JP2012149532A - Rotary fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To supply a sufficient amount of lubricating oil to a sliding part in a rotary fluid machine.SOLUTION: The rotary fluid machine (1) comprises a driving shaft (17) rotated by a driving mechanism (16) with one end disposed in an oil reservoir (13a) in a casing (10), a fluid mechanism (15) driven by the driving shaft (17) for compressing or expanding a fluid, a main oil supply path (63) extending from one end to the other end of the driving shaft (17), and an oil supply path (62) including at least one branched path (64a, 64b, 64c) branched from the main oil supply path (63). A fixed shaft (66) fixed to the casing (10) and inserted through the main oil supply path (63) is provided to form a plurality of screw grooves (65a, 65b, 65c, 67a, 67b, 67c) extending from one end to the other end side of the driving shaft (17) on the inner circumferential surface of the main oil supply path (63) or on the outer circumferential surface of the fixed shaft (66).

Description

  The present invention relates to a rotary fluid machine, and particularly relates to measures for stably supplying lubricating oil to each sliding portion of the rotary fluid machine.

  2. Description of the Related Art Conventionally, in a rotary fluid machine for compressing or expanding a fluid, various oil supply methods are used to supply lubricating oil to each sliding portion of the rotary fluid machine.

  For example, in a scroll type compressor (rotary fluid machine) disclosed in Patent Document 1, oil is supplied to each sliding portion by using a differential pressure and a centrifugal pump action in combination. Specifically, the drive shaft that drives the compression mechanism as the fluid mechanism includes a first oil supply passage (main oil supply passage) that extends upward from the lower end portion of the drive shaft, and an upper end of the first oil supply passage. An oil supply passage having a second oil supply passage (branch passage) branched from the portion and communicating with the intermediate pressure back pressure chamber is formed. Since the starting end of the main oil supply passage is immersed in the lubricating oil in the atmosphere of the refrigerant compressed to a high pressure, a differential pressure is generated between the upper end portion and the lower end portion of the first oil supply passage. Lubricating oil is sucked upward by this differential pressure and supplied to each sliding portion. The main oil supply passage extends obliquely upward in the drive shaft so that the inflow end is disposed on the shaft center side of the drive shaft and the outflow end is eccentric from the shaft center of the drive shaft. Is formed. Thereby, the lubricating oil which flows through the main oil supply passage is supplied to each sliding portion also by the centrifugal pump action.

  In addition, it is generally known to use only the differential pressure, use only the centrifugal pump action, or use a volumetric pump to supply oil to each sliding portion.

JP-A-8-261177

  By the way, even when the above-described oil supply method is used to supply the lubricating oil, there may be a case where a sufficient amount of the lubricating oil cannot be supplied depending on the operating conditions or the like.

  This invention is made | formed in view of this point, The objective is to supply sufficient quantity of lubricating oil to a sliding part reliably in a rotary fluid machine.

  A first invention is directed to a rotary fluid machine, and is rotated by a casing (10), a drive mechanism (16) accommodated in the casing (10), and the drive mechanism (16), one end of which is A drive shaft (17) disposed in an oil reservoir (13a) in the casing (10), a fluid mechanism (15) driven by the drive shaft (17) to compress or expand a fluid, and the drive shaft (17 A main oil supply passage (63) extending from one end to the other end of the main oil supply passage, and at least one branch passage (64a, 64b, 64c) branched from the main oil supply passage (63); A fixed shaft (66) fixed to the casing (10) and inserted through the main oil supply passage (63), on an inner peripheral surface of the main oil supply passage (63) or an outer peripheral surface of the fixed shaft (66) Is formed with a plurality of spiral grooves (65a, 65b, 65c, 67a, 67b, 67c) extending spirally from one end of the drive shaft (17) toward the other end. And features.

  In the first invention, when the drive mechanism (16) is driven, the drive shaft (17) is rotated. Then, the fluid is compressed or expanded by the fluid mechanism (15) driven by the drive shaft (17).

  In the first invention, when the drive shaft (17) is rotated, the inner peripheral surface of the main oil supply passage (63) is opposed to the outer peripheral surface of the fixed shaft (66) fixed to the casing (10). Rotate. Then, the lubricating oil in the portion of the plurality of spiral grooves (65a, 65b, 65c, 67a, 67b, 67c) arranged in the oil sump (13a) is distributed on the inner peripheral surface of the rotating main oil supply passage (63). As it is dragged, it flows in the spiral groove (65a, 65b, 65c, 67a, 67b, 67c) while rotating in the circumferential direction in the main oil supply passage (63). As a result, the lubricating oil flows from one end side to the other end side in the main oil supply passage (63) so as to be guided by the spiral grooves (65a, 65b, 65c, 67a, 67b, 67c). The lubricating oil that has flowed through the plurality of spiral grooves (65a, 65b, 65c, 67a, 67b, 67c) in this way from the inflow end of the branch path (64a, 64b, 64c) to the branch path (64a, 64b, 64c) Then, it is supplied to the sliding portion of the drive shaft (17) and the sliding portion of the fluid mechanism (15) to lubricate these sliding portions.

  In a second aspect based on the first aspect, the drive shaft (17) is formed with a plurality of branch paths (64a, 64b, 64c), and the plurality of spiral grooves (65a, 65b, 65c) The inner peripheral surface of the main oil supply passage (63) so that the outflow end portion of each spiral groove (65a, 65b, 65c) is connected to the inflow end portion of the corresponding branch passage (64a, 64b, 64c), respectively. It is characterized by being formed.

  When the plurality of spiral grooves (65a, 65b, 65c) are formed on the inner peripheral surface of the main oil supply passage (63) as in the second aspect of the invention, the plurality of spirals are maintained even if the drive shaft (17) rotates. The relative positional relationship between the groove (65a, 65b, 65c) and the plurality of branch paths (64a, 64b, 64c) is the same. Therefore, as in the second invention, the outflow end of each spiral groove (65a, 65b, 65c) and the inflow end of each branch path (64a, 64b, 64c) corresponding to each outflow end are always connected. Can be connected. For this reason, the lubricating oil flowing through each spiral groove (65a, 65b, 65c) passes through the inflow end of the branch path (64a, 64b, 64c) corresponding to the spiral groove (65a, 65b, 65c). It flows directly into (64a, 64b, 64c).

  In a third aspect based on the first aspect, the drive shaft (17) has a plurality of branch paths (64a, 64b, 64c), and the plurality of spiral grooves (67a, 67b, 67c) The at least one of the plurality of spiral grooves (67a, 67b, 67c) is formed on the outer peripheral surface of the fixed shaft (66), and the inflow ends of the two or more branch paths (64a, 64b, 64c) It extends so that it may straddle.

  When the plurality of spiral grooves (67a, 67b, 67c) are formed on the outer peripheral surface of the fixed shaft (66) as in the third invention, when the drive shaft (17) rotates, the plurality of spiral grooves (67a, 67b, 67c) and the relative positional relationship between the plurality of branch paths (64a, 64b, 64c) change. Specifically, the inflow ends of the branch paths (64a, 64b, 64c) rotate with respect to the plurality of spiral grooves (67a, 67b, 67c). And when the inflow end of the branch path (64a, 64b, 64c) overlaps with the spiral groove (67a, 67b, 67c), the spiral groove (67a, 67b, 67c) and the branch path (64a, 64b, 64c) Communicate. That is, in the third invention, the lubricating oil in the spiral grooves (67a, 67b, 67c) intermittently flows into the branch paths (64a, 64b, 64c).

  Here, since at least one of the plurality of spiral grooves (67a, 67b, 67c) extends so as to straddle the inflow end portions of the two or more branch paths (64a, 64b, 64c), this spiral groove The lubricating oil (67a, 67b, 67c) intermittently flows into the plurality of branch paths (64a, 64b, 64c).

  According to the first aspect, the fixed shaft (66) inserted through the main oil supply passage (63) is provided, and the spiral groove is formed on the outer peripheral surface of the fixed shaft (66) or the inner peripheral surface of the main oil supply passage (63). (65a, 65b, 65c, 67a, 67b, 67c) are formed. Thereby, even if the differential pressure in the main oil supply passage (63) is small, the lubricating oil can be reliably supplied to each sliding portion. Furthermore, each sliding part is supplied with lubricating oil from a plurality of spiral grooves (65a, 65b, 65c, 67a, 67b, 67c). Thus, a sufficient amount of lubricating oil can be supplied.

  According to the second aspect of the invention, each branch passage (64a, 64b, 64c) is lubricated from the spiral groove (65a, 65b, 65c) corresponding to each branch passage (64a, 64b, 64c). Oil flows in. As a result, the passage width, length and shape of each spiral groove (65a, 65b, 65c) are individually adjusted, and the amount of lubricating oil supplied to each branch passage (64a, 64b, 64c) is individually changed. it can. As a result, for example, a large amount of lubricating oil can be supplied to a bearing portion with a large bearing load, while a small amount of lubricating oil can be supplied to a bearing portion with a small bearing load. Further, since the branch paths (64a, 64b, 64c) do not communicate with each other in the drive shaft (17), the lubricating oil supplied to a certain branch path among the plurality of branch paths (64a, 64b, 64c) Even if the amount changes, the amount of lubricating oil supplied to the other branch passages does not change. Therefore, a stable amount of lubricating oil can be supplied to each branch path (64a, 64b, 64c).

  Further, according to the third invention, since the spiral grooves (67a, 67b, 67c) are formed so as to straddle the inflow end portions of the two or more branch paths (64a, 64b, 64c), one Lubricating oil can be reliably supplied from the spiral groove (67a, 67b, 67c) to the plurality of branch paths (64a, 64b, 64c).

FIG. 1 is a longitudinal sectional view of a scroll compressor according to the first embodiment. FIG. 2 is a view corresponding to FIG. 1 with the fixed shaft omitted. FIG. 3 is a development view of the inner peripheral surface of the main oil supply passage. FIG. 4 is a longitudinal sectional view of the scroll compressor according to the second embodiment. FIG. 5 is a longitudinal sectional view of a scroll compressor according to another embodiment. 6 is a view corresponding to FIG. 5 with the fixed shaft omitted.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The following embodiments are essentially preferable examples, and are not intended to limit the scope of the present invention, its application, or its use.

Embodiment 1 of the Invention
The scroll compressor (1) according to Embodiment 1 constitutes a rotary fluid mechanism. The scroll compressor (1) is connected to a refrigerant circuit (not shown) that performs a refrigeration cycle operation by circulating the refrigerant, and compresses the refrigerant.

-Overall configuration-
As shown in FIG. 1, the scroll compressor (1) includes a vertically long cylindrical sealed dome-shaped casing (10) and an electric motor (16) as a drive mechanism provided below the casing (10). And a drive shaft (17) extending vertically from the electric motor (16), and a compression mechanism (15) driven by the drive shaft (17) to compress the refrigerant.

  The casing (10) includes a casing body (11) that is a cylindrical body extending in the vertical direction, and a bowl-shaped upper wall portion (12) that is welded and integrally joined to the upper end of the casing (10), The casing body (11) is welded and integrally joined to the lower end portion of the casing main body (11), and is formed into a pressure vessel with a bowl-shaped bottom wall portion (13) protruding downward, and the inside thereof is a cavity.

  A suction pipe (19) for guiding the refrigerant of the refrigerant circuit to the compression mechanism (15) is inserted and fixed in the upper wall portion (12) of the casing (10). Further, a discharge pipe (20) for guiding the high-pressure refrigerant compressed by the compression mechanism (15) to the refrigerant circuit is inserted and fixed at the upper part of the casing body (11). The bottom wall (13) is formed with an oil reservoir (13a) for storing lubricating oil.

  The electric motor (16) is a so-called DC brushless motor. The electric motor (16) includes an annular stator (51) fixed to the inner wall surface of the casing (10), and a substantially columnar shape inserted into the stator (51) and configured to be rotatable with respect to the stator (51). And a rotor (52). The rotor (52) is formed with a through hole (52a) passing through the rotor (52) in the vertical direction so as to be coaxial with the central axis of the rotor (52).

  The drive shaft (17) includes a main shaft portion (17a) formed in an elongated bar shape extending in the vertical direction, and a columnar eccentric pin (17b) standing on the upper end of the main shaft portion (17a). . The lower end of the drive shaft (17) is immersed in the oil sump (13a). The eccentric pin (17b) is eccentric by a predetermined distance from the axis of the main shaft portion (17a). The drive shaft (17) is inserted and fixed in the through hole (52a) of the rotor (52). The drive shaft (17) is supported by an upper bearing (34) that supports an upper portion of the main shaft portion (17a) and a lower bearing (44) that supports a lower portion of the main shaft portion (17a). Yes.

  The drive shaft (17) includes a main oil passage (63) extending in the vertical direction and a plurality of (three in the first embodiment) branch passages (64a, 64b, 64c) extending in the horizontal direction from the main oil passage (63). ), And an oil supply passage (62) is formed. The main oil supply passage (63) has a lower end opened to the oil reservoir (13a), and an upper end formed slightly below the upper end of the drive shaft (17). The three branch paths include a lower bearing branch path (64a), an upper bearing branch path (64b), and a pin bearing branch path (64c). The outflow end of the lower bearing branch passage (64a) opens toward the inner peripheral surface of the lower bearing (44), and the outflow end of the upper bearing branch passage (64b) is the inner peripheral surface of the upper bearing (34). The outflow end of the pin bearing branch passage (64c) opens toward the inner peripheral surface of the pin bearing (26d) inserted and fixed in a movable scroll (26), which will be described in detail later.

  The inflow end of the main oil supply passage (63) is immersed in the lubricating oil stored in the oil sump (13a). This lubricating oil is exposed to the atmosphere of the high-pressure space (28) in the casing (10). The outflow end of the pin bearing branch (64c) communicates with the low pressure space (29) in the casing (10). As a result, in the main oil supply passage (63), the lower end portion has a relatively high pressure, while the upper end portion communicating with the low pressure space (29) has a lower pressure than the lower end portion.

  A plurality of (three in the first embodiment) spiral grooves (65a, 65b, 65c) are formed on the inner peripheral surface of the main oil supply passage (63). The shapes of the three spiral grooves (65a, 65b, 65c) will be described later in detail.

  The compression mechanism (15) includes a fixed scroll (24), a movable scroll (26) combined with the fixed scroll (24), and an upper housing (23) that supports the movable scroll (26).

The upper housing (23) is provided above the electric motor (16). The outer surface of the upper housing (23) is fixed in close contact with the casing body (11) over the entire circumferential direction. Thus, the inside of the casing (10) is partitioned by the upper housing (23) into a high pressure space (28) below the upper housing (23) and a low pressure space (29) above the upper housing (23). ) Are formed with a housing recess (31) recessed at the center of the upper surface and a cylindrical portion (32) projecting downward from the center of the lower surface and having a bearing hole (33). An upper bearing (34) that rotatably supports the drive shaft (17) is inserted and fixed in the bearing hole (33). The drive shaft (17) is inserted through the upper bearing (34). The upper housing (23) is formed with an oil drainage passage (37) extending in the horizontal direction from the lower portion of the housing recess (31).

  The scroll compressor (1) further includes a lower housing (41). The lower housing (41) includes a cylindrical part (42) in which a bearing hole (43) is formed, and a fixing part (45) for fixing the cylindrical part (42) to the inner peripheral surface of the casing body (11). Is included. A lower bearing (44) that rotatably supports the drive shaft (17) is inserted and fixed in the bearing hole (43) of the lower housing (41). The drive shaft (17) is inserted through the lower bearing (44).

  The fixed scroll (24) includes a mirror plate (24a) and a spiral (involute) wrap (24b) formed on the lower surface of the mirror plate (24a). The fixed scroll (24) is fastened and fixed to the upper housing (23) by fastening bolts (38) with the lower end surface thereof being in close contact with the upper end surface of the upper housing (23).

  The movable scroll (26) includes an end plate (26a), a spiral (involute) wrap (26b) formed on the upper surface of the end plate (26a), a boss portion (26c), and a pin bearing (26d). I have. The end plate (26a) is formed in a substantially disc shape and is located above the upper housing (23). The wrap (26b) is configured to mesh with the wrap (24b) of the fixed scroll (24). The boss portion (26c) is formed in a cylindrical shape and is integrally formed with the end plate (26a) so as to protrude from the lower surface of the end plate (26a). The pin bearing (26d) is inserted and fixed to the boss portion (26c). An eccentric pin (17b) of the drive shaft (17) is inserted through the pin bearing (26d). The movable scroll (26) is supported by the upper housing (23) via the Oldham coupling (39) and the upper end of the drive shaft (17) is fitted, and the upper part is not rotated by rotation of the drive shaft (17). The inside of the housing (23) is revolved.

  The wrap (24b) of the fixed scroll (24) and the wrap (26b) of the movable scroll (26) are meshed with each other, so that both wraps ( The space between the contact portions 24b and 26b) is configured as a compression chamber (40). The compression chamber (40) is configured to compress the refrigerant by reducing the volume between the wraps (24b, 26b) toward the center as the movable scroll (26) revolves.

  The fixed scroll (24) and the upper housing (23) are provided with a communication passage (46) formed between the fixed scroll (24) and the upper housing (23). The communication passage (46) is for guiding the compressed high-pressure refrigerant to the high-pressure space (28). The gas refrigerant flowing through the communication passage (46) is discharged to the high-pressure space (28) through the guide plate (58).

  The scroll compressor (1) further includes a fixed shaft (66). The fixed shaft (66) is formed in a round bar shape, and its outer diameter is formed to be slightly smaller than the inner diameter of the main oil supply passage (63). Note that the fixed shaft (66) may be formed to be slightly tapered as it goes upward. The fixed shaft (66) is inserted into the main oil supply passage (63) with one end fixed to the bottom wall (13) of the casing (10), and the other end is the inflow end of the pin bearing branch passage (64c). It extends to the vicinity. A slight gap is formed between the outer peripheral surface of the fixed shaft (66) and the inner peripheral surface of the main oil supply passage (63). The outer peripheral surface of the fixed shaft (66) constitutes a part of a viscous pump mechanism (60) described later in detail.

-Shape of spiral groove-
As described above, three spiral grooves (65a, 65b, 65c) are formed on the inner peripheral surface of the main oil supply passage (63). The three spiral grooves (65a, 65b, 65c) together with the outer peripheral surface of the fixed shaft (66) constitute a viscous pump mechanism (60). As shown in FIGS. 2 and 3, the three spiral grooves are composed of a lower bearing spiral groove (65a), an upper bearing spiral groove (65b), and a pin bearing spiral groove (65c). ing. Each of these spiral grooves (65a, 65b, 65c) has a start end formed at the inflow end portion of the main oil supply passage (63) and extends upward in a spiral manner. The width of these spiral grooves (65a, 65b, 65c) increases in the order of the lower bearing spiral groove (65a), the pin bearing spiral groove (65c), and the upper bearing spiral groove (65b). Each spiral groove (65a, 65b, 65c) extends upward from the lower end portion of the drive shaft (17), with the axis of the drive shaft (17) as the center, opposite to the rotational direction of the drive shaft (17). It is formed to extend while turning. The spiral grooves (65a, 65b, 65c) are arranged so as to be parallel to each other without crossing each other. In the present embodiment, the groove width is increased in the order of the lower bearing spiral groove (65a), the pin bearing spiral groove (65c), and the upper bearing spiral groove (65b). The groove width can be changed according to the amount of oil required for each bearing.

  Each spiral groove (65a, 65b, 65c) is connected to the inflow end of each branch path (64a, 64b, 64c) so as to correspond to each branch path (64a, 64b, 64c) in a one-to-one relationship. Has been. Specifically, the lower bearing spiral groove (65a) has an outflow end connected to the inflow end of the lower bearing branch passage (64a), and the upper bearing spiral groove (65b) has an outflow end at the outflow end. The pin bearing spiral groove (65c) is connected to the inflow end of the upper bearing branch (64b), and the outflow end of the pin bearing spiral groove (65c) is connected to the inflow end of the pin bearing branch (64c).

-Viscous pump mechanism-
The viscous pump mechanism (60) includes a plurality of spiral grooves (65a, 65b, 65c) formed on the inner peripheral surface of the main oil supply passage (63) and a fixed shaft (66) inserted through the main oil supply passage (63). ) Outer peripheral surface. When the drive shaft (17) is rotated, the viscous pump mechanism (60) operates so that the three spiral grooves (65a, 65b, 65c) viewed from the side turn upward while turning. The lubricating oil between the outer peripheral surface of the fixed shaft (66) and the spiral grooves (65a, 65b, 65c) is conveyed upward.

-Driving action-
Next, the operation of the scroll compressor (1) according to the first embodiment will be described. First, when the electric motor (16) is driven, the rotor (52) rotates with respect to the stator (51), whereby the drive shaft (17) rotates. When the drive shaft (17) rotates, the movable scroll (26) does not rotate with respect to the fixed scroll (24) but only revolves. As a result, the low-pressure refrigerant is sucked into the compression chamber (40) from the peripheral side of the compression chamber (40) through the suction pipe (19), and the refrigerant is compressed as the volume of the compression chamber (40) changes.

  The compressed gas refrigerant flows into the communication passage (46) at a high pressure and flows into the high-pressure space (28) through the communication passage (46) and the guide plate (58). And this gas refrigerant is discharged outside through a discharge pipe (20).

−Lubrication operation to each sliding part−
In the oil supply operation in the scroll compressor (1) according to Embodiment 1, the differential pressure between the upper end portion and the lower end portion of the main oil supply passage (63) is used, and at the same time, the viscous pump mechanism (60) is used. Is done.

  When the drive shaft (17) is rotationally driven, the compression mechanism (15) is driven as described above, and the high-pressure gas refrigerant compressed by the compression mechanism (15) flows into the high-pressure space (28). As a result, high pressure acts on the lubricating oil stored in the oil sump (13a) of the high pressure space (28), so that high pressure acts on the lower end portion of the main oil supply passage (63). On the other hand, since the upper end portion of the main oil supply passage (63) communicates with the low pressure space (29), a low pressure acts. As a result, the lubricating oil rises in the main oil supply passage (63) due to the differential pressure. Then, the lubricating oil flows radially outward through the branch paths (64a, 64b, 64c) by the centrifugal force of the drive shaft (17) that is rotationally driven, and the sliding portion of the compression mechanism (15) and the drive shaft (17 ) Lubricate the sliding part. Specifically, the lubricating oil that has flowed through the lower bearing branch (64a) mainly lubricates the sliding portion of the lower bearing (44) and flows through the upper bearing branch (64b). Mainly lubricates the sliding portion of the upper bearing (34), and the lubricating oil flowing through the pin bearing branch passage (64c) mainly lubricates the sliding portion of the pin bearing (26d). Thereafter, the lubricating oil is returned to the oil sump (13a) through the oil discharge passage (37) and the like.

  However, immediately after the compression mechanism (15) is driven, the inside of the high-pressure space (28) is not sufficiently high, so that the sliding portion is sufficiently lubricated with only the differential pressure as described above. There may not be.

  On the other hand, the viscosity pump mechanism (60) is also used in the oil supply operation in the scroll compressor (1) according to the first embodiment. Specifically, when the drive shaft (17) is driven to rotate, spiral grooves (65a, 65b, 65c) formed on the inner peripheral surface of the main oil supply passage (63) with respect to the outer peripheral surface of the fixed shaft (66) are formed. Rotate. Then, the lubricating oil is conveyed upward by the viscous pump mechanism (60) including the outer peripheral surface of the fixed shaft (66) and the spiral grooves (65a, 65b, 65c). Of the plurality of spiral grooves, the lubricant that has flowed through the lower bearing spiral groove (65a) flows to the lower bearing branch passage (64a), and the lubricant that has flowed through the upper bearing spiral groove (65b) The lubricating oil that flows to the upper bearing branch (64b) and the pin bearing spiral groove (65c) flows to the pin bearing branch (64c). The lubricating oil that has flowed through each branch path (64a, 64b, 64c) mainly lubricates the bearings (26d, 34, 44) in which the outflow ends of the respective branch paths (64a, 64b, 64c) open.

  As described above, the viscous pump mechanism (60) as described above is also used in the refueling operation of the scroll compressor (1). Thereby, even if it is a case where the above-mentioned differential pressure cannot be ensured enough, lubricating oil can be supplied to each sliding part using a viscous pump mechanism (60). In the scroll compressor (1) according to the first embodiment, since a plurality of spiral grooves (65a, 65b, 65c) are formed, for example, compared with a case where one spiral groove is formed. A sufficient amount of lubricating oil can be supplied to each sliding portion.

  In the first embodiment, the differential pressure and the viscous pump mechanism (60) are used to supply oil to each sliding portion. In this way, for example, when the drive shaft (17) rotates at a high speed and the amount of lubricating oil supplied by the viscous pump mechanism (60) increases, the differential pressure between the upper end and the lower end of the main oil supply passage (63) is reduced. By reducing the size, excessive supply of lubricating oil can be suppressed. That is, in the first embodiment, the supply amount of the lubricating oil can be changed by adjusting both the rotational speed and the differential pressure of the drive shaft (17).

  Further, the lubricating oil from the spiral grooves (65a, 65b, 65c) corresponding to the respective branch paths (64a, 64b, 64c) flows into the respective branch paths (64a, 64b, 64c). Thereby, lubricating oil can be reliably supplied to each branch path (64a, 64b, 64c). Moreover, as in Embodiment 1, the width of the spiral groove (65a, 65b, 65c) connected to each branch path (64a, 64b, 64c) is changed according to each branch path (64a, 64b, 64c). The flow rate of the lubricating oil flowing to each branch passage (64a, 64b, 64c) can be individually adjusted.

-Effect of Embodiment 1-
As described above, in the scroll compressor (1) according to the first embodiment, the spiral grooves (65a, 65b, 65c) formed on the inner peripheral surface of the main oil supply passage (63) and the fixed shaft (66) are provided. Lubricating oil can be supplied to each sliding part by the viscous pump mechanism (60) including. In this case, for example, even if the differential pressure between the upper end portion and the lower end portion of the main oil supply passage (63) is small and the lubricating oil cannot be pumped up due to the differential pressure, the viscous pump mechanism ( 60) makes it possible to reliably supply lubricating oil to each sliding part. In Embodiment 1, a sufficient amount of lubricating oil can be supplied to each sliding portion by the plurality of spiral grooves (65a, 65b, 65c).

  Moreover, in Embodiment 1, since the differential pressure and the viscous pump mechanism (60) are used to supply oil to each sliding portion, for example, when the oil supply by the viscous pump mechanism (60) is excessive, the differential pressure is increased. If it is made small, it can suppress that the amount of lubrication oil supply becomes excessive.

  In the first embodiment, each branch passage (64a, 64b, 64c) is supplied with lubricating oil from the spiral grooves (65a, 65b, 65c) corresponding to the respective branch passages (64a, 64b, 64c). Since it flows in, lubricating oil can be reliably supplied to each branch path (64a, 64b, 64c). Moreover, by changing the width of the spiral groove (65a, 65b, 65c) connected to each branch path (64a, 64b, 64c) for each branch path (64a, 64b, 64c), each branch path (64a, 64b, 64c, The amount of lubricating oil flowing to 64c) can be adjusted. In this way, the amount of lubricating oil supplied to each bearing part (26d, 34, 44) according to the bearing load of the bearing part (26d, 34, 44) corresponding to each branch path (64a, 64b, 64c) Can be adjusted respectively. In addition, since each branch path (64a, 64b, 64c) does not communicate with each other in the drive shaft (17), even if the amount of lubricating oil supplied to a certain branch path changes, another branch path The amount of lubricating oil supplied does not change. Therefore, a stable amount of lubricating oil can be supplied to each branch path (64a, 64b, 64c).

<< Embodiment 2 of the Invention >>
As shown in FIG. 5, the scroll compressor (1) of the second embodiment is different from the scroll compressor (1) of the first embodiment described above in the part where the spiral groove is formed. Specifically, in Embodiment 1, the spiral grooves (65a, 65b, 65c) are formed on the inner peripheral surface of the main oil supply passage (63), whereas in Embodiment 2, the spiral grooves (67a, 67b) are formed. , 67c) is formed on the outer peripheral surface of the fixed shaft (66). Hereinafter, differences from the first embodiment will be mainly described.

  The drive shaft (17) of the second embodiment is formed with an oil supply passage (62) having the same shape as that of the drive shaft (17) of the first embodiment. However, the spiral groove is not formed in the inner peripheral surface of the main oil supply passage (63) in the second embodiment, and the main oil supply passage (63) is formed in a cylindrical shape.

  A plurality of spiral grooves (67a, 67b, 67c) are formed on the outer peripheral surface of the fixed shaft (66) of the second embodiment. These spiral grooves (67a, 67b, 67c) are formed so as to extend from the lower end portion to the upper end portion of the fixed shaft (66). That is, all three spiral grooves (67a, 67b, 67c) extend upward from the lower end of the fixed shaft (66) so as to straddle all the inflow ends of the three branch paths (64a, 64b, 64c). ing. Each spiral groove (67a, 67b, 67c) is formed so as to extend while turning in the same direction as the rotation direction of the drive shaft (17) from the lower end portion to the upper end portion of the fixed shaft (66). The three spiral grooves (67a, 67b, 67c) are formed so that the widths thereof are substantially the same.

-Viscous pump mechanism-
The viscous pump mechanism (70) in the second embodiment includes an inner peripheral surface of the main oil supply passage (63) and a plurality of spiral grooves (67a, 67b, 67c) formed on the outer peripheral surface of the fixed shaft (66). ing. When the drive shaft (17) is rotated, the viscous pump mechanism (70) causes the inner peripheral surface of the main oil supply passage (63) to feed the lubricating oil in the spiral grooves (67a, 67b, 67c) to the spiral groove ( 67a, 67b, 67c), the lubricating oil between the spiral groove (67a, 67b, 67c) and the inner peripheral surface of the main oil supply passage (63) is conveyed upward by pushing upward.

-Lubrication operation to each sliding part by viscous pump mechanism-
As for the oil supply operation in the scroll compressor (1) according to the second embodiment, the differential pressure in the main oil supply passage (63) is used at the same time as in the case of the scroll compressor (1) according to the first embodiment. A viscous pump mechanism (70) is utilized. Since the oil supply using the differential pressure is the same as that of the first embodiment, the oil supply using the viscous pump mechanism (70) will be described here.

  In the scroll compressor (1) according to the second embodiment, when the drive shaft (17) is rotationally driven, the spiral groove (67a, 67b, 67c) formed on the outer peripheral surface of the fixed shaft (66) The inner peripheral surface of the oil supply passage (63) rotates. Then, the viscous oil rises through the helical grooves (67a, 67b, 67c) by the viscous pump mechanism (70).

  When the drive shaft (17) rotates, the three branch paths (64a, 64b, 64c) rotate with respect to the three spiral grooves (67a, 67b, 67c) together with the drive shaft (17) that is driven to rotate. As a result, each branch path (64a, 64b, 64c) intermittently communicates with all of the three spiral grooves (67a, 67b, 67c). Accordingly, the lubricating oil flowing through the spiral grooves (67a, 67b, 67c) intermittently flows into the branch paths (64a, 64b, 64c). The lubricating oil that has flowed through each branch passage (64a, 64b, 64c) lubricates each sliding portion, and then returns to the oil sump (13a) through the oil discharge passage (37).

-Effect of Embodiment 2-
As described above, in the scroll compressor (1) according to the second embodiment, the spiral grooves (67a, 67b, 67c) are formed on the outer peripheral surface of the fixed shaft (66). Both of these spiral grooves (67a, 67b, 67c) extend upward so as to straddle all the inflow ends of the plurality of branch paths (64a, 64b, 64c). As a result, the lubricating oil from all the spiral grooves (67a, 67b, 67c) can be supplied to all the branch paths (64a, 64b, 64c), which is sufficient for all the branch paths (64a, 64b, 64c). An amount of lubricating oil can be supplied.

-Other embodiments-
About each said embodiment, you may make it the following structures.

  In the first embodiment, the fixed shaft (66) is formed to extend to the vicinity of the upper end portion of the main oil supply passage (63). However, the present invention is not limited to this, and as shown in FIG. You may form so that it may extend to the lower end part vicinity of a path | route (63). Even with such a configuration, the lubricating oil can be supplied to the sliding portions through the main oil supply passage (63) and the branch passages (64a, 64b, 64c) by the viscous pump mechanism (60). In this case, as shown in FIG. 6, the terminal portion of the spiral groove (65a, 65b, 65c) formed on the inner peripheral surface of the main oil supply passage (63) extends at least to the vicinity of the upper end portion of the fixed shaft (66). What is necessary is just to form. Similarly, in the second embodiment, the fixed shaft (66) is formed so as to extend to the vicinity of the upper end of the main oil supply passage (63). However, the present invention is not limited to this, and the fixed shaft (66) is connected to the main oil supply passage (63). You may form so that it may extend to lower end vicinity.

  In the first embodiment, the outflow ends of the spiral grooves (65a, 65b, 65c) correspond to the inflow ends of the branch paths (64a, 64b, 64c). You don't have to. For example, the middle part in one spiral groove of the plurality of spiral grooves and the inflow end of the branch path may be connected.

  Further, in the first embodiment, by changing the width of each spiral groove (65a, 65b, 65c) for each branch path (64a, 64b, 64c), lubrication flowing to each branch path (64a, 64b, 64c) The amount of oil was adjusted, but this is not the case. For example, by changing the depth of the spiral groove (65a, 65b, 65c) or the inclination of each spiral groove (65a, 65b, 65c) within a range where the spiral grooves (65a, 65b, 65c) do not cross each other, It is also possible to adjust the amount of lubricating oil flowing to the passages (64a, 64b, 64c).

  Further, in each of the above embodiments, both the differential pressure and the viscous pump mechanism (60, 70) are used when performing the oil supply operation. However, this is not the only case, and only the viscous pump mechanism (60, 70) is used. Lubricating oil may be supplied to each sliding part by using. Moreover, you may supply lubricating oil to each sliding part using both a centrifugal pump and a viscous pump mechanism (60,70).

  In the second embodiment, all three spiral grooves (67a, 67b, 67c) are formed to extend upward so as to straddle all the inflow ends of the plurality of branch paths (64a, 64b, 64c). However, the present invention is not limited to this, and it is sufficient that at least one spiral groove is formed so as to straddle the inflow ends of two or more branch paths.

  In the second embodiment, three spiral grooves (67a, 67b, 67c) are formed. However, the present invention is not limited to this, and it is sufficient that at least two spiral grooves are formed.

  In each of the above embodiments, the scroll compressor (1) is targeted. However, the present invention is not limited to this, and a rotary compressor such as a rotary compressor or a rotary expander may be targeted.

  As described above, the present invention is useful for a rotary fluid machine such as a scroll compressor.

1 Scroll type compressor (rotary fluid mechanism)
10 Casing 13a Oil sump 15 Compression mechanism (fluid mechanism)
16 Electric motor (drive mechanism)
17 Drive shaft 62 Oil supply path 63 Main oil supply path 64a Lower bearing branch path (branch path)
64b Upper bearing branch (branch)
64c Pin bearing branch path (branch path)
65a Spiral groove for lower bearing (spiral groove)
65b Spiral groove for upper bearing (spiral groove)
65c Spiral groove for pin bearing (spiral groove)
66 Fixed shaft 67a, 67b, 67c Spiral groove

Claims (3)

A casing (10);
A drive mechanism (16) housed in the casing (10);
A drive shaft (17) rotated by the drive mechanism (16) and having one end disposed in an oil sump (13a) in the casing (10);
A fluid mechanism (15) driven by the drive shaft (17) to compress or expand the fluid;
A main oil supply passage (63) extending from one end of the drive shaft (17) toward the other end, and an oil supply passage including at least one branch passage (64a, 64b, 64c) branched from the main oil supply passage (63). (62)
A fixed shaft (66) fixed to the casing (10) and inserted through the main oil supply passage (63),
On the inner peripheral surface of the main oil supply passage (63) or the outer peripheral surface of the fixed shaft (66), a plurality of spiral grooves (65a, 65h) extending spirally from one end of the drive shaft (17) toward the other end. 65b, 65c, 67a, 67b, 67c) is formed. In claim 1,
A plurality of the branch paths (64a, 64b, 64c) are formed on the drive shaft (17),
The plurality of spiral grooves (65a, 65b, 65c) are connected to the inflow ends of the respective branch paths (64a, 64b, 64c) corresponding to the outflow ends of the spiral grooves (65a, 65b, 65c), respectively. Further, the rotary fluid machine is formed on the inner peripheral surface of the main oil supply passage (63). In claim 1,
A plurality of the branch paths (64a, 64b, 64c) are formed on the drive shaft (17),
The plurality of spiral grooves (67a, 67b, 67c) are formed on the outer peripheral surface of the fixed shaft (66),
At least one of the plurality of spiral grooves (67a, 67b, 67c) extends so as to straddle the inflow ends of the two or more branch paths (64a, 64b, 64c). Fluid machinery.

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