JP5100701B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor that intermittently supplies lubricating oil separated from a compressed refrigerant to a bearing that supports a drive shaft of the compressor.

2. Description of the Related Art Conventionally, a compressor is known in which a part of a refrigerant in a compression process is supplied to a low pressure side by a pressure difference so that a low pressure side sliding portion is lubricated with a lubricating oil contained in the refrigerant.
For example, Patent Document 1 discloses a so-called horizontal electric scroll compressor.
In such a compressor, the revolution of the orbiting scroll is used to intermittently depressurize the oil in the high pressure oil storage chamber and supply the oil to the bearing.
That is, in this compressor, the oil that has entered the oil supply passage in the crankshaft is distributed to the main bearing and the auxiliary bearing.

JP 2008-196415 A

  However, the following problems have been pointed out. That is, when a wound bush is used as the main bearing and the sub-bearing, the timing at which the oil pressure reducing portion (intermittent throttle) communicates with the timing at which the oil supply port to the bearing and the bush joint chamfer communicate with each other. In addition, it becomes difficult to control the amount of oil supplied to the main bearing and the sub-bearing, resulting in insufficient lubrication, and reliability may be impaired.

  The present invention has been proposed in order to solve the above-described problem, and the lubricating oil amount can be controlled by shifting the timing of opening and closing the passage on the lubricating oil feed side and the communication timing with the bearing joint. This is to provide a highly reliable compressor with a smooth flow.

The present invention provides a compressor according to each of the claims as means for solving the above-mentioned problems.
The compressor according to claim 1 is housed in a container (1), and includes a compression mechanism part (2) having a movable member (22) and a fixed member (23), and a compression mechanism part (2) as a shaft ( 4), and a driving mechanism that is driven via the fixed member (23) to the movable member (22), and an intermittent oil supply passage (7) that is provided so that the passage can be cut off. The compression mechanism portion (2) In the compressor (100) that circulates the lubricating oil separated from the working medium compressed by the step (1) into the container (1), the shaft (4) has a first oil release passage in the container (1). It is supported by the main bearing portion (5) through the one bearing member (51) and the auxiliary bearing portion (6) through the second bearing member (61) having the oil escape passage, and the intermittent oil supply passage (7 ) Communicating with the main oil passage (42), and communicating with the main bearing portion (5) from the main oil passage (42). A first sub oil supply passage (43) and a second sub oil supply passage (44) communicating from the main oil supply passage (42) to the sub bearing portion (6) are provided, and the main bearing portion (5) and the sub bearing portion are provided. The lubricating oil is supplied to (6), and while the intermittent oil supply passage (7) from the fixed member (23) to the movable member (22) is in communication, the opening of the first sub oil supply passage (43). Or at least one of the oil escape passages of the first bearing member (51) or the second bearing member (61) does not exist in the angular range in which the opening of the second sub oil supply passage (44) rotates. Then, the first bearing member (51) or the second bearing member (61) is press-fitted into the main bearing portion (5) and the auxiliary bearing portion (6), respectively, so that the movable member (22) is fixed from the fixed member (23). When the intermittent oil supply passage (7) is connected, and the main oil supply passage (42) and the main bearing in the shaft (4). (5) or sub bearing portion by shifting the time communication between the (6), characterized in that so as to control the fuel supply amount of the lubricating oil.
Thereby, the main oil passage (42) in the shaft (4) and the main bearing portion (5) or the sub-bearing portion (6) communicate with each other by shifting the intermittent oil passage (7). The amount of oil supplied to the bearing and the sub-bearing can be controlled, and the flow of lubricating oil can be made smooth.

In the compressor according to claim 2, the first and second bearing members (51, 61) are respectively connected to the first joint (51 a) or (61 a) as an oil release passage in the shaft (4). Further, the present invention is characterized in that the winding bushes are press-fitted into the main bearing portion (5) and the auxiliary bearing portion (6) so as to be shifted from the second auxiliary oil supply passage (43, 44).
Accordingly, at least one communication timing among the communication timings of the auxiliary oil supply passages (43) and (44) of the shaft (4) and the joints (51a) and (61a) in the winding bushes (51) and (61). By shifting the communication timing in the intermittent oil supply passage (7), the amount of oil supplied to the main bearing portion (5) and the sub-bearing portion (6) can be controlled, and the flow of lubricating oil is made smooth and reliable. A highly efficient compressor can be provided.

The compressor according to claim 3 is a bearing in which the first and second bearing members (51, 61) are provided with an oil groove as an oil escape passage.
The compressor according to claim 4 is a housing in which the first and second bearing members (51, 61) are provided with an oil groove as an oil escape passage.

In the compressor according to claim 5, the compression mechanism section (2) is of a scroll type.
Further, the invention according to claim 6 is characterized in that the refrigerant as the working medium is carbon dioxide (CO ₂ ).
In the case of using a CO ₂ refrigerant, the amount of oil supplied to the main bearing portion (5) and the sub bearing portion (6) can be controlled even in a refrigeration cycle that operates at a higher pressure than a conventional chlorofluorocarbon refrigerant, Since the oil flow is smooth, a highly reliable compressor can be obtained.

  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 of embodiment mentioned later.

  According to the present invention, when supplying the lubricating oil in the high-pressure oil storage chamber to the main bearing portion and the auxiliary bearing portion that support the shaft in the container, the pressure is intermittently reduced from the compression mechanism portion into the container. By shifting the communication timing and the communication timing of the lubricating oil from the oil supply passage in the shaft to the main bearing portion and the sub bearing portion, the amount of oil supplied to the main bearing portion and the sub bearing portion can be controlled. It is possible to provide a highly reliable compressor by smoothing the flow of the lubricating oil.

It is sectional drawing which shows an example of the scroll compressor concerning this invention. FIG. 2 is an explanatory diagram showing a communication range in an intermittent oil supply passage indicated by an arrow A in the scroll compressor shown in FIG. 1. In the scroll compressor shown in FIG. 1, it is a cutting arrow line view which follows a BB line. In the scroll compressor shown in FIG. 1, it is a cutting arrow line view which follows CC line. FIG. 2 shows the positional relationship between the revolution trajectory of the orbiting scroll, the first oil supply passage on the fixed scroll side, and the second oil supply passage on the orbiting scroll side, which is the basis for calculating the communication range in the intermittent oil supply passage shown in FIG. It is a diagram.

Hereinafter, a compressor according to the present invention will be described with reference to the accompanying drawings with an embodiment.
Here, as an example of the compressor, a scroll compressor in which the compression mechanism unit is of a scroll type will be described. Of course, the present invention can also be applied to a compressor having another type of compression mechanism. That is, the compressor applied to the present invention is not limited to the hermetic type, and is not limited to the electric type.
A scroll compressor 100 shown in FIG. 1 compresses refrigerant from an external refrigeration cycle system by the compression mechanism 2 in the container, separates lubricating oil (oil) from the compressed refrigerant, and transfers the refrigerant to the outside. It is designed to return to the refrigeration cycle system, and with the operation, the separated oil is constantly supplied to the movable part such as the compression mechanism part using the differential pressure between the discharge pressure and the suction pressure, and recovered. Yes.
In the compressor 100, carbon dioxide (CO ₂ ) is used as a refrigerant that is a working medium. In the case of using the CO ₂ refrigerant, higher pressure is required in terms of efficiency as compared with the conventional chlorofluorocarbon refrigerant, and the pressing force on the portion where the orbiting scroll and the fixed scroll as the compression mechanism unit 2 slide is excessive. However, since oil is always supplied and recovered during operation, CO ₂ can be used as a refrigerant.

  The scroll compressor 100 includes an outer housing 1 as a container, preferably a sealed container, a compression mechanism portion 2 and an electric motor portion 3 housed in the outer housing 1. A hermetic scroll compressor 100 shown in FIG. 1 is a horizontal type compressor, in which a lower surface is an installation surface, a compression mechanism unit 2 is disposed on the right side, and an electric motor unit 3 is disposed on the left side. They are connected by a shaft 4 as a main shaft. The compression mechanism 2 is driven by the electric motor 3. Of course, the scroll compressor 100 has the same function even in the vertical type, and is not limited to the horizontal type.

  The outer housing 1 includes a cylindrical main body housing 11, a front housing 12, and a rear housing 13. These housings 11, 12, and 13 are fixed to form a sealed space in the outer housing 1. The main body housing 11 is provided with a suction pipe (not shown) connected to the suction chamber 25 of the compression mechanism section 2 and a discharge pipe 18 connected to a discharge chamber 26 which is also the discharge side of the compression mechanism section 2. Yes. A gas mixed with a low-pressure refrigerant and low-temperature oil (lubricating oil) from the refrigeration cycle flows into the outer housing 1 from the suction pipe.

The electric motor unit 3 includes a rotor 31 that is fixed to a shaft 4 as a main shaft, and a stator 32 that is disposed on the outer peripheral side of the rotor 31.
The compression mechanism unit 2 includes a middle housing 21, a turning scroll 22 as a movable member, a fixed scroll 23 as a fixed member, a valve cover 24, and the like. The middle housing 21 is fixed to the inner peripheral surface of the main body housing 11 by shrink fitting or press fitting. A hole through which the shaft 4 is inserted is provided at the center of the middle housing 21, and a bearing (sliding bearing), which will be described in detail later, is fitted into the hole to rotatably support the shaft 4. The main bearing portion 5 is provided. On the other hand, a support member 14 for supporting the shaft 4 is fixed to the inner peripheral surface of the main body housing 12 on the motor unit 3 side of the main body housing 11, and a centering member is provided at the center of the support member 14. 15 is attached. A hole for penetrating the shaft 4 is also provided in the center portion of the centering member 15, and a bearing (described later) is inserted into the hole to form a sub-bearing portion 6 that rotatably supports the shaft 4.

  In the shaft 4, a main oil supply passage 42 penetrating the inside in the axial direction is provided, and a crank portion 41 eccentric from the central axis of the shaft 4 is provided at the tip of the shaft 4. By connecting the crank portion 41 to the orbiting scroll 22, the orbiting scroll 22 performs an eccentric rotational movement as the shaft 4 rotates.

  The orbiting scroll 22 has a substantially circular orbiting scroll end plate portion 22a, a boss portion 22c that is formed to protrude from one side of the end plate portion 22a, and an end plate on which the boss portion 22c is formed. It consists of the orbiting scroll blade | wing part 22b formed in the spiral shape which protrudes in the other surface side of the part 22a. A bearing b is press-fitted and fixed to the boss portion 22 c and is rotatably supported by the crank portion 41 of the shaft 4. An Oldham coupling (not shown) is disposed on the end surface of the middle housing 21 on the orbiting scroll side to prevent the orbiting scroll 22 from rotating. Thereby, the orbiting scroll 22 can perform a revolution operation.

  A fixed scroll 23 that is opposed to the orbiting scroll 22 at an eccentric position and meshes with the rotational direction shifted by 180 degrees is provided. The fixed scroll 23 is fixed to the middle housing 21 with bolts or the like. The fixed scroll 23 includes a substantially scroll-shaped fixed scroll end plate portion 23a and a spiral fixed scroll blade portion 23b having substantially the same shape as the orbiting scroll blade portion 22b, and is opposed to the orbiting scroll blade portion 22b. Assembled into. By engaging the orbiting scroll blade portion 22b and the fixed scroll blade portion 23b, a plurality of crescent-shaped working chambers (compression chambers) 27 are formed between the spiral blade portions 22b and 23b for taking in and compressing the refrigerant. However, only one high pressure working chamber in which the pressure of the compressed refrigerant is the highest is formed in the central region common to the two scrolls 22 and 23. A discharge port 23c for discharging the compressed refrigerant from the high-pressure working chamber is formed at substantially the center of the fixed scroll end plate portion 23a.

A suction chamber 25 is formed on the outer peripheral side where the two spiral blade portions 23 b and 22 b of the fixed scroll 23 and the orbiting scroll 22 are engaged with each other. The suction chamber 25 is connected to a suction pipe (not shown), and this suction pipe is connected to the low-pressure side of a refrigeration cycle (not shown). When the working chamber on the outermost outer side of the working chamber 27 formed by the two spiral blade portions 23b and 22b opens toward the outer periphery, the CO ₂ gas to be compressed from the suction chamber 25 enters the working chamber. It will be captured.

  A discharge chamber 26 that is recessed in a concave shape is provided at a substantially central portion opposite to the blade portion 23 b of the fixed scroll end plate portion 23 a, and the discharge chamber 26 is covered with a valve cover 24. The discharge chamber 26 communicates with a high pressure working chamber (compression chamber) 27 through a discharge port 23c. The discharge chamber 26 is provided with a reed valve 26a. In the discharge chamber 26, one end of the discharge pipe 18 is connected in the radial direction, and the other end of the discharge pipe 18 is connected tangentially to the cylindrical gas-liquid separation unit 28 outside the container 1. The compressed discharge gas enters the gas-liquid separator 28 from the discharge chamber 26, where it is separated into high-pressure refrigerant gas and high-temperature oil, and the high-pressure refrigerant gas is sent to the high-pressure side of a refrigeration cycle (not shown). The rear housing 13 is provided with a high-pressure side oil storage chamber 29 partitioned by a partition wall 16 and communicates with the lower part of the gas-liquid separator 28, and the high-temperature oil separated by the gas-liquid separator 28 is temporarily Thus, the oil is stored in the high pressure side oil storage chamber 29. Further, a heat insulating space S2 is formed between the compression mechanism portion 2 and the partition wall 16. The partition wall 16 is fixed to the rear housing 13 by welding.

  On the other hand, a low-pressure side oil sump 17 is formed in the lower part of the sealed space S in which the electric motor unit 3 partitioned in the outer housing 1 by the middle housing 21 is accommodated. The refrigerant gas suction chamber 25 communicates with a low-pressure side sealed space S in which a low-pressure side oil sump 17 is formed by a communication hole (not shown) provided in the middle housing 21 so that the oil is mist-like. Part of the mixed refrigerant refrigerant flows into the sealed space S. Further, the support member 14 is provided with a plurality of openings 14 a, opposite to the motor portion of the support member 14, and in the space S ′ and the low-pressure side reservoir 17 surrounded by the support member 14 and the outer housing 1. It comes to communicate. Further, the suction pipe (not shown) may be disposed so as to be connected to the low pressure side sealed space S.

Next, in the scroll compressor 100 configured as described above, a lubricating oil circulation system will be described.
The fixed scroll 23 and the orbiting scroll 22 are formed with an intermittent oil supply passage 7 for introducing the oil in the high pressure side oil storage chamber 29 into the back pressure space 22d in the boss portion 22c of the orbiting scroll 22. The intermittent oil supply passage 7 has a first oil supply passage 72 on the fixed scroll 23 side and a second oil supply passage 73 on the orbiting scroll 22 side that can be disconnected from each other. The first oil supply passage 72 on the fixed scroll 23 side and the second oil supply passage 73 on the orbiting scroll 22 side are intermittently communicated by the revolution operation of the orbiting scroll 22, as will be described in detail later.
The first oil supply passage 72 on the fixed scroll 23 side communicates with the high-pressure side oil storage chamber 29 via the oil supply pipe 71.

  Next, the back pressure space 22 d in the boss portion 22 c of the orbiting scroll 22 is connected to the main oil supply passage 42 in the shaft 4. In addition, a first auxiliary oil passage 43 in the radial direction is formed at a portion corresponding to the main bearing portion 5 of the shaft 4. Accordingly, a part of the oil flowing in the main oil supply passage 42 is supplied to the main bearing portion 5 through the first sub oil supply passage 43 and lubricates the bearing of the main bearing portion 5, and then the hole in the middle of the middle housing 21. It flows down to a low-pressure side oil sump 17 through a minute gap between the inner surface and the outer peripheral surface of the shaft 4.

  In addition, a radial second sub oil supply path 44 communicating with the main oil supply path 42 in the shaft 4 is also formed at a portion corresponding to the sub bearing portion 6 of the shaft 4. Accordingly, a part of the oil flowing in the main oil supply passage 42 is supplied to the auxiliary bearing portion 6 through the second auxiliary oil supply passage 44 and lubricates the bearing of the auxiliary bearing portion 6, and then the center of the centering member 15. The oil flows down to the low-pressure side oil sump 17 through a minute gap between the inner surface of the hole and the outer peripheral surface of the shaft 4.

Here, the first oil passage 72 on the fixed scroll 23 side and the orbiting scroll 22 side for guiding the lubricant to the main oil passage 42 of the shaft 4 by depressurizing intermittently from the high pressure side oil storage chamber 29 side. The intermittent communication function with the second oil supply passage 73 will be described.
In the first oil supply passage 72 on the fixed scroll 23 side, an aperture surface 72e having a narrow passage cross-sectional area is formed on the opening surface in contact with the second oil supply passage 73 on the orbiting scroll 22 side.
With such a configuration, the turning of the orbiting scroll 22 causes the first oil supply passage 72 on the fixed scroll 23 side and the second oil supply passage 73 on the orbiting scroll 22 side to communicate intermittently.
The range in which the first oil supply passage 72 on the fixed scroll 23 side and the second oil supply passage 73 on the side of the orbiting scroll 22 are intermittently communicated by the turning of the turning scroll 22 can be shown as shown in FIG. That is, FIG. 2 illustrates a locus of the second oil supply passage 73 on the side of the orbiting scroll 22 drawn by the revolution operation of the orbiting scroll 22, and the locus of the second oil supply passage 73 on the side of the orbiting scroll 22 is illustrated in FIG. In the middle, it overlaps with the first oil supply passage 72 on the fixed scroll 23 side in the range of Δθ, and shows that the first oil supply passage 72 on the fixed scroll 23 side communicates with the second oil supply passage 73 on the orbiting scroll 22 side.

The main bearing portion 5 and the sub-bearing portion 6 that support the shaft 4 in the motor portion 3 in the lubricating oil circulation system of the scroll compressor 100 as described above will be described in more detail.
First, the main bearing portion 5 includes a winding bush 51 at the center of the middle housing 21 as a first bearing member press-fitted into a hole through which the shaft 4 is inserted.
When the winding bush 51 is press-fitted into a hole penetrating the shaft 4, a joint 51 a as an oil release passage is provided on the outer periphery of the shaft of the first sub oil supply passage 43 in the shaft 4 in order to control the amount of lubricating oil supplied. The position is not coincident with the opening surface (see FIG. 3).

The direction θb of the first sub oil supply passage 43 in the shaft 4 is as shown in FIG.
90 ° − (Δθ / 2) <θb <90 ° + (Δθ / 2)
Exists in the range.
This will be described below.
The phase of the center of the second oil supply passage 73 rotates in the same phase in synchronization with the eccentric shaft center of the crank portion 41.
It is assumed that when the first oil supply passage 72 and the second oil supply passage 73 are coincident with each other, the first sub oil supply passage 43 is located upward, that is, at a position of 90 °.
In this case, the angle range in which the center of the second oil supply passage 73 and the first oil supply passage 72 communicate with each other is
90 ° − (Δθ / 2) <θb <90 ° + (Δθ / 2)
It becomes.

In this regard, in FIG. 3, when the first oil supply passage 72 and the second oil supply passage 73 from the fixed scroll 23 to the orbiting scroll 22 are in communication (in the range of Δθ in FIG. 2), the first sub oil supply passage in the shaft 4. 43 is set to face upward (90 °) with respect to the main oil supply passage 42. The direction of the first sub oil supply passage 43 is 90 ° − (Δθ / 2) <θb <90 ° + (Δθ / 2) with an axis extending vertically through the center of the shaft 4 in the drawing.
It is in the range.
Therefore, in order to prevent the joint 51a of the winding bush 51 from being aligned with the direction (the range of θb) of the first sub oil supply passage 43, the position range θ of the joint 51a of the winding bush 51 is
θ <90 ° − (Δθ / 2) or 90 ° + (Δθ / 2) <θ
Can be expressed as

On the other hand, in the auxiliary bearing portion 6, when the first oil supply passage 72 on the fixed scroll 23 side and the second oil supply passage 73 on the orbiting scroll 22 side are in communication (in the range of Δθ in FIG. 2), as shown in FIG. The radial direction of the second sub oil supply passage 44 is set so as to be directed vertically downward (270 °). The direction of the second sub oil supply passage 44 is in a range of θc (270 °) with an axis extending vertically through the center of the shaft 4 in the drawing.
Therefore, in order not to coincide with the direction (the range of θc) of the second auxiliary oil supply passage 44, the position range θ of the joint 61a of the winding bush 61 as the second bearing member is
θ <270 ° − (Δθ / 2) or 270 ° + (Δθ / 2) <θ
Can be expressed as
In the above description, it has been described that the first sub oil supply passage 43 is at a position of 90 ° when the axis of the first oil supply passage 72 and the second oil supply passage 73 coincide, but instead of 90 °. Even if it is at an arbitrary angle θ ₁ , θ can be similarly obtained by analogy.

Here, the communication range Δθ in which the first oil supply passage 72 on the fixed scroll 23 side communicates with the second oil supply passage 73 on the orbiting scroll 22 side will be described.
Such a communication range Δθ is obtained as follows based on FIG. FIG. 5 shows the revolution trajectory of the orbiting scroll, the first oil supply passage on the fixed scroll side, and the second oil supply passage on the orbiting scroll side, which are the basis for calculating the communication range in the intermittent oil supply passage shown in FIG. The positional relationship is shown.
That is, in FIG. 5, R: revolution radius of the orbiting scroll 22, r ₁ : cross-sectional radius of the first oil supply passage 72, r ₂ : cross-sectional radius of the second oil supply passage 73, Δθ: first and second oil supply passages 72, From the range where 73 communicates,
Δθ / 2 = cos ⁻¹ [1- (r ₁ + r ₂ ) ² / 2R ² ]
It becomes.

  Next, the operation and action of the scroll compressor 100 of the present invention configured as described above will be described. When electric power is supplied to the motor unit 3 from the outside, the rotor 31 is driven to rotate, and the shaft 4 rotates accordingly. As the shaft 4 rotates, the crank portion 41 at the tip of the shaft 4 rotates around the shaft 4 with a predetermined eccentric amount, and the orbiting scroll 22 connected to the crank portion 41 turns. Thereby, the operation of the compression mechanism unit 2 is performed.

The flow of refrigerant and oil (lubricating oil) associated with the operation of the compression mechanism unit 2 is performed as follows. In the present invention, carbon dioxide (CO ₂ ) is preferably used as the refrigerant.
First, by the operation of the compression mechanism unit 2, a mixed gas of low-pressure refrigerant and low-temperature oil flows into the suction chamber 25 of the compression mechanism unit 2 from the external refrigeration cycle system through the suction pipe. In principle, the refrigerant flowing from the suction pipe is a gas. The mixed gas enters the working chamber 27 of the compression mechanism unit 2 and is compressed, and then discharged from the discharge port 23 c into the discharge chamber 26. A part of the mixed gas in the suction chamber 25 flows into the low pressure side sealed space S through the communication hole of the middle housing 21.

  The compressed mixed gas in the discharge chamber 26 is conveyed to the gas-liquid separator 28 through the discharge pipe 18, where it is separated into high-temperature refrigerant gas and high-temperature oil, and the high-temperature refrigerant gas is externally frozen. Sent to the cycle system. On the other hand, high-temperature oil is temporarily stored in the high-pressure side oil storage chamber 29 and then supplied to the back pressure chamber 22d through the intermittent oil supply passage 7 including the oil supply pipe 71, the first oil supply passage 72, and the second oil supply passage 73. Is done. In the intermittent oil supply passage 7, the first oil supply passage 72 and the second oil supply passage 73 are intermittently communicated by the turning of the orbiting scroll 22, that is, the revolution operation, so that the high pressure side oil storage chamber 29 and the back pressure chamber 22 d are connected. The oil sent to is controlled in flow rate or back pressure flow rate.

Here, the oil fed to the back pressure chamber 22d is supplied to the main bearing portion 5 and the auxiliary bearing portion 6 through the main oil supply passage 42 of the shaft 4, and the winding bushes 51, which are their respective bearings, Lubricate 61.
The high-temperature oil supplied from the main oil supply passage 42 to the main bearing portion 5 through the first sub oil supply passage 43 then flows down to the low-pressure side oil sump 17 through a minute gap of the main bearing portion 5, and similarly. The oil flows down from the main oil supply passage 42 through the second auxiliary oil supply passage 44 to the low pressure side oil sump 17 through the minute gap of the auxiliary bearing portion 6.

As described above, the high-temperature oil temporarily stored in the high-pressure side oil storage chamber 29 is supplied to the back pressure chamber 22 d through the intermittent oil supply passage 7 including the first oil supply passage 72 and the second oil supply passage 73. At this time, the first oil supply passage 72 and the second oil supply passage 73 are intermittently communicated by the turning of the orbiting scroll 22, that is, the revolution operation, so that the pressure is intermittently reduced and the back pressure chamber 22 d is reached. At that time, the first oil supply passage 72 on the fixed scroll 23 side of the intermittent oil supply passage 7 and the second oil supply passage 73 on the orbiting scroll 22 side are connected to the first oil supply passage 72 on the fixed scroll 23 side as shown in FIG. On the other hand, a range Δθ in which the second oil supply passage 73 on the side of the orbiting scroll 22 moving by the revolution operation of the orbiting scroll 22 overlaps is a communication range.
When the first oil supply passage 72 and the second oil supply passage 73 communicate intermittently, the first sub oil supply passage 43 and the second sub oil supply passage are provided in the main bearing portion 5 and the sub bearing portion 6 that support the shaft 4. The position 44 is located in the position range of θb and θc shown in FIGS. 3 and 4, respectively.
Correspondingly, the winding bushes 51 and 61 press-fitted into the main bearing portion 5 and the sub-bearing portion 6 are shifted so that the position range θ of the joints 51a and 61a does not enter the position ranges of θb and θc. Therefore, the oil intermittently brought from the high-pressure side oil storage chamber 29 to the back pressure chamber 22d via the intermittent oil supply passage 7 passes through the main oil supply passage 42 of the shaft 4 to the main bearing portion 5 and the auxiliary bearing portion. 6, the oil does not flow out at once, the oil can be supplied at an appropriate flow rate to the main bearing portion 5 and the sub-bearing portion 6 side, good lubrication can be ensured, and high reliability. A compressor can be provided.

As described above, the scroll compressor 1 according to the present invention has been described with reference to an embodiment. However, in the above-described embodiment, the first oil supply passage 72 on the side of the fixed scroll 23 and the orbiting scroll having an intermittent oil communication function. It is assumed that the time delay required for pressure to be transmitted from the second oil supply passage 73 on the 22 side to each main bearing portion 5 and sub bearing portion 6 is small enough to be ignored.
Therefore, when such a time delay cannot be ignored, it is necessary to correct the press-fitting range of the winding bush as follows. That is,
Main bearing: θ <θb− (Δθ / 2), θb + (Δθ / 2) + Δθd <θ
Secondary bearing: θ <θc− (Δθ / 2) or θc + (Δθ / 2) + Δθd <θ
Where Δθd is the angle at which the shaft 4 rotates during the time delay

  In the above-described embodiment, the position specification of the joint of the winding bush is described. However, the present invention is not limited to the winding bush, and an oil groove provided in a normal slide bearing or a housing is used directly as a bearing. The same effect can be obtained if the position of the provided oil groove is also defined in the above-mentioned angle range.

DESCRIPTION OF SYMBOLS 100 Scroll compressor 1 Outer housing 11 Main body housing 12 Front housing 13 Rear housing 14 Support member 15 Centering member 16 Bulkhead 17 Low pressure oil reservoir 18 Discharge pipe 2 Compression mechanism part 21 Middle housing 22 Orbiting scroll 22a Orbiting scroll end plate part 22b Orbiting scroll blade portion 22c Boss portion 22d Back pressure space 23 Fixed scroll 23a Fixed scroll end plate portion 23b Fixed scroll blade portion 23c Discharge port 24 Valve cover 25 Suction chamber 26 Discharge chamber 26a Reed valve 27 Working chamber 28 Gas-liquid separation portion 29 High pressure Oil storage chamber 3 Motor section 31 Rotor 32 Stator 4 Shaft 41 Crank section 42 Main oil supply path 43 First sub oil supply path 44 Second sub oil supply path 5 Main bearing section 51 Winding bush 51a Joint 6 Sub bearing section 61 Winding bush 61a 7 oil supply passage 71 oil pipe 72 first oil supply passage 72e aperture section 73 second oil supply passage

Claims (6)

A compression mechanism (2) housed in the container (1) and having a movable member (22) and a fixed member (23), and a drive unit for driving the compression mechanism (2) via the shaft (4) And an intermittent oil supply passage (7) provided so that the passage can be cut off from the fixed member (23) to the movable member (22), and the working medium compressed by the compression mechanism section (2) In the compressor (100) for circulating the lubricating oil separated from the back into the container (1),
The shaft (4) has a main bearing portion (5) and a second bearing member (61) having an oil relief passage through a first bearing member (51) having an oil relief passage in the container (1). A main oil passage (42) that is supported by the sub-bearing portion (6) through the intermediate oil passage and communicates with the intermittent oil supply passage (7), and the main oil supply passage (42) to the main bearing portion (5). A first sub oil supply passage (43) communicating with the main oil supply passage (42) and a second sub oil supply passage (44) communicating with the sub bearing portion (6) from the main oil supply passage (42) are provided, and the main bearing portion (5 ) And the sub-bearing part (6).
While the intermittent oil supply passage (7) from the fixed member (23) to the movable member (22) communicates, the opening of the first sub oil supply passage (43) or the second sub oil supply passage (44). In the angle range in which the opening of the first bearing member (51) is rotated, at least one of the oil escape passages of the first bearing member (51) or the second bearing member (61) does not exist. ) Or the second bearing member (61) is press-fitted into the main bearing portion (5) and the sub-bearing portion (6), respectively, so that intermittent oil supply passages extending from the fixed member (23) to the movable member (22) are performed. The amount of lubricating oil supplied is controlled by shifting the time of communication (7) and the time of communication between the main oil supply passage (42) in the shaft (4) and the main bearing portion (5) or the auxiliary bearing portion (6). A compressor characterized by that.   The first and second bearing members (51, 61) are connected to the first and second auxiliary oil passages (51a) and (61a) as oil escape passages in the shaft (4), respectively. 43. The compressor according to claim 1, wherein the compressor is a wound bush press-fitted into each of the main bearing portion (5) and the sub-bearing portion (6) so as to be displaced from 43, 44).   The compressor according to claim 1, wherein the first and second bearing members (51, 61) are sliding bearings having an oil groove as an oil escape passage.   The compressor according to claim 1, wherein the first and second bearing members (51, 61) are housings having oil grooves as oil relief passages.   The compressor according to any one of claims 1 to 4, wherein the compression mechanism section (2) is of a scroll type. The compressor according to any one of claims 1 to 5, wherein the refrigerant that is a working medium is carbon dioxide (CO ₂ ).

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