JP3078269B2 - Fluid compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art As conventional compressors, reciprocating compressors and rotary compressors have been known. In addition, for example, as shown in Japanese Patent Application No. 62-191564, the suction end of a cylinder is known. A helical blade type fluid compressor is provided which compresses and discharges refrigerant while sequentially transferring refrigerant flowing into a working chamber from a side to a working chamber on a discharge end side of a cylinder.

The outline of the helical blade type compressor is as follows.
For example, as shown in FIG. 7, a driving unit 105 including a fixed stator 101 and a rotatable rotor 103, a cylinder 107 integrally connected to the rotor 103,
A rotation rod 111 is disposed eccentrically within the cylinder 107 by e and is rotatable relative to the cylinder 107 via an Oldham ring 109. Rotating rod 1
A spiral groove 113 is formed on the outer peripheral surface of the rotary rod 111 over substantially the entire length thereof, and a spiral blade 115 is fitted into the groove 113 so as to be able to enter and exit. Blade 11
The outer peripheral surface of 5 comes into contact with the inner peripheral surface of cylinder 107, and blade 115 rotates integrally with cylinder 107.

The rotating rod 111 with respect to the cylinder 107
The eccentric rotation causes a relative velocity between the outer peripheral surface of the rod and the inner peripheral surface of the cylinder opposed thereto, and the rotation of the rotating rod 111 and the cylinder 107 by the blade 115 entering and exiting the spiral groove 113. A plurality of working chambers 117 are formed in the space between and along the axial direction. The volume of the working chamber 117 is determined by the pitch of the spiral groove 113 into which the blade 115 is fitted.
The pitch of No. 3 gradually decreases from one end of the rotating rod 111 to the other end. Therefore, the volume of the working chamber 117 formed by the blade 115 is changed from the suction end side on the suction pipe bus 119 side to the discharge pipe 12 side.
Because it gradually decreases toward the discharge end side, which is the first side,
The refrigerant is gradually compressed and discharged while being sequentially transferred to the discharge end side.

[0005]

In a helical blade type fluid compressor, a cylinder and a rotating rod are driven to rotate at a high speed, and one end of the cylinder and the rotating rod has a high-pressure discharge portion and the other end has a high pressure. Is a low-pressure suction part, so that a large thrust force is generated from the high-pressure side to the low-pressure side. Therefore, the end face of the cylinder or the rotating rod in the thrust direction may come into sliding contact with the bearing member that supports them at high speed at high speed, increasing the sliding loss and adversely affecting the compression efficiency.

Accordingly, an object of the present invention is to provide a fluid compressor capable of improving compression efficiency by reducing sliding loss.

[0007]

In order to achieve the above object, according to the present invention, a cylinder, a rotating body eccentrically arranged in the cylinder, and a circumferential surface of the rotating body are provided. A helical blade provided along the helical blade, a helical blade which is fitted into the helical groove so as to be able to freely enter and exit, and defines a space with the cylinder into a plurality of working chambers, and an eccentric engaging with the rotating body. A main shaft having a shaft portion for rotating and rotating the rotating body; and a driving means for transmitting a driving force to the main shaft, the rotating body being partially thinned to form a cavity in the inner peripheral portion. .

As a result, the rotating body revolves with respect to the cylinder, compresses the refrigerant taken in from the suction side to the discharge side by the working chamber, and discharges the refrigerant.

During this operation, a large thrust force is generated from the high pressure side to the low pressure side. However, since the peripheral speed on the thrust surface is only the turning motion of the rotating body, the sliding loss can be reduced. Further, since the rotating mass of the rotating body can be small, the occurrence of vibration can be reduced.

According to a second aspect of the present invention, a balance weight is provided on the main shaft, and the balance weight is disposed in a hollow portion formed in an inner peripheral portion of the rotating body.

As a result, the vibration of the main shaft can be reduced, and the space for disposing the balance weight can be taken in the cavity of the rotating body.
It is possible to shorten the axial length of the compression mechanism by the arrangement space, and it is possible to reduce the axial dimension of the entire fluid compressor.

According to a third aspect of the present invention, the main shaft is supported by a bearing member, and at least a part of the bearing member is located in a hollow portion formed in an inner peripheral portion of the rotating body. To be placed.

As a result, a part of the bearing member can be disposed in the hollow portion of the rotating body. As a result, the axial length of the compression mechanism can be shortened by the arrangement space, and the fluid compressor can be reduced. The overall axial dimension can be reduced.

According to a fourth aspect of the present invention, a cylinder, a rotating body eccentrically arranged in the cylinder, a spiral groove provided along a peripheral surface of the rotating body, and a spiral A helical blade which is fitted into the groove so as to be able to freely enter and exit, and defines a space between the cylinder and a plurality of working chambers; and a main shaft having an eccentric shaft portion engaged with the rotator for rotating the rotator. And a driving means for transmitting a driving force to the main shaft, and a bearing member for supporting the main shaft, wherein the bearing member is a first bearing member located between the rotating body and the driving means. , A second bearing member located on the opposite side to the driving means,
The discharge side of the working chamber is located on the first bearing member side, and the suction side of the working chamber is located on the second bearing member side.

Accordingly, the thrust force generated during operation is in one direction from the first bearing member on the discharge side to the second bearing member on the suction side, so that the rotating body can be stably moved in the axial direction. This makes it possible to maintain the noise, thereby suppressing generation of abnormal noise.

According to the fifth aspect of the present invention, the cylinder, the rotating body eccentrically arranged in the cylinder, the spiral groove provided along the peripheral surface of the rotating body, and the spiral A helical blade which is fitted into the groove so as to be able to freely enter and exit, and defines a space between the cylinder and a plurality of working chambers; and a main shaft having an eccentric shaft portion engaged with the rotator for rotating the rotator. And a driving means for transmitting a driving force to the main shaft, wherein the eccentric shaft portion of the main shaft is located in a region where a gas force generated at the time of compression is generated.

As a result, there is no one-side contact between the main shaft and the inner peripheral bearing portion of the rotating body, so that leakage of refrigerant gas can be prevented and sliding loss can be reduced.

According to the sixth aspect of the present invention, the inner peripheral bearing portion of the rotating body that engages with the eccentric shaft portion of the main shaft is located in a region where gas force generated during compression is generated.

As a result, there is no one-side contact between the main shaft and the inner peripheral bearing portion of the rotating body, so that leakage of refrigerant gas can be prevented and sliding loss can be reduced.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to FIGS.

In FIG. 1, reference numeral 1 denotes a sealed case of a sealed type fluid compressor 3 used in a refrigeration cycle, which is a vertical type. A suction pipe 5 of the refrigeration cycle is provided on one lower side of the closed case 1 and a discharge pipe 7 is provided on the other upper side. An electric mechanism 9 as a driving means is provided in a substantially upper half portion in the closed case 1.
However, a compression mechanism 11 is disposed in the lower half.

The electric mechanism 9 has a substantially annular stator 13 fixed to the inner surface of the sealed case 1 and a rotatable annular rotor 15 provided inside the stator 13.

The rotor 15 has a bearing portion 19 of a first bearing member 17 fixed to the inside of the sealed case 1 and opposed to the rotor 15.
A main shaft 25 rotatably supported by the bearing portion 23 of the bearing member 21 is fixedly connected thereto, and the main shaft 25 extends to a region of the compression mechanism portion 11 on the lower side.

The compression mechanism 11 has a cylinder 27 and a rotating body 29, and the cylinder 27 is fixedly supported on the inner peripheral surface of the closed case 1.

The rotating body 29 is formed in a thin cylindrical shape smaller than the inner diameter of the cylinder 27, and has a hollow portion serving as an arrangement space inside. The center of the rotating body 29 is a boss 31 serving as an inner peripheral bearing, and has a shape along the axial direction of the cylinder 27. Boss part 31 of rotating body 29
Is inserted into an eccentric shaft portion 33 formed eccentrically from the axis of the main shaft 25 by e, and vibration during rotation of the eccentric shaft portion 33 is suppressed by a balance weight 53 described later.

The eccentric shaft portion 33 of the main shaft 25 into which the boss portion 31 of the rotating body 29 is inserted is a force acting on a region where the gas force F generated at the time of compression is generated, specifically, an outer peripheral surface of the rotating body 29. , And both ends are supported by the bearing portions 19 and 23 of the first and second bearing members 17 and 21, respectively. A part of the bearing portion 19 of the first bearing member 17 and the bearing portion 23 of the second bearing member 21
The compression mechanism 11 has a structure in which the axial length of the compression mechanism 11 is shortened by the space in which the bearings 17 and 23 are arranged.

When the main shaft 25 rotates, the rotating body 29 is rotated by the Oldham coupling 35 while part of the outer peripheral surface of the rotating body 29 is in line contact with the inner peripheral surface 27a of the cylinder 27. I have.

The Oldham coupling 35 is located in a hollow portion inside the rotating body 29 and is formed in a ring shape as shown in FIG.
A pair of projections 37, 37 are provided on the upper surface of the ring so as to face each other, and a pair of projections 39, 39 are provided on the lower surface of the ring so as to face each other. The upper-side projection 37 and the lower-side projection 39 are arranged in a positional relationship shifted by 90 degrees, and the upper-side projection 37 is located within the first Oldham receiving groove 41 provided on the boss 31 of the rotating body 29. Is engaged. Further, the lower projection 39 is provided on the second bearing member 21 and is provided on the first bearing member 21.
The second Oldham receiving groove 43 is formed so as to be shifted from the Oldham receiving groove 41 by approximately 90 degrees.

A spiral groove 45 is formed on the outer peripheral surface of the rotating body 29 along the axial direction. The pitch of the spiral groove 45 is the largest on the suction pipe 5 side, and is successively toward the discharge pipe 7 side. It is set to be smaller. This spiral groove 4
A helical blade 47 made of an elastic material such as a synthetic resin is attached to 5 so as to be able to move in and out by utilizing elastic force. The length of the blade 47 is slightly shorter than the length of the spiral groove 45, and the width thereof is set to substantially the same dimension as the spiral groove width. I have.

The outer peripheral surface of the blade 47 is in sliding contact with the inner peripheral surface of the cylinder 27, and the space between the inner peripheral surface of the cylinder 27 and the outer peripheral surface of the rotating body 29 is divided into a plurality of working chambers by the blade 47. It is partitioned into 49. Each working chamber 49
Is formed between two adjacent turns of the blade 47, and the next portion is formed along the blade 47 from the sliding contact portion between the rotating body 29 and the inner peripheral surface of the cylinder 27 along the blade 47 as shown in FIG. It is an almost crescent-shaped area that extends to the sliding contact part.

The capacity of the working chamber 49 is set so that the suction end side (the lower side in FIG. 1) of the cylinder 27 becomes maximum, and then gradually decreases toward the discharge end side (the upper side in FIG. 1).

The first working chamber 49 on the suction end side is connected and connected to the suction pipe 5, so that the refrigerant gas is reliably introduced without interruption. The final working chamber 49 on the discharge end side is connected to the discharge pipe 7 via an opening 51 provided in the first bearing member 17.

The balance weight 53 is connected to the rotating body 29
Is fixed to the main shaft 25 between the bearing 19 of the first bearing member 17 and the boss 31 of the rotating body 29, and the weight of the balance weight 53 is fixed to the eccentric shaft 33. Is located 180 degrees opposite to the eccentric portion of the main shaft 25, and can rotate together with the main shaft 25.

In FIG. 1, reference numeral 55 denotes each bearing 1
9 and 23 show lubricating oils for lubricating.

The operation of the thus constructed fluid compressor will be described.

First, when power is supplied to the electric mechanism 9, the rotor 15 rotates and, at the same time, the main shaft 25 also rotates. When the main shaft 25 rotates, the Oldham coupling 35 imparts a rotating motion to the rotating body 29 as shown in FIGS. As a result, the refrigerant gas sent into the working chamber 49 on the suction end side is compressed while being sequentially sent to the final working chamber 49 on the discharge end side, is once discharged into the closed case 1, and is then discharged. From the outside.
In this operation, the first working chamber 49 is the cylinder 2
By increasing the diameter of 7, the volume is increased, so that unreasonable twisting of the blade 33 does not occur and a stable operation state can be obtained for a long period of time.

Moreover, since the rotating mass of the rotating body 29 can be small, the generation of vibration can be reduced.

The radial gas force F generated during operation is input to the eccentric shaft 33 of the main shaft 25 via the boss 31. At this time, while the vibration is suppressed by the balance weight 53, the eccentric shaft portion 33 is located in the region where the gas force F is generated, so that the bending moment acting on the rotating body 29 does not act, and the eccentric shaft portion 33 is eccentric with the boss portion 31. There is no one-side contact with the shaft portion 35, and the gas leakage of the refrigerant gas is prevented, and the sliding loss can be reduced.

Since both ends are supported by the bearing portions 19 and 23, the thrust force acting on the main shaft 25 is in one direction toward the second bearing member 21.
The rotating body 29 can be stably held in the axial direction, and generation of abnormal noise can be suppressed.

Although the vertical type is used in this embodiment, it can be used as a horizontal type. Further, it may be used as a vacuum pump.

[0041]

As described above, according to the fluid compressor of the present invention, the following effects can be obtained.

(1) When a thrust force is generated, the peripheral speed on the thrust surface is only the turning movement of the rotating body, so that the sliding loss can be suppressed to a small value.

Further, since the rotating mass of the rotating body can be reduced by the hollow portion, the generation of vibration can be reduced.

(2) The balance weight can reduce the vibration of the main shaft, and the first and second bearings including the balance weight can be arranged in the cavity inside the rotating body. Accordingly, the axial length of the compression mechanism can be reduced by the arrangement space, and the axial dimension of the entire fluid compressor can be reduced.

(3) Since the gas force is located in the region of the eccentric shaft portion, there is no contact between the rotating shaft and the boss portion, so that refrigerant gas leakage is prevented and vibration loss can be reduced.

(4) The rotating body can be stably held in the axial direction, and generation of abnormal noise can be suppressed.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing the entire fluid compressor.

FIG. 2 is a perspective view of an Oldham coupling.

FIG. 3 is an operation explanatory diagram.

FIG. 4 is an operation explanatory view.

FIG. 5 is an operation explanatory diagram.

FIG. 6 is an operation explanatory diagram.

FIG. 7 is a longitudinal sectional view showing the whole of a conventional helical blade type compressor.

FIG. 8 is a perspective view of a rotary rod showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Sealing case 5 Suction port (suction pipe) 7 Discharge port (discharge pipe) 9 Electric mechanism part (drive means) 25 Main shaft 27 Cylinder 29 Rotating body 33 Eccentric shaft part 45 Groove 47 Blade 49 Working chamber

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Masayuki Okuda 8 Shinsugita-cho, Isogo-ku, Yokohama-shi, Kanagawa Prefecture Inside the Home Appliances Research Laboratory Toshiba Yokohama Office (72) Inventor Takuya Hirayama 8 Shin-Sugita-cho, Isogo-ku, Yokohama-shi, Kanagawa (72) Inventor Satoru Oikawa Satoshihara 336, Fuji-shi, Shizuoka Pref. Toshiba Corporation Fuji Factory (56) References JP-A-1-69789 (JP, A) JP-A-59 JP-A-93995 (JP, A) JP-A-64-36990 (JP, A) JP-A-61-114090 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04C 18/30- 18/352

Claims (6)

(57) [Claims] 1. A cylinder, a rotating body eccentrically arranged in the cylinder, a spiral groove provided along a peripheral surface of the rotating body, and A helical blade for forming a space with a cylinder into a plurality of working chambers, a main shaft having an eccentric shaft portion engaged with the rotating body and rotating and rotating the rotating body, and transmitting a driving force to the main shaft. A fluid compressor, comprising: a driving unit for performing rotation of the rotating body, wherein a part of the rotating body is thinned to form a cavity in an inner peripheral portion. 2. The fluid compressor according to claim 1, wherein the main shaft includes a balance weight, and the balance weight is disposed in a cavity formed in an inner peripheral portion of the rotating body. 3. The main shaft is supported by a bearing member, and at least a part of the bearing member is disposed so as to be located in a cavity formed in an inner peripheral portion of the rotating body. The fluid compressor according to claim 1. 4. A cylinder, a rotating body eccentrically arranged in the cylinder, a spiral groove provided along a peripheral surface of the rotating body, and A helical blade for defining a space with a cylinder into a plurality of working chambers, a main shaft having an eccentric shaft portion engaged with the rotator and rotating the rotator, and transmitting a driving force to the main shaft. And a bearing member that supports the main shaft, wherein the bearing member is located on a side opposite to the first bearing member located between the rotating body and the drive unit, and the drive unit. And a second bearing member that is located, wherein the discharge side of the working chamber is located on the first bearing member side, and the suction side of the working chamber is located on the second bearing member side. Characteristic fluid compressor. 5. A cylinder, a rotating body eccentrically arranged in the cylinder, a spiral groove provided along a peripheral surface of the rotating body, and A helical blade for defining a space with a cylinder into a plurality of working chambers, a main shaft having an eccentric shaft portion engaged with the rotator and rotating the rotator, and transmitting a driving force to the main shaft. A fluid compressor comprising: a driving unit that drives the eccentric shaft portion of the main shaft in a region where gas force generated during compression is generated. 6. The fluid compressor according to claim 5, wherein an inner peripheral bearing portion of the rotating body that engages with the eccentric shaft portion of the main shaft is located in a region where a gas force generated during compression is generated.