KR100225277B1 - Fluid machine - Google Patents

Abstract

The present invention relates to a fluid machine, which is a helical blade type compressor, which reliably releases the pressure when the operating chamber becomes abnormally high pressure for some reason, at the same time to relieve stress on the blade and improve the reliability of the blade. At the same time, there is provided a fluid machine that reliably prevents overcompression and contributes to improved performance, and includes a cylinder 5 and a roller 11 disposed eccentrically in the cylinder and a spiral groove 14 provided along the circumferential surface of the roller; And a helical blade-type actuating mechanism (3) having a spiral blade (15) which fits freely into the spiral groove and partitions a space with a cylinder into a plurality of operating chambers (16). A release passage 20 for discharging the pressure into the operation chamber on the discharge side when the inside of the operation chamber exceeds the predetermined pressure on the discharge side wall surface The.

Description

Fluid machinery

The present invention relates to a fluid machine, for example a helical blade type compressor used in a refrigeration cycle device.

The compressor constituting the refrigeration cycle in the category of the fluid machine is conventionally used in various types such as a receiver method, a rotary method, etc., but the structure of the drive unit and the compression unit that transmits the rotational force to the compression mechanism unit is complicated and there are many component points.

In addition, although a check valve is provided on the discharge side in order to increase the compression efficiency, since the pressure difference between both sides of the check valve is considerably large, gas is likely to leak from the check valve. In order to solve this problem, it is necessary to increase the dimensional accuracy and the assembly precision of each component, resulting in high manufacturing costs.

Therefore, a helical blade compressor, also referred to as a fluid compressor, has recently been proposed. The roller which is a rotating body is eccentrically arrange | positioned in the cylinder connected to a rotation drive source, and is rotated in synchronization with a cylinder. Spiral grooves are provided on the circumferential surface of the roller, and the blade is mounted freely in and out.

A compression chamber, which is a working chamber, is formed between the blades and the circumference of the roller and the inner circumferential surface of the cylinder, and the refrigerant gas, which is a working fluid, is sucked from one end of the compression chamber and gradually transported to the other end side.

Therefore, the problems as described above in the conventional compressor can be eliminated, and the comparatively simple configuration improves the sealing property, enables efficient compression, and facilitates the manufacture and assembly of parts.

By the way, in this type of compressor, the compression ratio is determined by the helical phase, and overcompression occurs and the compression performance is remarkably deteriorated in a low compression operation condition such as at low rotation and starting, which are areas that deviate from the design compression ratio.

For example, there is a liquid backflow phenomenon when the air conditioning load is small. The compression chamber becomes abnormally high pressure beyond a predetermined pressure, and in particular, the blade, which is an elastic member of the synthetic resin system, is stressed and easily breaks.

The abnormally high pressure state of the compression chamber is surely generated under predetermined conditions and cannot be avoided. In this state, it is necessary to have a means for preventing the breakage of the blade, and the present applicant has first proposed a fluid compressor disclosed in Japanese Patent Laid-Open No. 5-71482.

This technique is characterized in that the blade which partitions the compression chamber is provided with a discharge passage for releasing the pressure into the operation chamber on the discharge side when the pressure in the compression process exceeds a predetermined pressure, and the stress applied to the blade is reduced.

Therefore, since the thickness of the blade is reduced as much as the discharge passage is provided, the blade is easily broken by deformation such as torsion, and reliability decreases.

In addition, since the blade is formed into a predetermined shape as the shaping means of the blade once, the discharge passage is provided by cutting, the manufacturability is poor.

The present invention has been made on the basis of the above circumstances, and its object is to release the pressure reliably when the operating chamber becomes abnormally high pressure for some reason, to relieve stress on the blade and to improve the reliability of the blade. It is to provide a fluid machine that reliably prevents overcompression and contributes to improved performance.

1 is a longitudinal side view of a helical blade compressor as a fluid machine according to one embodiment of the present invention;

2 is a perspective view of a roller mounted with a blade in a spiral groove of the same embodiment;

3A is an explanatory diagram showing a relationship between a blade and a spiral groove in a normal compression step of the same embodiment;

3B is an explanatory diagram in an overcompression state in a normal compression step of the same embodiment;

4 is a partial perspective view of a roller of another embodiment,

5 is a partial perspective view of a roller of another embodiment;

6 is a longitudinal side view of a helical blade compressor of another embodiment;

7 is a longitudinal side view of a helical blade compressor of another embodiment;

8 is a partial perspective view of a roller of another embodiment;

9 is a partial perspective view of a roller of another embodiment.

* Explanation of symbols for main parts of the drawings

5, 50: cylinder 11, 54, 54A ,: roller

14, 62: spiral groove 16, 64: operating chamber

15, 63: blades 3, 51, 51A, 51B: implement mechanism

20, 20A, 20B, 20C, 20D: release passage

In order to achieve the above object, the fluid machine of the present invention, as a claim 1, has a cylinder and a roller eccentrically arranged in the cylinder, a spiral groove provided along the circumferential surface of the roller, and freely fits into the spiral groove so that A fluid machine having a helical blade-type actuating mechanism having a spiral blade for partitioning a space into a plurality of working chambers, wherein the fluid chamber is provided on the discharge side wall of the spiral groove and the working chamber exceeds a predetermined pressure. It is characterized by including the release passage for discharging the pressure to the operation chamber on the discharge side.

The release passage of claim 1 is provided along the radial direction in the spiral groove wall surface facing the respective operation chambers at the suction side from the suction side, and gradually increases the passage area from each suction side to the operation chambers at the discharge side. It is characterized by one.

The release passage of claim 1 is provided along a spiral groove wall surface facing each working chamber on the discharge side at the suction side, and at the same time, the number of passages is gradually increased along each operating chamber on the discharge side at the suction side. do.

As for the said release passage of Claim 1 thru | or 3 as Claim 4, the depth from the said roller peripheral surface was formed shallower than the depth of the said spiral groove, It is characterized by the above-mentioned.

The method according to claim 1, wherein the operating mechanism is a twin-type two pairs are installed in the left and right symmetrical with respect to the central portion of the cylinder, the release passage is characterized in that provided in the same phase with each other in the operating mechanism. .

By providing a means for solving this problem, the invention of claim 1 can release a predetermined pressure or more from the operating chamber to the operating chamber on the discharge side, and furthermore, there is no stress applied to the blade and no special processing for the blade is necessary.

In the invention of Claims 2 and 3, the discharge passage area becomes larger than that of the operating chamber on the high pressure side, and therefore, the release passage can be promoted, and the release passage is also provided on the suction side, thereby releasing the overcompression and the liquid compression generated at the beginning of the compression process. do.

In the invention according to claim 4, in a normal compression step of a predetermined pressure or less, leakage at the bottom of the helical grooves between adjacent operating chambers is prevented.

In the invention of claim 5, since each operating system can be released at the same time when the same pressure is reached, the pressure of each operating system is completed without becoming uneven.

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment of this invention is described based on drawing, The helical blade type compressor which is a fluid machine disclosed here is used for the refrigeration cycle of an air conditioner, for example.

As shown in FIG. 1, in the sealed case 1, the right part is accommodated as the compression mechanism part 3 and the left part is respectively accommodated as the electric motor part 4 in the figure on the border of the substantially axial center part of the sealed case 1, respectively. .

The compression mechanism 3 is a hollow cylinder having both ends open at the same time and has a cylinder 5 in which the shading portions 5a and 5b are integrally projected on the outer circumferential surfaces of the both ends.

The main bearing 6 is attached and fixed to the side of one end (left side of the drawing) of the cylinder 5 through the fixing member 7 and the opening of the cylinder is closed. On the side of the other end side (right side of the drawing), the sub-bearing 8 is attached and fixed through the fixing member 7 and the opening of the cylinder is closed.

Along the shaft center of the main bearing 6 and the sub-bearing 8, the crankshaft 9 is inserted and supported freely to rotate. The crankshaft 9 not only penetrates into the cylinder 5 between the main bearing 6 and the sub-bearing 8 but also protrudes in the left direction of the drawing from the main bearing 6 and the motor part 4 Constitutes a rotating shaft portion 9Z.

The crankshaft 9 will be described again in a circumferential surface between the main bearing 6 and the sub-bearing 8 and at a distance from each other and at the same time eccentric with the crankshaft shaft center a by a predetermined size e. Two crank portions 9a and 9b of one shaft center b are integrally provided.

The crank part 9a on the left side of the figure is called a first crank part, and the right crank part 9b is called a second crank part. The crank parts 9a and 9b of each other are formed with the same predetermined width dimension.

The counter balance portion 9c is provided integrally with the crankshaft adjacent to the left side portion of the first crank portion 9a. This counter balance part 9c is eccentric to the circumferential surface part on the opposite side through the axial center from the eccentric protrusion direction of the said 1 crank part 9a.

The counter balance 10, which is separate from the crankshaft 9, is fitted to be adjacent to the further right portion of the second crank portion 9b. The counter balance 10 is eccentric to the peripheral surface portion on the side opposite to the eccentric protrusion direction of the second crank portion 9b.

Between such a crankshaft 9 and the said cylinder 5, the roller 11 of the aluminum alloy material, for example, whose specific gravity is smaller than iron is fitted. This roller 11 is a cylindrical body which is open at both ends and its axial length coincides with the axial length of the cylinder.

Stepped inner cavities 12 are formed in the inner circumferential portion of the roller 11, and in particular, the portions facing the first and second crank portions 9a and 9b of the crankshaft 9 are these crank portions. And the first and second internal cavity pivot portions 12a and 12b which are in the same width as and also in sliding contact with the outer circumferential surface freely.

As a result, the shaft center b of the roller 11 coincides with the shaft center b of the first and second crank portions 9a and 9b and is eccentric with respect to the shaft center a of the cylinder 5 or the like by e dimension. . And a part of the outer peripheral wall of the roller 11 is dimensioned so that it may roll-contact with the part of the inner peripheral wall of the cylinder 5 along an axial direction.

The Oldhams mechanism 13 is interposed between the main bearing 6 side end of the roller 11 and the roller 11 portion. This Oldhams mechanism 13 restricts the rotation of the roller 11.

On the outer circumferential surface of the roller 11 is provided a spiral groove 14 for gradually reducing the pitch from the attachment side end of the sub-bearing 8 to the attachment side end of the main bearing 6, in which the spiral blade 15 is provided. It is mounted freely in and out.

The blade 15 is made of, for example, a highly active material such as a fluororesin, and the inner diameter thereof is larger than the outer diameter of the roller 11. That is, the blade 15 is inserted into the helical groove 14 in a state of forcibly reduced diameter, and as a result, the outer circumferential surface of the blade 15 is always assembled in the cylinder 5 for each roller 11. It expands and deforms to elastically contact the inner wall of the cylinder.

When the cylinders 5 and the rollers 11 are sectional views along the radial direction, the rollers 11 are eccentrically accommodated with respect to the cylinders 5 and at the same time a part of the circumferential surface of the rollers is in a rolling contact with the cylinders. A crescent shaped space is formed between the cylinder and the roller.

In addition, when the space portion is viewed along the axial direction, the blade 15 is mounted in the spiral groove 14 of the roller 11 and its outer peripheral surface is in rolling contact with the inner circumferential wall of the cylinder 5. The space between the cylinders is partitioned into a plurality of spaces by the blades.

These spaces which become membranes are called operation chambers 16. The volume of each operating chamber 16 gradually decreases along the main bearing 6 side end at the sub-bearing 8 side end at the pitch setting of the helical groove 14.

Each operation chamber 16 is provided with a release passage 20 which will be described later.

On the side of the sealed case 1, a suction pipe 17 communicating with a heavy machinery constituting a refrigeration cycle (not shown) penetrates and is connected to a connection part 8a installed in the sub bearing 8 inside the sealed case 1. Connected. This connection part 8a is opened with respect to the recessed part 19 provided in the cylinder shading part 5b, and communicates with the buffer part 21 provided in the outer peripheral surface of the cylinder 11 edge part.

A discharge hole 24 is provided in the side portion of the bearing 6. Through this discharge hole 24, the cylinder 5 and the roller 11 side end space portion communicate with the motor portion 4 side space portion.

By setting the pitch of the helical groove 14, the operation chamber 16 on the side where the buffer portion 21 is installed becomes the suction portion A, and the operation on the side on which the discharge hole 24 on the opposite side is provided. The seal 16 becomes the discharge part B. FIG.

The first space 25 is formed around the main bearing 6, the crankshaft 9 and the roller 11, and the second space is surrounded by the crankshaft 9 and the roller 11. A portion 26 is formed and at the same time a third bearing portion 27 is formed which surrounds the surroundings as the sub-bearing 8, the crankshaft 9 and the roller 11.

A guide hole 28 is provided along the axis of the crankshaft over the pivot portion of the main bearing 6, which is the intermediate portion, at the side end face of the sub-bearing 8 of the crankshaft 9. The opening end of this guide hole 28 and the shaft pivot part opening end of the sub-bearing 8 are closed by the closing plate 30 provided in the sub-bearing end surface via the fixing member 29. As shown in FIG.

The guiding hole 28 and the outer circumferential surface of the crankshaft 9 and the respective bearings 6 and 8 communicate with a plurality of gas holes 31 and 32. In the upper side of the figure of the cylinder shading part 5a, the gas guide hole 43 is provided through both sides.

The motor unit 4 has a rotor 45 fitted to the rotating portion 9Z of the crankshaft 9 protruding from the main bearing 6 and the case body at a predetermined distance from the outer peripheral surface of the rotor ( 1a) It is composed of a stator 46 fitted to the inner circumferential surface.

As shown in FIGS. 1 and 2, the release passage 20 is provided on the wall of the spiral groove 14 at a position for each one (spiral position angle 360 °) of the spiral groove 14 formed on the roller 11. . In addition, each release channel | path 20 is provided only in the wall surface of the discharge part B side opposite each operation chamber 16. As shown in FIG.

The release passage 20 has a semicircular cross section, one end of which is opened on the circumferential surface of the roller 11 and the other end of which is substantially the same as the bottom surface of the spiral groove 14 along the radial direction of the roller 11. Is installed.

It is a helical blade type compressor comprised in this way, it energizes the electric motor part 4, and rotates the crankshaft 9 integrally with the roller 45. As shown in FIG. The rotational force of this crankshaft 9 is transmitted to the roller 11 via the 1st, 2nd crank part 9a, 9b.

That is, since the crank parts 9a and 9b are provided eccentrically and the pivot parts 12a and 12b of the internal cavity of the roller 11 are rotatably engaged with it, the roller 11 is pressed by the crank part. In addition, since the Oldhams mechanism 13 installed between the crankshaft 9 and the roller 11 regulates the rotation of the roller, the roller makes an orbital motion.

On the other hand, low pressure refrigerant gas is sucked from the suction pipe 17 and temporarily stopped at the buffer portion 21 formed in the cylinder 5 and the roller 11. And it is led to the operation chamber 16 of the suction part A side.

According to the orbiting motion of the roller 11, the rolling contact position with respect to the inner peripheral surface of the cylinder 5 of a roller moves one by one in the circumferential direction, and the blade 15 enters and exits with respect to the spiral groove 14. That is, the blade 15 breaks through in the radial direction of the roller.

Since the coolant gas guided to the operation chamber 16 on the suction part A side is formed in a spiral shape, the operation chamber 16 in the discharge part B direction in accordance with the orbital motion of the roller 11. Are transferred sequentially.

The blade 15 is set such that the pitch is gradually reduced from the suction part A to the discharge part B side, and the volume of the operating chamber 16 which becomes a partition by the blade is gradually reduced, so that the refrigerant gas is separated from the operating chamber. It is compressed in between to be sequentially transferred, and is raised to a predetermined pressure in the operating chamber on the discharge part B side and is increased in pressure.

The high pressure gas is discharged from the operation chamber 16 of the discharge part B, filled with the first space 25, and then through the discharge hole 24 provided in the main bearing 6 to the electric motor part 4 side. Is led to the space department. Then, the gas is guided to the space part on the side of the compression mechanism part 3 through the gas guide hole 43 provided in the shade part 5a of the cylinder 5, and is filled.

Since the open end of the discharge tube 18 faces this space portion, the high pressure gas is led to the discharge tube 18 and is led to the condenser therefrom.

In addition, the release passage 20 is effective in the following state. That is, in the normal compression process, as shown in FIG. 3A, the discharge part B is formed in the left part of the figure, and the suction part A is formed in the right part. 16b is in a high pressure state.

Thus, the blade 15 fitted into the spiral groove 14 is pressed against the right side of the spiral groove 14 by applying pressure to the left side of the figure. The blade 15 which partitions the operation chamber 16b is pressed against the wall surface of the adjacent operation chamber 16a side (suction part A side), and at the same time the wall surface on the opposite side to the adjacent operation chamber 16c, ie, this discharge It is pressed by the wall surface on the opposite side to the release passage 20 attached to the part B side.

It is formed in the same shape from the winding start part to the winding end part of the blade, so that the seal of each operating chamber 16 is made reliably.

In some circumstances, it may be in an overcompression state or the pressure in the operating chamber 16b may exceed a predetermined pressure. At this time, as shown in Fig. 3B, the blades 15 which partition the operating chamber 16b are pressed to the left and right adjacent operating chambers 16a and 16c.

That is, the blade 15 is pressed into the operation chamber 16a side on the suction side portion A side does not change as in the normal compression operation. On the other hand, the blade 15 on the side of the operating chamber 16c adjacent to it is pressed against the release passage 20 provided in the discharge side B of this operating chamber 16b. Thus, the blade 15 is separated from the wall surface of the half-release passageway, which is in a close state so as to be spaced apart from the wall surface.

In the operation chamber 16b in the abnormally high pressure state, the high pressure gas is discharged into the spiral groove 14 on the operating chamber 16c side due to the distance between the wall of the spiral groove 14 and the blade 15. Since the release channel | path 20 is formed in this helical groove 14, high pressure gas is guide | induced to the operation chamber 16c of the discharge part B side via this release channel | path.

As a result, pressure control in which the pressure in the operating chamber 16b in the abnormally high pressure state drops immediately is carried out, prevention of pressure loss is achieved, and the blade 15 is finished without a large load, thereby maintaining this reliability.

The release passage may have the following configuration.

As shown in Fig. 4, the release passages 20a, 20b, 20c ... are provided on the wall surface of the spiral groove 14 so as to oppose each operating chamber not shown here. In each release passage 20a, however, the passage area gradually increases from the suction part A side to the discharge chamber B side operating chamber.

In addition, since each cross-section is formed in semicircle shape, each release channel | path 20a ... is the width | variety dimension D, E, F ... of the release channel which is the diameter of the discharge part B side from the suction part A side. It gradually increases over the operating room.

In the case of such a release passage 20a, since the release passage 20a is also provided on the suction side, the pressure drop is extremely effective against overcompression or liquid compression occurring at the beginning of the compression step.

In addition, the width dimensions D, E, F ... of the release passage which are not shown in figure may all be the structure of the same width.

As shown in FIG. 5, the number of release passages 20 provided to the respective operation chambers not shown in the spiral groove 14 wall surface is transferred from the suction part A side to the operation chamber at the discharge part B side. You may comprise so that it may gradually increase over. Naturally, the area of each release passage is the same.

The configuration of such a release passage 20 is also the same, and the pressure drop is effectively reduced for overcompression or liquid compression.

It is also applicable to the helical blade type compressor as shown in FIG.

The compression mechanism part 51 and the electric motor part 52 are accommodated in the sealed case 50. In the compression mechanism (51), roller pistons (hereinafter referred to as rollers) 54 are disposed eccentrically in the cylinder 53.

The roller 54 is pivotally rotatably inserted in the pivot holes of the main bearing 55 and the sub bearing 56 whose shaft portions 54a and 54b are fixed to the inner wall of the sealed case 51.

On the other hand, the cylinder bearings 57 and 58 made of metal are pressed and fitted to the inner diameters of both ends of the cylinder 53, respectively, and are sandwiched between the outer peripheries of the main and secondary bearings 55 and 56, respectively. The shaft center of the roller 54 is eccentric with the shaft center of the cylinder 53 by e. The rotational force transmission mechanism 66 is fitted between the cylinder 53 and the roller 54 so as to transmit the rotational force of the cylinder 53 to the roller 54.

Here, the cylinder bearing 57 of the main bearing 55 side which is the right side of the figure is called a 1st cylinder bearing. The cylinder bearing 58 on the side of the sub bearing 56 on the left side of the figure is called a second cylinder bearing.

The gas passage G is provided only in the second cylinder bearing 58. Since this gas passage G is used as the discharge passage, it is called a discharge passage by this. And the discharge pipe 65 is provided in the circumferential wall of the sealed case 50 of the side in which this discharge path G is provided.

The first and second cylinder bearings 57 and 58 are formed in a ring shape with a thick thickness. The discharge passage G is composed of a pair of holes provided in the thickness portion of the second cylinder bearing 58 at the same position along the axis in the axial symmetry of the cylinder bearing.

A suction pipe 59 is connected to one side of the sealed case 50, and a suction guide passage 60 communicating with the suction pipe 59 is provided in the main bearing 55. The guide suction passage 60 is provided along one axis of the roller shaft portion 54a along this axial direction and is opened to the outer peripheral surface of the end of the roller body 54c between the roller shaft portions 54a and 54b. 61).

On the circumferential surface of the roller body 54c, a spiral groove 62 is formed to gradually reduce the pitch from one end side to the other end side, and the spiral blade 63 is fitted to the groove so as to freely enter and exit. Accordingly, the space between the inner circumferential surface of the cylinder 53 and the circumferential surface of the roller 54 is plurally partitioned by the blade 63, and the discharge portion (the discharge portion (A) on the other end side, that is, the suction side (A) side from these one end side). A plurality of operating chambers 64 are formed to gradually reduce the volume to the B) side.

On the wall surface of the discharge part B side of the helical groove 62 which opposes these operation chambers 64, the release passage 20A of the same form as the release passage 20 of the blade-type compressor demonstrated previously is provided, respectively.

However, here, each release passage 20A is specified to be 360 degrees or less in the spiral position angle.

The cylinder 53 is rotated according to the electric current of the electric motor unit 52 by the compressor comprised in this way, and the rotational force of the cylinder is transmitted to the roller 54 through the rotational force transmission mechanism 66. As shown in FIG. Since the cylinder 53 and the roller 54 differ in radius from each other, the cylinder 53 and the roller 54 rotate synchronously while maintaining a relative speed and positional relationship with each other.

As the cylinders 53 and the rollers 54 rotate, the blade 63 enters and exits the spiral groove 62 and rushes in the radial direction of the roller. For example, refrigerant gas is sucked into the suction pipe 59 and guided into the cylinder 53 through the guide passage 60 formed in the main bearing 55 and the suction passage 61 provided in the roller 54.

The refrigerant gas sucked into the cylinder 53 passes from the operation chamber 64 positioned at the suction part A side to the operation chamber 64 positioned at the discharge part B side in the operation chamber 64. Are transported sequentially. In addition, the refrigerant gas is gradually compressed while the operation chamber 64 is sequentially transferred.

At the point most conveyed to the operation chamber on the discharge part B side, it rises to a predetermined pressure and is guided along the discharge passage G of the second cylinder bearing 58 here. The high pressure gas is discharged into the sealed case 60 in the discharge passage G, and once filled in the case, guided to the discharge tube 65 and led to an external refrigerant cycle device.

In such a helical blade compressor, when the operating chamber 64 is in an overcompressed state, the release passage 20A provided at the discharge part B side of the operating chamber is opened at the blade 63 and the high pressure gas is released. Is delivered.

Therefore, the high pressure gas is sequentially delivered from the operation chamber 64 to the operation chamber 64 on the discharge part B side through the release passage 20A, respectively, and finally in the operation chamber on the discharge part B side. It is guided into the sealed case 50 through the discharge passage G, and the high pressure decreases quickly, suppresses the loss due to overcompression, and changes to a stable compression action.

FIG. 7 is provided with two systems of compression mechanisms 51A and 51B symmetrically with respect to the central portion of the cylinder 53A on the assumption that the helical blade compressor unit 51 described above with reference to FIG. 6 is provided. The compressor is called a twin type. (In addition, since the compressor is based on the compressor described in Fig. 6, its detailed configuration will be omitted here).

The release passage 20B is provided on the wall surface of the discharge part B side of each operation chamber 64. That is, the release passage 20B is provided in the same phase with each other in the compression mechanism part 51A, 52B of each system. By providing the release passages 20B in the compression mechanism sections 51A and 51B of each system, the effects are the same as those of the helical blade type compressor described with reference to FIGS. 1 and 6.

In addition, in the compressor having twin compressor units 51A and 51B, the release passage 20B is provided at the same phase of the bidirectional compressor unit, so that the high pressure drops at the same time when the same pressure is reached in each system of the compressor unit. The action is initiated.

Therefore, in the compression process of the bidirectional compression mechanism sections 51A and 51B, there is no pressure unevenness and stable compression performance can be obtained. And since there is no pressure nonuniformity, the roller 54A does not move to either thrust direction, and it does not touch another part, such as a bearing, and generate a noise.

As shown in FIG. 8, the depth dimension L of the release passage 20C (that is, the dimension from the circumferential surface of the roller 11 to the bottom surface) of the release passage 20 is the depth dimension of the spiral groove 14 (that is, the circumferential surface of the helical 11 from the peripheral surface to the bottom surface). By setting it to be shallower (L <D), it is possible to prevent gas leakage through the release passage 20C from the bottom of the spiral groove 14 to the adjacent working chamber in the normal compression state.

As shown in Fig. 9, when the width dimension (diameter) of the release passage 20D is X and the bottom diameter of the helical groove 14 is ψd0, the relationship of X≤0.6d0 is set.

And the tool (byte) 65 which actually produces the release passage 20D uses the tool which produced the spiral groove 20D as it is. That is, when the circumferential surface of the roller 11 is cut and the helical groove 14 is provided, it transfers to the process of the release passage 20D, without replacing the tool.

Therefore, the trouble of tool change can be omitted and troublesome positioning is unnecessary by tool change.

In addition, although all the operating machines demonstrated above were demonstrated as the compressor provided with the helical blade type | mold compression mechanism, this is not limited and it is applicable also to the pump provided with the pump mechanism provided with the helical blade type pump mechanism.

As described above, according to the invention of claim 1, a release passage is provided on the suction side wall surface of the spiral groove so that when the pressure inside the operating chamber exceeds the predetermined pressure, the pressure is discharged into the operating chamber on the discharge side. The above pressure can be reliably released from the operating chamber, and the effect of high pressure drop with good efficiency is to prevent pressure loss and to improve reliability.

According to the invention of claim 2, the release passage is opposed to each operation chamber, and the passage area is gradually increased from the suction side to each operation chamber on the discharge side. According to the third invention, the release passage gradually increases the number of passages from the suction side to the operation chamber on the discharge side.

Therefore, according to the inventions of claims 2 and 3, the release passage area becomes larger than that of the operating chamber on the high pressure side, and therefore, a reliable release is also achieved for the overcompression and the liquid compression generated at the beginning of the high pressure process.

According to the invention of claim 4, since the depth dimension of the release passage is made shallower than the depth dimension of the spiral groove, the release passage reliably prevents leakage at the bottom of the spiral grooves between adjacent operating chambers in the normal compression process. do.

According to the invention of claim 5, the actuating mechanism is a twin type which is symmetrically installed at the center of the cylinder, and the release passage is provided between the two actuating systems because the release passage is provided in the same phase to reach the same pressure. There is no pressure unevenness at, and stable compression performance can be obtained.

Claims (5)

Helical blades having a cylinder, a roller eccentrically arranged in the cylinder, a spiral groove provided along the circumferential surface of the roller, and a spiral blade which freely fits into the spiral groove to partition the space with the cylinder into a plurality of operating chambers. In a fluid machine having an actuator And a release passage provided on the discharge side wall surface of the spiral groove and discharging the pressure into the operation chamber on the discharge side when the operating chamber exceeds a predetermined pressure. The method of claim 1, The release passage is provided along the radial direction in the spiral groove wall surface facing the respective operation chambers on the suction side and the discharge side, and at the same time, the passage area is gradually enlarged from the suction side to the operation chambers on the discharge side. . The method of claim 1, And the release passage is provided along the radial direction on the spiral groove wall surface opposite the respective operation chambers at the suction side to the discharge side, and at the same time, the number of passages gradually increases from the suction side to the operation chambers at the discharge side. The method according to any one of claims 1 to 3, And the release passage has a depth dimension smaller than the depth dimension of the spiral groove from the roller circumferential surface. The method of claim 1, The actuating mechanism is a twin-type two pairs of left and right symmetrically arranged at the center of the cylinder, and the release passage is provided in the same phase to reach the same pressure with each other in the actuating mechanism.

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