JP2950441B2 - Scroll fluid machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll fluid machine suitably used, for example, as a scroll compressor.
In particular, the present invention relates to a scroll fluid machine that prevents lubricating oil in a casing from entering into each compression chamber between an orbiting scroll and a fixed scroll.

[0002]

2. Description of the Related Art Generally, scroll compressors include an oil-supply type (oil-cooled) scroll compressor and an oil-free type scroll compressor.

[0003] Among them, the oil-supply scroll compressor stores lubricating oil in a casing and compresses air while supplying the lubricating oil to a bearing, a sliding portion between the orbiting scroll and the fixed scroll, and the like. Excellent lubrication and cooling properties. In addition, the refueling scroll compressor has a back pressure introduction hole in the orbiting scroll, applies compressed air in the middle of compression to the back of the orbiting scroll to apply a pressing force to the orbiting scroll, and orbits by the compressed air in the compression chamber. The structure can be configured to balance with the separating force acting on the scroll, and there is also an advantage that the compression efficiency can be increased.

[0004] However, since the lubricating oil is supplied into the compression chamber of the oil supply type scroll compressor and the oil is discharged together with the compressed air from the discharge port, completely clean air can be obtained even by using an oil separator or the like. There is a drawback that you can not do.

On the other hand, an oilless scroll compressor does not require an oil separator, an oil cooler, a temperature control valve, and the like.
The configuration is simpler than that of a refueling scroll compressor,
Also, there is an advantage that completely clean compressed air can be obtained.

However, the oilless scroll compressor is inferior in lubricity and cooling performance, and has a drawback that bearings, sliding parts between the orbiting scroll and the fixed scroll, etc. are apt to be abraded or seized early. is there. Oil-free scroll compressors are equipped with thrust and radial bearings in the bearings that support the drive shaft and the orbiting scroll in anticipation of the thermal expansion of the orbiting scroll and fixed scroll due to the heat of compression during the compression action. In addition to the configuration used, a suitable thrust clearance is secured between the root of the head plate and the tip of the lap, but the compression is maintained until the lap is thermally expanded and the thrust clearance decreases. When the thrust clearance is reduced, the efficiency is reduced, and the galling phenomenon occurs.

Therefore, it is possible to improve the above-mentioned drawbacks of the oil-supply type and oil-free type scroll compressors, and to obtain completely clean compressed air containing no oil while performing lubrication and cooling using lubricating oil. A semi-refueling scroll compressor is also known.

Referring to FIG. 4, the semi-lubricating scroll compressor will be described.

In FIG. 4, reference numeral 1 denotes a cylindrical casing;
Denotes a casing main body that constitutes the casing 1 together with a front casing 3 to be described later. The casing main body 2 includes a disc-shaped bottom 2A, and a bearing 2B extending from the inner peripheral side of the bottom 2A into the casing main body 2. And a cylindrical portion 2C extending in the direction of the front casing 3 from the outer peripheral side of the bottom 2A.

Reference numeral 3 denotes a stepped cylindrical front casing fixed to the tip of the cylindrical portion 2C of the casing main body 2. A radially inward thrust receiving portion 3A is integrally formed on the inner peripheral side of the front casing 3. The thrust receiving portion 3 </ b> A is slidably in contact with the rear surface of the orbiting scroll 6 described later and receives a load in the thrust direction.

Reference numeral 4 denotes a drive shaft rotatably supported by bearings 2B of the casing main body 2 via bearings 5 and 5. The distal end of the drive shaft 4 extends into the casing 1 to extend the crankshaft 4A. The axis of the crankshaft 4A is eccentric by a predetermined dimension d with respect to the axis of the drive shaft. The base end of the drive shaft 4 is connected to an electric motor (not shown) outside the casing 1 so as to be driven by the electric motor.

Reference numeral 6 denotes a thrust receiving portion 3A of the front casing 3.
And an orbiting scroll that is rotatably provided on the crankshaft 4A and is located between the thrust receiving portion 12A of the annular plate 12 and the orbiting scroll 12 described later. The orbiting scroll 6 includes a mirror-shaped end plate 6A and a A spiral-shaped wrap portion 6B erected on the front side of the end plate 6A, and a cylindrical tube diametrically located outside the wrap portion 6B and erected in a cylindrical shape and protruding more in the axial direction than the wrap portion 6B. The end portion 6C includes a boss 6D provided at the center on the rear side of the end plate 6A. A crankshaft 4A is rotatably mounted in the boss 6D via a swivel bearing 7.

Here, the end plate 6A of the orbiting scroll 6
Key grooves (not shown) are formed on the outer peripheral side of the rear surface at predetermined intervals in the circumferential direction, and an Oldham coupling (not shown) as a rotation preventing mechanism is provided between each key groove and a thrust receiving portion 3A of the front casing 3. Are arranged. When the orbiting scroll 6 rotationally drives the drive shaft 4, a circular motion having a orbital radius of dimension d is given by the crankshaft 4 </ b> A, rotation is prevented by the Oldham coupling, and the orbiting scroll 6 is rotated about the axis of the drive shaft 4. And keep turning (orbiting).

Reference numeral 8 denotes a fixed scroll which is provided to abut on the front end surface of the front casing 3 so as to cover the front end side of the casing 1 and faces the orbiting scroll 6. The fixed scroll 8 is driven at its center. An end plate 8A arranged on the center side so as to coincide with the axis of the shaft 4, a spiral wrap portion 8B erected on the end plate 8A in the same manner as the wrap portion 6B of the orbiting scroll 6, and an end plate 8A And a cylindrical portion 6C of the orbiting scroll 6 and an annular accommodating portion 8C for accommodating a sealing member 13 and the like to be described later. ing.

Here, the wrap portion 8B of the fixed scroll 8 is disposed so as to overlap with the wrap portion 6B of the orbiting scroll 6 by a predetermined angle.
The plurality of compression chambers 9, which continuously decrease while the
9, ... are defined. Also, 10,11
Indicates a suction port and a discharge port provided on the fixed scroll 8, respectively. The suction port 10 is formed on the outer peripheral side of the housing portion 8C so as to communicate with the compression chamber 9 on the outermost peripheral side (low pressure side). The port 11 is bored at the center of the end plate 8A so as to communicate with the innermost (high-pressure) compression chamber 9.

Reference numeral 12 denotes an annular plate fixed to the opening of the accommodation portion 8C of the fixed scroll 8 and constituting a part of the front casing 3 or the fixed scroll 8, and an orbiting scroll is provided on the inner peripheral side of the annular plate 12. Thrust receiving portion 12 that receives a load in the thrust direction by sliding contact with the end plate 6A
A is formed, and the thrust receiving portion 12A faces the thrust receiving portion 3A of the front casing 3. The annular plate 12 is provided with a cylindrical tubular portion 12B protruding into the accommodation portion 8C of the fixed scroll 8, and the tubular portion 12B is located radially outward of the tubular portion 6C of the orbiting scroll 6. It is located in.

Reference numeral 13 denotes a sealing member which surrounds the wrap portion 6B of the orbiting scroll 6 and the wrap portion 8B of the fixed scroll 8 from the outside in the radial direction, and blocks each compression chamber 9 from the inside of the casing 1. As shown in FIG. 5, is molded in an U-shaped cross section at the position of the curved portion 13A by using an elastic resin material, and the inner end and the outer end are fixed rings 14, 15 respectively. The cylindrical portion 6C of the orbiting scroll 6 and the cylindrical portion 12B of the annular plate 12
It is fixed gas- and liquid-tight. And the sealing member 1
Reference numeral 3 denotes a suction port 10 in the accommodation portion 8C of the fixed scroll 8.
And an oil chamber B in the casing 1 is defined.
And the suction chamber A are sealed.

Reference numeral 16 denotes a lubricating oil accommodated in an oil chamber B of the casing 1, and 17 denotes a lubricating oil which is located in the casing 1 and is fitted and fixed to the drive shaft 4, for scraping the lubricating oil 16 into the casing 1. An oil scraper 18 indicates a counterweight provided on the oil scraper 17, and the counterweight 18 is adapted to balance the orbiting movement of the orbiting scroll 6.

The scroll compressor according to the prior art has the above-described configuration. When the drive shaft 4 is driven to rotate,
This rotation is transmitted from the crankshaft 4A to the orbiting scroll 6 via the orbiting bearing 7, and the orbiting scroll 6 orbits around the drive shaft 4 with a turning radius of the dimension d. Then, each of the compression chambers 9 is continuously reduced by the swirling motion, compresses the air sucked from the suction port 10, and discharges the compressed air from the discharge port 11 to an external air tank (not shown).

At this time, the disk 17 provided on the drive shaft 4 scoops up the lubricating oil 14 in the casing 1, and the thrust receiving portion 3A of the bearing 5, the turning bearing 7, and the front casing 3 as well as the back of the orbiting scroll 6. Thrust receiving portion 1 of annular plate 12
This lubricating oil is supplied to 2A, Oldham's joint, etc. to perform lubrication and cooling.

On the other hand, since the suction chamber A is separated from the oil chamber B of the casing 1 by the seal member 13, oil is not mixed into the compressed air discharged from the suction port 10 and discharged from the discharge port 11. , And clean compressed air can be obtained.

[0022]

In the above-mentioned prior art, a sealing member 13 for sealing between the suction chamber A and the oil chamber B in the casing 1 is formed of an elastic resin material into a U-shaped cross section. The curved portion 13A is formed in a folded shape in advance. Therefore, when the inner and outer ends of the seal member 13 are mounted on the orbiting scroll 6 and the cylindrical portions 6C and 12B of the annular plate 12 with the fixing rings 14 and 15, if the mounting positions are displaced in the axial direction, When the inner peripheral side or the outer peripheral side of the seal member 13 is displaced in the axial direction from the regular mounting position, the curved portion 13A is deformed and the curved portion 13A is distorted. When the orbiting scroll 6 is turned in this state, Stress may concentrate on the curved portion 13A and abnormal deformation may occur.

For this reason, in the prior art, while the scroll compressor is operated for a long period of time, the sealing member 1 is not used.
3 is damaged or broken from an abnormally deformed portion such as the curved portion 13A, and the reliability cannot be improved.

In another prior art, as shown in FIG.
The core material 19A is formed by knitting core materials 19A, 19A,... Made of flexible high-strength fiber or metal wire into a mesh shape.
9 is formed, and the core member 19 is buried in the seal member 13 to reinforce the seal member 13. However, in this case, the followability of the seal member 13 with respect to the orbiting motion of the orbiting scroll 6 is deteriorated by the core material 19. It is necessary to make the overall length very long, which causes a problem that not only the whole becomes large, but also that it is difficult to mass-produce the seal member 13 because it has a complicated shape.

The present invention has been made in view of the above-mentioned problems of the prior art, and can be easily mass-produced by molding a seal member into a simple shape, and abnormal deformation occurs due to an error in mounting. It is an object of the present invention to provide a scroll fluid machine which can prevent the occurrence of the scroll and improve the reliability and the life.

[0026]

A feature of the present invention to solve the above-mentioned problem is that the sealing member is made of an elastic material and has a tapered cylinder whose diameter gradually increases from one end in the axial direction to the other end. In a state in which the axially intermediate portion of the tapered cylinder is folded back, one end in the axial direction is fixed to the orbiting scroll side, and the other end is fixed to the casing or the fixed scroll side.

[0027]

According to the above construction, a sealing member can be formed by folding a tapered cylinder made of an elastic material whose diameter gradually increases from one end in the axial direction toward the other end at an intermediate portion in the axial direction. The member can be displaced by following the mounting position of the member, and the occurrence of stress concentration and the like can be suppressed.

[0028]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 1 to 3 taking a scroll compressor as an example. In the embodiment, the same components as those in the conventional technique shown in FIG. 4 described above are denoted by the same reference numerals, and description thereof will be omitted.

In the drawing, reference numeral 21 denotes a casing constituting a main body of the scroll compressor. The casing 21 has a bottom portion 22A, almost in the same manner as the casing 1 described in the prior art.
A casing main body 22 having a bearing portion 22B and a cylindrical portion 22C; and a radially inwardly projecting protruding portion from the distal end of the cylindrical portion 22C of the casing main body 22;
And the front casing 23 that has become A. A drive shaft 26 is rotatably supported by bearings 22B of the casing body 22 via bearings 24 and 25, and a distal end side of the drive shaft 26 is a crankshaft 26A eccentric by a predetermined dimension d.

Reference numeral 27 denotes an orbiting scroll mounted on the crankshaft 26A via an orbiting bearing 28 so as to be able to orbit.
The orbiting scroll 27 has substantially the same configuration as the orbiting scroll 6 described in the related art, and includes a head plate 27A and a wrap portion 27.
B and a boss 27C. The orbiting scroll 27 is connected to the rear surface of the end plate 27A and the front casing 23.
Joint 2 disposed between the thrust receiving portion 23A of the
The rotation of the crankshaft 26A imparts a turning motion having a turning radius of the dimension d by the rotation of the crankshaft 26A.

Numeral 30 denotes a fixed scroll fixed to the casing 21 in abutment with the front end face of the front casing 23. The fixed scroll 30 is also configured substantially in the same manner as the fixed scroll 8 described in the prior art, and includes end plates 30A, It has a lap portion 30B and a housing portion 30C, and an annular step portion 30D is formed on the outer peripheral side of the housing portion 30C. Further, the fixed scroll 30 is provided with a suction port 31 at the position of the housing portion 30C, and the discharge port 3 is provided at the center of the end plate 30A.
2 are formed. The wrap portion 30B of the orbiting scroll 27 corresponds to the wrap portion 30B of the fixed scroll 30.
Are formed between them, and when the orbiting scroll 27 performs the orbiting motion, each of the compression chambers 33 compresses the air sucked from the suction port 31 and the compressed air from the discharge port 32. Is discharged.

Reference numeral 34 denotes a wrap portion 27 of the orbiting scroll 27.
A mounting cylinder fixed radially outside of B to the end plate 27A via bolts 35, the mounting tube 34 is formed in a stepped cylindrical shape, and a base end side is fitted to the front side of the end plate 27A to form a plurality of mounting tubes. Orbiting scroll 2 with bolt 35 (only one is shown)
7 are integrated. The distal end side of the mounting cylinder 34 projects into the housing portion 30C of the fixed scroll 30, and a seal member 38 described later is mounted thereon.

Reference numeral 36 is located radially outside the mounting cylinder 34,
FIG. 3 shows another mounting cylinder fixed between the front end surface of the front casing 23 and the step portion 30D of the fixed scroll 30, and the mounting cylinder 36 is formed to have a larger diameter than the mounting cylinder 34 as shown in FIG. It comprises a cylindrical mounting portion 36A and an annular fixing portion 36B projecting radially outward from the base end side of the mounting portion 36A. The fixing portion 36B has a bolt insertion hole at a predetermined circumferential interval. 36C (only one is shown) is formed. In the mounting cylinder 36, a fixing portion 36B is fixed to the front casing 23 by each bolt 37 inserted into each bolt insertion hole 36C, and a seal member 38 is mounted on the outer periphery of the distal end side of the mounting portion 36A.

Reference numeral 38 denotes a housing portion 30C for the fixed scroll 30.
2 shows a sealing member provided between the mounting cylinders 34 and 36, and the sealing member 38 is previously molded as a tapered cylinder 39 by means of injection molding or the like from an elastic resin material as shown in FIG. The cylinder 39 is located at one end and has a thick small-diameter portion 39B having a ring groove 39A formed on the outer peripheral surface, and a thick large diameter having a ring groove 39C formed on the inner peripheral surface at the other end. It comprises a portion 39D and a tapered portion 39E whose diameter gradually increases from the small diameter portion 39B toward the large diameter portion 39D. The seal member 38 is formed by folding a tapered portion 39E of the tapered cylinder 39 at an intermediate portion in the axial direction into a substantially V-shaped cross section as shown in FIG. 3, and the position of the folded portion 38A is set to the mounting cylinders 34 and 36. It can be freely displaced according to the mounting position.

That is, the small diameter portion 39B of the tapered cylinder 39 winds the fixing ring 40 such as a double-wound band in the ring groove 39A, so that the sealing member 38 is air-liquid-tight around the outer periphery of the tip end of the mounting cylinder 34. The large-diameter portion 39D is fixed around the mounting portion 36A of the mounting cylinder 36 in a gas-liquid-tight manner by winding a similar fixing ring 41 around the ring groove 39C. The sealing member 38 fixes the mounting cylinder 34 to the orbiting scroll 27 and connects the mounting cylinder 36 to the fixed scroll 30.
The suction chamber A is provided in the housing portion 30C of the fixed scroll 30 by being fixed between the housing and the front casing 23, and defines a suction chamber A communicating with the suction port 31 in the housing portion 30C. The seal member 38 defines an annular chamber B1 communicating with the oil chamber B in the casing 1 inside the seal member 38, and shuts off the annular chamber B1 and the oil chamber B with respect to the suction chamber A.
This prevents the lubricating oil 16 in the oil chamber B from entering the suction chamber A and each compression chamber 33.

The scroll compressor according to the present embodiment has the above-described configuration, and its basic operation is not particularly different from that of the prior art.

However, in this embodiment, the sealing member 38 for shutting off the oil chamber B and the suction chamber A in the casing 1 is formed in advance as a tapered cylinder 39 from an elastic resin material. The small-diameter portion 39B is fixed to the mounting cylinder 34 by a fixing ring 40 in a state where the portion is folded into a V-shaped cross section, and the large-diameter portion 39D is fixed to the mounting cylinder 3 by a fixing ring 41.
6 and fix the mounting cylinders 34, 36 to the orbiting scroll 27,
Since the seal member 38 is provided in the housing portion 30C of the fixed scroll 30 by being fixed to the fixed scroll 30 side, the following operation and effect can be obtained.

That is, since the folded portion 38A of the seal member 38 is formed by folding a tapered cylinder 39 formed as shown in FIG. 2 at an intermediate portion in the axial direction, the small diameter portion 39B and the large diameter of the tapered cylinder 39 are formed. When the portion 39D is mounted on the distal end side of the mounting tube 34 and the mounting portion 36A of the mounting tube 36 using the fixing rings 40 and 41, even if the mounting position is shifted, the folded portion 38A is formed by the tapered portion 39E of the tapered tube 39. The position can be freely changed on the way, and it is possible to prevent wrinkles, large distortion, and the like from being generated in the vicinity of the folded portion 38A.

Also, when the orbiting scroll 27 makes a revolving motion, the folded portion 38A of the seal member 38 can be freely displaced in the axial direction and the radial direction following the revolving scroll, and the pulling force applied from the orbiting scroll 27 and the like. In addition, it is possible to effectively prevent stress concentration from occurring near the folded portion 38A due to the compressive force and the shear force.

Therefore, according to the present embodiment, the sealing member 3
8 can be reliably prevented from being damaged or damaged at an early stage, and by sealing the suction chamber A and the oil chamber B for a long period of time, clean compressed air can be discharged from the discharge port 32. And life can be greatly improved.

Further, since the tapered cylinder 39, which is a material of the seal member 38, has a simple shape, mass production can be easily carried out by means such as injection molding, and cost reduction can be achieved. As compared with the prior art shown in FIG. 6, the seal member 38 can be formed to be shorter, and various effects can be obtained, such as the whole scroll compressor can be reduced in size.

In the above-described embodiment, the seal member 38 is formed by folding the tapered cylinder 39 made of an elastic resin material into a substantially V shape in the middle of the tapered portion 39E. The shape is not limited to a substantially V-shape.
Even when 8A is curved in an arc, substantially the same operation and effect as in the above embodiment can be obtained.

In the above embodiment, the large-diameter portion 39D of the seal member 38 is connected to the front casing 23 via the mounting cylinder 36.
However, instead of this, the large diameter portion 39D of the seal member 38 may be fixed to the outer peripheral side of the fixed scroll 30 via the mounting cylinder 36.

Further, in the above-described embodiment, the mounting cylinder 34 is formed separately from the orbiting scroll 27. However, the mounting cylinder 34 is formed integrally with the orbiting scroll 27 in advance. Other mounting cylinder 36
May also be formed integrally with the front casing 23, for example.

Further, in the above-described embodiment, the scroll compressor has been described as an example. However, the present invention is not limited to this, and may be applied to, for example, a scroll vacuum pump.

[0046]

As described in detail above, according to the present invention, the sealing member is formed as a tapered cylinder from an elastic material, and this tapered cylinder is folded back at the axially intermediate portion so that one end and the other end are on the orbiting scroll side. Since it is configured to be fixed to the casing or fixed scroll side, even if the seal member is displaced when it is attached, it is possible to prevent wrinkles and large distortions from being generated near the folded portion, and to reduce the life and reliability. It can be improved effectively. In addition, various effects can be achieved such that the tapered cylinder as the material of the seal member can be easily mass-produced by means such as injection molding, the cost can be reduced, and the whole can be reduced in size.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a scroll compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged longitudinal sectional view showing a tapered cylinder used as a material of a seal member.

FIG. 3 is an enlarged longitudinal sectional view of a seal member showing a state in which the tapered cylinder in FIG. 2 is folded at an intermediate position and then attached to a mounting cylinder.

FIG. 4 is a longitudinal sectional view showing a scroll compressor according to the related art.

FIG. 5 is an enlarged perspective view showing a seal member in FIG. 4;

FIG. 6 is an enlarged perspective view showing another conventional sealing member.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 21 Casing 26 Drive shaft 26A Crankshaft 27 Orbiting scroll 27A, 30A End plate 27B, 30B Lapping part 30 Fixed scroll 31 Suction port 32 Discharge port 33 Compression chamber 34, 36 Mounting cylinder 38 Sealing member 38A Folding part 39 Tapered cylinder 39B Small diameter part ( 39D Large diameter part (other end) A Suction chamber B Oil chamber

Claims (1)

(57) [Claims] 1. A casing containing lubricating oil therein,
A drive shaft rotatably provided on the casing and extending into the casing and having a distal end side serving as a crankshaft, and a swivel-shaped wrap portion provided upright on the end plate, rotatably provided on the crankshaft of the drive shaft. And a fixed scroll fixed to the casing facing the orbiting scroll and having a spiral plate-shaped wrap portion formed in a plurality of compression chambers between the end plate and the wrap portion of the orbiting scroll. When,
Of the compression chambers, a suction port communicating with the outermost compression chamber and a discharge port communicating with the innermost compression chamber, and each of the compression chambers are shut off from the inside of the casing.
In a scroll fluid machine including a seal member surrounding a wrap portion of the orbiting scroll and the fixed scroll from a radial outside, the seal member is a tapered cylinder whose diameter gradually increases from one axial end to the other axial end by an elastic material. In the state where the axial middle part of the tapered cylinder is turned back, one end in the axial direction is fixed to the orbiting scroll side, and the other end is fixed to the casing or the fixed scroll side. And scroll fluid machinery.