JP2804053B2 - Compressor - Google Patents

Description

The present invention relates to a compressor for compressing a fluid such as a refrigerant gas in a refrigeration cycle, and more particularly to a helical blade type compressor. About.

(Prior Art) As one type of hermetic compressor, a helical blade type is known. The helical blade type compressor is basically eccentrically arranged inside the cylinder and the cylinder.
A piston in which a spiral groove whose pitch gradually changes is formed on a peripheral surface, a blade inserted in the groove, and means for rotating the piston relative to the cylinder (eccentric rotation). It is configured as a subject.

An operating chamber for compressing the fluid to be compressed is formed between the cylinder and the piston, and the operating chamber is partitioned by a blade into a plurality of enclosed spaces whose volume gradually changes along the longitudinal direction. Both ends of the cylinder and piston are
It is rotatably supported by the main bearing and the sub bearing. Also,
A discharge port communicating with the operation chamber is formed in the auxiliary bearing (see FIG. 5).

When the cylinder and the piston are relatively swirled by the motor in such a configuration, the fluid to be compressed sucked into the operation chamber is gradually compressed by sequentially moving to the closed space having a small volume, and finally is discharged. Is discharged through.

However, in a compressor having such a structure, when the amount of eccentricity of the piston with respect to the cylinder (l ₁ -l ₂ , see FIG. 5) is increased, the compressor slides in and out of a groove formed on the peripheral surface of the piston. It is necessary to increase the width of the blade, and the blade is easily deformed due to the pressure difference between the sealed spaces on both sides of the blade. Therefore, the amount of eccentricity cannot be made too large. Therefore, as shown in FIG. 5, when the diameter of the discharge port provided in the sub-bearing is increased, a part of the discharge port is blocked by the end face of the piston.

Therefore, the diameter of the discharge port cannot be increased,
The flow path resistance to the discharge fluid, that is, the fluid to be compressed after compression, has been increased.

(Problems to be Solved by the Invention) As described above, in the conventional helical blade type compressor, the diameter of the discharge port cannot be increased, so that there is a problem that the flow path resistance to the discharge fluid increases. .

SUMMARY OF THE INVENTION It is an object of the present invention to provide a compressor capable of sufficiently securing the size of a discharge port and reducing flow path resistance to a discharge fluid.

[Configuration of the Invention] (Means for Solving the Problems) In order to achieve the above object, a compressor according to the present invention comprises:
A sealed case, a cylinder housed in the sealed case, and an eccentrically arranged operation chamber for compressing the fluid to be compressed between the cylinder and the cylinder, and a helical spiral formed on the peripheral surface. A piston having an annular groove,
Means for rotating the piston relative to the cylinder, and a plurality of seals which are inserted into the groove of the piston so as to be in close contact with the inner peripheral surface of the cylinder and gradually change the working chamber in the longitudinal direction. A blade that partitions into a space, and a discharge that is provided on the peripheral wall of the cylinder so as to communicate with a closed space having the smallest volume among the plurality of closed spaces partitioned by the blade, and that opens toward the space in the closed case. And a port.

(Operation) In the compressor configured as described above, the discharge port can be increased without being limited by the amount of eccentricity of the piston with respect to the cylinder, and the flow path resistance to the discharge fluid is significantly reduced.

In addition, since a discharge port is provided on the peripheral wall of the cylinder so as to open toward the space in the sealed case, the discharge fluid discharged from the discharge port is discharged in the radial direction of the cylinder and the piston, and the fluid between the cylinder and the piston is formed. Because the centrifugal separation action by relative swirling motion works, like refrigerant gas,
In the case of a compressed fluid in which oil is contained in the discharge fluid,
The contained oil can be separated.

(Example) Hereinafter, an example of the present invention is described with reference to drawings.

FIG. 1 is a sectional view of a compressor according to one embodiment of the present invention. As shown in FIG. 1, a motor unit 11 including a stator 12 fixed to an inner wall surface of the case 10 and a rotor 13 disposed inside the stator 12 is driven in the closed case 10. A compression unit 14 is provided.

The compression unit 14 includes a cylinder 15, a pair of bearings 17a, 17b (hereinafter, 17a is a main bearing, and a pair of bearings 17a and 17b installed opposite to the inner wall surface of the case 10 and a piston 16 eccentrically arranged in the cylinder 15).
17b is referred to as an auxiliary bearing). The main bearing 17a and the sub-bearing 17b have a cylindrical portion, and both ends of the cylinder 15 are fitted to the outer peripheral surface of the cylindrical portion. Cylinder 15
Is fixed to the rotor 13. Also the piston
Both ends of 16 are fitted inside the cylindrical portions of the bearings 17a and 17b. In this case, with respect to the rotation center axis l ₁ of the cylinder 15, the rotation center axis l ₂ of the piston 16 is displaced by a predetermined amount. The space between the cylinder 15 and the piston 16 is an operation chamber 23 for compressing the fluid to be compressed.

FIG. 2 is a perspective view showing an Oldham mechanism for relatively rotating the cylinder 15 and the piston 16 without rotating the piston 16, and the outer peripheral surface of the cylindrical portion of the piston 16 on the side of the main bearing 17 a and the cylinder 15. The auxiliary cylinder 18 is press-fitted to the inner peripheral surface of the cylinder. Further, inside the auxiliary cylinder 18, a partition plate 19 whose axial position is regulated by a step (different diameter step) between the auxiliary cylinder 18 and the inner surface of the cylinder 15 is press-fitted into the cylinder 15. This partition plate 19 has a square hole
19a (this is referred to as a first rectangular hole), and the periphery of the rectangular hole 19a has a step. This partition plate 19
A rectangular Oldham ring 20 is slidably fitted in a first direction x in a plane parallel to the partition plate 19 in a first square hole 19a provided in the first hole 19a. This Oldham ring 20 has a square hole
20a (this is called a second rectangular hole). And
The second position of the piston 16 facing the Oldham ring 20 is
Inside the rectangular hole 20a in a plane parallel to the partition plate 19 and in a second direction y perpendicular to the first direction x.
Are formed.

With such a mechanism, the rotation of the rotor 13 is
After being transmitted to the
It is transmitted to the piston 16 via 20. In this case, the Oldham ring 20 reciprocates in the first direction x with respect to the partition plate 19, and the piston 16 moves in the second direction y perpendicular to the direction of reciprocation of the Oldham ring 20 with respect to the Oldham ring 20. Reciprocate. Therefore, the piston 16 rotates and relatively rotates by rotating and contacting the inner surface of the cylinder 15 without rotating. In this case, since the piston 16 does not rotate, the rotation speeds of the cylinder 15 and the piston 16 match.

A spiral groove 21 whose pitch gradually decreases from one end on the main bearing 17a side toward the auxiliary bearing 17b side is formed in the piston 16. The blade 22 is inserted into the groove 21. The outer peripheral edge of the blade 22 comes into close contact with the inner surface of the cylinder 15 and rolls.
Following the swiveling motion, the inside of the groove 21 can be slid and contacted up and down. The blade 22 is the third blade in this embodiment.
As shown in the figure, it is composed of a laminate of a plurality of plate members.

The main bearing 17a is formed with a hollow portion 24 communicating with one end of the operation chamber 23, and a suction port 25 is connected to the hollow portion 24. On the other hand, a discharge port 26 that communicates with the other end of the operation chamber 23 is formed at a position of the cylinder 15 closer to the sub-bearing 17b. That is, the other end of the operation chamber 23 communicates with the inside of the sealed case 10 through the discharge port 26. A discharge pipe 27 is connected to the closed case 10.

In the above configuration, the motor unit 11 controls the cylinder 15
Is rotated, the fluid to be compressed introduced into the working chamber 23 from the suction pipe 25 through the hollow portion 24 moves while moving through the working chamber 23 partitioned by the blade 22 into a closed space whose volume is gradually reduced. And is finally discharged from the discharge pipe 27 through the discharge port 26 and inside the sealed case 10.

Here, since the discharge port 26 is formed in the cylinder 15, the size (diameter) of the discharge port 26 can be significantly increased as compared with the case where the discharge port is formed in the sub bearing. Thereby, the flow path resistance to the discharge fluid is reduced.

However, since the discharge fluid from the discharge port 26 is discharged in the radial direction of the cylinder 15 and the piston 16, the cylinder 15
A secondary effect that oil contained in the discharge fluid can be separated can be expected by the centrifugal separation effect due to the relative swirling motion between the piston and the piston 16.

Also, in the conventional compressor, since the Oldham mechanism is composed of an Oldham pin fixed to the inner surface of the cylinder by welding or an adhesive and an Oldham ring, when the Oldham pin is welded, the cylinder is distorted and the adhesive is removed. When used, there is a problem that gas leaks. However, in this embodiment, as shown in FIG.
Because the Oldham mechanism is composed of the partition plate 19, the Oldham ring 20, and the prismatic portion 16a that are press-fitted on the inner surface,
The above-mentioned problem of the conventional Oldham mechanism is solved.

Further, by providing the partition plate 19 on the suction side, it is possible to fix the piston 16 in the axial direction by receiving a thrust force due to a difference between a suction pressure and a discharge pressure acting on the piston 16 by the partition plate 19 and the Oldham ring 20. Since there is no need to provide a member for fixing the piston by receiving a thrust force separately from the Oldham mechanism, the configuration is simplified.

Further, in this embodiment, since the blade 22 is formed of a laminate of a plurality of plate members, even if a large torsion force is generated in a portion where the pitch of the blade 22 is large, the plate members slide in the radial direction with each other. , Groove on piston 16
The gap between 21 and blade 22 is reduced. Therefore, leakage of fluid between the adjacent closed spaces of the operation chamber 23 is reduced, and the compression efficiency is improved.

FIG. 4 is a sectional view of a compressor according to another embodiment of the present invention.
Are arranged at substantially the same pitch, and a portion of the blade 32 having no action of partitioning the operation chamber 23 is selectively provided in the longitudinal direction of the operation chamber 23. In the figure, blade 32
The portion that does not adhere to the inner surface of the cylinder 15 is selectively formed in the longitudinal direction of the operation chamber 23.
As in the previous embodiment using grooves 21 of unequal pitch,
The blade 32 may be configured so that the blade 32 can be partitioned into a plurality of sealed spaces whose volume gradually changes in the longitudinal direction.

According to the present embodiment, the pitch of the spiral groove 31 can be made substantially equal, so that the twist of the blade 32 is reduced, and the blade 32 can slide smoothly in the groove 31. Become. Therefore, there is an advantage that the sliding loss is reduced and the compression efficiency is improved.

According to the present invention, since the discharge port is formed in the cylinder, the discharge port can be enlarged without being limited by the eccentric amount of the piston with respect to the cylinder. It can be significantly reduced.

In addition, since the centrifugal separation action by the relative swirling motion of the cylinder and the piston acts on the discharge fluid from this discharge port, in the case of a compressed fluid containing oil in the discharge fluid, such as a refrigerant gas, The oil contained in the compressor can be separated, and the compressor can have a filter effect.

[Brief description of the drawings]

FIG. 1 is a sectional view of a compressor according to an embodiment of the present invention, and FIG.
FIG. 3 is a perspective view showing the configuration of an Oldham mechanism in the embodiment, FIG. 3 is a diagram showing the configuration of a blade in the embodiment, FIG. 4 is a cross-sectional view of a compression section according to another embodiment of the present invention, and FIG. FIG. 5 is a sectional view of a main part of a conventional helical blade type compressor. 10 ... sealed case, 11 ... motor, 12 ... stator,
13 ... rotor, 14 ... compression part, 15 ... cylinder, 16 ...
Piston, 16a ... prismatic part, 17a, 17b ... bearing, 18 ... auxiliary cylinder, 19 ... partition plate, 19a ... first rectangular hole, 20 ...
... Oldham ring, 20a ... second rectangular hole, 21 ... spiral groove, 22 ... blade, 23 ... operating chamber, 24 ... hollow part, 25 ... suction pipe, 26 ... discharge port, 27 ... discharge pipe, 31 ... spiral groove, 32 ... blade.

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Hitoshi Hattori 8 Shinsugita-cho, Isogo-ku, Yokohama-shi, Kanagawa Prefecture Inside the Home Appliances Research Laboratory, Toshiba Yokohama Office (72) Inventor Naoya Sogakushi Shinsugita-cho, Isogo-ku, Yokohama-shi, Kanagawa No. 8 Toshiba Yokohama Works Home Appliances Research Laboratory (72) Inventor Masayuki Okuda 8 Shinsugita-cho, Isogo-ku, Yokohama-shi, Kanagawa Prefecture Toshiba Yokohama Works Home Appliances Research Laboratory (56) References Shokai Sho 61 -51401 (JP, U) US Patent 2,527,536 (US, A) US Patent 2,401,189 (US, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04C 18/30-18/352 F04C 23 / 00-29/10

Claims (1)

(57) [Claims] An operating chamber for compressing a fluid to be compressed is formed between a sealed case, a cylinder housed in the sealed case, and an eccentric state disposed inside the cylinder. A piston having a spiral groove on the peripheral surface thereof, means for rotating the piston relative to the cylinder, and a piston inserted into the groove of the piston so as to be in close contact with the inner peripheral surface of the cylinder. A blade for partitioning the operation chamber into a plurality of sealed spaces that gradually change in a longitudinal direction; and a blade provided on a peripheral wall of the cylinder so as to communicate with a closed space having the smallest volume among the plurality of sealed spaces partitioned by the blades. And a discharge port that opens toward a space in the closed case.