JP2009275698A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric compressor capable of maintaining proper lubrication of a bearing even when the number of revolution of a shaft is increased. <P>SOLUTION: The compressor is provided with: a housing 2; a compression mechanism part 4 arranged in the housing 2; the shaft 30 rotated/driven and rotating/driving the compression mechanism part 4; and a first bearing 13 and a second bearing 14 for rotatably supporting the shaft 30. The shaft 30 is provided with a main oil feeding passage 31 extending in an axial direction in the shaft 30; a first sub-oil feeding passage and a second sub-oil feeding passage 34 penetrated/extended to a sidewall of the shaft 30 in order to lubricate the first bearing 13 and the second bearing 14 respectively; and lubricant distribution members 35, 135 provided on the main oil feeding passage 31. The lubricant distribution member is provided with branch parts 40, 140 for branching the lubricant circulated through the main oil feeding passage 31 toward the first sub-oil feeding passage 33 and the second sub-oil feeding passage 34. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a compressor.

  The compressor includes a sealed casing, a shaft, a compression mechanism connected to the shaft, a main bearing and a secondary bearing that rotatably support the shaft, and an oil separator that separates lubricating oil from the refrigerant. Yes. Patent Document 1 describes such a compressor, and a shaft of the compressor penetrates a shaft side wall in a radial direction in order to supply oil to an axially penetrating oil passage and a main bearing and a sub bearing. Two sub oil supply passages (radial holes). Lubricating oil is supplied from a high-pressure oil storage chamber provided below the oil separator, flows from one end of the shaft closer to the compression mechanism into the lubricating oil passage, and enters the two auxiliary oil supply passages at a predetermined ratio. It is distributed and flows. The lubricating oil supplied from the high-pressure oil storage chamber usually contains a refrigerant, and flows into the shaft as a gas-liquid two-phase fluid in which the refrigerant is foamed under reduced pressure.

JP 2007-321588 A

  In a compressor, it is required that proper lubrication with respect to the bearing is maintained regardless of increase / decrease in the rotation speed of the shaft. However, in the compressor shown in Patent Document 1, when the rotation speed of the shaft increases, The distribution ratio of the lubricating oil to the upstream and downstream auxiliary oil supply passages changes so that the lubricating oil flowing into the auxiliary oil supply passages increases, and as a result, the downstream secondary bearings may become insufficiently lubricated. This is because when the shaft rotates, the lubricating oil containing the refrigerant is separated into a gas phase refrigerant and a liquid phase lubricating oil at the central portion and the peripheral portion of the shaft main oil supply passage, respectively. At high speed, the flow to the first auxiliary oil passage on the upstream side that opens to the side wall of the shaft increases the proportion of liquid lubricating oil that is susceptible to centrifugal force, and as a result, the liquid contained in the fluid that flows downstream The reason for this is that the ratio of the lubricating oil decreases.

  The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to provide a compressor capable of maintaining proper lubrication of a bearing even when the number of rotations of a shaft increases.

  The present invention provides a compressor described in each of the claims as technical means for achieving the above object.

  According to the first aspect of the present invention, the housing (2), the compression mechanism portion (4) disposed in the housing (2), and the rotation mechanism is driven to rotate the compression mechanism portion (4). A compressor comprising a shaft (30), and a first bearing (13) and a second bearing (14) that rotatably support the shaft (30), wherein the shaft (30) is the shaft (30). ) A first oil supply passage (31) extending in the axial direction in the interior of the shaft (30) and through the side wall of the shaft (30) for lubricating the first bearing (13) and the second bearing (14), respectively. The auxiliary oil supply passage (33) and the second auxiliary oil supply passage (34), and the lubricating oil distribution member (35, 135, 235) provided in the main oil supply passage (31), the lubricating oil distribution member, Lubricating oil flowing through the main oil supply passage (31) is supplied to the first sub oil supply passage (3 ) And is characterized in further comprising a branch portion (40, 140) for branching toward the second sub-supply passage (34).

  According to the first aspect of the present invention, the lubricating oil flowing to the first and second auxiliary oil supply passages (33; 34) is branched at one branch portion (40, 140), so that the gas-liquid ratio is substantially equal to each other. As a result, even when the rotational speed of the shaft (30) increases, the distribution ratio of the lubricating oil supplied to the first and second auxiliary oil supply passages is maintained substantially constant, and the bearings (13, 14). The proper lubrication can be maintained.

  The invention according to claim 2 is the invention according to claim 1, wherein the lubricating oil distribution means (35, 235) is provided in the main oil supply passage (31) and is provided in the main oil supply passage (31). A third oil supply passage (36, 236) is formed, and an outlet of the third oil supply passage (36, 236) is between the first auxiliary oil supply passage (33) and the second auxiliary oil supply passage (34) in the axial direction. It is characterized by being located.

  As a result, the lubricating oil flowing to the first auxiliary oil passage (33) and the second auxiliary oil passage (34) is formed between the first auxiliary oil passage (33) and the second auxiliary oil passage (34). Since the branch portion (40) is branched from the lubricating oil in the common third oil supply passage, they have substantially the same gas-liquid ratio, and as a result, the effects described above can be obtained. Further, various distribution ratios can be obtained by changing the position of the outlet of the third oil supply passage (36, 236).

  The lubricating oil distribution member (35, 235) according to the second aspect of the present invention preferably includes a large-diameter shaft portion (35a) that is fitted and fixed in the main oil supply passage (31), and the large-diameter portion. It is formed in a stepped columnar shape including a small diameter shaft portion (35b) having a smaller diameter than the shaft portion (35a).

  According to a fourth aspect of the present invention, in the first aspect of the present invention, the lubricating oil distribution member (135) has an outer peripheral surface fixed by being inserted into the main oil supply passage (31) of the shaft (30). The substantially cylindrical lubricating oil distribution member (135) has an axial flow path (137) formed coaxially with the rotation axis (Ar) of the shaft (30), and the shaft A first branch path (138) and a second branch path (139) branched in the radial direction at the same position (140) in the axial direction in the directional flow path (137) are formed, and the first branch is formed. The lubricating oil flowing through the passage (138) is led to the first sub oil supply passage (33), and the lubricating oil flowing through the second branch passage (139) is led to the second sub oil supply passage. .

  As a result, the lubricating oil flowing to the first auxiliary oil passage (33) and the second auxiliary oil passage (34) is branched from the common lubricating oil at the same position (140), and therefore has substantially the same gas-liquid ratio. As a result, even when the rotational speed of the shaft (30) increases, the distribution ratio of the lubricating oil supplied to the first and second auxiliary oil supply passages is maintained substantially constant, and the bearings (13, 14) Proper lubrication can be maintained.

  The invention according to claim 5 is the invention according to claim 4, wherein the downstream portion (31d) of the shaft (30) is smaller in diameter than the upstream portion (31u) of the lubricating oil distribution member. It is characterized by. Positioning the lubricating oil distribution member (135) when it is fixed is facilitated by bringing the lubricating oil distribution member (135) into contact with a step formed in the main oil supply passage. It is also suitable when it is desired to reduce the flow resistance based on the centrifugal force acting on the lubricating oil flowing through the downstream portion (31d).

  The invention according to claim 6 is the invention according to claim 3, wherein the compressor further comprises a flow path area reducing member (41) extending in the axial direction in the main oil supply passage (31), At least a part of the flow path leading from the outlet of the third oil supply path (36) to the second sub oil supply path (34) is the outer peripheral surface of the flow path area reducing member (41) and the inner peripheral surface of the main oil supply path (31). It is characterized by being formed between.

  By comprising in this way, lubricating oil becomes easier to flow into the 2nd sub oil supply path (34) than the case of the invention of Claim 1. This is because the gas flow velocity is increased and the annular oil phase is driven first, because the flow passage cross-sectional area leading to the second sub oil supply passage (34) is reduced by the flow passage area reduction member (41). It is conceivable that the shearing force at the gas-liquid interface, which is a force, increases, and secondly, the flow mode in the main oil supply passage (31) changes from an annular flow to a slag flow.

  According to a ninth aspect of the present invention, in the compressor according to the third aspect, the small-diameter shaft portion (235b) of the lubricating oil distribution member (235) is a pipe-shaped portion in which the third oil supply passage (236) is formed ( 235b1) and a solid portion (235b2) extending from the end of the third oil supply passage (236) to the second sub oil supply passage (34) side, and from the outlet (236d1, 236d2) of the third oil supply passage (236). At least a part of the flow path leading to the two sub oil supply passages (34) is formed between the outer peripheral surface of the solid portion (235b2) and the inner peripheral surface of the main oil supply passage (31). It is.

  Thus, the invention described in claim 9 operates in the same manner as the invention described in claim 6, and the same effect can be realized.

  In the scroll-type electric compressor according to claims 12 and 13, the main bearing and the sub-bearing are arranged with the motor portion interposed therebetween, but even if the distance between the bearings is relatively long, the oil can be reliably supplied. The present invention is more effective.

  According to the fourteenth aspect, the refrigerant is CO2 gas, and the pressure of the CO2 refrigerant is higher than that of a general refrigerant, and therefore the solubility of the refrigerant in the lubricating oil is high. The gas ratio in the decompressed lubricating oil is high, the frequency of the gas-liquid two-phase state is high, and the distribution failure is more likely to occur, and the present invention is more effective.

  In addition, the code | symbol in the bracket | parenthesis of each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

1 is a longitudinal sectional view of an electric compressor according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the shaft of the electric compressor by 1st Embodiment. It is a longitudinal cross-sectional view of the shaft of the electric compressor by the 2nd Embodiment of this invention. It is a partial detail longitudinal cross-sectional view of the shaft of the electric compressor by 2nd Embodiment. It is a longitudinal cross-sectional view of the shaft of the electric compressor by the modification of the 2nd Embodiment of this invention. It is a partial detail longitudinal cross-sectional view of the shaft of the electric compressor by the modification of 2nd Embodiment. It is a longitudinal cross-sectional view of the shaft of the electric compressor by the 3rd Embodiment of this invention. It is a cross-sectional view by the AA cut line of FIG. 7 of the shaft of the electric compressor by 3rd Embodiment. It is a longitudinal cross-sectional view of the shaft of the electric compressor by 4th Embodiment. It is a longitudinal cross-sectional view of the shaft of the electric compressor by 5th Embodiment. It is a longitudinal cross-sectional view of the electric compressor by the example of a change of 4th Embodiment.

(First embodiment)
Hereinafter, a compressor according to a preferred first embodiment of the present invention will be described with reference to the drawings. First, the overall structure of the compressor will be described with reference to FIG. A compressor 1 in FIG. 1 is a scroll-type electric compressor, and an electric motor unit 3 and a compression mechanism unit 4 are accommodated in a sealed container 2 formed in a substantially cylindrical shape, and refrigerant from an external refrigerant circuit is received. After compression in the compression mechanism section 4, the oil separator 5 integrally attached to one end thereof separates the lubricating oil from the refrigerant and sends the refrigerant to an external refrigerant circuit, while the separated lubricating oil is sent to the oil separator 5. Is stored in a high-pressure oil storage chamber 6 provided below, and the stored lubricating oil is returned to the compression mechanism portion 4 and a movable portion such as a bearing described later. In the present embodiment, CO2 is used as the refrigerant. Of course, refrigerants having other compositions can also be applied to the compressor according to the present invention.

  The hermetic container 2 of the compressor is formed of a cylindrical case 7 and a cylindrical first end member 8 and a second end member 9 which are coupled to the left end side and the right end side in FIG. ing. Further, a substantially disk-shaped oil storage chamber wall member 10 is coupled to form a space for the high-pressure oil storage chamber 6 inside the second end member 9 on the right end side. The sealed container 2 forms a so-called internal low-pressure container in which the pressure therein is lower than the refrigerant discharge pressure.

  The electric motor unit 3 includes a stator 11 fixed to the inner peripheral surface of the cylindrical case 7 and a rotor 12, and the rotor 12 is fixed to a shaft 30.

  As shown in FIG. 2 which is a longitudinal sectional view of the shaft 30, the shaft 30 is formed in a pipe shape having a main oil supply passage 31 therein, and is eccentric to the right end (one end) side of the drawing. A flange-shaped flange 32a is provided. One end of the shaft 30 is provided by a main bearing 13 provided on a bearing member 16 to be described later, and the other end is provided by a sub-bearing 14 fixed to a disk-like support member 15 provided near the left end of the cylindrical case 7. It is supported horizontally.

  The compression mechanism portion 4 is disposed so as to face the movable scroll 17, the bearing member 16 fixed to the cylindrical case 7 at a position adjacent to the motor portion 3, the movable scroll 17 revolving by the crank portion 32 of the shaft 30. A fixed scroll 19 which is fixed to the cylindrical case 7 and forms a working chamber 18 together with the movable scroll 17 is provided.

  The bearing member 16 has a three-stage cylindrical shape in which the diameter gradually increases from the motor unit 3 side to the fixed scroll 19 side, and the small-diameter cylindrical unit 16a close to the motor unit 3 constitutes the main bearing 13; The medium-diameter cylindrical portion 16b adjacent to the small-diameter cylindrical portion 16a accommodates the crank portion 32, and the large-diameter cylindrical portion 16c close to the fixed scroll 19 accommodates the movable scroll 17 therein and is formed on the inner peripheral surface of the cylindrical case 7. It is fixed by fixing means such as shrink fitting.

  Each of the fixed scroll 19 and the movable scroll 17 has a spiral groove, and the volume of the working chambers 18 formed by the engagement of the grooves is reduced to reduce the volume of the spiral groove of the fixed scroll 19. The refrigerant supplied to the suction chamber (not shown) communicating with the outermost peripheral side is configured to be compressed. A discharge chamber 21 connected to the working chamber 18 of the compression mechanism unit 4 through a discharge port 20 and the oil separator 5 are connected by a discharge pipe 22.

  An oil feed pipe 23 extending from the bottom of the high-pressure oil storage chamber 6 is connected to a lubricating oil return passage 24 formed in the lower side of the fixed scroll 19 in the figure. The lubricating oil return passage 24 is movable with the fixed scroll 19. It leads to the sliding interface with the scroll 17. The movable scroll 17 has a lubricating oil passage 25 having one end continuous with the lubricating oil return passage 24 inside the movable scroll 17, and the other end of the lubricating oil passage 25 is connected to one end of the shaft 30 and the movable scroll 17. It opens in the clearance gap 26 between the boss | hub parts.

  Next, the shaft 30 will be described with reference to FIG. The shaft 30 has a main oil supply passage 31 formed as a circular center hole coaxial with the rotation axis Ar thereof. The main oil supply passage 31 has an inlet 31a on one end (the right end in FIG. 2) side of the shaft 30. Have. The shaft 30 includes a first sub oil supply passage 33 and a second sub oil supply passage 34 that extend through the side walls of the shaft 30 to lubricate the main bearing 13 and the sub bearing 14, respectively. The first sub oil supply passage 33 has a small hole portion 33a passing through the side wall of the shaft 30 in the radial direction from the main oil supply passage 31 toward the bearing surface of the main bearing 13, and the outer peripheral surface of the shaft 30 in the axial direction on the right side of the figure. It is formed from the groove part 33b extended toward the direction. The second sub oil supply passage 34 is formed of a small hole that penetrates the side wall of the shaft 30 in the radial direction toward the bearing surface of the sub bearing 14. Further, in the present embodiment, the first sub oil supply passage 33 and the second sub oil supply passage 34 are provided at angular positions facing each other at 180 degrees, but may be provided at other arbitrary angular positions. .

  The shaft 30 includes a lubricating oil distribution member 35 that is fitted and fixed in the main oil supply passage 31, and the main oil supply passage 31 is separated from the upstream portion 31 u and the downstream portion 31 d by the lubricating oil distribution member 35. It is divided into. In the first embodiment, the lubricating oil distribution member 35 is formed in a stepped columnar shape including a large-diameter shaft portion 35a and a small-diameter shaft portion 35b coaxial therewith, and is formed so as to penetrate along the rotation axis Ar. The third oil supply passage 36 is provided. In the present embodiment, the third oil supply passage 36 is formed by a large-diameter hole 36a inside the large-diameter shaft portion 35a and a small-diameter hole 36b inside the small-diameter shaft portion 35b. The lubricating oil distribution member 35 is inserted into the main oil supply passage 31 of the shaft 30 in such a manner that the large diameter shaft portion 35a is closer to the inlet 31a of the main oil supply passage 31 than the small diameter shaft portion 35b, and is attached to the shaft 30 by brazing or the like. It is fixed. Accordingly, the inlet 36c of the third oil supply passage 36 opens to the end surface of the large diameter shaft portion 35a, and the outlet 36d opens to the end surface of the small diameter shaft portion 35b. The lubricating oil distribution member 35 includes an outlet 36d of the third oil supply path 36 between the first auxiliary oil supply path 33 and the second auxiliary oil supply path 34 that are spaced apart in the axial direction, and the first auxiliary oil supply. The passage 33 is disposed so as to open to the downstream portion 31 d of the main oil supply passage 31.

  Next, how the lubricating oil flows to the main bearing 13 and the sub bearing 14 will be described. Usually, the lubricant contains a refrigerant, but in this specification, the lubricant containing the refrigerant is also referred to as “lubricant”. Further, the lubricating oil flows from the high pressure oil storage chamber 6 toward each bearing based on a pressure difference between the high pressure oil storage chamber 6 and a relatively low pressure space in which each bearing is disposed.

  When the lubricating oil flows through the lubricating oil passage 25 of the movable scroll 17, the movable scroll 17 undergoes a revolving motion, whereby the pressure is intermittently reduced, and as a result, the refrigerant contained in the lubricating oil is decompressed and foamed, and the liquid-phase lubricating oil In the gas-liquid two-phase state in which the gas-phase refrigerant is mixed, it enters the upstream portion 31u of the main oil supply passage 31 from the inlet 31a on one end side of the shaft 30 as indicated by the arrow in FIG. The lubricating oil flowing into the main oil supply passage 31 of the shaft 30 flows into the third oil supply passage 36 of the lubricating oil distribution member 35 and is discharged from the outlet 36d to the downstream portion 31d of the main oil supply passage 31 of the shaft 30. Since the outlet 36d of the third oil supply path 36 is located between the first auxiliary oil supply path 33 and the second auxiliary oil supply path 34, the first auxiliary oil supply path is located immediately downstream of the outlet 36d of the third oil supply path 36. A branching portion 40 of the flow toward 33 and the flow toward the second sub oil supply passage 34 is formed. The lubricating oil that has flowed into the first sub oil supply passage 33 lubricates the main bearing 13, and the lubricating oil that has flowed into the second sub oil supply passage 34 lubricates the sub bearing 14.

  At this time, the respective lubricating oils flowing to the first and second sub oil supply passages 34 are branched immediately from the lubricating oil that has passed through the common third oil supply passage, and therefore are substantially equal to each other regardless of the rotational speed. Therefore, the distribution ratio of the lubricating oil supplied to the first sub oil supply passage 33 and the second sub oil supply passage 34 is kept substantially constant even when the rotation speed of the shaft 30 is increased. It is.

(Second Embodiment)
Next, an electric compressor according to a second embodiment of the present invention will be described with reference to FIG. 3 which is a longitudinal sectional view of the shaft 30 and the lubricating oil distribution member 135 and FIG. 4 which is an enlarged detailed view thereof. In the electric compressor of this embodiment, the lubricating oil distribution member 135 is different from that of the electric compressor of the first embodiment.

  The lubricating oil distribution member 135 in the second embodiment is formed in a substantially cylindrical shape having an outer diameter that fits into the main oil supply passage 31 of the shaft 30. Inside the lubricating oil distribution member 135 is an axial flow path 137 having a circular cross section extending in the axial direction from the right end of FIG. 4 to the middle along the central axis Ax coinciding with the rotational axis Ar of the shaft 30, and the axial direction Near the end of the flow path 137, a first branch path 138 and a second branch path 139 are formed in the axial flow path 137 so as to intersect with each other in the radial direction from above and below. The first branch path 138 includes a first small-diameter channel 138a having a small diameter extending in the radial direction and a first large-diameter channel 138b having a relatively large diameter. The second branch path 139 includes a second small-diameter channel 139a having a small diameter extending in the radial direction and a groove-shaped channel 139b extending on the outer peripheral portion of the lubricating oil distribution member 35 toward the downstream side in the axial direction. In addition, the third oil supply path 136 is configured by the axial flow path 137, the first branch path 138, and the second branch path 139, and the inlet 136 c of the third oil supply path 136 coincides with the inlet of the axial flow path 137. Since the third oil supply passage 136 is formed in this way, a flow branching portion 140 is formed near the end of the axial flow 137.

  In the lubricating oil distribution member 135 in the second embodiment, the first branch passage 138 is directly connected to the first sub oil supply passage 33 of the shaft 30, and the groove-like passage 139 b of the second branch passage 139 is the main shaft 30. It is fixed to the shaft 30 so as to open to the downstream portion 31 d of the oil supply passage 31.

  In the second embodiment, the lubricating oil that has flowed from the inlet 31a on one end side of the shaft 30 into the upstream portion 31u of the main oil supply passage 31 flows in the axial direction of the distribution member 135 as shown by the arrows in the figure. It flows into the path 137 and branches into the first branch path 138 and the second branch path 139 at the branching section 140. The lubricating oil branched to the first branch passage 138 flows into the first sub oil supply passage 33 of the shaft 30 to lubricate the main bearing 13, and the lubricating oil branched to the second branch passage 139 passes through the second branch passage 139. The sub-bearing 14 is lubricated by flowing from the groove-shaped flow path 139 b through the downstream portion 31 d of the main oil supply passage 31 of the shaft 30 to the second sub oil supply passage 34.

  The fluids flowing to the first and second branch paths 138 and 139 are branched at one branch section 140 in the axial flow path 137, that is, branched at a branch section at the same axial position and the same inner diameter. Therefore, the fluids have the same gas-liquid ratio and are not affected by the rotation of the shaft 30. Thus, the distribution ratio is maintained substantially constant even when the rotation speed of the shaft is increased.

(Modification of the second embodiment)
Next, a modification of the second embodiment will be described with reference to FIG. 5 which is a longitudinal sectional view of the shaft 30 and the lubricating oil distribution member 135 and FIG. 6 which is an enlarged detailed view thereof. In this modification, the main oil supply passage 31 of the shaft 30 is formed such that the inner diameter of the downstream portion 31d is narrower than the inner diameter of the upstream portion 31u, and the lubricating oil distribution member 135 changes the inner diameter of the main oil supply passage 31. The left end (downstream end) of the lubricating oil distribution member 135 is in contact with the stepped portion and fixed to the shaft 30. Accordingly, the lubricating oil distribution member 135 of this modification is provided with a recess 135a at the left end thereof, which is different from the lubricating oil distribution member 135 in the second embodiment described above. The recess 135a is formed in such a manner that the outlet of the groove-shaped channel 139b of the second branch 139 is enlarged.

(Third embodiment)
A third embodiment will be described with reference to FIG. 7 which is a longitudinal sectional view of the shaft 230 and FIG. 8 which is a transverse sectional view taken along the line AA of FIG. The shaft 230 of the electric compressor of this embodiment does not include a lubricating oil distribution member. Further, the central axis Ax of the main oil supply passage 231 of the shaft 230 is formed to be eccentric from the rotation axis Ar of the shaft 230 by ε in the direction of the second auxiliary oil supply passage 234. Moreover, in this embodiment, the 1st sub oil supply path 233 and the 2nd sub oil supply path 234 are provided in the angular position which mutually opposes at about 180 degree | times.

  In this embodiment, when the shaft rotates, the effect of the centrifugal force causes the lubricating oil to hardly flow from the inlet 231a of the main oil supply passage 231 to the second auxiliary oil supply passage 234, and in the radial direction, the second auxiliary oil supply passage 234 is formed. There is an effect that the lubricating oil increases on the wall surface on the opening side, but these two effects are offset to suppress the change in the distribution ratio between the first sub oil supply path 233 and the second sub oil supply path 234. Can do.

(Fourth embodiment)
Next, an electric compressor according to a fourth embodiment of the present invention will be described with reference to FIG. 9 which is a longitudinal sectional view of the shaft 30 and the lubricating oil distribution member 35. The electric compressor of this embodiment further includes a flow passage area reducing member 41 that extends coaxially with the lubricating oil distribution member 35 in the main oil supply passage 31 of the shaft 30. Although it is different from the machine, the configuration of other parts is the same.

  The flow path area reducing member 41 in the present embodiment is formed in a substantially cylindrical shape, and most of the flow path area reducing member 41 has an outer diameter equal to the outer diameter of the small-diameter shaft portion 35b of the lubricating oil distribution member 35. Only the end on the left side of FIG. The flow path area reducing member 41 is fixed to the shaft 30 by brazing or the like at the enlarged diameter portion at the left end portion thereof. Further, the lubricating oil that has exited the outlet 36d of the third oil supply passage 36 of the lubricating oil distribution member 35 is branched at the branching portion 40 between the other end of the flow path area reducing member 41 and the end of the small diameter shaft portion 35b. Thus, a predetermined space is formed so as to flow toward the first auxiliary oil passage 33 and the second auxiliary oil passage 34, respectively. As a result, the flow reaching the second sub oil supply passage 34 flows between the outer peripheral surface of the flow path area reducing member 41 and the inner peripheral surface of the main oil supply passage 31.

  With this configuration, it can be expected that the lubricating oil will flow more easily into the second auxiliary oil supply passage. In fact, the inventor of the present application is directed to the second auxiliary oil supply passage 34 in the electric compressor thus configured. It has been experimentally confirmed that the supply of the lubricating oil is sufficiently maintained even when the shaft 30 rotates at a high speed. This is because the flow cross-sectional area leading to the second sub oil supply passage 34 is reduced by the flow passage area reducing member 41, and firstly, the gas-liquid interface that increases the gas flow velocity and becomes the driving force of the annular oil phase. The second factor is considered to be the increase in the shearing force at the first and second, and the change in the flow pattern in the oil supply passage from the annular flow to the slag flow.

  In the fourth embodiment, the outer diameter of the flow path area reducing member 41 and the outer diameter of the small-diameter shaft portion 35b of the lubricating oil distribution member 35 are the same, but they may be different from each other.

  The flow path area reducing member 41 is a separate member from the shaft 30 in the fourth embodiment, but may be formed integrally with the shaft 30.

(Fifth embodiment)
Next, an electric compressor according to a fifth embodiment of the present invention will be described with reference to FIG. 10 which is a longitudinal sectional view of the shaft and the lubricating oil distribution member 235. The electric compressor of this embodiment is different from the electric compressor of the fourth embodiment in that the lubricating oil distribution member is integrally provided with the flow path area reducing member in the fourth embodiment, but other configurations are the same. It is the same as that of the electric compressor of 4th Embodiment.

  The lubricating oil distribution member 235 according to the fifth embodiment is formed in a stepped columnar shape including a large-diameter shaft portion 235a, a small-diameter shaft portion 235b coaxial therewith, and a large-diameter fixed end portion 235c on the left end side in FIG. Has been. The small-diameter shaft portion 235b extends to the left side in FIG. 10, that is, to the second sub oil supply passage 34 side from the pipe-like portion 235b1 including the third oil supply passage 236 formed along the rotation axis Ar. And a solid portion 235b2. In this embodiment, the third oil supply path 236 is formed by a large diameter hole 236a inside the large diameter shaft portion 35a and a small diameter hole 236b inside the pipe-shaped portion 235b1 of the small diameter shaft portion 235b. Near the end of the path 236, two outlets, that is, first outlets 236d1 and 236d2, are formed through the wall surface of the pipe-shaped portion 235b1 of the small diameter shaft portion 235b in the radial direction. The lubricating oil distribution member 235 is fixed to the shaft 30 by brazing or the like at the large diameter shaft portion 235a and the large diameter fixed end portion 235c.

  Also in the fifth embodiment, as in the case of the first embodiment, the lubricating oil is supplied from the upstream portion 31u of the main oil supply passage 31 to the first lubricating oil distribution member 235 as shown by the arrows in FIG. 3 flows into the oil supply passage 236 and branches in front of the outlets 236d1 and d2, and flows toward the first auxiliary oil supply passage 33 and the second auxiliary oil supply passage 34 are formed. However, it is considered that the flow is branched toward the first sub oil supply passage 33 and the second sub oil supply passage 34 also on the outer sides of the outlets 236d1 and d2.

  As described above, the cross-sectional area of the flow path toward the second sub oil supply path 34 is reduced by the solid portion 235b2, so that the lubricating oil can easily flow into the second sub oil supply path as in the case of the fourth embodiment.

  In the fifth embodiment, the large-diameter shaft portion 235c is provided at the left end of FIG. 10 of the lubricating oil distribution member 235, but the lubricating oil distribution member 235 may not include the large-diameter shaft portion 235c. In that case, the lubricating oil distribution member is fixed to the shaft 30 only by the large-diameter shaft portion 235a.

  In the fifth embodiment, the solid portion 235b2 of the small-diameter shaft portion 235b of the lubricating oil distribution member 235 extends from the end of the third oil supply path 236 until reaching the second sub oil supply path 34. It does not have to reach to. In other words, the downstream portion 31d of the main oil supply passage 31 may have a portion without the solid portion 235b2.

  In the lubricating oil distribution member 235 shown in FIG. 10, the outer diameter of the pipe-shaped portion 235b1 and the outer diameter of the solid portion 235b2 of the small-diameter shaft portion are the same, but they may be different from each other.

In the fifth embodiment, two outlets, that is, first outlets 236d1 and 236d2 are provided in the third oil supply path 236, but the number of outlets may be one or three or more.
(Other embodiments)
In the embodiment described above, the shaft is supported by two bearings, ie, a main bearing and a sub-bearing. However, in the present invention, it is obvious that the shaft may be supported by three or more bearings. Let's go. In this case, the additional bearing pivotally supports the shaft between the main bearing and the secondary bearing, and an additional secondary oil supply passage is provided on the side wall of the shaft corresponding to the additional bearing.

  Further, the compressor according to the above-described embodiment was a hermetic horizontal scroll type electric compression, but the embodiment of the present invention is an open type compressor, a compressor having a vertical shaft, a swash plate type compressor, Or the compressor which does not include an electric motor part is also possible.

  As an example of the vertical type compressor having the vertical shaft, FIG. 11 shows a modified example in which the electric compressor of the fourth embodiment including the flow path area reducing member 41 is changed to the vertical type. In the vertical type electric compressor of FIG. 11, the oil separator 5 is disposed on the side of the cylindrical case 7 of the hermetic container 2, and the oil storage part on the low pressure side is on the upper surface of the large-diameter cylindrical part 16 c of the bearing member 16. It is different from a horizontal (horizontal) type electric compressor in that it is formed, but the large size of the sealed container 2, the electric motor unit 3, the compression mechanism unit 4, the shaft 30, the distribution member 35, the flow path area reducing member 41, etc. The portion is the same as that of the electric compressor according to the fourth embodiment of the horizontal type. In the case of the vertical type electric compressor, gravity acts on the lubricating oil flowing upward in the main oil supply path 31 toward the second sub oil supply path 34, so that the first is compared to the horizontal type. Although the conditions for securing the amount of lubricating oil to the second auxiliary oil passage 34 become more severe, according to the present invention, it is possible to ensure the amount of lubricating oil to the second auxiliary oil passage 34 even in the vertical installation type where the conditions are more severe. it can.

30 Shaft 31 Main oil supply path 31a Inlet 31u Upstream part 31d Downstream part 33 First sub oil supply path 34 Second sub oil supply path 35 Lubricating oil distribution member 36 Third oil supply path 36d Third oil supply path outlet 40 Branch part

Claims (14)

A housing (2);
A compression mechanism (4) disposed in the housing (2);
A shaft (30) that is rotationally driven to rotationally drive the compression mechanism (4);
A compressor comprising a first bearing (13) and a second bearing (14) for rotatably supporting the shaft (30),
The shaft (30) includes a main oil passage (31) extending in the axial direction within the shaft (30), the first bearing (13), and the second bearing (14) to lubricate the shaft (30). 30) a first sub oil supply passage (33) and a second sub oil supply passage (34) extending through the side wall, and a lubricating oil distribution member (35, 135, 235) provided in the main oil supply passage (31). And
The lubricating oil distribution member branches a lubricating oil flowing through the main oil supply passage (31) toward the first sub oil supply passage (33) and the second sub oil supply passage (34) (40, 140), the compressor. The lubricating oil distribution member (35, 235) is provided in the main oil supply passage (31) to form a third oil supply passage (36, 236) in the main oil supply passage (31),
The outlet of the third oil supply passage (36, 236) is located between the first sub oil supply passage (33) and the second sub oil supply passage (34) in the axial direction. The compressor described.   The lubricating oil distribution member (35, 235) includes a large-diameter shaft portion (35a, 235a) that is fitted and fixed in the main oil supply passage (31), and the large-diameter shaft portion (35a, 235a). The compressor according to claim 2, wherein the compressor is formed in a stepped columnar shape including small-diameter shaft portions (35b, 235b). The lubricating oil distribution member (135) is formed in a substantially cylindrical shape having an outer peripheral surface that is fitted and fixed in the main oil supply passage (31) of the shaft (30),
The substantially cylindrical lubricating oil distribution member (135) includes an axial flow path (137) formed coaxially with the rotation axis (Ar) of the shaft (30), and the axial flow path (137). A first branch path (138) and a second branch path (139) branched in the radial direction at the same position (140) in the axial direction are formed by being drilled,
Lubricating oil flowing through the first branch passage (138) is guided to the first sub oil supply passage (33), and lubricating oil flowing through the second branch passage (139) is guided to the second sub oil supply passage. The compressor according to claim 1, wherein   The compressor according to claim 4, characterized in that, in the shaft (30), the downstream part (31d) of the lubricating oil distribution member has a smaller diameter than the upstream part (31u).   The compressor according to claim 3, further comprising a flow passage area reducing member (41) extending in the axial direction in the main oil supply passage (31), wherein the outlet of the third oil supply passage (36) is provided. At least part of the flow path leading to the second sub oil supply passage (34) is formed between the outer peripheral surface of the flow passage area reducing member (41) and the inner peripheral surface of the main oil supply passage (31). The compressor according to claim 3, wherein   The compressor according to claim 6, wherein an outer diameter of the flow path area reducing member (41) is equal to an outer diameter of the small-diameter shaft portion (35b) of the lubricating oil distribution member (35).   The compressor according to claim 6, wherein the outer diameter of the flow path area reducing member (41) is different from the outer diameter of the small-diameter shaft portion (35b) of the lubricating oil distribution member (35). The small-diameter shaft portion (235b) of the lubricating oil distribution member (235) has a pipe-like portion (235b1) in which the third oil supply passage (236) is formed and a second sub-portion from the end of the third oil supply passage (236). It consists of a solid part (235b2) extending to the oil supply passage (34) side,
At least part of the flow path leading from the outlet (236d1, 236d2) of the third oil supply path (236) to the second sub oil supply path (34) is the outer peripheral surface of the solid part (235b2) and the main oil supply path. The compressor according to claim 3, wherein the compressor is formed between the inner peripheral surface of (31).   The outer diameter of the solid portion (235b2) of the small-diameter shaft portion (235b) of the lubricating oil distribution member (235) is equal to the outer diameter of the pipe-shaped portion (235b1). The compressor described.   The outer diameter of the solid portion (235b2) of the small-diameter shaft portion (235b) of the lubricating oil distribution member (235) is different from the outer diameter of the pipe-shaped portion (235b1). The compressor described.   The compressor according to any one of claims 1 to 11, wherein the compression mechanism section (4) is a scroll type compression mechanism section.   The compressor according to claim 12, wherein a drive source of the compression mechanism section is an electric motor.   The compressor according to claim 13, characterized in that the working refrigerant is carbon dioxide.

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