JPH07224762A - Fluid compressor - Google Patents

Abstract

PURPOSE:To improve the oiling efficiency and secure the lubrication in a sliding section by preventing the disturbance of the high-pressure fluid obtained by compression or the lubricant of the oil sump of a driver, which rotates a cylinder. CONSTITUTION:This fluid compressor is equipped with an oiling mechanism S which soaks oil suckers 20a and 20b in the lubricant of a oil sump 19 collecting lubricant in a sealed case 2 and feeds lubricant sucked with these oil suckers to each sliding section, and herein at least either a guide cover 18 or a wave preventive plate 22 as an oil disturbance preventive member is provided in the vicinity of the oil sucker of this oiling mechanism.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid compressor for compressing a refrigerant of a refrigeration cycle, for example.

[0002]

2. Description of the Related Art For example, a fluid compressor (hereinafter referred to as a compressor) has been proposed by the present applicant. this is,
The cylinder and piston are eccentrically arranged in the closed case,
A spiral groove having a gradually smaller pitch is formed in the piston. A spiral blade is also fitted in this groove.

The blade is divided into a plurality of spaces between the cylinder and the piston, and a plurality of working chambers whose volume is gradually reduced are formed in the cylinder from one end side to the other end side.

The rotational force of the cylinder is transmitted to the piston through the rotational force transmission mechanism, and the cylinder and the piston rotate while maintaining the positional relationship. Further, as the blades rotate, the blades move in and out of the groove, and project and retract in the radial direction of the piston.

A compressed gas, for example, a refrigerant gas in a refrigeration cycle is sucked into the cylinder and is transferred from the suction chamber located on the most suction side of the working chambers to the discharge chamber located on the most discharge side. , And gradually compressed during transfer.

When it reaches the discharge chamber, it rises to a predetermined pressure and is once discharged into the closed case through a guide hole provided in the cylinder. The high-pressure gas filled in here is introduced into the refrigeration cycle from the discharge pipe connected to the closed case.

[0007]

By the way, an oil reservoir for collecting lubricating oil is formed in the closed case. The oil suction portion of the oil supply mechanism is immersed in the lubricating oil of the oil sump portion. This oil supply mechanism acts to suck up the lubricating oil with the rotation of the rotating body, and between the cylinder shaft portion and the bearing member, between the piston shaft portion and the bearing member, between the blade and groove, and between the blade and Oil is supplied to and from the cylinder and all other sliding parts.

However, when the gas whose pressure has been increased in the working chamber in the cylinder is guided out through the discharge guide hole into the closed case, a part of this high pressure gas is used as the lubricating oil surface of the oil reservoir. Be sprayed on.

Due to this effect, the oil surface fluctuates or bubbles, and the lubricating oil is further disturbed. It is conceivable that the lubricating oil wets the guide hole due to the fluctuation of the oil surface, and the high-pressure gas blows directly into the lubricating oil. On the other hand, since the oil suction portion of the oil supply mechanism is immersed in the lubricating oil in the oil sump portion, the smooth suction is hindered due to the disturbance of the lubricating oil.

Also in this type of compressor, the operating frequency may be adjusted to adapt to the load, and the cylinder may be driven to rotate at high speed. At this time, the oil level shakes further and the oil supply efficiency decreases. There is a fear of.

Further, the rotor of the electric motor unit, which is a rotary drive source, is fitted to the cylinder, and it is set so as to be at a position on the oil level of the lubricating oil. If there is swaying, a part of the lubricating oil will come into contact with the rotor, resulting in agitation. That is, the swaying of the oil level is expanded, and the oil supply efficiency is further reduced.

The present invention has been made in view of the above circumstances, and its object is to disturb high-pressure fluid obtained by compression or to disturb the lubricating oil in an oil sump portion by a driving source for rotationally driving a cylinder. The present invention is to provide a fluid compressor that prevents the above-mentioned problem, improves the oil supply efficiency by reliably sucking oil, and ensures the lubricity in the sliding portion.

[0013]

In order to achieve the above object, a fluid compressor according to a first aspect of the present invention is characterized in that, in claim 1, a hermetically sealed case accommodates a cylinder which is rotationally driven. The rotator having a spiral groove formed at a gradually decreasing pitch is eccentrically arranged, and a spiral blade is inserted into and retractable from the groove, and the volume is gradually divided by the blade in the cylinder. A plurality of small working chambers are formed, the cylinder and the rotating body are synchronously rotated, and the compressed fluid sucked into the cylinder is gradually transferred to the working chamber to be compressed. An oil sump for collecting lubricating oil is provided in the sealed case, the oil suction part is immersed in the lubricating oil of this oil sump, and the lubricating oil sucked up by this oil suction part is supplied to each sliding part. This refueling system is equipped with Characterized by providing an oil disrupting preventing member in the vicinity of the oil suction portion of the structure.

According to a second aspect of the present invention, in the oil disturbance preventing member according to the first aspect, at least the lubricating oil surface of the oil sump portion and the fluid whose pressure has been increased to a predetermined pressure in the working chamber are temporarily introduced into the closed case. It is characterized in that it is provided between the lead-out guide hole for guiding. In Claim 3, the oil disturbance prevention member according to Claim 1 is provided at least between the oil suction portion of the oil supply mechanism and the rotary drive source of the rotating body.

[0015]

Even if the lubricating oil in the oil sump is disturbed, the oil disturbance preventive member prevents the oil suction part from being affected, so that the lubricating oil is sucked up reliably. Further, since the oil disturbance preventive member is provided between the lubricating oil surface and the guide hole, the high pressure gas discharged from the guide hole is not blown onto the lubricating oil surface, so that there is no disturbance of the lubricating oil.

Further, since the oil disturbance preventing member is provided between the oil suction portion of the oil supply mechanism and the rotary drive source of the rotating body, even if the oil surface is disturbed by the rotary drive source, the oil suction portion can reach the oil suction portion. It will not be affected.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIG. The compressor body 1 is composed of a hermetic case 2 whose both ends whose axial direction is oriented in the horizontal direction is closed, and a compression mechanism section 3 and an electric motor section 4 which are housed in the hermetic case 2.

The compression mechanism section 3 has a cylinder 5 made of a hollow cylinder whose both ends are open, and a rotor 6 is fitted on the outer peripheral surface of this cylinder. A stator 7 is fitted on the inner peripheral surface of the closed case 2, and the rotor 6 and the electric motor portion 4 are configured. The electric motor section 4 is a rotary drive source for rotationally driving the cylinder 5.

A piston 8 as a rotating body is eccentrically arranged in the cylinder 5. That is, a part of the peripheral wall of the piston 8 along the axial direction is accommodated so as to be in rolling contact with a part of the inner peripheral wall of the cylinder 5 along the axial direction.

On the peripheral surface of the piston 8, a pair of left and right spiral grooves 9 and 9 having a pitch gradually decreasing from the center to both ends are formed, and a spiral blade is formed in each groove. 10 and 10 are fitted in freely. Therefore, the space between the cylinder 5 and the piston 8 is divided into a plurality of spaces by the blades 10 on the left and right sides of the central portion as a boundary. In the cylinder 5, a plurality of working chambers 11, 11 are formed whose volume is gradually reduced from the center of the cylinder to both end sides, that is, from the suction side to the discharge side.

The main shaft 8 and the auxiliary shaft 8 are provided at both ends of the piston 8.
a and 8b are formed, and these shafts are fixed to the inner wall of the hermetically sealed case 2. The pivotal support hole 12 of the main and auxiliary bearings 12 and 13 is formed.
It is inserted into a and 13a and is rotatably supported.

The pivot holes 12a and 13a are provided eccentrically in the main and auxiliary bearings 12 and 13, and the piston 8 inserted therein is pivotally supported in an eccentric position.

The main bearing 12 in the closed case 2
A suction pipe 14 is connected to a portion communicating with the pivot hole 12a. A suction guide passage 15 communicating with the suction pipe 14 through the pivot hole 12a is provided from the end surface of the main shaft portion 8a of the piston 8 in the axial direction.

The leading end of the suction guide passage 15 is formed in a bent shape at substantially the center of the piston 8 and opens at this peripheral surface. This opening position corresponds to the pair of left and right blades 1 described above.
It corresponds to a value between 0 and 10.

Each of the main and sub bearings 12, 13 is a flange portion 12 which is attached and fixed to the inner wall of the hermetically sealed case 2.
b, 13b, and pivot support shaft portions 12c, 13c integrally projectingly provided on the flange portion.

On the other hand, the cylinder bearings 16 and 16 made of metal are press-fitted to the inner peripheral surfaces of both ends of the cylinder 5, respectively, and the outer peripheral surfaces of the pivot shaft portions 12c and 13c of the main and auxiliary bearing members 12 and 13, respectively. Intervened between.

Each cylinder bearing 16 is formed in a thick ring shape, and one side surface of the cylinder bearing 16 is the main bearing and the sub bearing 1.
The end faces of the pivot shaft portions 12c and 13c of the shafts 2 and 13 are flush with each other. The other side is flush with the cylinder 5 end face,
There is a gap between the flanges 12b and 13b of the bearings 12 and 13.

Further, each cylinder bearing 16 is provided with a plurality of lead-out guide holes 17 ... Which are provided along the axial direction and open on both side surfaces of the bearing. There are at least one pair of these guide guide holes 17 at symmetrical positions in the radial direction of the cylinder bearing 16.

Guide covers 18, 18 which are first oil disturbance preventing members are attached to the end faces of the flange portions 12b, 13b of the main and auxiliary bearings 12, 13, respectively. As shown in FIG. 2, the guide cover 18 is positioned to cover the outer peripheral surface of the end portion of the cylinder 5 with a gap, and the flange portion 12b,
An end surface opposite to the mounting portion for 13b is open. That is, the guide cover 18 is a hollow cylindrical body having a short axial length.

As shown in FIG. 1 again, an oil reservoir 19 for collecting lubricating oil is formed at the inner bottom of the closed case 2. The height of the lubricating oil surface of the oil reservoir 19 is set lower than the height of the bottom of the guide cover 18.

Oil suction pipes 20a and 20b are connected to the main and auxiliary bearings 12 and 13, respectively. In addition, the upper end portions of the oil suction pipes 20a and 20b are provided on the main and auxiliary bearing flange portions 12b and 13b, respectively.
oil supply passages 21a, 21 provided in communication with a, 13a
It is connected to one end of b. And the oil suction pipe 20a,
The lower end of 20b is immersed in the lubricating oil of the oil sump 19.

The oil supply passage 21a provided in the main bearing 12 is open to the pivot hole 12a as described above, but the piston main shaft 8a faces the opening end here.

The open end of the oil supply passage 21b provided in the sub bearing 13 faces the space between the end face of the piston sub shaft 8b and the end face of the pivot hole 13a. This auxiliary shaft portion 8b
An oil guide passage 22 is provided along the axial direction of the piston 8 from the end surface.

The midway portion of the oil guide passage 22 is the auxiliary shaft portion 8b.
It is branched so as to open to the peripheral surface, and the tip portion is bent and formed to open to the peripheral surface of the piston 8. In this way, each bearing 1
The oil suction pipe 2 is provided on both ends of the pistons 2 and 13 and the piston 8.
An oil supply mechanism S including 0a, 20b and oil supply passages 21a, 21b is provided.

Further, the oil sump portion 19 has a second position between the rotor 6 and the stator 7 constituting the electric motor portion 4, in other words, between the electric motor portion 4 and the oil suction pipes 20a, 20b. Wave breaker plates 22 and 22 which are oil disturbance prevention members of No. 2
Is provided.

As shown in FIG. 3, this wave preventing plate 22 is
Its upper edge is at a position higher than the height of the lubricating oil surface. This position is also higher than the bottom of the rotor 6. Further, a plurality of through holes 23 ... Are provided in the portion of the oil sump portion 19 where the lubricating oil is immersed, and the lubricating oil is conducted and guided.

As shown in FIG. 1 again, the Oldham mechanism 24 as a mechanism for transmitting the rotational force of the cylinder 5 to the piston 8 is provided between the cylinder bearing 16 on the auxiliary bearing 13 side and the shaft end surface of the piston 8. On the other hand, a discharge pipe 25 is connected to the end of the closed case 2.

The compressor constructed in this way is
As the motor section 4 is energized, the rotor 6 and the cylinder 5
And rotate together. The rotational force of the cylinder 5 is transmitted to the piston 8 via the Oldham mechanism 24. The piston 8 is pivotally supported at an eccentric position with respect to the cylinder 5, but due to the action of the Oldham mechanism 24, the cylinder 5 and the piston 8 have a relative peripheral speed due to the difference in radius between them.
In addition, they rotate synchronously while maintaining their mutual positional relationship.

With the rotation of the cylinder 5 and the piston 8, a pair of blades 10, 10 are simultaneously formed in the grooves 9,
It goes in and out of 9 and projects in and out in the radial direction of the piston. A compressed gas, for example, a refrigerant gas in a refrigeration cycle is sucked in from the suction pipe 14, and is passed through the pivotal support hole 12a formed in the main bearing 12 and the suction guide passage 15 to the cylinder 5
Is led to almost the center.

The substantially central portion of the cylinder 5 between the blades 10 and 10 is the working chamber located on the most suction side among the working chambers 11 formed on both the left and right sides, and from this point to the most discharging side. It is sequentially transferred to the working chambers on both the left and right ends to be located.

The refrigerant gas is gradually compressed while being sequentially transferred through these working chambers 11. Then, when it is transferred to the most discharge side working chambers 11, 11 at both left and right ends, the pressure rises to a predetermined pressure.

This high-pressure gas exits the working chamber 11 and is guided to the guide holes 17 ... Derived in the cylinder bearings 16, 16.
Once it collides with the flange end surfaces of the main and auxiliary bearings 12 and 13, it is guided into the gap between the outer peripheral surface of the cylinder 5 and the inner peripheral surface of the guide cover 18, and is guided into the closed case 2.

The high-pressure gas that is guided out into the closed case 2 and fills the sealed case 2 is guided to the discharge pipe 25 and discharged to the external refrigeration cycle equipment. The high-pressure gas led out from the cylinder 5 is guided by the guide cover 18 described above.
The presence of the oil fills the sealed case 2 without spraying the lubricating oil surface of the oil sump 19.

That is, since the guide cover 18 is interposed between the guide hole 17 and the lubricating oil surface, the lubricating oil surface is not directly affected by the high pressure gas, and the oil surface No disturbance occurs.

On the other hand, the oil supply mechanism S functions as the cylinder 5 and the piston 8 rotate. That is, the oil suction pipes 20a, 2 provided in the main and auxiliary bearings 12, 13
0b sucks up the lubricating oil in the oil reservoir 19.

At this time, since the oil level is not disturbed by the action of the guide cover 17, the oil suction pipes 20a and 20b smoothly suck up the lubricating oil. Then, it is guided to each sliding portion of the compression mechanism portion 3 via the oil supply passages 21a and 21b communicating with each other, and the lubricity thereof is secured.

The lubricating oil guided to each sliding portion and lubricated is mixed with the gas compressed in the working chamber 11 and finally discharged from the working chamber 11 on the discharge side together with the high pressure gas. That is, the guide hole 17 extending from the discharge side working chamber 11
Immediately after this, it is guided into the sealed case while repeatedly colliding with the end faces of the main and auxiliary bearing flange portions 12b and 13b and the guide cover 18.

By repeating such collisions, the oil droplets of the lubricating oil mixed with the high pressure gas are separated, and only the lubricating oil returns to the oil reservoir 19. Therefore, when the high pressure gas is discharged from the discharge pipe 25, the proportion of the lubricating oil mixed in this gas is reduced, and the oil level in the oil sump 19 is prevented from lowering.

Furthermore, the oil level of the lubricating oil in the oil sump 19 may fluctuate due to various factors such as the oil supply state. When the oil level rises, the cylinder 5 may come into contact with the rotor 6 that is being rotationally driven.

To explain further, at least the bottommost portion of the rotor 6 is immersed in the lubricating oil, and the lubricating oil is splashed and agitated as the rotor rotates. Along with that, the lubricating oil surface also shakes significantly.

However, here, the oil suction pipe 2 is used.
0a, 20b near both sides of the rotor 6, that is, between the rotor and the oil suction pipe.
Since this is installed, this wave preventive plate prevents the oil surface from shaking.

Therefore, even if the rotor 6 disturbs the lubricating oil, it prevents the oil surface of the wave preventive plate 22 provided near the oil suction pipes 20a and 20b from swaying and affects the oil suction pipe. I don't need it. Each oil suction pipe 20a, 20
b has a smooth oil suction action, and the oil supply mechanism S maintains a reliable oil supply action.

In the above embodiment, each cylinder bearing 16 is fitted on the inner peripheral surface of the cylinder 5 and is interposed between the pivot shaft portions 12c and 13c of the main and auxiliary bearing members 12 and 13, respectively. The sliding speed of the cylinder bearing is low, and a reduction in sliding loss can be obtained.

Since each of the cylinder bearings 16 is provided with a plurality of lead-out guide holes 17 penetrating both side end faces of the cylinder bearing 16, a sufficient flow rate of the compressed gas is secured to prevent abnormalities such as overcompression and overexpansion. By suppressing the state, the compression efficiency can be improved.

Further, in the above-mentioned embodiment, the guide cover 18 as the oil disturbance preventing member is formed in the shape of a hollow cylinder, but it is not limited to this, and as shown in FIG. The guide cover 18A may be curved in a lower semicircular shape so as to face the lubricating oil surface of 19.

Even with the guide cover 18A having such a shape, the high-pressure gas led out from the lead-out guide hole 17 of the cylinder bearing 16 is not directly sprayed on the lubricating oil surface of the oil sump portion 19, Therefore, the disturbance of the oil surface can be prevented.

A guide cover 18B as shown in FIG. 5 may be used. In this case, the guide cover 18B is made of a flat plate parallel to the oil surface, and the same action and effect as the guide cover 18A shown in FIG. 4 can be obtained.

Further, the wave preventing plate 22 serves as an oil disturbance preventing member.
Has its upper edge higher than the lubricating oil surface of the oil sump 19,
Moreover, although it is set at a position lower than the bottom of the cylinder 5, the present invention is not limited to this.

A wave preventive plate 22A as shown in FIG. 6, that is, a semi-circular cutout portion a along the lower portion of the cylinder 5 is provided, and its upper end edge is aligned at substantially the same height as the center axis position of the cylinder. May be.

In this case, even if the inside of the hermetically sealed case 2 is extremely decompressed due to some factor and the oil level suddenly rises, it is unlikely that the lubricating oil will pass over the wave preventing plate 22A. It is the same as that of the above-mentioned embodiment that there is no hindrance to the suction action of the oil suction pipes 20a and 20b even if the accompanying oil level shakes greatly.

FIG. 7 shows a so-called single type fluid compressor, and even a compressor of this type of structure can be provided with the structure which is the gist of the present invention. That is, 30 is a compressor body, 31 is a sealed case, and 32 and 33 are a compression mechanism part and an electric motor part housed in this sealed case.

Reference numeral 34 is a cylinder, 35 is a rotor fitted to the cylinder, 36 is a stator fitted to the inner peripheral surface of the closed case 31, the stator 36 and the rotor 3
The motor unit 33 is composed of 5 and. This motor part 3
Reference numeral 3 is a rotary drive source for rotationally driving the cylinder 34.

Reference numeral 37 is a piston as an eccentric member which is eccentrically arranged in the cylinder 34, 38 is a spiral groove in which the pitch is gradually reduced from one end to the other end on the circumferential surface of the piston 37, and 39 is this groove. 38 is a blade that is inserted into and removed from the blade 38.

A is a space between the cylinder 34 and the piston 37, and is a working chamber partitioned by the blade 39 into a plurality of chambers. The cylinder gradually moves from one end side to the other end side, that is, from the suction side to the discharge side. The volume is small.

Reference numerals 37a and 37b denote main and auxiliary shaft portions formed at both end portions of the piston 37, and these are the closed case 3
It is inserted into main and auxiliary bearings 40 and 41 fixed to the inner wall of No. 1 and is rotatably supported.

Reference numeral 42 is a suction pipe connected to the above-mentioned closed case 31 and communicating with a hole 40a provided in the main bearing 40, and 43 is communicated with this suction pipe 42 through the hole 40a and of the piston 37. The suction guide passage is provided along the axial direction from the end surface of the main shaft portion 37a, and the tip thereof is a suction guide passage opening to the peripheral surface of the end portion of the piston.

Reference numerals 44 and 44 denote metal cylinder bearings press-fitted to the inner peripheral surfaces of both ends of the cylinder 34, and the pivot shaft portions 4 of the main and auxiliary bearing members 40 and 41, respectively.
It is interposed between the outer peripheral surface of 0b and 41b.

Each cylinder bearing 44 is formed in a thick ring shape, and one side surface of the cylinder bearing 44 is the main bearing and the sub bearing 4.
0, 41 are arranged flush with the end faces of the pivot shaft portions 40b, 41b, and the other side faces are flush with the end face of the cylinder 34,
There is a gap between the surfaces of the flanges 40c and 41c of each bearing.

Reference numeral 45 denotes a plurality of lead-out guide holes which are limited to only the cylinder bearing 44 on the side of the sub-bearing 41 and are provided so as to penetrate along the axial direction and open on both side surfaces of the bearing.

Reference numeral 46 denotes the flange portion 4 of the sub bearing 41.
1c is a guide cover that is a first oil disturbance prevention member attached to the end face. The guide cover 46 is provided on the cylinder 34.
Is a hollow cylindrical body that is located at a position covering the outer peripheral surface of the end portion with a gap, and the end surface on the side opposite to the mounting portion with respect to the flange portion has a short axial length that opens.

Reference numeral 47 denotes an oil reservoir portion formed in the inner bottom portion of the closed case 31 for collecting the lubricating oil. The height of the lubricating oil surface of the oil reservoir portion 47 is lower than the height of the bottom portion of the guide cover 46. Is set.

Reference numeral 48 denotes the flange portion 4 of the sub bearing 41.
1c is an oil suction part projecting from a part and immersed in the lubricating oil of the oil sump part 47, and 49 is communicated with this oil suction part 48, and lubrication guides the sucked lubricating oil to each sliding part. It is a passage, and these constitute the refueling mechanism 50.

Reference numeral 51 denotes a second portion provided in the oil sump portion 47.
This is a wave-preventing plate which is an oil disturbance preventing member of
Is located between the oil suction part 48 and the rotor 35 and the stator 36 that constitute the electric motor part 33.

The upper edge of the wave preventing plate 51 is higher than the height of the lubricating oil surface and higher than the bottom of the rotor 35. A plurality of through holes (not shown) are provided in the portion of the oil sump 47 that is immersed in the lubricating oil.

Reference numeral 52 is a rotational force transmission mechanism provided over one end of the cylinder 34 and the piston 37, and 53 is a discharge pipe connected to the end of the closed case 31. In the compressor configured as described above, the rotor 35 and the cylinder 34 rotate integrally with the energization of the electric motor unit 33, and the rotor 35 and the cylinder 34 are transmitted to the piston 37 via the rotational force transmission mechanism 52.

The cylinder 34 and the piston 37 rotate at a relative peripheral speed due to the difference in radius between them and in synchronization with each other while maintaining their mutual positional relationship. The blade 39 moves in and out of the groove 38 and projects in and out in the radial direction of the piston 37.

A compressed gas, for example, a refrigerant gas in the refrigeration cycle is sucked from the suction pipe 42 and guided through the suction guide passage 43 to the working chamber A located at the most suction side which is one end of the cylinder. To the working chamber A located closest to the other end on the discharge side.

The refrigerant gas is gradually compressed while being sequentially transferred through the working chamber A. Then, when it is transferred to the working chamber A on the most discharge side, it rises to a predetermined pressure. This high-pressure gas is discharged from the guide hole 45 of the cylinder bearing 44,
The space between the outer peripheral surface of the cylinder 34 and the inner peripheral surface of the guide cover 46 is guided and guided into the closed case 31 to be filled. Then, the high-pressure gas is discharged from the discharge pipe 53 to the external refrigeration cycle equipment. The high-pressure gas guided out of the cylinder 34 is guided by the presence of the guide cover 46, and the oil sump 4
The lubricating oil surface of No. 7 fills the sealed case 31 without spraying. Lubricating oil Since the oil surface is not directly affected by the high pressure gas, this oil surface is not disturbed.

On the other hand, the oil suction portion 48 sucks up the lubricating oil in the oil sump portion 47 and guides it to the oil supply passage 49. This lubricating oil is guided to each sliding portion of the compression mechanism portion 32 to ensure lubricity.
Further, the lubricating oil is discharged from the working chamber A on the discharge side together with the high pressure gas.

When the high-pressure gas mixed with the oil is discharged from the working chamber A through the guide hole 45, the high-pressure gas is repeatedly collided with the end face of the auxiliary bearing flange 41b and the guide cover 46. The oil droplets of the lubricating oil to be mixed are separated and only the lubricating oil returns to the oil reservoir 47.

That is, when the high-pressure gas filled in the closed case 31 is discharged from the discharge pipe 53, the proportion of the lubricating oil mixed in this gas is reduced to prevent the oil level in the oil sump 47 from lowering. .

In some cases, the oil level of the lubricating oil in the oil sump portion 47 rises, and at least the bottom of the rotor 35, which is rotating the cylinder 34, is immersed in the lubricating oil. At this time, the lubricating oil is splashed and agitated as the rotor 35 rotates, and the lubricating oil surface vibrates greatly.

The wave preventive plate 51 prevents this oil level fluctuation and does not affect the oil suction portion 48. Oil suction part 48
Provides a smooth oil suction action, and the oil supply mechanism 50 maintains a reliable oil supply action.

Of course, the application of the fluid compressor of the present invention is not limited to the refrigeration cycle. The present invention can be variously modified without departing from the scope of the invention.

[0085]

As described above, according to the present invention, the oil sump portion for collecting the lubricating oil is provided in the sealed case, and the oil suction portion is immersed in the lubricating oil of the oil sump portion to suck the oil suction portion. Since a lubrication mechanism that supplies the sliding oil that has been sucked up to each sliding part is provided and an oil disturbance prevention member is provided near the oil suction part of this lubrication mechanism, high pressure fluid obtained by compression and cylinder The effect of preventing disturbance of lubricating oil in the oil sump by the drive source that rotationally drives the oil, ensuring reliable oil suction, improving refueling efficiency, and ensuring lubricity in sliding parts .

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a fluid compressor according to an embodiment of the present invention.

FIG. 2 is a vertical sectional front view of a guide cover and its peripheral portion in the embodiment.

FIG. 3 is a vertical cross-sectional front view of the breakwater plate and its peripheral portion in the embodiment.

FIG. 4 is a vertical sectional front view of a guide cover and its peripheral portion according to another embodiment.

FIG. 5 is a vertical cross-sectional front view of a guide cover and its peripheral portion according to another embodiment.

FIG. 6 is a vertical sectional front view of a wave preventing plate and its peripheral portion in another embodiment.

FIG. 7 is a vertical sectional view of a fluid compressor according to another embodiment.

[Explanation of symbols]

2 ... airtight case, 5 ... cylinder, 9 ... spiral groove, 8 ...
Rotating body (piston), 10 ... blade, 11 ... working chamber,
19 ... Oil sump portion, 20a, 20b ... Oil suction portion (oil suction pipe), S ... Oil supply mechanism, 18 ... First oil disturbance prevention member (guide cover), 22 ... Second oil disturbance prevention member ( Wave plate).

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁶ Identification code Internal reference number FI Technical indication location F04C 29/02 361 A (72) Inventor Takashi Motokatsu 70 Yanagicho, Kawasaki-shi, Kanagawa Prefecture Inside the Toshiba Yanagimachi Plant (72) Inventor Kazumi Takashima 336 Tatehara, Fuji City, Shizuoka Prefecture Inside the Toshiba Fuji Plant

Claims (3)

[Claims] 1. A hermetically-sealed case accommodates a rotationally driven cylinder, and a rotator having eccentric spiral grooves formed at a gradually decreasing pitch is eccentrically arranged in the cylinder, and the spiral is provided in the groove. -Shaped blades are fitted in and out to form a plurality of working chambers that are partitioned by the blades and gradually reduce the volume in the cylinder, and the cylinder and the rotating body are synchronously rotated, In a fluid compressor that compresses the fluid to be compressed sucked into it while gradually transferring it to the working chamber, an oil reservoir for collecting lubricating oil is provided in the closed case, and the lubricating oil in the oil reservoir is The oil suction unit was immersed, and the lubrication mechanism that sucked the lubricating oil sucked by this oil suction unit was supplied to each sliding unit.An oil disturbance prevention member was provided near the oil suction unit of this oil suction mechanism. A fluid compressor characterized by the above. 2. The oil disturbance preventing member is at least between a lubricating oil surface of the oil sump and a guide hole for guiding a fluid, which has been pressurized to a predetermined pressure in the working chamber, into a closed case. The fluid compressor according to claim 1, wherein the fluid compressor is provided in the. 3. The fluid compressor according to claim 1, wherein the oil disturbance preventing member is provided at least between an oil suction portion of an oil supply mechanism and a rotary drive source of the rotating body.