JP3140119B2 - 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 helical fluid compressor suitable for compressing refrigerant gas in a refrigeration cycle, for example.

[0002]

2. Description of the Related Art Reciprocating compressors, rotary compressors and the like are generally known as conventional compressors. In addition, refrigerant flowing into a working chamber from a suction end side of a cylinder is discharged to a discharge end side of the cylinder. The spiral type fluid compressor which compresses while sequentially transferring the fluid to the working chamber and discharges the fluid to the outside is provided.

[0003] An outline of the spiral type fluid compressor is, for example,
As shown in FIG. 6 and FIG.
A cylinder 105 rotated by a driving means comprising:
A rotating rod 109 which is disposed eccentrically within the cylinder 105 by e and is rotatable relative to the cylinder 105 via an Oldham ring 107; Groove 1
The spiral blade 11 is formed in the groove 111.
3 are fitted so as to be able to enter and exit freely. The outer peripheral surface of the blade 113 is mutually closely the inner peripheral surface of the cylinder 105, the blade 1
13 rotates integrally with the rotating rod 109 . Rod 1
The volume of the plurality of working chambers 115 formed in the space between the cylinder 09 and the cylinder 105 is, as shown in FIG.
Is determined by the pitch P of the spiral groove 111 to be fitted, and the pitch P of the groove 111 gradually decreases from one end of the rotating rod 109 to the other end. Therefore, the working chamber 11 formed by the blade 113
The volume of the rotary rod 10 on the suction pipe 117 side is
9 gradually decreases from the suction end side to the discharge end side that is the discharge pipe 119 side, so that the refrigerant is compressed and discharged to the outside while being sequentially transferred to the discharge end side. I have.

[0004]

As described above, in the spiral-type fluid compressor, the working chamber 115 is formed by blades 113 having different pitches, and discharges the volume when the refrigerant is enclosed in the working chamber 115 and discharges the same. Working chamber 11 immediately before
Since the volume of the first working chamber 115 is determined mechanically, for example, in order to increase the compression capacity, the first working chamber 115 on the suction side is used.
And the amount of intake into the working chamber 115 needs to be increased.

In order to enlarge the working chamber 115, for example,
Means such as increasing the pitch P of the first spiral groove 111 on the suction side forming the working chamber 115, securing a large amount of eccentricity e, or increasing the diameter of the cylinder 105 Can be considered.

However, the first means is that the blade 1
As a result, a strong contact pressure acts on the blade wall of the spiral groove 111 due to an increase in the torsion angle of the blade 13, resulting in sliding resistance during the ingress and egress operations, leading to faster wear of the blade 113 and damage to the blade 113. There is a risk of connection.

The second means has a large working stroke when the blade 113 is moved in and out, so that when the blade 113 projects from the groove 111, the bending moment is strongly affected by the pressure difference. For this reason, it is necessary to take measures such as increasing the width of the blade 113 so as not to lose the bending moment, and accordingly, the malfunction that the working chamber 115 becomes small occurs.

[0008] The third means causes a problem that the entire apparatus becomes large.

Therefore, the present invention is to provide a fluid compressor which has solved the above-mentioned problems.

[0010]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides an outer cylinder and a cylindrical body disposed axially and concentrically within the outer cylinder.
An eccentric arrangement is provided between the outer cylinder and the cylindrical body along the axial direction, and a part of the outer peripheral surface is in contact with the inner peripheral surface of the outer cylinder and a part of the inner peripheral surface is an outer peripheral surface of the cylindrical body. An inner cylinder arranged so as to be pivotable relative to the outer cylinder and the columnar body in a contact state, and a spiral groove formed in the inner cylinder and formed at a pitch gradually decreasing from a suction side to a discharge side. A helical blade that fits in and out of the groove so as to freely move in and out of the groove, and defines a plurality of working chambers between the outer cylinder and the inner cylinder and between the inner cylinder and the columnar body, respectively; through the drilled window hole and a spacer provided so as to be in contact with the outer peripheral surface of the inner peripheral surface and said cylindrical body of said outer cylinder, relative of said inner cylinder relative to the outer cylinder and the cylindrical body The pivoting movement by flowing into the working chamber fluid was to transfer while sequentially compressing the working chamber of the groove pitch becomes smaller side.

[0011]

According to this fluid compressor, the fluid taken in the working chamber on the suction side is sequentially transferred to the working chamber on the discharge side by the relative rotation of the inner cylinder with respect to the outer cylinder and the columnar body. It is compressed and can be taken out from the discharge side. In this case, sandwich the inner cylinder,
Two working chambers are formed inside and outside, so that the compression capacity can be easily expanded.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of the present invention will be described in detail with reference to FIGS. In FIG. 1, 1
1 shows a closed case of a hermetic type fluid compressor 3 used for a refrigeration cycle. One of the closed cases 1 is provided with a suction pipe 5 for the refrigeration cycle, and the other is provided with a discharge pipe 7. An electric element 9 as a driving unit and a compression element 11 as a compression unit are arranged in the closed case 1.

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

The compression element 11 has an outer cylinder 17, and one end of the outer cylinder 17 is rotatably supported by a main bearing 19 fixed to the inner surface of the sealed case 1. The main bearing 19 includes a boss 19a in which one end of the outer cylinder 17 is rotatably fitted, and a base 19b having a diameter larger than that of the boss 19a and fixed to the inner surface of the sealed case 1. One end of the outer cylinder 17 is hermetically closed.

Inside the outer cylinder 17, an inner cylinder 21 smaller than the inner diameter of the outer cylinder 17 is disposed along the axial direction, and its central axis A is spaced from the central axis B of the outer cylinder 17 by a distance e. In FIG. 1, it is disposed eccentrically downward, and a part thereof is in line contact with the inner peripheral surface of the outer cylinder 17.

The inner cylinder 21 has a cylindrical portion 23 having one open side and a support shaft 25. The support shaft 25 is rotatable in a bearing hole 19c formed in a boss 19a of the main bearing 19. It is inserted and supported.

On the other hand, the open side of the cylindrical portion 23 is rotatably inserted and supported by a boss portion 27a of a sub bearing 27 fixed inside the closed case 1, and this bearing region is hermetically closed.

Inside the cylindrical portion 23 of the inner cylinder 21, a columnar body 31 having a shaft end 29 on one side is disposed along the axial direction, and the shaft end 29 is provided on the boss 27a of the sub bearing 27. And is rotatably fitted and supported in a bearing hole 27b provided in the hole . As shown in FIG. 2, a pair of spacers are provided between the outer cylinder 17 and the cylindrical body 31 through a window hole 33 formed in the inner cylinder 21 and fixed via a transmission member 35 described later. 37, 37, cylindrical body
31 is assembled such that its center line C coincides with the center axis B of the outer cylinder 17 . As a result, working spaces are formed between the outer cylinder 17 and the inner cylinder 21 and between the inner cylinder 21 and the cylindrical body 31, respectively. Further, the cylindrical body 31 is interposed through the transmission member 35.
So that the rotational power from the outer cylinder 17 is given.
become.

On the other hand, as shown in FIG.
1 through an Oldham ring 39, so that given the rotational power from the outer side cylinder 17.

That is, the Oldham ring 39 is provided on the support shaft 25 side of the inner cylinder 21 as shown in FIG. 3, and the support shaft 25 is formed with a square column 41 having a square cross section functioning as a power transmission surface. Have been.

The prism 41 is formed by the Oldham ring 3
Along with the rectangular elongated hole 43 formed in the groove 9, the rectangular column portion 41 can slide within the range of the play while fitting with play with the play. On the outer peripheral surface of the Oldham ring 39, one ends of a pair of transmission pins 45, 45 are slidably fitted in a radial direction orthogonal to the longitudinal direction of the long hole 43, respectively. The end is fitted and fixed in a fitting hole 47 formed in the peripheral wall of the outer cylinder 17. Thereby, the inner cylinder 21 is easily connected to the outer cylinder 17 at a position eccentric to the outer cylinder 17, and the rotational force of the outer cylinder 17 is transmitted to the inner cylinder 21 via the Oldham ring 39. ing.

The transmission member 35 is disposed at two places, on the right side on the suction end side and on the left side on the discharge end side, and penetrates the cylindrical body 31 and the spacers 37, 37, as shown in FIG. 17 is inserted and supported.

Accordingly, the outer cylinder 17 and the cylindrical body 31 rotate synchronously with the rotation of the outer cylinder 17 and the rotor 15 by the operation of the electric element 9, and the inner cylinder 21 is rotated with respect to the cylindrical body 31 by the Oldham ring 39. And eccentrically rotate through.

[0024]

Further, a spiral groove 47 is formed in the inner cylinder 21 along the axial direction. Spiral groove 47
Is set so that each pitch P is gradually reduced from the suction end (right side in FIG. 1) to the discharge end (left side in FIG. 1). A helical blade 49 made of a synthetic resin-based elastic material that is in contact with the surface and whose inner peripheral surface is in contact with the outer peripheral surface of the columnar body 31 is inserted and removed freely. Thus, a plurality of first working chambers 50 are provided between the outer cylinder 17 and the inner cylinder 21.
However, a plurality of second working chambers 51 are defined between the inner cylinder 21 and the column 31.

The volumes of the first and second working chambers 50 and 51 are as follows:
It gradually decreases from the suction end to the discharge end (left side in the figure), and the first working chambers 50 and 51 on the suction side.
Is set to be maximum, and thereafter, gradually decrease toward working chambers 50 and 51 on the discharge side. The first working chambers 50 and 51 on the suction end side communicate with the suction pipe 5 via a communication passage 53 provided in the main bearing 19. The second working chamber 51 communicates with the first working chamber 50 via a communication hole 55 provided in the inner cylinder 21 to ensure that the fluid is introduced into the working chambers 50 and 51 without interruption.

On the other hand, the first and second working chambers 50 and 51 having the smallest volume are provided with communication holes 5 provided in the inner cylinder 21.
The first working chamber 50 is connected to and communicated via the opening 7, and is opened into the closed casing 1 at the end of the outer cylinder 17.

The cylinder 31 is provided with an oil introduction passage 59 as shown in FIG. One end of the oil introduction passage 59 communicates with the inner peripheral portion of the blade 49, and the other end thereof communicates with the oil introduction passage 61 of the inner cylinder 17 and is connected and communicated with an introduction pipe 63 whose suction port faces the bottom of the sealed case 1. ing. Therefore, if the pressure in the closed case 1 increases, the closed case 1
The lubricating oil stored at the bottom of the blade 4 is fed through the oil introduction passages 61 and 59 to the inner peripheral portion of the blade 49,
The lubrication at the time of the in / out operation of No. 9 is maintained.

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

First, when a current flows through the stator 13, the outer cylinder 17 rotates integrally with the rotor 15. The rotational power of the outer cylinder 17 is transmitted to the column 31 via the transmission member 35, and the column 31 rotates synchronously with the outer cylinder 17. On the other hand, the rotational power is transmitted via the Oldham ring 39, the inner cylinder 21 is the outer cylinder 17,
It makes a revolving motion relative to the cylindrical body 31. As a result of this swirling motion, the fluid is first taken into the first working chamber 50 as shown by A, B, C, D, E, F and G in FIG.
After 80 °, it is taken into the second working chamber 51 this time. The fluid taken in each of the working chambers 50 and 51 is compressed while being sequentially transferred toward the discharge end side, and is compressed.
Is discharged to the outside. During this operation, the first and second
The working capacity of the working chambers 50 and 51 can increase the compression capacity.

[0031] Figure 5 shows a second embodiment, a pair
First, in which the second working chamber 50 and 51 provided symmetrically of.

That is, an inner cylinder 21 having both ends opened is eccentrically arranged by e inside the outer cylinder 17 and both ends of the inner cylinder 21 are fixed to the inside of the sealed case 1 at the boss portion of the main bearing 19. 19a and auxiliary bearing 2
7, both ends of which are rotatably supported by a boss 27a.

A cylindrical body 31 having left and right shaft ends 65 and 65 is disposed inside the inner cylinder 21.
5, 65 are boss portions 19a of the main bearing 19 and the sub bearing 27,
It is rotatably fitted and supported in bearing holes 19b and 27b provided in 27a. Both shaft ends 65 and 6 of the cylindrical body 31
5 is arranged on the same axis as the center axis B of the outer cylinder 17. Thus, the outer peripheral surface of the inner cylinder 21 is in line contact with the inner peripheral surface of the outer cylinder 17 and the inner peripheral surface of the inner cylinder 21 is in line contact with the outer peripheral surface of the cylindrical body 31, so that the outer and inner cylinders An operating space is formed between the inner cylinder 17 and the inner cylinder 21 and between the inner cylinder 21 and the cylindrical body 31.

The inner cylinder 21 is provided with a pair of helical grooves 67 whose pitch P gradually decreases from the central portion toward both sides. , And a spiral blade 69 whose inner surface is in contact with the outer peripheral surface of the columnar body 31 is inserted and removed freely.

Thus, a plurality of first working chambers 50 are formed between the outer cylinder 17 and the inner cylinder 21, while a plurality of second working chambers 51 are formed between the inner cylinder 21 and the column 31. Is formed. Each working chamber 50, 51
The central portion is set to have the largest volume, and is set so as to gradually decrease outward.

The first and second working chambers 50, 51 at the central part
Communicates with the suction pipe 5 through a fluid passage 71 provided in the cylindrical body 31. Each of the smallest outer working chambers 50 and 51 communicates with the discharge pipe 7 opened in the sealed case 1. In the case of this structure, the discharge pressure is applied to both sides, but the volumes of the outer working chambers 50 and 51 are maximized, and are gradually reduced toward the central portion so that the central portion has the discharge pressure. Is also possible.

Further, balance passages 73, 73 are provided on the left and right sides of the cylindrical body 31, and the suction pressure is guided to the bearing holes 19c, 27b to eliminate the thrust force .

The other components are the same as those of the above embodiment, and the same reference numerals are given and the detailed description is omitted.

Therefore, according to this embodiment, in addition to the functions and effects of the first embodiment, the outer cylinder 17, the inner cylinder 21, and the cylindrical body 31 have a structure in which the thrust force hardly acts on all of them. The state is obtained .

[0040]

As described above, according to the present invention, the compression capacity can be increased without increasing the size of the apparatus.

[Brief description of the drawings]

FIG. 1 is a sectional view of a fluid compressor embodying the present invention.

FIG. 2 is a cross-sectional view showing an attached state of a transmission member.

FIG. 3 is a sectional view taken along line AA of FIG. 1;

FIG. 4 is an operation explanatory view.

FIG. 5 is a sectional view similar to FIG. 1, showing a second embodiment.

FIG. 6 is a sectional view similar to FIG. 1 showing a conventional example.

FIG. 7 is a perspective view of a rotating rod showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Sealing case 9 Driving means 17 Outer cylinder 21 Inner cylinder 31 Cylindrical body 47 Spiral groove 49 Blade 50, 51 Working chamber

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F04C 18/344 311 F04C 23/00

Claims (1)

(57) [Claims] An outer cylinder, a cylindrical body disposed axially and concentrically in the outer cylinder, and eccentrically disposed along the axial direction between the outer cylinder and the cylindrical body, A part of the outer peripheral surface is arranged to be rotatable relative to the outer cylinder and the cylindrical body while a part of the inner peripheral surface is in contact with the inner peripheral surface of the outer cylinder and a part of the inner peripheral surface is in contact with the outer peripheral surface of the cylindrical body. An inner cylinder, a helical groove provided on the inner cylinder and formed at a pitch that gradually decreases from the suction side to the discharge side, and fits into and out of the groove so that the outer cylinder and the inner cylinder And a spiral blade defining a plurality of working chambers between the inner cylinder and the columnar body, respectively, and an inner peripheral surface of the outer cylinder passing through a window formed in the inner cylinder. On the outer peripheral surface of the cylinder And a spacer provided so as to be in contact with the outer cylinder and the inner cylinder with respect to the cylindrical body. A fluid compressor characterized by the following.