Pin bearing portion 23 Upper bearing housing 24 Fixed scroll 26 Movable scroll 26c Boss portion 27 Lower bearing portion 28 Lower bearing housing 32 Upper bearing portion 37 Pin shaft upper space 38 Pin shaft circumferential space 40 Compression chambers 60, 260, 360, 460, 560 check space 79 positive displacement pump 90, 390, 490, 590 check member 290a first check member (check member)
290b Second check member (check member)
679 Differential pressure pump P Lower oil sump

JP 2011-1854 A

Claims (4)

A casing (10);
A compression mechanism (15) housed in the casing and having a fixed scroll (24) and a movable scroll (26) forming a compression chamber between the fixed scroll;
A crankshaft (17) rotatably connected to the upper bearing portion (32) and the lower bearing portion (27);
A motor (16) for rotationally driving the crankshaft;
A lower oil sump portion (P) provided in a space below the lower bearing portion (27) in the casing and for accumulating lubricating oil;
In the scroll compressor with
An oil supply passage (17a) formed to extend in the axial direction inside the crankshaft;
A check structure (5, 205, 305) that connects the oil supply passage when the crankshaft is rotationally driven and blocks the flow of lubricating oil from the top to the bottom when the crankshaft is stopped. 405, 505),
Scroll compressor (1, 201, 301, 401, 501, 601). The non-return structure is above the lower oil sump portion and is more radial than the outer periphery of the crankshaft at a position closer to the lower bearing portion or closer to the upper bearing portion than the lower oil sump portion. Inside the crankshaft on the inside, it is configured to have a check member (90, 290a, 290b, 490, 590) provided separately from the crankshaft,
The check member is
In a state where the crankshaft is rotationally driven, the oil supply passage extending in the axial direction is communicated by moving by a centrifugal force,
In the state where the crankshaft is stopped, the centrifugal force is released to close the middle of the oil supply passage extending in the axial direction.
The scroll compressor (1, 201, 401, 501, 601) according to claim 1. In the state where the crankshaft is stopped, the check member is in a position to close the middle of the oil supply passage extending in the axial direction by both the release of the centrifugal force and the pressure of the upper lubricating oil. Moving,
The scroll compressor according to claim 2. The axis of the oil supply passage of the crankshaft is eccentric with respect to the axis with respect to the outer periphery of the crankshaft.
The scroll compressor according to any one of claims 1 to 3.

Images