JP7089957B2 - Open compressor - Google Patents

Description

The present invention relates to an open compressor.

As a kind of compressor, a device called an open compressor is known. The open compressor has a drive shaft that is rotatably supported in the internal space of the housing. The end of the drive shaft projects to the outside of the housing, and a driving force from the outside is applied to the end of the drive shaft. Therefore, a differential pressure is generated inside and outside the housing along the drive shaft.
A sealing device is provided on the drive shaft for the purpose of sealing oil such as lubricating oil leaking due to this differential pressure.

In an open compressor, the sealing member of the sealing device may be hardened or deteriorated over time to deteriorate the sealing function, so that the lubricating oil may leak from the sealing device. Patent Document 1 describes a mechanism for adsorbing lubricating oil leaked from a sealing device by a felt ring.

Jikkenhei 2-145649A Gazette

By the way, in the open compressor described in Patent Document 1, when the felt ring is saturated, the lubricating oil adsorbed on the felt ring exudes. There is a problem that the lubricating oil seeps out and adheres to the clutch provided at the end of the drive shaft, causing the clutch to slip.

An object of the present invention is to provide an open compressor capable of preventing leakage of lubricating oil, preventing clutch slippage, and promptly discharging sealed lubricating oil.

According to the first aspect of the present invention, the open type compressor is housed in a housing having an internal space, a through hole communicating the internal space with the outside, and the internal space to compress gas. A compression mechanism, a drive shaft connected to the compression mechanism and having one end in the axial direction projecting to the outside, a clutch provided at one end in the axial direction of the drive shaft, and the through hole. A mechanical seal arranged between the inner peripheral surface of the drive shaft and the outer peripheral surface of the drive shaft to seal the gas and liquid leaking from the compression mechanism, and the inner peripheral surface of the through hole and the outer peripheral surface of the drive shaft. A base portion provided on one side of the mechanical seal in the axial direction and fixed to the inner peripheral surface of the through hole, and a lip portion formed of a solid elastomer and projecting radially inward from the base portion. An oil seal having a The lip portion is provided with an oil discharge path main body connecting the opening and the outer surface of the housing, and the lip portion is radially inward from one end of the base portion in the axial direction. A protruding portion and a lip tip that protrudes from the radially inner end of the protruding portion to the other side in the axial direction and is located on one side in the axial direction from the other end in the axial direction of the base. A portion of the opening is overlapped with the base when viewed from the radial direction, and a portion of the opening different from the portion is the same as the base when viewed from the radial direction. It does not overlap.

According to such a configuration, the oil seal can seal the oil leaked from the mechanical seal. This makes it possible to prevent the clutch from slipping due to the adhesion of oil.
Further, by introducing the oil fastened by the oil seal into the opening, the oil can be discharged through the oil discharge path.
In addition, the lubricating oil that overflows from the base of the oil seal is immediately introduced into the opening. As a result, the oil held by the oil seal can be quickly discharged.

In the open compressor, a gap may be provided between the radial inner end of the lip and the outer peripheral surface of the drive shaft.

According to such a configuration, since the contact between the lip portion and the drive shaft is eliminated, the wear of the lip portion can be suppressed.

In the open compressor, 0 <C / D <0.08, where D is the diameter of the drive shaft and C is the radial distance between the lip portion and the outer peripheral surface of the drive shaft. It's okay.

According to such a configuration, oil leakage can be reliably prevented by defining the radial distance between the lip portion and the drive shaft.

According to the present invention, the oil seal can seal the oil leaked from the mechanical seal. This makes it possible to prevent the clutch from slipping due to the adhesion of oil.
Further, by introducing the oil fastened by the oil seal into the opening, the oil can be discharged through the oil discharge path.

It is sectional drawing of the open type compressor of embodiment of this invention. It is an enlarged sectional view around the mechanical seal and the oil seal of the open type compressor of embodiment of this invention. It is sectional drawing explaining the operation of the mechanical seal, the oil seal, and the oil discharge path of the open type compressor of embodiment of this invention.

Hereinafter, the open compressor according to the embodiment of the present invention will be described in detail with reference to the drawings.
As shown in FIG. 1, the open compressor 1 includes a housing 2, a compression mechanism 19 housed in an internal space V of the housing 2, and a drive shaft 9 connected to the compression mechanism 19. ..
In the following description, the direction in which the axis A of the drive shaft 9 extends is referred to as the axis direction Da. Further, the direction orthogonal to the axis A is the radial direction, the side away from the axis A in the radial direction is called the radial outside, and the side approaching the axis A in the radial direction is called the radial inside. In the axial direction Da, the protruding direction of the drive shaft 9 is referred to as Da1 on one side in the axial direction (left side in FIG. 1), and the opposite side of Da1 on one side in the axial direction is referred to as Da2 on the other side in the axial direction (right side in FIG. 1).

The housing 2 has a housing main body 3 that houses the compression mechanism 19, and a boss portion 13 that is integrally attached to Da1 on one side in the axial direction of the housing main body 3 via a bolt 38.
The housing main body 3 has a front housing 3A and a rear housing 3B having a bottomed shape. The front housing 3A and the rear housing 3B are integrally fastened via bolts 5.

A bearing member 6 is fixed to Da2 on the other side in the axial direction on the front housing 3A side in the housing 2 via bolts 7. The drive shaft 9 is rotatably supported by the radial bearing portion 6A of the bearing member 6 and the first rolling bearing 8 installed in the front housing 3A.
The end portion of Da1 on one side in the axial direction of the drive shaft 9 penetrates the through hole 12 provided in the front housing 3A and the boss portion 13 and protrudes to the outside. Power from an external drive source such as an engine is input to one end (protruding portion) of the drive shaft 9 via the pulley 10 and the electromagnetic clutch 11.

The boss portion 13 has a cylindrical boss portion main body 13A coaxial with the drive shaft 9, and a flange portion 13B formed on the other side Da2 in the axial direction of the boss portion main body 13A. The flange portion 13B projects radially outward from the end portion of Da2 on the other side in the axial direction of the boss portion main body 13A. The boss portion 13 is fixed to the housing body 3 by fastening the flange portion 13B to the front housing 3A via the bolt 38.
In the present embodiment, the boss portion 13 is fixed to the housing main body 3 by using the bolt 38, but the present invention is not limited to this. For example, the boss portion 13 and the housing body 3 may be integrally formed.

The electromagnetic clutch 11 includes a rotor 11A that is rotationally driven by power from an external drive source such as an engine, an armature 16 that is arranged to face the rotor 11A, and an electromagnetic coil unit 15 that magnetically attracts the rotor 11A and the armature 16. Have.

The rotor 11A is formed in an annular shape. The inner peripheral surface of the rotor 11A is rotatably supported on the outer peripheral surface of the boss portion main body 13A via the second rolling bearing 14. A belt groove 11B is formed on the outer peripheral surface of the rotor 11A. The outer peripheral surface of the rotor 11A functions as a pulley 10.

The armature 16 has a tubular hub 16A having a flange portion, a disc-shaped armature plate 16B formed of a magnetic material, and a leaf spring 16C. The hub 16A is fixed to one end of a drive shaft 9 projecting to the outside of the housing 2 via bolts 17. The armature plate 16B is arranged to face the end face of the rotor 11A. The leaf spring 16C urges the armature plate 16B in a direction away from the end face of the rotor 11A.

When power is supplied from the outside, the electromagnetic coil unit 15 energizes the electromagnetic coil to generate an electromagnetic force, and magnetically attracts the armature plate 16B to the end face of the rotor 11A against the urging force of the leaf spring 16C. As a result, the rotor 11A and the armature 16 are coupled, the rotational force of the rotor 11A is transmitted to the armature 16, and further transmitted to the drive shaft 9 of the open compressor 1 to operate the open compressor 1. ..
On the other hand, when the supply of power to the electromagnetic coil unit 15 is stopped, the armature plate 16B is separated from the end face of the rotor 11A by the urging force of the leaf spring 16C. As a result, the transmission of the rotational force of the rotor 11A is cut off, and the open compressor 1 is stopped.

A compression mechanism 19 is provided in the internal space V on the rear housing 3B side of the housing 2. Here, the compression mechanism 19 is a scroll compression mechanism including a pair of fixed scrolls 20 and a swivel scroll 21. The scroll compression mechanism 19 meshes a pair of fixed scrolls 20 and a swivel scroll 21 with a phase shift of 180 ° to form a plurality of compression chambers 22 between the scrolls 20 and 21. Such a scroll compression mechanism 19 19 itself is well known.

The fixed scroll 20 is fixed to the bearing member 6 via a bolt 23. A discharge cavity 26 is formed between the back surface of the end plate 20A of the fixed scroll 20 and the inner surface of the rear housing 3B. The end plate 20A of the fixed scroll 20 is provided with a discharge port 24 for discharging the compressed gas into the discharge cavity 26 and a discharge valve 25 for opening and closing the discharge port 24.

The rear housing 3B is formed with a discharge port 27 for discharging the compressed gas discharged into the discharge cavity 26 to the outside. A discharge pipe constituting a refrigeration cycle can be connected to the discharge port 27.
A boss 28 is provided on the back surface of the end plate 21A of the swivel scroll 21. The crankpin 9A provided on the other side Da2 of the drive shaft 9 in the axial direction is connected to the boss 28 via the drive bush 29 and the swivel bearing 30. The swivel scroll 21 is swiveled and driven via the crankpin 9A by the rotation of the drive shaft 9.

The back surface of the end plate 21A of the swivel scroll 21 is supported by a thrust bearing 31 provided in the bearing member 6. A well-known rotation prevention mechanism 32 made of an old dam link, a pin ring, or the like is provided between the back surface of the end plate 21A of the swivel scroll 21 and the bearing member 6. The rotation of the turning scroll 21 is blocked by the rotation preventing mechanism 32. The swivel scroll 21 revolves and swivels with respect to the fixed scroll 20.

The rear housing 3B is provided with a suction port 33 for connecting a suction pipe on the refrigeration cycle side. The low-pressure gas sucked into the suction cavity 34 from the suction port 33 is sucked into the compression chamber 22 of the scroll compression mechanism 19 and compressed.

In the present embodiment, the compression mechanism 19 is provided with a step portion for changing the lap height in the spiral direction of the fixed scroll 20 and the swivel scroll 21, and the lap height on the outer peripheral side is relative to the lap height on the inner peripheral side. It is a so-called stepped scroll compression mechanism 19 capable of three-dimensional compression capable of compressing gas not only in the circumferential direction but also in the axial direction Da. However, the compression mechanism 19 is not limited to this.

The inside of the front housing 3A is filled with a required amount of lubricating oil. Lubricating oil is collected in the oil reservoir 35 by making the lower space in the front housing 3A an oil reservoir 35. The oil in the oil reservoir 35 is sucked into the oil supply pump 37 via the suction passage 36. The refueling pump 37 is a known rotary type positive displacement pump.

As shown in FIG. 2, one end of the drive shaft 9 is surrounded by a boss main body 13A (through hole 12). The outer peripheral surface 9B of the drive shaft 9 and the inner peripheral surface 12A of the through hole 12 face each other in the radial direction.
A mechanical seal 18 is provided between the inner peripheral surface 12A of the through hole 12 and the outer peripheral surface 9B of the drive shaft 9. Da1 on one side in the axial direction of the mechanical seal 18 is in contact with a ridge 41 formed in the circumferential direction on the inner peripheral surface 12A of the through hole 12. That is, the mechanical seal 18 is restricted from moving to Da1 on one side in the axial direction by the ridge 41.

The mechanical seal 18 is a sealing device that forms a liquid film on a sliding surface and seals it while lubricating it with lubricating oil to be sealed. The mechanical seal 18 is movable in the axial direction Da via a mating ring 60 mounted in a non-rotating state on the through hole 12 side via an O-ring 61, and a case 62 and an O-ring 63 on the drive shaft 9 side. It includes a seal ring 64 that is mounted and rotated integrally with the drive shaft 9, and a coil spring 65 that is held by the case 62 and presses the seal ring 64 against the mating ring 60.

The mechanical seal 18 forms a sealed sliding portion S between the mating ring 60, which is a sliding ring on the stationary side, and the seal ring 64, which is a sliding ring on the rotating side, and lubricates the inside of the pump chamber 39, which will be described later. It prevents oil and gas from leaking to Da1 on one side in the axial direction of the mechanical seal 18.

That is, the mechanical seal 18 has a seal ring 64 that can move in the axial direction Da by a coil spring 65 that is an elastic member, and a mating ring 60 that does not move. In the mechanical seal 18, the sliding surface orthogonal to the axis A of the seal ring 64 and the sliding surface orthogonal to the axis A of the mating ring 60 come into contact with each other and rotate relatively to seal the fluid.

The oil pumped from the oil reservoir 35 by the oil supply pump 37 is discharged into the pump chamber 39 formed between the drive shaft 9, the boss portion 13, and the mechanical seal 18. The lubricating oil pumped up to the pump chamber 39 passes through a lubrication passage (not shown) provided in the drive shaft 9 to a sliding portion such as a radial bearing portion 6A, a drive bush 29, a swivel bearing 30, a thrust bearing 31, or a mechanical seal. It is supplied to 18 sliding parts and the like.

An oil seal 50 is attached to the inner peripheral surface 12A of the through hole 12, which is Da1 on one side in the axial direction of the mechanical seal 18 and the ridge 41. The oil seal 50 is an annular seal device that prevents lubricating oil from leaking from between the drive shaft 9 and the through hole 12. The oil seal 50 has a base portion 51 fixed to the inner peripheral surface 12A of the through hole 12, and a lip portion 52 protruding radially inward from the base portion 51.

The base 51 has an annular shape. The outer peripheral surface of the base 51 is fitted to the inner peripheral surface 12A of the through hole 12.
The lip portion 52 has an annular shape. The lip portion 52 projects radially inward from one end of Da1 on one side in the axial direction of the base portion 51.

A metal ring 53 is embedded inside the base portion 51 and the lip portion 52. The metal ring 53 forms a ring and is a portion forming the skeleton of the base 51.
The oil seal 50 is manufactured by baking and adhering an elastomer to be a base 51 and a lip 52 to a metal ring 53. The base 51 and the lip 52 are formed of a solid elastomer. The elastomer forming the base 51 and the lip 52 is not porous. The base portion 51 and the lip portion 52 are formed so that the liquid does not penetrate into the base portion 51 and the lip portion 52.

The lip portion 52 includes a protruding portion 52A protruding radially outward from one end of the axial one-sided Da1 of the base 51, and a lip tip portion 52B protruding radially outward from the radial inner end of the protruding portion 52A to the axially opposite side Da2. It has a spring portion 52C embedded inside the lip tip portion 52B in the radial direction. The spring portion 52C is an annular coil spring.

In the oil seal 50 of the present embodiment, the base 51 is formed of the elastomer and the metal ring 53, but the present invention is not limited to this, and the base 51 may be formed only of the metal ring 53.

A gap G is formed between the lip tip portion 52B of the lip portion 52 and the outer peripheral surface 9B of the drive shaft 9. That is, Da1 on one side in the axial direction of the oil seal 50 and Da2 on the other side in the axial direction of the oil seal 50 communicate with each other through the gap G.
When the diameter of the drive shaft 9 facing the lip tip portion 52B of the oil seal 50 in the radial direction is D, and the distance between the lip portion 52 and the outer peripheral surface 9B of the drive shaft 9 (dimension of the gap G) is C, the drive is driven. The shaft 9 and the oil seal 50 are formed so as to satisfy the following formula (1).
0 <C / D <0.08 ・ ・ ・ (1)
For example, assuming that the diameter D of the drive shaft 9 is 13.5 mm, the oil seal 50 is selected so that the distance C between the lip portion 52 and the outer peripheral surface 9B of the drive shaft 9 is 1.08 mm or less. ..

An oil discharge path 46 is formed in the lower part of the boss portion 13. The oil discharge path 46 has an opening 48 that opens to the inner peripheral surface 12A of the through hole 12, and an oil discharge path main body 47 that connects the opening 48 and the outer surface of the flange portion 13B. The cross-sectional area of the opening 48 is larger than the cross-sectional area of the oil discharge path main body 47. The opening 48 has a larger diameter than the oil discharge path main body 47. The cross-sectional shape of the opening 48 and the oil discharge path main body 47 may be circular or polygonal.

The opening 48 is opened at Da2 on the other side in the axial direction from the end of Da1 on one side in the axial direction of the base 51 of the oil seal 50, and Da1 on the one side in the axial direction from the mechanical seal 18. A part of the opening 48 overlaps with the base 51 of the oil seal 50 when viewed from the radial direction, and a part different from the part of the opening 48 does not overlap with the base 51 when viewed from the radial direction. That is, a part of the opening 48 when viewed from the inside in the radial direction is closed by the oil seal 50.

Next, the operation of the open compressor 1 of the present embodiment will be described.
In the open compressor 1, when the electromagnetic clutch 11 is turned on, power is input from an external drive source via the rotor 11A (pulley 10). The input power is transmitted to the drive shaft 9, and the drive shaft 9 is rotationally driven. As a result, the swivel scroll 21 of the scroll compression mechanism 19 is driven to revolve around the fixed scroll 20. By this revolution rotation drive, the low pressure gas is sucked into the suction cavity 34 from the suction port 33. The low pressure gas is compressed in the compression chamber 22. The high-pressure gas is discharged into the discharge cavity 26 via the discharge port 24, and is discharged from the discharge port 27 into the refrigeration cycle.

During this time, the lubrication pump 37 driven by the rotation of the drive shaft 9 sucks the lubricating oil in the oil reservoir 35 through the suction passage 36 and pumps it into the pump chamber 39. The lubricating oil pumped up in the pump chamber 39 is supplied to the sliding parts of the mechanical seal 18, the radial bearing part 6A, the drive bush 29, the swivel bearing 30, the thrust bearing 31, and the like, and each sliding part is supplied. Lubricate moving parts. The oil that lubricates each sliding portion is collected in the oil reservoir 35 at the bottom of the housing 2 and recirculated.

Next, with reference to FIG. 3, the operations of the mechanical seal 18, the oil seal 50, and the oil discharge path 46 in the open compressor 1 of the present embodiment will be described.
The lubricating oil stored in the pump chamber 39 (see FIG. 1) is sealed by the mechanical seal 18. Of the lubricating oil that leaks from the mechanical seal 18 to Da1 on one side in the axial direction, the lubricating oil that has fallen due to gravity is either sealed by the oil seal 50 as shown in the path C1 or discharged as shown in the path C2. It is discharged by the route 46.

Further, the lubricating oil transmitted through the drive shaft 9 without falling due to gravity is scattered outward in the radial direction due to the centrifugal force due to the rotation of the drive shaft 9, as shown in the path C3, and then sealed by the oil seal 50. ..
The lubricating oil scattered above the drive shaft 9 travels downward along the oil seal 50. The lubricating oil is sealed by the oil seal 50 and then discharged by the oil discharge path 46.

According to the above embodiment, the oil seal 50 can seal the lubricating oil leaked from the mechanical seal 18. This makes it possible to prevent the clutch from slipping due to the adhesion of the lubricating oil. Further, by introducing the lubricating oil fastened by the oil seal 50 into the opening 48, the lubricating oil can be discharged through the oil discharge path 46.

Further, since the gap G is provided between the lip portion 52 and the drive shaft 9, the contact between the lip portion 52 and the drive shaft 9 is eliminated, so that the wear of the lip portion 52 can be suppressed.

Further, the diameter of the drive shaft 9 is D, the distance between the lip portion 52 and the outer peripheral surface 9B of the drive shaft 9 is C, and the radial distance C between the lip portion 52 and the drive shaft 9 is 0 <C. By specifying with the formula / D <0.08, leakage of lubricating oil can be reliably prevented.

Further, since a part of the opening 48 overlaps with the base 51 when viewed from the radial direction, the lubricating oil overflowing from the base 51 of the oil seal 50 is immediately introduced into the opening 48. As a result, the lubricating oil retained by the oil seal 50 can be quickly discharged.

Although the embodiment of the present invention has been described in detail with reference to the drawings, the specific configuration is not limited to this embodiment and includes design changes and the like within a range not deviating from the gist of the present invention. ..
For example, in the above embodiment, an example applied to a scroll type compressor has been described as an example of the open type compressor 1, but other types such as a rotary type, a swash plate type, a reciprocating type, and the like may be used for the open type compressor 1. Can be applied in the same way.

1 Open type compressor 2 Housing 3 Housing body 3A Front housing 3B Rear housing 6 Bearing member 6A Radial bearing 8 First rolling bearing 9 Drive shaft 9A Crank pin 9B Outer peripheral surface 10 Pulley 11 Electromagnetic clutch 11A Rotor 11B Belt groove 12 Through hole 12A Inner peripheral surface 13 Boss 13A Boss body 13B Flange 14 Second rolling bearing 15 Electromagnetic coil unit 16 Armature 16A Hub 16B Armature plate 16C Leaf spring 18 Mechanical seal 19 Compression mechanism 20 Fixed scroll 20A End plate 21 Swivel scroll 21A Plate 22 Compression chamber 24 Discharge port 25 Discharge valve 26 Discharge cavity 27 Discharge port 28 Boss 29 Drive bush 30 Swivel bearing 31 Thrust bearing 32 Rotation prevention mechanism 33 Suction port 34 Suction cavity 35 Oil reservoir 36 Suction passage 37 Refueling pump 39 Pump room 41 Lump 46 Oil discharge route 47 Oil discharge route Main body 48 Opening 50 Oil seal 51 Base 52 Lip 53 Metal ring 60 Mating ring 61 O ring 62 Case 63 O ring 64 Seal ring 65 Coil spring A Axis Da Axis direction Da1 Axis One side in the direction Da2 The other side in the axial direction V Internal space

Claims (3)

A housing having an internal space and a through hole that communicates the internal space with the outside.
A compression mechanism that is housed in the internal space and compresses the gas,
A drive shaft that is connected to the compression mechanism and whose one end in the axial direction protrudes to the outside.
A clutch provided at one end of the drive shaft on one side in the axial direction,
A mechanical seal arranged between the inner peripheral surface of the through hole and the outer peripheral surface of the drive shaft to seal the gas and liquid leaking from the compression mechanism.
A base portion provided on one side of the mechanical seal in the axial direction between the inner peripheral surface of the through hole and the outer peripheral surface of the drive shaft and fixed to the inner peripheral surface of the through hole, and a solid elastomer. An oil seal having a lip portion formed by the base and protruding radially inward from the base.
An opening that opens to the inner peripheral surface of the through hole, an opening that opens to the inner peripheral surface of the through hole, an opening that opens to the inner peripheral surface of the through hole, an opening that opens to the inner peripheral surface of the through hole, and an opening that opens to the inner peripheral surface of the through hole on the other side of the base in the axial direction from the end on one side in the axial direction, and the opening and the housing. With an oil discharge path body that connects to the outer surface of the
The lip part is
A protrusion protruding inward in the radial direction from one end of the base in the axial direction,
A lip tip portion that protrudes from the radially inner end of the protruding portion to the other side in the axial direction and is located on one side in the axial direction from the end portion of the base portion on the other side in the axial direction.
Have,
A part of the opening overlaps with the base when viewed from the radial direction, and a portion of the opening different from the part of the opening does not overlap with the base when viewed from the radial direction. .. The open compressor according to claim 1, wherein a gap is provided between the radial inner end of the lip tip and the outer peripheral surface of the drive shaft. Let D be the diameter of the drive shaft, and C be the radial distance between the lip portion and the outer peripheral surface of the drive shaft.
0 <C / D <0.08
The open compressor according to claim 2.

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