JPH0458085A - Fluid compressor - Google Patents

Abstract

PURPOSE:To prevent load from being concentrated onto a part of a blade by carrying fluid which comes in a working chamber from the inlet end side of a cylinder when a rotor is relatively turned against a cylinder, to a working chamber at a discharge end side so as to be discharged outside, and thereby making the capacity of the first chamber at the inlet end side maximum. CONSTITUTION:The cylinder 7 of a fluid compressor is made gradually small in inner diameter toward the discharge end side from the inlet end side. In addition, a rotor 21 is formed into a conical shape which is made gradually small in inner diameter toward the discharge end side from the inlet end side in such a way that the first working chamber 35 at the inlet end side is made to secure the maximum capacity even if a large twisting angle is not given to a blade 33. Excessive load is not thereby concentrated to a part of the blade 33 which is formed in the outer circumferential surface of a rotor 21 at an equal pitch, and also is fitted in a groove 31 in a spiral shape in such a way as to be freely accessed to, stable operations can thereby be secured for a long time.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a helical blade type fluid compressor suitable for compressing refrigerant gas in a refrigeration cycle, for example.

(Prior Art) Conventionally, general compressors such as reciprocating type and rotary type are known. A helical blade type fluid compressor is provided that compresses fluid while sequentially transferring it to a working chamber and then discharges the fluid to the outside.

For an overview of the helical blade type compressor, see, for example, Part 9.
As shown in the figure, there is a cylinder 101 and e inside the cylinder 101.
a rotary rod 1 which is arranged eccentrically by the angle of rotation and is rotatable relative to the cylinder 101 via an Oldham ring 102;
03, and a rod 10 on the outer peripheral surface of the rotary mouth rad 103.
A spiral groove 105 is formed over substantially the entire length of the blade 3, and a spiral blade 107 is fitted into this groove 105 so as to be able to move in and out. The outer peripheral surface of the blade 107 is in close contact with the inner peripheral surface of the cylinder]01, and the blade 107 is connected to the rotating rod 103.
Rotate relative to. Since the rotating rod 103 rotates eccentrically with respect to the cylinder 101, a relative speed is generated between the outer circumferential surface of the rod and the inner circumferential surface of the cylinder that opposes it.
Furthermore, this relative speed changes over one period of one revolution. Therefore, as mentioned above, the blade 107 has a spiral groove 1.
05, a plurality of working chambers 109 are formed in the space between the rotating rod 103 and the cylinder 101 along the axial direction. The volume of the working chamber 104 is
The pitch of the spiral groove 105 in which the blade 107 is fitted is determined by the pitch of the spiral groove 105, and the pitch of the groove 105 is
It gradually becomes smaller from one end of 03 to the other end. Therefore, the volume of the working chamber 109 formed by the blade 107 gradually decreases from the suction end side of the rotary rod 103, which is the suction tube 111 side, to the discharge end side, which is the discharge tube 113 side. The structure is such that the refrigerant is gradually compressed and discharged outside while being sequentially transferred toward the side.

(Problems to be Solved by the Invention) As mentioned above, in the helical blade type fluid compressor,
The refrigerant sent into the working chamber 109 from the suction end side of the cylinder 103 is transferred to the working chamber 109 at the discharge end side of the cylinder 101.
The operating capacity of the fluid compressor is determined by the volume of the first working chamber 109 on the suction end side into which the refrigerant is fed. Therefore, in order to increase the volume of the first working chamber 109, as shown in FIG.
It is necessary to ensure a large pitch P of 05. For this reason, the blade 107 is twisted greatly and the groove 107 is forced into the groove.
05, the twisted region is likely to be subject to load and fatigue, which is undesirable from the viewpoint of durability. In some cases, this may lead to problems such as damage.

Therefore, an object of the present invention is to provide a fluid compressor that does not require excessive twisting of one blade during assembly and is highly desirable in terms of durability.

[Structure of the Invention] (Means for Solving the Problem) In order to achieve the above-mentioned object, the present invention has a suction end side and a discharge end side, and has a suction end side and a discharge end side. a cylinder whose inner diameter gradually decreases, and a cylinder which is arranged eccentrically along the axial direction of the cylinder, is rotatable relative to the cylinder with a part of the cylinder in contact with the inner circumferential surface of the cylinder, and which has a suction A conical rotating body whose inner diameter gradually decreases from the end side to the discharge end side, a spiral groove formed on the outer periphery of this rotating body with approximately the same pitch, and a spiral groove that is inserted into and out of this groove freely. a spiral blade having an outer circumferential surface that is fitted together and in close contact with an inner circumferential surface of the cylinder, and partitions a plurality of working chambers between the inner circumferential surface of the cylinder and the outer circumferential surface of the rotating body; and the rotating body. and a driving means for relatively rotating the rotating body and the cylinder, and sequentially transfers fluid flowing into the working chamber from the suction end side of the cylinder to the working chamber on the discharge end side when the rotating body and the cylinder rotate relative to each other. It is discharged to the outside.

(Function) The cylinder of such a fluid compressor has an inner diameter that gradually decreases from the suction end to the discharge end, and the rotating body has a conical shape that gradually decreases the inner diameter from the suction end to the discharge end. Because of the shape, it is possible to secure a large volume of the first working chamber on the suction end side without giving a large twist to the blade. Therefore, an unreasonable load is not concentrated on a portion of the blade, and stable operation can be expected over a long period of time.

(Embodiment) Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings of FIGS. 1 to 6. In Fig. 1, reference numeral 1 indicates a sealed case of a hermetic fluid compressor 3 used in a refrigeration cycle.One side of the sealed case 1 has a suction tube 5 of the refrigeration cycle, and the other side has a discharge tube 7. Each is provided. Inside the closed case 1, an electric element 9 and a compression element 11 as driving means are respectively arranged. The electric element 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.

The compression element 11 has a cylinder 17, the cylinder 1
7 is the inner diameter from the suction end side which is the suction hole 41 side to the discharge hole 3
It has a shape that gradually becomes smaller toward the other side, the discharge end.

Both ends of the cylinder 17 are rotatably supported by bearings 19 and 20 fixed to the inner surface of the sealed case 1.

The bearings 19 and 20 have boss parts 19a and 20a into which the ends of the cylinder 17 are rotatably fitted, and these boss parts 19a and 20.
It consists of base parts 19b and 20b which have a diameter larger than that of cylinder a and are fixed to the inner surface of the sealed case 1, and both ends of the cylinder 17 are hermetically closed.

Inside the cylinder 17, a conical rotating body 21 having an outer diameter smaller than the inner diameter of the cylinder 17 and gradually becoming smaller from the suction end side to the discharge end side is disposed along the axial direction of the cylinder 17. There is. The rotating body 21 is made of iron or other material, and its central axis IJIA is eccentrically arranged downward in FIG. 1 by a distance e with respect to the central axis B of the cylinder 17, and is in line contact with the inner peripheral surface.

At both ends of the rotating body 21, there are support shafts 21a each having a narrow diameter.
, 21b are provided, and these support shaft portions 21g, 21b are rotatably inserted and supported in bearing holes 19c, 20c formed in boss portions 19a, 20a of the bearings 19.20, respectively.

An Oldham ring 2 is attached to one support shaft 21a of the rotating body 21.
A prismatic portion 25 having a square cross section is formed to function as a power transmission surface to which rotational power from the cylinder 17 side is transmitted via the cylinder 17 side. This prismatic portion 25 fits into a rectangular long hole 26 formed in the Oldham ring 23 with some play, and the prismatic portion 25 can slide within the range of the play. Furthermore, one end portion of a pair of transmission pins 27 and 27 is slidably inserted into the outer peripheral surface of the Oldham ring 23 in a radial direction perpendicular to the longitudinal direction of the elongated hole 26, and the other end portion of the transmission pin 27 is inserted into the outer peripheral surface of the Oldham ring 23. It is fitted and fixed into a fitting hole 29 bored in the peripheral wall of the cylinder 17. As a result, the rotary body 21 is easily connected to the cylinder 17 at an eccentric position, and the rotational force of the cylinder 17 is transmitted to the rotary body through the Oldham ring 23.
1.

Therefore, the electric element 9 is energized and the cylinder 17 is moved to the rotor 1.
5, the rotating body 21 rotates at an eccentric position with respect to the cylinder 17 via the Oldham ring 25, so that the outer circumferential surface of the rotating body 21 and the inner circumferential surface of the cylinder 17 opposing it rotate. A relative speed is generated between the cylinder 17 and the cylinder 17, and the cylinder 17 rotates internally while changing with one revolution as one period, and rotates relative to the cylinder 17.

On the other hand, a spiral groove 31 is formed along the axial direction on the outer peripheral surface of the rotating body 21, and each pitch P of the spiral groove 31 is set to be substantially the same. In this spiral groove 31,
A spiral blade 33 made of an elastic material such as a synthetic resin is assembled to be movable in and out using elastic force.

The width of the blade 33 is set to be approximately the same as the width of the spiral groove, and the thickness is set to be smaller than the dimension up to the bottom of the spiral groove. It is possible to enter and exit (arrow A in Figure 1).

The outer circumferential surface of the blade 33 is in close contact with the inner circumferential surface of the cylinder 17, and the space between the inner circumferential surface of the cylinder 17 and the outer circumferential surface of the rotating body 21 is partitioned into a plurality of working chambers 35 by the blade 33. ing. Each working chamber 35 has a blade 33
It is now formed between two adjacent windings of
As shown in the figure, there is a substantially crescent-shaped region extending along the blade 33 from one contact point between the rotating body 21 and the inner circumferential surface of the cylinder 17 to the next contact point.

The volume of the working chamber 35 is such that the first working chamber 35 on the suction end side has a cross-sectional radius that gradually decreases from the suction end side (right side in Figure 1) to the discharge end side (left side in Figure 1) of the cylinder 17. It is set to be the maximum, and then gradually become smaller toward the working chamber 35 on the discharge end side. The first working chamber 35 on the suction end side is connected to the suction tube 5 of the refrigeration cycle through a communication suction groove 37 formed on the outer peripheral surface of the end of the rotating body 21 and a suction hole 39 penetrated through the bearing 20. It is connected and communicated with. Thereby, the refrigerant gas sucked into the cylinder 17 from the suction tube 5 is reliably introduced into the first working chamber 35 through the suction groove 37 without interruption.

On the other hand, the working chamber 35 having the smallest volume on the discharge end side has the bearing 19
It is connected and communicated with a discharge hole 41 formed in and opened in the sealed case 1.

In addition, the rotating body 21 has an oil introduction passage 43 as shown in FIG.
is bored along the central axis A of the rotating body 21. One end of this oil introduction path 43 communicates with the bottom of the spiral groove 31 on the discharge side, and the other end communicates with the bottom of the sealed case 1 through a communication hole 45 formed in the bearing 20 on the suction end side. Mouth 47a
It is connected and communicated with an inlet pipe 47 facing. Therefore, when the pressure inside the sealed case 1 increases, the lubricating oil 49 stored at the bottom of the sealed case 1 is sent into the bottom of the groove 31 through the introduction pipe 47, the communication 45 and the oil introduction path 43, and the blade 33 is ensured to move in and out smoothly.

The operation of the fluid compressor configured in this way will be explained.

First, when the electric element 9 is energized, the rotor 15 rotates, and the cylinder 17 also rotates together with the rotor 15. When the cylinder 17 rotates, the rotating body 21 also rotates via the Oldham ring 23. Since the rotating body 21 rotates at an eccentric position with respect to the cylinder 17, a relative speed occurs between the outer circumferential surface of the rotating body 21 and the inner circumferential surface of the cylinder 17 that opposes it. The rotating body 21 internally rotates within the cylinder 17 while changing as the rotational force changes, and the rotating body 21 makes a turning movement with respect to the cylinder 17. As a result, as shown in FIGS. 4 to 8, the refrigerant gas fed into the working chamber 35 on the suction end side is compressed while being sequentially sent toward the working chamber 35 on the discharge end side, and is discharged outside from the discharge tube 7. Become so. During this operation, the blade 33 is not unreasonably twisted, so that a stable operating state can be obtained for a long period of time.

[Effects of the Invention] As explained above, according to the fluid compressor of the present invention, the inner diameter of the cylinder and the outer diameter of the rotating body are shaped to gradually decrease from the suction end side to the discharge end side. It becomes possible to set the pitch of the helical grooves to be - between paths, and the volume of the first working chamber on the suction end side can be maximized, and the blade can be assembled into the helical grooves without difficulty. As a result, it becomes possible to prevent a concentrated load from acting on a portion of the blade, which tends to provide stable operating conditions over a long period of time.

[Brief explanation of the drawing]

1 to 8 show an embodiment of the present invention, in which FIG. 1 is a vertical sectional view showing the entire fluid compressor, FIG. 2 is a perspective view of a rotating body with blades assembled, and FIG. Figure 1 is a sectional view taken along the line ■-■, Figures 4, 5, 6, 7, and 8 are operation explanatory diagrams, and Figure 9 shows the entire conventional helical blade type compressor. The longitudinal sectional view shown in FIG. 10 is a perspective view similar to FIG. 2 showing the conventional example. 9... Electric element (driving means) 17... Cylinder 21... Rotating body 31... Groove 33... Blade 35... Working chamber

Claims (1)

[Claims] A cylinder having a suction end side and a discharge end side, the inner diameter of which gradually decreases from the suction end side to the discharge end side, and an inner circumferential surface of the cylinder, which is eccentrically arranged along the axial direction of the cylinder. a conical rotating body that is rotatable relative to the cylinder with a part of the body in contact with the cylinder, and whose inner diameter gradually decreases from the suction end side to the discharge end side; a spiral groove formed at substantially the same pitch, and an outer circumferential surface that is fitted into the groove so as to be able to move in and out and is in close contact with the inner circumferential surface of the cylinder, and the inner circumferential surface of the cylinder and the outer circumference of the rotating body. A spiral blade that partitions the space between the rotating body and the cylinder into a plurality of working chambers, and a drive means that rotates the rotating body and the cylinder relative to each other, and when the rotating body and the cylinder rotate relative to each other, the cylinder A fluid compressor characterized in that fluid that flows into a working chamber from a suction end is sequentially transferred to a working chamber on a discharge end and is discharged to the outside.