WO1998029660A1

WO1998029660A1 - Structure for recovering leakage oil in compressor

Info

Publication number: WO1998029660A1
Application number: PCT/JP1996/003823
Authority: WO
Inventors: Kazuya Kimura; Masafumi Ito
Original assignee: Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Priority date: 1995-12-18
Filing date: 1996-12-26
Publication date: 1998-07-09
Also published as: EP0887550A4; EP0887550A1; KR100292784B1; KR19990087230A

Abstract

A housing (11, 12, 13) houses a compression mechanism. A driving shaft (15) is supported by the housing (11, 12, 13) and is connected to the compression mechanism. A boss (16) is provided on the external wall of the housing (11, 12, 13) so as to surround the portion of the driving shaft (15) which projects from the housing (11, 12, 13). A rotor (18) is connected to the driving shaft (15) and transmits the power of an external driving source to the driving shaft (15). A shaft sealing device (17) is disposed in the housing (11, 12, 13) and seals the gap between the driving shaft (15) and the inner circumferential surface of the housing (11, 12, 13). A recovery unit (35, 36, 38) is provided for recovering a leakage oil which leaks from the shaft sealing device (17). A stepped portion (40) is formed to extend around the periphery of a rotating portion (15, 21α) which is positioned on the side of an opening (16α) of the boss (16) with respect to the shaft sealing device (17) in the housing (11, 12, 13). The stepped portion (40) is disposed opposite to the recovery unit (35, 36, 38).

Description

Description Structure for collecting oil leaked from a compressor

The present invention relates to, for example, a compressor used for an air conditioner of a vehicle, and more particularly to a structure for collecting oil leaking from inside the compressor. Background art

As this type of compressor, for example, there is a technique disclosed in Japanese Utility Model Laid-Open Publication No. 55-39328. That is, as shown in FIG. 5, the drive shaft 51 is supported by a housing 52 that houses the compression mechanism. The drive shaft 51 is connected to the compression mechanism, and a part of the drive shaft 51 projects from the housing 52. The boss 53 is provided on the outer wall surface of the housing 52 and surrounds the protruding end of the drive shaft 51. The shaft sealing device 54 is interposed between the boss 53 and the drive shaft 51 to seal the inside of the housing 52. The rotor 56 of the electromagnetic clutch 55 is rotatably supported by the boss 53. The armature 57 of the electromagnetic clutch 55 is fixed to the projecting end of the drive shaft 51 via the hub 58.

Accordingly, by excitation of the core 59 arranged on the rotor 56 side, the armature 57 is attracted to the rotor 56, and the driving force from the vehicle engine is transmitted to the drive shaft 51. Then, the compression mechanism is operated by the rotation of the drive shaft 51, and the refrigerant gas is compressed.

By the way, in the compressor having the above-described configuration, the seal member is hardened by frictional heat between the continuously rotating drive shaft 51 and the seal member of the shaft sealing device 54, and the seal member deteriorates with time. However, the sealing function of the shaft sealing device 54 is degraded due to foreign matter entering the seal portion. Therefore, the lubricating oil inside the housing 52 does not leak out of the housing 52 through the opening 53a of the boss 53. This leaked lubricating oil is attached to, for example, the suction surface of the electromagnetic clutch 55. For this reason, rotor 5 6 and armature 5

7 and slippage occurred, reducing the power transmission efficiency. Therefore, in the technology of the above publication, the ring-shaped damming member 60 is disposed on the periphery of the boss portion 53 around the opening 53 a of the boss portion 53 from the shaft sealing device 54. The damping member 60 blocks the leaked lubricating oil that is to be moved to the opening 53 α side along the inner peripheral surface of the boss 53. The oil absorbing member 61 is held by a housing 52, and the oil absorbing member 61 is connected to the inner space of the boss portion 53 via an oil guide passage 62. The oil guide passage 62 is open on the inner peripheral surface of the boss 53 between the damming member 60 and the shaft sealing device 54. Accordingly, the leaked lubricating oil blocked by the damming member 60 is guided to the oil absorbing member 61 through the oil guide passage 62, and is absorbed and held by the oil absorbing member 61.

However, some of the leaked lubricating oils travel along the surface of the drive shaft 51 in a film form. In addition, a gap is provided between the dam members 60 and 60 so that the dam members 60 do not cause sliding contact with the drive shaft 51. Therefore, according to the technique disclosed in the above publication, the leakage lubricating oil transmitted on the surface of the drive shaft 51 is guided to the oil absorbing member 61, that is, the leakage lubricating oil is transmitted from the damming member 60 to the shaft sealing device 54 on the drive shaft 5 side. Could not drop from 1.

In order to solve such a problem, for example, there is a technique disclosed in Japanese Utility Model Laid-Open Publication No. H11-124394. In the technique of the publication, as shown by a two-dot chain line in FIG. Mated. The lubricating oil traveling on the outer surface of the drive shaft 51 is shaken off from the ring member 63 toward the shaft sealing device 54 of the dam member 60 by centrifugal force.

However, in the technique disclosed in Japanese Utility Model Application Laid-Open No. 1-124394, the following problem has occurred.

(1) A ring member 63 separate from the drive shaft 51 is required, and the number of components constituting the compressor increases.

(2) At the time of assembling the compressor, a step of fitting the ring member 63 to the drive shaft 51 is required, so that the number of steps is increased and there is no flexibility in the assembling order. That is, after the ring member 63 is mounted on the drive shaft 51, the ring member 63 becomes an obstacle and the shaft sealing device 54 is moved to a predetermined position between the drive shaft 51 and the boss portion 53. Place I can't do that. In other words, it is impossible to fix the ring member 63 to the drive shaft 51 in advance and insert the drive shaft 51 into the housing 52. Therefore, assembling of the ring member 63 must be performed in the narrow inner space of the boss 53, which is a troublesome operation.

(3) The ring member 63 protruding into the inner space of the boss part 53 enhances the shielding between the shaft sealing device 54 and the housing 52, and the thermal environment of the shaft sealing rhino 54 is severe. Become. This causes the seal member of the shaft sealing device 54 to thermally deteriorate.

SUMMARY OF THE INVENTION The present invention has been made in view of the problems existing in the prior art described above, and has as its object to reduce leakage oil transmitted through a drive shaft with a simple configuration without increasing the number of parts in an inner space of a housing. An object of the present invention is to provide a structure for collecting leaked oil in a compressor that can be dropped at a predetermined position. Disclosure of the invention

In order to achieve the above object, a compressor of the present invention includes a housing for accommodating a compression mechanism. The drive shaft is supported by the housing and connected to the compression mechanism. The boss portion is provided on an outer wall surface of the housing so as to surround a protruding portion of the drive shaft from the housing. The rotating body is connected to the drive shaft, and transmits power from an external drive source to the drive shaft. The shaft sealing device is disposed in the inner space of the housing, and seals between the inner peripheral surface of the housing and the drive shaft. The recovery means is provided for recovering oil leaked from the shaft sealing device. The step portion is recessed on the outer peripheral surface of the rotating portion located on the opening side of the boss portion with respect to the shaft sealing device in the inner space of the housing. This step is provided so as to face the collecting means.

Therefore, according to the present invention, of the leaked oil due to the deterioration of the sealing function of the shaft sealing device, the oil that travels along the inner peripheral surface of the boss portion is recovered by the recovery means. Therefore, the leaked oil is not scattered toward the rotating body through the opening of the boss.

In addition, leaked oil that travels in a film form on the drive shaft is stopped at a step formed in a rotating portion such as the drive shaft or a rotating body, and is shaken down toward the inner peripheral surface of the boss by centrifugal force. Then, it is collected by the collecting means in the same manner as described above. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the present invention. FIG. 2A is an enlarged view of a main part of FIG.

FIG. 2 (b) is an enlarged view of a main part of FIG. 2 (a).

FIG. 3A is an enlarged cross-sectional view of a main part of the compressor according to the second embodiment.

FIG. 3B is a front view showing a part of the hub in the second embodiment.

FIG. 4A is an enlarged sectional view of a main part of a compressor according to the third embodiment.

FIG. 4B is a rear view showing a part of the cushion rubber according to the third embodiment. FIG. 5 is an enlarged sectional view of a main part showing a conventional compressor. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, an embodiment in which the present invention is embodied in a compressor for a vehicle air conditioner will be described. In the second and third embodiments, the same members as those in the first embodiment are denoted by the same reference numerals.

(First Embodiment)

First, a first embodiment will be described with reference to FIGS. As shown in FIG. 1, the front housing 11 is joined and fixed to the front of the cylinder block 12. The rear housing 13 is joined and fixed to the rear of the cylinder block 12 via a valve plate 34. The crank chamber 14 is formed by an air gap surrounded by the cylinder block 12 and the front housing 11. The drive shaft 15 is rotatably supported by the front housing 11 and the cylinder block 12 so as to pass through the crank chamber 14. The front end of the drive shaft 15 projects outward from the front housing 11. The boss 16 is integrally formed on the outer wall surface of the front housing 11 so as to surround the protruding end of the drive shaft 15.

As shown in FIG. 2, the lip seal 17 as a shaft sealing device is disposed in the inner space of the boss portion 16, and the lip ring 17 "of the lip seal 17 is driven by the pressure in the crank chamber 14. The crank chamber 14 is sealed by being pressed against the shaft 15.

The electromagnetic clutch 18 as a rotating body is connected to a vehicle end (not shown) as an external drive source. It is interposed between the gin and the drive shaft 15. That is, the rotor 19 constituting the electromagnetic clutch ¹⁸ is rotatably supported on the outer peripheral surface of the boss 16 via the angular bearing 20. A belt 42 connected to the vehicle engine is wound around the outer periphery of the rotor 19. The hub 21 is fixed to the protruding end of the drive shaft 15 with a bush 21 α formed integrally with the hub. The armature 22 is fixed to the hub 21 via a circular cushion rubber 23. The cushioning rubber 23 is located on the power transmission path between the hub 21 and the armature 22, and the elastic force of the cushioning rubber 23 periodically transmits the driving torque transmitted to the belt 42 via the rotor 19. Small fluctuations.

When the core 24 accommodated in the rotor 19 is excited, the armature 22 is piled on the spring force of the cushion rubber 23 supporting the armature 22 and pressed against the rotor 19. Therefore, the driving force of the vehicle engine is transmitted to the drive shaft 15. Further, when the core 24 is demagnetized, the armature 22 is separated from the rotor 19 by the panel force of the cushion rubber 23, and the transmission of the driving force is interrupted.

Next, the compression mechanism housed in the crank chamber 14 will be described.

As shown in FIG. 1, the lug plate 25 is press-fitted and fixed to the drive shaft 15, and a guide hole 25) 3 is formed in the support arm 25α of the lug plate 25. The swash plate 26 is supported so as to be tiltable and slideable with respect to the drive shaft 15. The guide pin 26α is fixed to the swash plate 26 and is engaged with the guide hole 25 | 3. Therefore, the swash plate 26 can swing in the direction of the axis L, and can rotate together with the drive shaft 15.

The cylinder bore 12a is formed in the cylinder block 12, and connects the crank chamber 14 with the suction chamber 13α and the discharge chamber 13β in the rear housing 13 to each other. The single-headed piston 27 is housed in the cylinder bore 12α. The swash plate 26 is moored with a single-headed piston 27 via a pair of shoes 28 in a state of entering into a recess 27 formed in a single-headed biston 27. Therefore, the rotating motion of the swash plate 26 is converted to the back and forth reciprocating motion of the single-headed biston 27 via the shoe 28. As a result, the refrigerant gas is sucked from the suction chamber 13α into the cylinder pore 12α via the suction valve 34α of the valve plate 34, and the sucked refrigerant gas is compressed. While being discharged to the discharge chambers 13 | 8 through the discharge valve 34/4.

The pressure supply passage 29 connects the discharge chamber 13) 3 to the crank chamber 14, and the electromagnetic valve ³⁰ is disposed on the pressure supply passage 29. When the solenoid 30 α of the solenoid valve 30 is excited or de-energized, the spool 30) 3 closes or opens the port 30 γ, that is, the pressure supply passage 29 is closed or opened. .

By opening and closing the pressure supply passage 29, the differential pressure between the pressure in the crank chamber 14 acting before and after the single-headed piston 27 and the pressure in the cylinder bore 12a is adjusted, and the swash plate 2 The tilt angle of 6 is controlled.

In other words, when the pressure supply passage 29 is closed, the pressure in the crank chamber 14 is only released to the suction chamber 13 α via the pressure release hole 31 and the pressure release passage 32. The suction chamber 13 approaches the low pressure of α. Therefore, the tilt angle of the swash plate 26 is maintained at the maximum tilt angle, the piston stroke increases, and the discharge capacity increases. When the pressure supply passage 29 is open, the high pressure in the discharge chamber 13 β is introduced into the crank chamber 14, and the inclination of the swash plate 26 is increased by the increase in the pressure of the crank chamber 14 內. Is shifted to the minimum inclination. Therefore, the discharge capacity is reduced.

The maximum inclination angle of the swash plate 26 is defined by the contact between the stopper 2613 provided on the swash plate 26 and the lug plate 25. Further, the minimum inclination is defined by the contact between the swash plate 26 and the ring 33 attached to the drive shaft 15.

Next, features of the present embodiment will be described.

As shown in FIGS. 2 (a) and 2 (b), the ring-shaped damming member 35 is formed on the inner peripheral surface of the boss 16 by an opening 16 a of the boss 16 from the lip seal 17. Fixed on the side. The felt-made oil absorbing member 36 is accommodated and arranged in an accommodating portion 37 recessed at a lower portion of the outer wall surface of the front housing 11. The oil guide passage 38 extends from the peripheral wall of the boss portion 16 to the outer wall surface of the front housing 11, and the oil guide passage 38 connects the oil absorbing member 36 to the inner space of the boss portion 16. I have. The oil guide passage 38 is opened on the inner peripheral surface of the boss 16 between the dam member 35 and the lip seal 17. In the present embodiment, the collecting means includes the dam member 35, the oil absorbing member 36, the oil guide passage 38, and the like. In addition, the formation position of the storage part 37 is in a horizontal plane including the axis L of the drive shaft 15 (the axis L of this compressor is It is arranged in the engine room so that it is almost horizontal. The drive shaft 1 5, the outer diameter between the portion 1 5 0 sites 1 5 _alpha and the hub 2 1 Bush 2 1 alpha lip seal 1 7 is in sliding contact is secured is, both sites 1 The diameter is smaller than 5 and 15. Then, the annular groove 39 is formed at a position corresponding to a portion between the lip seal 17 and the dam member 35 constituting a part of the collecting means in the small-diameter portion 15 γ of the drive shaft 15. ing. The corner portion connecting the inner bottom surface of the annular groove 39 and the wall surface 40α is formed in a curved shape. The step on the side of the lip seal 17 that forms the annular groove 39 forms a step 40 in the present embodiment. The inner wall surface 40α of the step portion 40 is substantially perpendicular to the axis L.

The plurality of through holes 41 as pressure adjusting means are formed in the hub 21 of the electromagnetic clutch 18 at positions facing the openings 16 a of the boss 16. Due to the through holes 41, even when the armature 22 is pressed against the rotor 19, a space A surrounded by the electromagnetic clutch 18 and the boss 16 is opened to the outside of the compressor. By the way, when the sealing function of the lip seal 17 is deteriorated, the lubricating oil in the crank chamber 14 leaks over the lip seal 17. The leaking lubricating oil tends to move to the opening 16 α side along the circumferential surface of the boss 16, but since the damming member 35 is opposed to the flow of the leaking lubricating oil, any further Movement is blocked. Therefore, the leak lubricating oil is retained between the dam member 35 and the lip seal 1 において in the lower part of the space inside the boss portion 16. The stopped lubricating oil is guided to the oil absorbing member 36 through the oil guide passage 38 opened to the stopped portion, and is absorbed and held by the oil absorbing member 36.

Here, part of the leaked lubricating oil forms a film on the outer surface of the drive shaft 15 and tends to move to the opening 16 _α side of the boss 16 along the outer surface of the drive shaft 15. . However, the leakage lubricating oil is prevented from further moving to the opening 16α side at the step portion 40 of the annular groove 39. That is, since the wall surface 40α of the step portion 40 is substantially perpendicular to the axis L, the leakage lubricating oil transmitted on the surface of the drive shaft 15 resists the centrifugal force caused by the rotation of the drive shaft 15. The wall 40 α cannot be moved to the axis L side.

Therefore, the leaked lubricating oil stays at the outer edge of the step portion 40 and the centrifugal force Is swung in a radial direction perpendicular to the axis L. The leaked lubricating oil that has been shaken off is guided to the oil absorbing member 36 through the oil guide passage 38 by its own weight, and is absorbed and held by the oil absorbing member 36.

By the way, in the conventional compressor shown in FIG. 5, when the drive shaft 51 is rotated at high speed, the space A surrounded by the electromagnetic clutch 55 and the boss 53 becomes negative pressure. . This is because the air in the space A is sucked out by centrifugal force from the slight gap of the suction surface in the suction state between the armature 57 of the electromagnetic clutch 55 and the rotor 56 due to the excitation of the core 59. it is conceivable that. Due to this phenomenon, the fluidity of the leaked lubricating oil in the oil guide passage 62 is deteriorated, and the leaked lubricating oil is more likely to pass through the dam member 60. Therefore, the leaked lubricating oil flows out of the opening 53 a of the boss portion 53 over the dam member 60.

However, in the present embodiment, the space れた surrounded by the electromagnetic clutch 18 and the boss 16 is opened to the outside of the compressor by the through hole 41 formed in the haptic 21 of the electromagnetic clutch 18. Have been. Therefore, the inside of the space A does not always have a negative pressure, and the leakage of the lubricating oil from the damming member 35 can be prevented.

As described above, almost all of the lubricating oil leaked from the lip seal 17 can be recovered by the oil absorbing member 36. For this reason, it is possible to prevent the adverse effect caused by the leakage lubricating oil scattered through the opening 16α of the boss portion 16, for example, the adverse effect such as slippage of the electromagnetic clutch 18.

The first embodiment having the above configuration has the following effects.

(1 -1) With a simple configuration, only an annular groove 39 is recessed on the outer peripheral surface of the drive shaft 15, leakage lubricating oil transmitted on the outer surface of the drive shaft 15 is applied to the dam member 35. It can be reliably dropped to the lip seal 17 side. In addition, the implementation of this configuration does not involve an increase in the number of parts, and thus can prevent the compressor assembly process and the like.

(1-2) The annular groove 39 is, of course, not projected into the inner space of the boss 16. Therefore, by forming the annular groove 39, the lip seal 17 side is not sealed and the thermal environment does not become severe, and the annular groove 39 causes the thermal deterioration of the lip seal 17 Does not.

(1-3) The wall surface 40α of the step portion 40 is a vertical wall. Therefore, the table of drive shaft 15 The lubrication oil leaking down the surface is effectively shaken off at the step portion 40, and the drive shaft 15 is easily cut.

(1-4) The connecting portion between the bottom surface and the wall surface of the annular groove 39 has a circular curved surface. Therefore, the stress acting on the drive shaft 15 does not concentrate on the connection portion, and the strength reduction of the drive shaft 15 due to the provision of the annular groove 39 can be prevented.

(1-5) The space A surrounded by the electromagnetic clutch 18 and the boss 16 is opened to the outside of the compressor by a through hole 41 formed in the hub 21. Therefore, a negative pressure in the space A can be prevented, and leakage of lubricating oil from the lip seal 17 can be reduced. Further, the leaked lubricating oil can be smoothly sent to the oil absorbing member 36 via the oil guide passage 38. By providing this configuration together with the configuration of the step portion 40, the effect of collecting the leaked lubricating oil is enhanced.

(Second embodiment)

FIGS. 3 (a) and 3 (b) show a second embodiment. In the present embodiment, the outer opening 45α of the through hole 45 is disposed on the 內 side of the radial direction of the hub 21 from the inner opening 45β. Therefore, the through hole 45 is inclined with respect to the radial direction of the hub 21 to form a centrifugal fan. As a result, the outside air is positively introduced into the space 介 through the through hole 45 by the rotation of the hub 21.

The present embodiment has the following effects.

(2-1) The air gap A とする can be positive pressure, and the effect of (1-5) in the first embodiment is synergistically achieved.

(2-2) In order to introduce the outside air into the airspace A, it is not required separately from the ventilation holes 45 and other members. For this reason, the number of parts can be suppressed and the air blowing configuration can be simplified.

(Third embodiment)

FIGS. 4A and 4B show a third embodiment. In the present embodiment, in addition to the configuration of the second embodiment, a plurality of ventilation grooves 46α are formed in the radial direction on the surface of the cushioning rubber 46 facing the armature 22.

Therefore, the rotation of the hub 21 causes the through-hole 45 and the cushion rubber 46 to form a centrifugal fan, and an external air flow flowing through the through-hole 45 → space Α → vent groove 46α is formed. Due to this external air flow, the heat radiation effect of the hub 21 and the armature 22 is enhanced, and as a result, The temperature of the entire electromagnetic clutch 18 is reduced. This is effective in lowering the temperature of the lip seal 17 adjacent to the electromagnetic clutch 18, and can suppress the deterioration of the sealing function due to the thermal deterioration of the lip seal 17.

In addition, since a part of the outside air flow from the through hole 45 is introduced into the space A, the space A # can be maintained at a positive pressure.

The present invention can be practiced in the following modes without departing from the spirit of the present invention.

(1) a degree of inclination with respect to the axis L of the wall surface 40 _alpha of the stepped portion 40, to be gentle only slightly from a right angle. Or, conversely, overhang the outer edge wedge to make an acute angle.

(2) The oil absorbing member 36 is fixedly arranged at the radial position of the step portion 40 in the inner space of the boss portion 16.

(3) Omit the oil absorbing member 36 and provide a drain tank for storing leaked lubricating oil in the housing (11, 12, 23) of the compressor.

(4) The oil guide passage 38 shall be composed of a tube separate from the compressor housing (11, 12, 23). In this way, maintenance such as removal when foreign matter is clogged in the oil guide passage 38 can be easily performed only by removing the pipe.

(5) The dam section forest 35 is abolished, and the inner peripheral surface of the boss section 16 is inclined toward the opening side of the oil guide passage 38.

(6) In the second and third embodiments, the through hole 45 is inclined in the radial direction of the hub 21, but this is changed and the through hole 45 is inclined in the rotation direction of the hap 21.

(7) In the above embodiment, the rotating body is the electromagnetic clutch 18, but this may be changed to a pulley having no intermittent power structure. That is, the present invention may be embodied in a clutchless compressor.

(8) An annular groove 39 is formed on the outer peripheral surface of the push 21α (rotating part) of the hap 21 to form a step portion 40. In this case, the dam member 35 is moved to the opening 16α side of the boss 16 from the position shown in FIG.

(9) In the above embodiment, the compressor is a variable displacement swash plate compressor, but other compressors include a fixed displacement swash plate compressor, a scroll compressor, a wave force compressor, and the like. It may be embodied. (10) A blower fin shall be attached near the through hole 41 in the hub 21 and outside air shall be introduced into the space A by the blower fin. Industrial applicability

As described in detail above, in the compressor according to the present invention, not only can the adverse effect of the leaked oil be reliably prevented, but also the number of parts can be reduced by reducing the number of parts, and the compressor can be reduced in number. Can be easily assembled. Moreover, the thermal environment of the shaft sealing device can be improved.

Claims

The scope of the claims

1. a housing (11,12,13) for accommodating the compression mechanism;

A drive shaft (15) supported by the housing (11, 12, 23) and connected to the compression mechanism;

A boss (16) provided on an outer wall surface of the housing (11, 12, 23) and surrounding a protruding portion of the drive shaft (15) from the housing (11, 12, 23); A rotating body (18) connected to the drive shaft (15) and transmitting power from an external drive source to the drive shaft (15);

A shaft seal which is arranged in the space of the housing (11, 12, 13) and seals between the inner peripheral surface of the housing (11, 12, 13) and the drive shaft (15). Equipment (1 7)

Recovery means (35, 36, 38) for recovering oil leaked from the shaft sealing device (17)

In a compressor equipped with

In the inner space of the housing (1 1, 1 2, 1 3), the shaft sealing device <1 7) good rotating part (1 5 located in the opening (1 6 _alpha) side of Ribosu section (1 6), 2 A stepped portion (40) is recessed in the outer peripheral surface of 1α) so as to face the collecting means (35, 36, 38). .

2. The leakage oil recovery structure according to claim 1, wherein the wall surface (40α) of the step portion (40) is substantially perpendicular to the axis (L) of the drive shaft (15). Characterized by the leaked oil recovery structure.

3. In the leakage oil collecting structure according to claim 1 or 2, the step portion (40) forms an annular groove (39) on the outer peripheral surface of the rotating portion (15, 21α). A structure for recovering spilled oil, characterized by comprising

4. In the leakage oil recovery structure according to any one of claims 1 to 3, The collection means,

An oil-absorbing member (36) arranged outside the housing (11, 12, 13) and a boss portion on the peripheral surface of the housing (11, 12, 23) by a step (40) A ring-shaped damming member (3 5) arranged on the opening (16 α) side of (16),

An oil guide passage connecting the oil absorbing member (36) and the inner space of the housing (11, 12, 23) with an opening between the damming member (35) and the shaft sealing device (17); (3 8) and

A structure for collecting leaked oil, comprising:

5. The leaked oil recovery structure according to claim 4, wherein the rotating body (18) includes a space (Α) surrounded by the rotating body (18) and the boss portion (16). A leaked oil recovery structure characterized by a pressure adjusting means (41) for preventing negative pressure.

6. The leaked oil recovery structure according to claim 5, wherein the pressure adjusting means opens a space (Α) between the rotating body (18) and the boss (16) to the outside of the compressor. A leaking oil recovery structure characterized by including a through hole (41; 45) formed in the rotating body (18).

7. The leaked oil recovery structure according to claim 6, wherein the rotating body (18) includes an air gap (Α) surrounded by the rotating body (18) and the boss portion (16). A structure for collecting leaked oil, characterized in that a ventilation means (45) is provided for actively introducing outside air to the area.

8. The leaked oil collecting structure according to claim 7, wherein the blower means is configured such that a through hole (45) forms an oblique hole.