JP2000356195A - Oscillating seal type rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent burning of a rotor due to mixing of the wearing powder, by decreasing friction by an in-groove reciprocating motion of a carbon blade to the utmost particularly at the time of high pressure and high speed. SOLUTION: This compressor is rotatably provided with outer rotors 17d, 17e, 17f in the circumference of a complete circular eccentric rotor integrally provided in a drive shaft 20 provided in compression chambers 12a, 12b, 12c of a cylinder 10, and integrally provided with reverse L-shaped oscillating pieces 24a, 24b, 24c having a carbon seal in the tip end in an oscillating shaft 22 provided in oscillating part storage chambers 14a, 14b, 14c so as to make the carbon seal 26 reciprocation point move in an external periphery of the outer rotor to be prevented from sliding. In this way, the oscillating seal type rotary compressor of high pressure, high speed, low noise, and low vibration, preventing generation of sliding heat to prevent an influence from being given to an oscillating motion, even when a high pressure is generated, by applying the pressure to the reverse L-shaped oscillating piece toward the center of the oscillating shaft, is obtained.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oscillating seal type rotary compressor, and more particularly, to a small oscillating seal type rotary compressor in which the tip of an oscillating blade does not slide on the outer peripheral surface of the outer rotor. The present invention relates to an oscillating seal type rotary compressor that moves a reciprocating point at a required angle while keeping the cylinder closed, prevents leakage of compressed gas, and enables high pressure, high speed, low noise, and low vibration rotation.

[0002]

2. Description of the Related Art In FIG. 11, a slide vane type oil-free compressor 1 has already been proposed.
The tip of the carbon vane 4 contacts the rotor 6 and the pressure P
The carbon vane 4 linearly moves in the longitudinal direction in the groove 2 while receiving the pressure. However, since the rocking friction is severe, a high pressure cannot be obtained and the bearing cannot be used.

In the known rotary vane type oil-free compressor 1 shown in FIG. 12, the tip of a carbon vane 4 is partially slidably fitted in a groove 6a around a rotor 6. Due to the structure, when the pressure increases, the load due to friction increases, and the carbon vanes 4 are extremely worn.

In FIG. 13, the carbon vanes 4 are reciprocated by connecting rods 8 similarly to Rotasco, but since the rotor 6 is not a perfect circle, machining is particularly difficult and the production efficiency is low. Furthermore, since the reciprocating linear motion of the carbon vane 4 is used, vibration becomes a problem when the speed is increased.

[0005]

Therefore, the carbon
Since the blade 4 receives the pressure in the groove 2 and moves linearly while sliding, when the pressure is high, the load due to friction increases, the noise increases, and the carbon vane 4 has a defect that it is extremely worn. Since the carbon blades 4 become severely worn, they need to be replaced frequently. Further, since the powder of the carbon blades 4 is mixed on the discharge side, various defects such as easy burning of the rotor 6 occur. Was inevitable.

Further, as shown in FIGS.
The plate valve 3 in the rotor by the crank mechanism (rotary shaft)
6 does not oscillate in a reciprocating linear motion toward the center of the rotor 6, but since the cross section of the rotor (rotating shaft) 6 is not a perfect circle, it is extremely difficult to manufacture the rotor 6.
Is rotatably provided, and is constantly pressed against the rotor 6 by a spring separating the suction side and the discharge side. Since it is not oil-free, it has only a small size, a low pressure and a small capacity, and has a high speed and a high pressure. Could not. As a result, these rotary vane type and slide vane type oil-free compressors cannot increase the discharge pressure to 0.5 kgf / cm ² or more.

[0007]

SUMMARY OF THE INVENTION The present invention is directed to a plurality of compression chambers formed at a required position in a longitudinal direction at a required position in a diametrical direction and a plurality of partition plates therein and having a cooling portion on an outer peripheral wall surface. And a cylinder communicating with the plurality of compression chambers, forming a discharge port at a required location in the diameter direction at a required location in the longitudinal direction, and a swinging part storage chamber provided in communication with each of the compression chambers. Eccentric at a required distance on the diameter line from the center line in the longitudinal direction, guided into each of the compression chambers of the compression chamber, and eccentrically provided with each of the perfect circular rotors around the circumference, and rotatable with respect to the eccentric perfect rotor, respectively. The outer rotor is rotated while maintaining a small gap with the inner wall surface of each compression chamber, and has a drive shaft at one end and a contact with the outer peripheral surface of the outer rotor at the tip. To have a carbon seal,
An inverted L-shaped rocking piece having a balance weight at the rear end and being rockably fitted so as to be positioned in each of the rocking part storage chambers is integrally provided in parallel with the drive shaft. A swing shaft provided, a swing unit formed by connecting the other end of the drive shaft on the opposite side of the drive unit and a corresponding other end of the drive shaft, and being covered with a cover; The rotation of the drive shaft in the compression chamber causes the inner eccentric rotors in each of the compression chambers to rotate, the outer rotor to revolve, and the inverted L-shaped rocking piece to rock in the rocking part storage chamber. An oscillating seal type rotary compressor characterized in that a tip carbon seal is reciprocated at a required angle on the outer wall surface of the outer rotor at a required angle to supply high-speed, high-pressure, long-life, and clean discharge air. .

[0008]

According to the present invention, according to the prior art, a structure in which a carbon blade slides in a groove of a rotor or a cylinder is improved, and the structure is provided on a rocking plate which is rocked by a link device connected to the rotor. The carbon blade attached to the outer groove follows the outer circumference of the eccentric rotor without sliding in the groove and keeps the cylinder closed, thereby moving the reciprocating point at the required angle on the outer rotor surface, No sliding heat is generated, the tip carbon seal does not wear, and the pressure is directed to the center of the oscillating shaft so that both ends are loaded. , Which can be driven at a high speed and at a high pressure, and oscillates while keeping the discharge chamber hermetically closed, so that a long-life oscillating seal type rotary compressor in which carbon abrasion powder does not enter the discharge side can be obtained.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An oscillating seal type rotary according to claims 1 to 4.
An embodiment of the compressor shown in the attached drawings will be described. As shown in FIGS. 1 to 3, in the longitudinal direction of the cylinder 10 having the required thickness, diameter and length,
a, 14b, 14c with respect to the diameter direction
0b and 10c are formed, and the discharge ports 10 are formed in the diameter direction of the first compression chamber 12a, the second compression chamber 12b, and the third compression chamber 12c.
d, 10e, and 10f are formed.

An upper cover 2 provided on the upper part of the cylinder 10
8, a suction port 28a is formed at a location corresponding to the suction ports 10a, 10b, 10c, and the discharge ports 10d, 10e, 1c.
The upper cover 2 having a suction port 28b formed at a location corresponding to
8 is provided integrally on the upper part of the cylinder 10.

A fin 10g is provided as a cooling unit on the outer peripheral wall surface of the compression chamber 12 where the drive shaft 20 is provided.
Is provided adjacent to the fan 10h.

A plurality of grooves 10f, 10g formed at required intervals on the inner wall surface of the cylinder 10 have partitioning plates 18a,
8b are partially fitted into the three first compression chambers 12.
a, a second compression chamber 12b and a third compression chamber 12c are formed.
The compression chamber 12 is configured such that its volume is gradually reduced from the first to third, that is, from the suction port side to the discharge port side.

Oscillating part storage chambers 14a, 14b, 14 formed adjacent to the three compression chambers 12a, 12b, 12c.
c is the compression chamber 1 partitioned by the partition plates 18a and 18b.
2a, 12b, and 12c.
0 in the longitudinal direction of the wall.
Cuts 12a ', 12b', 12c 'are formed in the longitudinal direction along the ceilings 14a', 14b ', 14c' of the compression chambers 12a, 12b, 12c and the oscillating part storage chamber 14.
a, 14b, and 14c.

In FIG. 4, three compression chambers 12a and 12
b, 12c around the drive shaft 20, each eccentrically has a round rotor 16a, 16b, 16c around it, bearings at both ends around the eccentric round rotor 16a, 16b, 16c. Outer rotors 17d, 17e, 17f are provided via 17a, 17b, 17c, and these outer rotors 17
d, 17e and 17f are the compression chambers 12a, 12b and 12
c so as to rotate while maintaining a slight gap with the inner wall surface.

In FIGS. 4 to 6, two balancing through holes 16a ', 16a', 16b ', 16b', 16b are provided on the surfaces of the three eccentric perfect circle rotors 16a, 16b, 16c, respectively.
C 'and 16c' are drilled.

In FIGS. 5 and 6, the swinging part storage chamber 14a,
Oscillating shafts 22 arranged in the respective 14b, 14c are provided in parallel with the drive shaft 20, and the portions corresponding to the oscillating portion storage chambers 14a, 14b, 14c in the longitudinal direction around the oscillating shaft 22. Are provided integrally with inverted L-shaped rocking pieces 24a, 24b, 24c, and springs 27 are respectively provided in grooves 24a ', 24b', 24c 'formed at the tips of these inverted L-shaped rocking pieces 24a, 24b, 24c. The carbon seal 26 is fitted through the cuts 12a ', 12
b ', 12c' and the outer rotor 17d,
Points 17e and 17f are brought into point contact with each other.

In FIG. 2, counter weights 24a ", 24b", 24c "are integrally formed below the inverted L-shaped rocking pieces 24a, 24b, 24c provided on the rocking shaft 22. And the inverted L-shaped rocking pieces 24a, 24b, 24c
Air inlets 24d, 24e, 24f perpendicular to the longitudinal direction of
To form

In FIG. 5, the swinging part storage chambers 14a, 14
b, 14c, the cuts 12a ', 12b', 12
grooves 14a ', 14
b ', 14c', and each of the grooves 14a ', 14b',
14c 'are fitted with carbon seals 26a via springs 26, respectively, and the inverted L-shaped rocking pieces 24a,
b, 24c, the inverted L-shaped rocking pieces 24a,
4b and 24c can be sealed.

Suction ports 14a ', 14b', 14c 'are formed in the ceilings of the swinging part storage chambers 14a, 14b, 14c, respectively.

In FIG. 2, the compression chamber 1 of the cylinder 10
Compressed air passages 13a and 13b are formed from 2a to the compression chamber 12b and from the compression chamber 12b to the compression chamber 12c.

One side plate 3 having through holes 30a and 30b through which one ends of the drive shaft 20 and the swing shaft 22 pass.
0 is fixed to one end of the cylinder 10, and the bearing housing portions 30 a ′ and 3 of the through holes 30 a and 30 b of the side plate 30 are fixed.
0b ', the bearings 31, 31 are respectively loosely fitted to allow the respective ends of the drive shaft 20 and the swing shaft 22 to pass therethrough.
A belt is suspended on a pulley 21 fixed to one end of the shaft 0, and the belt is connected to a required drive motor (both not shown) to rotate the drive shaft 20.

The other side plate 3 having through holes 32a, 32b through which the other ends of the drive shaft 20 and the swing shaft 22 pass.
2 is fixed to the other end of the cylinder 10, and the bearing storage portions 32 a ′ and 3 of the through holes 32 a and 32 b of the side plate 32 are provided.
Bearings 331 and 31 are loosely fitted in 2b ', respectively, so that one ends of the drive shaft 20 and the swing shaft 22 pass through.

One end of an eccentric lever 42 is pivotally connected to the other end of the drive shaft 20, one end of a lever 44 is connected to the other end of the eccentric lever 42, and the other end of the lever 44 is connected to the swing shaft 22. The swinging part 40 is pivotally attached.

The swinging part 40 is covered with a cover 46 and fixed to the side plate 32.

Accordingly, as shown in FIG. 6, the relationship between the drive shaft 20 and the swing portion 40 of the swing shaft 22 is as follows: a: drive shaft eccentricity; Distance; c: swing axis center-vane tip center distance; d: swing axis center-drive shaft center distance.

According to a third aspect of the present invention, there is provided an oscillating seal type rotary compressor having the cooling portion of the cylinder 10, a cooling jacket, and the oscillating portion 40 as a four-bar linkage. .

The eccentricity of the inner eccentric rotor 24 provided integrally with the drive shaft 20 is, as shown in FIG.
The center line 24e of the inner eccentric rotor 24 is eccentric with respect to the center line 20b of zero.

When the driving shaft 20 is rotated, the oscillating shaft 22 is simultaneously oscillated via the oscillating portion 40, and the oscillating shaft 22 is rotated.
Since the inverted L-shaped rocking pieces 24a, 24b, 24c integrated with the rocking parts rock in the rocking part storage chambers 14a, 14b, 14c, the suction ports 14a ', 14b', 14c ' Guided into each of the swinging part storage chambers 14a, 14b, 14c,
Each compression chamber 12 passes through each of the air suction ports 24d, 24e, 24f of each of the inverted L-shaped rocking pieces 24a, 24b, 24c.
a, is guided into the second compression chamber 12b and the third compression chamber 12c.

The oscillating shaft 2 oscillated by the oscillating portion 40
2 and the inverted L-shaped rocking pieces 24a, 24b, 24c
Swings in the swinging part storage chambers 14a, 14b, 14c, and the carbon seals 26 at the tips of the inverted L-shaped swinging pieces 24a, 24b, 24c are attached to the outer rotor 17
Point contact with d, 17e and 17f surfaces is enabled.

According to a fourth aspect of the present invention, there is provided an oscillating seal type rotary compressor in which the cooling portion 10h of the cylinder 10 is used as a cooling jacket.

[0031]

The oscillating seal type rotary according to the present invention
According to the compressor, it is eccentric at a required distance on the diameter line from the center line in the longitudinal direction, is guided into each of the compression chambers 12a, 12b, and 12c, and surrounds the respective perfect circle rotors 16a, 16b, and 16c.
c is eccentric and integrally provided, and the eccentric perfect circle rotors 16a, 1
The outer rotors 17d, 17e and 17f rotatably fitted to the compression chambers 12a and 12c, respectively.
b, 12c, while maintaining a small gap with the inner wall surface, a carbon shaft that rotates while maintaining a slight gap at one end, and a drive shaft 20 having a drive portion at one end and an outer circumferential surface of the outer rotors 17d, 17e, 17f at the end. 26, and a balance weight 24c 'at the rear end.
a, 14b, and 14c are integrally provided with inverted L-shaped rocking pieces 24a, 24b, and 24c that are rockably fitted so as to be positioned in the respective ones, and a rocking shaft 22 is provided in parallel with the drive shaft 20. The eccentric perfect circle rotors 16a, 16b, 16c are rotated in the respective compression chambers 12a, 12b, 12c, the outer rotors 17d, 17e, 17f are revolved, and the tip carbon seal 26 is attached to the outer・ Rotors 17d, 17
e, the reciprocating point is moved at a required angle on the outer wall surface of 17f.

[0032]

As described above, according to the oscillating seal type rotary compressor according to the present invention, (1) the outer shaft, which is eccentrically provided with the drive shaft 20 which rotates in the cylinder 10, is integrally provided. Rotor 17d,
Since 17e and 17f can be made perfect circles, manufacture becomes easy and high precision can be achieved. Therefore, the gap can be made extremely small, and there is no need for a special-purpose machine capable of manufacturing a high-performance compressor.
Both ends of the drive shaft 20 can be pivotally supported by bearings, and the carbon seals 26 of the inverted L-shaped rocking pieces 24a, 24b, 24c are attached to the outer rotors 17d, 17e, 1c.
Since the reciprocating point moves at the required angle to the outer periphery of 7f, the carbon blade 26 does not slide in the groove, so that it does not wear,
No sliding heat is generated.

(2) Then, the inverted L-shaped rocking piece 24a,
Since each of the carbon seals 24b and 24c follows the circular outer rotors 17d, 17e and 17f and swings reliably, the cylinder 10 is kept tightly sealed, and the carbon seal does not wear. , High pressure, high speed, long life,
It supplies clean discharge air and enables low noise and low vibration driving.

(3) Since the drive shaft and the oscillating shaft can be structured to be indicated at both ends of the shaft, it can be manufactured from a small one of several hundred watts to one exceeding 100 kW.

(4) As shown in FIGS. 5, 6, and 10, the inverted L-shaped rocking pieces 24a, 2
The pressure P applied to the inverted L-shaped rocking pieces 24a, 24b, 24c by the carbon blades 26 of 4b, 24c is directed to the center 22a of the rocking shaft 22, so that a load is applied to both ends of the rocking shaft 22. Therefore, the bearing can be pivoted, so that even if the pressure increases, it does not affect the swinging motion,
The carbon blade 26 does not wear and does not lead to an increase in load due to the wear.

(5) Therefore, the carbon powder is not mixed into the discharge side, and the drive is performed while maintaining high efficiency and cleanliness.
A long life swing seal type rotary compressor can be obtained.

(7) As a result, powder feeding, stirring, packaging,
This is an oscillating seal type rotary compressor most suitable for aeration, food, pharmaceutical, electronics, chemical, textile industries, etc.

[Brief description of the drawings]

FIG. 1 is a partially transparent front schematic view of an oscillating seal type rotary compressor according to the present invention.

FIG. 2 is a schematic perspective plan view of the oscillating seal type rotary compressor of FIG.

FIG. 3 is a schematic rear view of FIG. 1 showing a swinging unit with a side cover removed.

FIG. 4 is a schematic cross-sectional view taken along the line IV-IV of FIG. 2;

FIG. 5 is a schematic sectional view taken along line VV of FIG. 4;

6 is a schematic diagram showing the relationship between the drive shaft and the swinging portion of the swing shaft in FIG. 5 by a dotted line.

FIG. 7 is a partially transparent front schematic view of a drive shaft.

FIG. 8 is a right side view of FIG. 7;

FIG. 9 is a schematic front elevational view of a part of a swing shaft.

FIG. 10 is a right side view of FIG. 9;

FIG. 11 is a schematic sectional view of a known rotary compressor.

FIG. 12 is a schematic sectional view of another embodiment of a known rotary compressor.

FIG. 13 is a schematic sectional view of still another embodiment of the known rotary compressor.

[Explanation of symbols]

 10: cylinder; 10a, 10b, 10c: suction port; 10d, 10e, 10f: discharge port: 10g: fin; 10h: fan; 10f: groove: 12a, 12b; 12c: compression chamber; 13a, 13b: compressed air passage; 14a, 14b, 14c: swinging part storage chamber; 14a ', 14b', 14c ': suction port; ... Eccentric perfect circle rotor; 16a ', 16b', 16c '... Through-hole; 17a, 17b, 17c ... Bearing; 17d, 17e, 17f ... Outer rotor; 18a, 18b ... Partition plate; 20: drive shaft; 22: swing shaft; 24a, 24b, 24c: inverted L-shaped swing piece; 26: carbon seal; 28: top cover;・ Inlet: 28b ・And discharge ports; 40 ... swinging portion; 46 ... cover.

Claims (4)

[Claims] 1. A plurality of compression chambers formed by a plurality of partitioning plates inside a plurality of compression chambers formed by a plurality of partition plates therein, and a plurality of compression chambers having a cooling portion on an outer peripheral wall surface. A cylinder formed with a discharge port at a required location in the diameter direction at a required location in the longitudinal direction and a swinging part storage chamber provided in communication with each of the compression chambers; An outer rotor that is eccentric at a required distance, is guided into each of the compression chambers of the compression chamber, is eccentrically integrated with each other, and is rotatably fitted to the eccentric true rotor. A drive shaft that rotates while maintaining a slight gap with the inner wall surface of each compression chamber, and has a drive portion at one end; and a carbon seal at the tip that contacts the outer peripheral surface of the outer rotor, It has a balance weight at the rear end and stores each swinging part. A swinging shaft integrally provided with an inverted L-shaped swinging piece which is swingably fitted so as to be positioned in the inside thereof, and a swinging shaft provided in parallel with the drive shaft; A swinging part which connects the other end of the shaft and the corresponding other end of the drive shaft and is covered with a cover; rotation of the drive shaft in the compression chamber causes the inner eccentricity in each compression chamber to rotate. The rotor rotates, the outer rotor revolves, the inverted L-shaped rocking piece is rocked in the rocking part storage chamber, and the tip carbon seal reciprocates at the required angle on the outer wall surface of the outer rotor. An oscillating seal type rotary compressor characterized by moving a point. 2. The swing mechanism according to claim 1, wherein the swing mechanism is a link mechanism.
The oscillating seal type rotary compressor as described in the above. 3. An oscillating seal type rotary compressor according to claim 1, wherein said cooling portion of said cylinder is a fin, and a fan is provided adjacent to said fin. 4. The oscillating seal type rotary compressor according to claim 1, wherein said cooling portion of said cylinder is formed as a cooling jacket.