JPS62203997A - Centrifugal compressor - Google Patents

Abstract

PURPOSE:To reduce a leakage loss by providing a centrifugal compressing passage, a centripetal passage, and a circumferential diffuser on a rotor itself which is rotated. CONSTITUTION:A rotor 14 in a casing 11 compresses a gas sucked in from an inlet pipe 14a and sends it out to a discharge pipe 14b. A centrifugal compressing passage 33, a centripetal passage 34, and circumferential diffusers 35, 36 are provided in each stage. A gas-flow rotation preventing body 40 which is always positioned in a lower part even during the rotation of the rotor 14, is positioned on the lower part of the circumferential diffusers 35, 36. Thereby, a leakage loss and a mechanical loss between compressing blades and a fixed casing as in the case of the conventional device can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION TECHNICAL FIELD The present invention relates to a centrifugal compressor that compresses gas such as refrigerant gas in a refrigeration cycle, for example.

"Prior Art and its Problems" Compressors are broadly classified into centrifugal compressors, reciprocating compressors, and rotary compressors.Among them, the centrifugal compressors that are the subject of the present invention have conventionally been fixed compressors with a circumferential differential user. The basic structure is that a rotating compression vane is placed inside the casing, and the compressed gas is introduced into the casing from the rotation center shaft of the compression vane, and the gas is discharged through the casing's circumferential differential user. The efficiency of conventional centrifugal compressors with this basic structure is affected by high friction between air and equipment, and by machining accuracy such as gap accuracy between the casing and compression vanes. Therefore, there is a decisive problem that mechanical loss, leakage loss, disk friction loss, etc. are large.

``Object of the Invention'' The present invention is a centrifugal compressor with a completely new structure, which breaks the common sense of conventional centrifugal compressors in which compression vanes rotate within a fixed casing, and which reduces mechanical loss, leakage loss, It is an object of the present invention to provide a centrifugal compressor that can reduce losses such as disk friction loss to the maximum extent possible, and that can obtain a large compression ratio with a small capacity.

``Summary of the Invention'' The centrifugal compressor of the present invention includes a rotor that is rotationally driven around a shaft, and an inlet located at one end of the shaft. At least one centrifugal compression path extending: an annular circumferential differential user communicating with the outer end of the centrifugal compression path; and at least one centripetal path extending from the circumferential differential user toward the rotation center; communicating with the centripetal path. The rotor is characterized by being provided with an outflow port provided on the other end shaft portion of the rotor, and a gas flow rotation prevention body that prevents rotation of the gas flow in the circumferential differential user.

The above rotor can be held in a hollow casing together with a motor that drives the rotor, in which case the interface between the inlet and/or outlet and the casing is passed as a high-speed gas stream. Airtight vacuum enclosure with structure] IFi: By providing IFi, it is possible to lower the pressure inside the casing, reduce disc friction, and obtain a motor cooling effect. The high-speed gas flow injected from the rough pressure vacuum device can be smoothly decelerated and increased in pressure by guiding it to the centrifugal deceleration and pressure intensification device.

"Embodiments of the Invention" The present invention will be described below with reference to illustrated embodiments. Figure 1 shows
This figure shows the basic structure of the first embodiment of the centrifugal compressor of the present invention, and the fixing elements are a casing 11, a heat insulating material 12 covering the outside of the casing 11, and an electric motor 13 sealed inside the casing 1. It consists of a stator 13a. Casing 1
Unlike the casing of a conventional centrifugal compressor, the casing 1 is constructed as a simple hollow body that does not include a circumferential differential user. The shape of the small diameter portion 1 corresponding to the motor 13 is
1a and a large diameter portion 1]b corresponding to the rotor 14 portion, it has a stepped shape and is placed so that its axis is horizontal. The stator 13a of the motor 13 is located inside the small diameter portion 11a via the annular space 15! The fixed motor casing 13b is roughly fixed. +1c indicates a joint portion of the casing 11 made up of a plurality of members.

A rotor 14 is rotatably supported within the casing 11. The rotor 14 has inflow pipes (
The inflow pipe 14a extends into the small diameter portion 11a of the casing 11 and is supported by the casing 11 by bearings 16 and 17. The tube 14b is supported by the casing 11 by bearings 18 and 19. A rotor 13C of the motor 13 is fixed to the outer periphery of the inflow pipe 14a, so that when the motor 3 is energized, the rotor 14 rotates within the casing 11.

The casing 1 is formed with an inlet hole 20 communicating with the inflow pipe 14a and an outlet hole 21 communicating with the discharge pipe 14b. Also, the boundary part where the gas flow moves from the casing 11 to the inflow pipe 14a, and the boundary part where the gas flow moves from the discharge pipe 14b to the casing 11.
At the boundary between the two, air and vacuum devices 22 and 23 are provided to pass the boundary as a high-velocity gas stream.

This hermetic vacuum function 22, 23 has no mechanical friction, serves both as an airtight enclosure and a vacuum device, and generates a high-speed flow thermally or mechanically. In this example, since the temperature is set to supersonic speed, the expansion structure has a tapered and widened shape having an expansion path and a diaphragm. The gas passage cross-sectional area of this airtight vacuum function can be configured to automatically change according to the pressure and temperature of the gas used.

When the gas flow passes through this boundary at high speed, the dynamic pressure of the gas flow increases and the static pressure decreases, so the casing 11
The gas inside (inside the motor casing 13b) is connected to the inflow pipe +4a
Then, it is sucked into the discharge pipe 14b and the pressure is reduced or a vacuum is created. Therefore, disc friction between the rotor 14 and the motor 13 is reduced, a cooling effect of the motor 13 can be obtained, and leakage of the compressed gas can also be prevented.

Therefore, this hermetic vacuum function is effective for at least the rotor]4
It is necessary to provide it at the gas outlet (high pressure side).

The inlet hole 20 communicates with the annular space 15 via a radial passage 26% of the casing 11, and an inlet 27 for compressed gas opens into the annular space 15. Further, a bypass pipe 30 is opened at this inlet hole 20 portion. At the opening end of this bypass pipe 30, a nozzle constituting an executor with an inlet hole 200 Å is provided, and the compressed gas aft
At the same time, the flow velocity within the inlet-side hermetic vacuum drawing 22 can be increased, and the final enthalpy can be increased. On the other hand, this bypass pipe 30 is connected to the casing 1 which communicates with the discharge pipe 14b.
The air for preventing surging provided in the first gas flow path communicates with the vacuum device 32. This airtight vacuum device@32 maintains the airtight chamber function and prevents backflow of gas until the gas flow rate is reduced, but when the gas flow rate is reduced, excess fluid is automatically bypassed from here. It is circulated to the inlet side through the pipe 30 to prevent surging. At this time, the rotor 14
Since the air chamber vacuum device M23 on the outlet side continues its airtight vacuum function, the disc friction between the rotor 14 and the motor 13 is reduced, and the cooling effect of the motor 13 is maintained.

The rotor 14 performs the most important function of the centrifugal compressor of the present invention, compressing the gas taken in from the inflow pipe +4a and sending it out to the discharge pipe +4b. This example performs six stages of compression, each stage consisting of a centrifugal compression path 33 extending from the center of the rotor 14 to the outer periphery, and a centripetal compression path 3 extending from the outer periphery toward the inner periphery.
4. An annular circumferential differential user 35 concentric with the rotor 4, which connects the outer ends of the centrifugal compression path 33 and the centripetal path 34;
and the inner end of the adjacent centripetal path 34 and the centrifugal compression path 3
It consists of a circular differential user 36, which is also concentric with the rotor 14 and connected to the inner end of the rotor 14. The centrifugal compression path 33 on the most inlet side communicates with the inflow pipe 14a, and the centripetal path 34 on the exit side communicates with the discharge pipe 14b.

This compression path may have at least one stage, but in that case, the centripetal differential user 36 is unnecessary and the centripetal path 34 directly communicates with the discharge pipe 14b.

The centrifugal compression path 33 is formed by compression vanes 37 whose planar shape is shown in FIG. The centrifugal compression path 33 is
When the rotor 14 rotates, the action of the compression vanes 37 causes the gas to flow from the inside to the outside due to centrifugal force, and in the process a static head is obtained. In order to send this gas from the circumferential differential user 35 on the return flow side to the centrifugal differential user 36, there are a The gas flow rotation prevention body 4° is always located below. That is, this gas flow rotation prevention body 40 basically functions as a baffle plate that forces the gas sent out from the centrifugal compression path 33 to flow from the circumferential defuser 35 to the circumferential defuser 36. Therefore, it has a structure in which it does not rotate together with the rotor 14, that is, it is always located at a lower position in the figure even while the rotor 14 is rotating. A dynamic head is obtained in this process. This gas flow rotation prevention body 40 may be provided midway between the circumferential differential user 35 and the centripetal path 34.

Examples of the structure of this gas flow rotation prevention body 4o are shown in Figures 3 to 1.
This will be explained with reference to Figure 1. This gas flow rotation prevention body 40 is
It has a fan-like shape when viewed from above, and the rotor 14 is located at the center of the fan-like shape.
It has a central shaft 41 that fits into the central hole +4d of the. An angular hair ring is used for the central shaft 41. A columnar part 42 which fits into the circular differential user 36, a plate-shaped part 43 which fits into the centripetal path 34, and a columnar part 44 which fits into the circumferential differential user 35 are formed in the fan-shaped part in order from the center side,
These columnar portions 42) block the gas flow that attempts to rotate within the circular differential user 36, the centripetal path 34, and the circumferential differential user 35 at the plate portion 43, columnar portion 44, or below the rotor 14, and further rotate in the opposite direction. . These are made of a sufficiently heavy material so as not to rotate due to friction with the center hole 14d, the circular differential user 36, the centripetal path 34, and the circumferential differential user 35, and reduce the friction with these contact walls as much as possible. A bearing 45 and a gas flow path 46 are provided in order to allow the gas to contact or not to contact each other.

As shown in FIG. 11, the hair ring 45 has triple laces 45b, 45c and 45C on the outside of its support shaft 45a.
It is a hair ring with a double structure in which a ball 45e is inserted between each of the triple laces, and the outermost lace 45
Even if the rotation of the pole 45e increases, the rotation speed of the pole 45e does not increase accordingly, making it suitable for high-speed rotation.

Further, a recess 47 is formed in the end face of the columnar part 44 on the side that blocks the gas flow rotating due to the rotation of the rotor 4, and an inflow hole 46a at one end of the gas flow path 46 is opened in this recess 47. ing. This gas flow path 46 extends into the columnar part 44, and the ejection hole 46b at the other end is connected to the columnar part 44.
Both sides of 4, that is, the rotor] are opened on both sides of 4 in the axial direction. The recess 47 is for effectively guiding the gas to the gas flow path 46, and is used to guide gas into the gas flow path 46, such as pressurized gas ejected from the ejection hole 46b, or
The columnar part 44 is held in a floating state with respect to the rotor ] 4 (circumferential differential user 35), and the friction between the columnar part 44 and the circumferential differential user 35 is minimized. Therefore, in combination with setting the weight of the gas flow rotation preventer 40, the gas flow rotation preventer 4o can be held stationary even during particularly high speed rotation of the rotor 14.

In this example, can the bearing 45 and the gas flow path 46 be provided only on the side of the columnar part 44 where the circumferential speed of the rotor 4 is large?
Similarly, these can be provided on the columnar part 42 side as well.

It is also possible to make the gas flow rotation preventive body 40 from a magnetic material and to attract the gas flow rotation preventive body 4078 using a magnet placed outside the rotor 4 to make it stationary.

Upper 8c! The configuration of this centrifugal compressor is as follows: motor 13
When the rotor 14 is rotated by energizing, the centrifugal compression path 33, the circumferential differential user 35, and the centripetal path 34 in the rotor taco 4
The gas passing through the centrifugal differential user 36 is compressed by the action of the centrifugal compression vanes 37 and the gas flow rotation preventer 40. Thus, the inlet 27, the radial passage 26, the inlet hole 20. The gas supplied into the rotor taco 4 through the inflow pipe 14a can be taken out as compressed gas from the discharge pipe 14b and the outlet hole 31. That is, when the gas passing through the centrifugal compression path 33 reaches the circumferential differential user 35 due to centrifugal force, the gas flow rotation prevention body 40 prevents the gas from remaining within the circumferential differential user 35, the centripetal path 34, and the circular differential user 36. centrifugal compression path 3 from the next centrifugal differential user 36 to prevent it from rotating together with the rotor 14.
3. In this process, multi-stage compression is performed. In other words, the gas flow rotation preventer 40 functions to reduce the speed of gas that is attempting to rotate at high speed and convert the kinetic energy of the gas into pressure. This action provides a compression effect.

In this compression action, the axial thrust of each compression stage in the rotor 14 is canceled out, and no backflow occurs between the stages. Furthermore, by increasing the number of compression stages, high pressure can be extracted even at low speed rotation.

The rotor 14 is constructed as a laminated structure of a plurality of flat plate-shaped members, which are fastened together with fastening bolts 14e, or a heat insulating layer 48 made of a material with low thermal conductivity is interposed between each flat plate-shaped member. It is desirable to prevent heat backflow and improve adiabatic compression efficiency. The insulation material 12 covering the casing 11 also serves to promote insulation changes. By applying a reflective material to the inside of the casing 11 and the outside of the rotor 14, radiant heat can be reflected and adiabatic changes can be promoted. In order to improve the adiabatic compression efficiency, the compressor of the present invention, except for the motor 13, is constructed almost entirely of a material such as invar or stainless steel 4, which has a low thermal conductivity, and is equipped with an air and vacuum device 22, 23. 32 and bearing 16
-19 may be made of wear-resistant high speed steel, stellite, super hard alloy, etc. In particular, the bearings 16 to 19 may be oil-less bearings, and the gas flow rotation prevention body 40 may be made of lead, amber, stainless steel, etc., so that it can be made heavy with a small expansion coefficient.

Furthermore, in the compressor of the present invention, when the flow rate is throttled, as described above, gas is circulated from the surging prevention pneumatic thrust device 32 to the inlet side via the bypass pipe 30, thereby preventing surging. normal operation at all times. Note that the bypass pipe 30 is equipped with an airtight vacuum device 2 on the inlet side.
A check valve to prevent a gas flow from flowing from 2 to the anti-surging air guide device 32, a pressure sensor to control the drive, etc. can be provided. Further, the high-pressure gas passage may be provided with a safety valve or the like that opens when the pressure becomes excessive, if necessary.

In addition, as for the prevention of surging, as a simple method,
When the flow rate is throttled, the check valve 4 is removed from the outlet airtight vacuum chamber 23 between the casing 11 and the discharge pipe 14b of the rotor 14.
9 can be opened to perform a circulation operation where the water flows to the inlet side. At this time, it is desirable to provide centrifugal compression vanes 31 for backflow prevention on the outside of the rotor 14 so that high-temperature gas does not flow into the motor 13.

12 to 16 show a second embodiment of the present invention. This embodiment differs from the first embodiment in the following points:
As a means for preventing the gas that has reached the circumferential differential user 35 from rotating together with the rotor 14, a centripetal non-acting vane 50 is provided in the centripetal path 34, and the circumferential differential user 3
5 and the center differential user 36, a gas flow rotation preventing body 51 is provided respectively. The other parts are the same as those in the first embodiment, and the same parts are given the same reference numerals. The gas flow rotation prevention body 51 blocks the flow of gas flowing in the rotational direction of the rotor 14, causing it to roughly rotate in the opposite direction, and generates a flow from the centrifugal compression path 33 to the centripetal path 34. The centripetal non-acting vanes 50 always direct the absolute velocity vector of the flowing gas flow toward the center, and guide the gas flow from the circumferential tiff user 35 to the central diff user 36 without changing the head.

FIG. 13 shows an example of the shape of the centripetal non-acting vane 50.

The centripetal vane 50 guides the compressed gas to the circular differential user without changing its head, but is it possible to provide a nozzle at its inlet and adiabatically expand it within the centripetal vane 50 to obtain the flow velocity? good. The centripetal passive vanes 50 act as turbine vanes or compression vanes when the flow rate of the gas stream changes and its ratio to the rotational speed of the rotor 14 changes.

The gas flow rotation prevention body 51 may have any structure as long as it has the above-mentioned effect, but an example of its structure will be explained with reference to FIGS. 14 and 15.

The gas flow rotation prevention bodies 51 may be arranged only in the circumferential differential user 35, but here, a large number of gas flow rotation prevention bodies 51 are disposed throughout the circumferential direction of both the circumferential differential user 35 and the central differential user 36. The ball is made up of a group of 52 elliptical balls 52, of which 173 of the elliptical balls 52 are heavy solid bodies, and the rest are light hollow bodies. When a difference in weight is provided in this way, the heavy elliptical ball 52 is located at the lower part of the annular circumferential differential user 35 and the circular center differential user 36 due to gravity, so that the entire group of elliptical poles 52 is moved to the circumferential differential user 35.
And it can be in a stationary state within the center-centered differential user 36. In this example as well, it is possible to keep the elliptical ball 52 stationary using magnetic force, as described in the first embodiment.

Each elliptical ball 52 is formed in a shape that minimizes the gap with the circumferential differential user 35 (circular differential user 36), and has annular grooves 52a, 5 in the upper, lower, and center portions thereof.
2b and 52c, and are arranged in two rows in a staggered manner in the unfolded state. An annular guide rail 53a fixed to the rotor 14 side is fitted into the upper and lower annular grooves 52a and 52b, and an annular guide rail 53a fixed to the rotor 14 side is fitted into the central annular groove 52c. The provided protrusion 54 is fitted. Furthermore, a free annular guide rail 53b is fitted between the two rows of elliptical balls 52, which ensures free rotation of the elliptical balls 52 and prevents them from falling. Also, when the rotor 14 accelerates, the inertia of the annular guide rail 53b is reduced by the elliptical ball 5.
2 to a stationary state. According to this structure, since only rolling friction acts on each oval ball 52,
Since there is little friction, these can be kept stationary and the above operations can be carried out well. This oval ball 5
2 and the guide rails 53a, 53b are preferably made of high speed steel, stellite, super hard alloy, etc.

16 and 17 show other examples of the gas flow rotation prevention body 51. FIG. This gas flow rotation prevention body 51 is connected to a guide rail 57 in the circumferential differential user 35 (circular differential user 36).
．． Two rows of base balls 55 are arranged between the two rows of base balls 55, and sub balls 56 are arranged so as to straddle the center of the two rows of base balls 55. The base sphere 55 and the sub spheres 56, like the elliptical balls 52, are arranged over the entire circumferential direction of the circumferential differential user 35 (the central differential user 36), and are, for example, 1/1/2 of the total number. 3 is a heavy solid body, and the rest are light weight hollow bodies.The heavy base sphere 55 and sub sphere 56 are positioned below the circumferential differential user 35 (center differential user 36), and the whole is stationary. It can be a state.

These base spheres 55 and sub spheres 56 are in contact with adjacent base spheres 55 and sub spheres 56 at one point, respectively,
Further, since it comes into contact with the linear rail 55a and rotates due to rolling friction as the rotor 14 rotates, it is possible to keep it stationary with little friction. The base ball 55 and the sub-ball 56 are made of lead, amber, stainless steel, titanium,
Alternatively, it is preferable to use a titanium alloy or the like.

Note that the gaps between the elliptical balls 52 and between the base sphere 55 and the sub-sphere 56 can be arranged at appropriate intervals to provide a space between the centrifugal compression path 33 and the centripetal path 34, or from the centripetal path 34 to the centrifugal compression path 34. A flow of gas to the compression path 33 can be generated.

The heavy elliptical ball 52, base ball 55, and sub-ball 56 are located below the circumferential differential user 35 (center differential user 36) when the operation of the rotor 14 is stable.
In order to stabilize the drive from the beginning, it is possible, for example, to drive the morph 13 by using an old-fashioned soft starter with automatic frequency change so that the rotational speed of the rotor 14 gradually increases.

18 to 20 show a third embodiment of the present invention. This embodiment is similar to the compression vane 3 in the second embodiment.
a centrifugal compression path 33 with 7 and a centrifugal passive vane 5
The centripetal compression path 34 with 0%
, and a centripetal non-acting vibro 2, and a circumferential differential user 35 and a circular differential user 36 communicating therewith are also configured from a vibrator body. The other parts are the same as the second embodiment. A heat insulating layer 48 is interposed between the centrifugal compression vibro] and the centripetal action vibro 2, and the space between the circumferential differential users 36 is reinforced by a reinforcing plate 63.

19 and 20 show examples of the planar shapes of the centrifugal compression vibro 1 and the centripetal non-acting vibro 2. The shape is almost the same as that of the non-acting blade 50. According to such a tube structure, the structure of the rotor 14 can be simplified and the weight can be reduced, so that the starting torque of the motor 13 is small and acceleration becomes easier.

Roughly speaking, in this embodiment, a centrifugal deceleration and pressure increase device 70 is attached to the outlet hole 31 of the casing 11. This centrifugal deceleration and pressure increase device 70 can of course be applied to the devices of the first and second embodiments. This device is shown in Figures 18 and 21.
As shown in FIGS. 23 to 23, an inflow pipe 72 is opened at one end of an annular cylinder 7 having a constant height and closed at both ends in a substantially tangential direction of the annular cylinder 71, At the other end, an outflow pipe 73 is opened, which is also substantially tangential to the annular space 71 and is oriented in the rotational direction of the gas flow in the annular cylinder 71 . The outflow pipe 73 has a larger diameter than the inflow pipe 72, and the annular cylinder 7] has a larger diameter than the outflow pipe 73. Further, the inflow pipe 72 is connected to the outlet hole 21 of the casing 11, and the outflow pipe 73 is provided with a check valve 74. It is preferable that the annular cylinder 71 has a double right circular truncated cone shape whose radius gradually increases from the end on the inflow pipe 72 side to the end on the outflow pipe 73 side as shown in the illustrated example. It may be a closed cylindrical tube or a hollow truncated cone. It is preferable to cover the outside with a heat insulating material to increase the heat insulation properties.

The kinetic energy of the gas flow flowing into the I5-shaped cylinder 71 at high speed (for example, supersonic speed) becomes the rotational force of the gas flow inside the annular cylinder 71, and the inertia of this rotational gas flow It acts to facilitate the inflow of the gas flow and prevents the generation of shock waves. While the gas flow repeats rotation within the annular cylinder 71 between the inflow pipe 72 and the outflow pipe 73, the gas flow is decelerated (below the speed of sound) by the frictional force with the circumferential wall of the annular cylinder 71 due to centrifugal force. ),
It exits through the outflow pipe 73 with increased pressure. That is, as the high-speed gas flow is decelerated within the annular cylinder 71, the dynamic pressure decreases, the static pressure increases, and the gas flows out as a high-pressure low-velocity flow. This is an adiabatic change and an isentropic change, in which the gas that flows into the annular gap 71 with low enthalpy flows out with high enthalpy and recovers to the enthalpy before entering the air chamber vacuum arrangement 23.

At this time, if the radius of the annular gap 71 is set to be larger on the outlet side than on the inlet side as shown in the illustrated example, the centrifugal force will act more strongly on the outlet side, and the radius will be larger on the inlet side. Lowering the pressure makes it easier for the inflow gas to flow in, increasing the pressure increase effect, and preventing recompression of the high-speed gas flow, thereby improving the vacuum function. In this example, since the annular cylinder 71 has a double structure, backflow of gas can be roughly prevented. The check valve 74 prevents backflow due to sudden changes in flow rate such as when the operation is stopped.In other words, this centrifugal deceleration and pressure increase device is effective in recovering the enthalpy of the high-speed gas flow injected from the air chamber vacuum device. This is to prevent shock waves and recompression.

Although the centrifugal compressor of the present invention can be applied to any field, FIG. 24 shows an example in which it is used as a compressor 101 of an underground heat exchange device 100. This underground heat exchange device 100 consists of a heat exchange unit 103 consisting of a vibrator in which refrigerant gas (liquefied gas) is sealed inside a hole +02 that is polled underground.
% and circulates the refrigerant within the heat exchange unit 103 and the above-ground circulation pipe 104. A liquefied refrigerant reservoir 105 is provided at the lower end of the heat exchange unit 103.

The underground heat exchange system 100 is used to compress the refrigerant that has changed into a gas phase in the heat exchange unit 103 and change it into a liquid phase. In this underground heat exchange device 100, heat exchange is performed between the underground heat exchange device 106 and the above ground heat exchange device 106, and hot water is stored in a hot water storage tank 107, for example. 108 is an expansion valve.

Since the centrifugal compressor of the present invention does not cause a large amount of lubricating oil to accumulate in the circulation path and block the pipeline, it can be used in such underground heat exchange equipment without requiring excessive power. , the refrigerant can be compressed and circulated smoothly.

"Nine Achievements of the Invention" As described above, the centrifugal compressor of the present invention has a centrifugal compression path, a centripetal path, and a circumferential differential user in the rotor itself, which is rotatably supported within the casing and rotationally driven by the motor. Moreover, since it is located at the compressed gas outlet or at the shaft of the rotor, the problem of gas leakage is fundamentally solved. In other words, there are leakage losses, mechanical losses, and disc friction between the compression vanes and the fixed casing as in conventional centrifugal compressors.
Therefore, it is possible to obtain an efficient centrifugal compressor with almost no loss. In addition, since it is small, light and heavy, and has a small capacity, it can be used as a centrifugal compressor with a high compression ratio, so it can be expected to have a wide range of applications. It is especially dangerous as a compressor for air conditioning, hot water supply, and refrigeration cycles.

[Brief Description of the Drawings] Fig. 1 is a longitudinal sectional view showing a first embodiment of the centrifugal compressor of the present invention, Fig. 2 is a sectional view taken along line II-II in Fig. 1,
3, 4, and 5 are a plan view, a side view, and a rear view of the gas flow rotation prevention body inserted into the rotor's circular differential user, centripetal path, and circumferential differential user, and FIG. 6 is a Figure 5 is a partially enlarged view, Figure 7 is a right side view of Figure 6, Figures 8, 9, and 10 are the ■, ■ lines, and IX-
11 is a sectional view taken along line IX and X-X, FIG. 11 is a sectional view taken along line K-XI in FIG. 9, and FIG. 12 is a longitudinal section showing a second embodiment of the centrifugal compressor of the present invention. Figure 13 is a cross-sectional view taken along the line - 16 is a partially enlarged view corresponding to FIG. 14 showing another example of the gas flow rotation prevention body, and FIG.
6 is a sectional view taken along the line X■-X■, FIG. 18 is a longitudinal sectional view showing a third embodiment of the centrifugal compressor of the present invention, FIG. 19,
Figure 20 is the same as Figure 18 (7) XIX-XIX, x
21 is a front view of the centrifugal deceleration and pressure increase device, and 22 and 23 are XX in FIG.
FIG. 24 is a cross-sectional view taken along line II-X 11...Casing, 12...Insulating material, 13...
Motor, ]4... Rotor, +4a... Suction pipe, 14
b...Discharge pipe, 15...Annular space, 16-19...
・Bearing, 20...Inlet hole, 2]...Outlet hole, 22・
... Inlet side air-tight vacuum system, 23... Outlet side air-tight vacuum system =, 30... Bypass pipe, 32... Air-tight vacuum drawing for surging prevention, 33... Centrifugal compression path, 34.・・・
Centripetal path, 35... Circumferential differential user, 36... Circular differential user, 37... Centrifugal compression vane, 4o, 51...
- Gas flow rotation prevention body, 48... heat insulation layer, 50... centripetal non-acting vane, 61... centrifugal compression vibe, 62...
Centripetal non-acting pipe, 70...Centrifugal deceleration and pressure increase device.

Claims (24)

[Claims] (1) An inflow port located at one end of the shaft of the rotor that is driven to rotate; at least one centrifugal compression path that communicates with the inflow port and extends outward from the rotation center; an annular circumferential diffuser communicating with the outer end; at least one centripetal path extending from the circumferential diffuser toward the rotation center; an outlet provided on the other end shaft of the rotor communicating with the centripetal path; A centrifugal compressor comprising: a gas flow rotation prevention member that prevents rotation of the gas flow in the circumferential diffuser; (2) In claim 1, a centrifugal compression path;
A centrifugal compressor in which a circumferential diffuser and a centripetal path are provided in multiple stages, and the inner ends of the adjacent centripetal path and centrifugal compression path communicate with an annular circular center diffuser. (3) In claim 1 or 2, the gas flow rotation prevention body is a part of the circumferential diffuser and the centripetal path, or a part of the circumferential diffuser, the centripetal path, and the circular diffuser. , and while the rotor is rotating,
A centrifugal compressor that prevents rotation of the gas flow in a stationary state. (4) In claim 1 or 2, the gas flow rotation prevention body is located within a circumferential diffuser, or within a circumferential diffuser and a circular center diffuser, and is located within each diffuser. A centrifugal compressor in which the centripetal path is provided with centripetal passive vanes that direct the gas flow to a circular diffuser without changing its head. (5) A centrifugal compressor according to claim 4, wherein the centripetal non-acting vane has a nozzle formed on its inlet side for obtaining a gas flow velocity. (6) In any one of claims 1 to 5, between the adjacent centrifugal compression path and the centripetal path,
A centrifugal compressor with a heat insulating layer. (7) A centrifugal compressor according to any one of claims 1 to 6, wherein both the centrifugal compression path and the centripetal path are constructed from pipe bodies. (8) The centrifugal compressor according to any one of claims 1 to 7, wherein the circumferential diffuser and/or the central diffuser are both made of pipe bodies. (9) An inlet and an outlet are provided at both ends of the shaft of the rotor that is driven to rotate, and the rotor is rotatably supported in a hollow casing, and the rotor is connected to the inlet and the rotation center is a centrifugal compression path extending outward from the side; an annular circumferential diffuser communicating with the outer end of the centrifugal compression path; a centripetal path extending from the circumferential diffuser toward the center of rotation; and a centripetal path communicating with the centripetal path. an outflow port; and a gas flow rotation prevention body that prevents rotation of the gas flow in the circumferential diffuser; further, the gas flow passes through the boundary between the outflow port or (and) the inflow port and the casing as a high-speed gas flow. A centrifugal compressor characterized by being equipped with an airtight vacuum device. (10) In claim 9, the centrifugal compression path, the circumferential diffuser, and the centripetal path are provided in multiple stages,
In the centrifugal compressor, the inner ends of the adjacent centripetal path and centrifugal compression path communicate with an annular circular diffuser. (11) In claim 9 or 10, the gas flow rotation prevention body is a part of the circumferential diffuser and the centripetal path, or a part of the circumferential diffuser, the centripetal path, and the circular diffuser. A centrifugal compressor that is located in a stationary state and prevents the gas flow from rotating while the rotor is rotating. (12) In claim 9 or 10, the gas flow rotation prevention body is located within the circumferential diffuser, or within the circumferential diffuser and the circular diffuser, and A centrifugal compressor that prevents rotation of the gas flow and in which the centripetal path is provided with centripetal passive vanes that direct the gas flow to a circular diffuser without changing its head. (13) A centrifugal compressor according to claim 12, wherein the centripetal non-acting vane has a nozzle formed on its inlet side for obtaining a gas flow rate. (14) The centrifugal compressor according to any one of claims 9 to 13, wherein a heat insulating layer is interposed between the adjacent centrifugal compression path and the centripetal path. (15) A centrifugal compressor according to any one of claims 9 to 14, wherein a motor for driving a rotor is sealed in a casing. (16) In any one of claims 9 to 15, a slit portion that communicates with the inlet of the rotor via a bypass pipe in the gas flow path of the casing that communicates with the outlet of the rotor. A centrifugal compressor equipped with an airtight vacuum device to prevent surging, which allows gas to pass through as a high-speed gas flow. (17) In any one of claims 9 to 16, the outlet hole of the casing communicating with the outlet of the rotor has a cylindrical tube with both ends closed; , an inflow pipe tangential to the cylindrical tube communicating with an outlet hole of the casing; and an inlet pipe opening at the other end of the cylindrical tube in the direction of rotation of the gas flow in the cylindrical tube; A centrifugal compressor is provided with a centrifugal reducer and pressure booster having a tangential outflow pipe of a cylindrical tube. (18) The centrifugal compressor according to claim 17, wherein the cylindrical tube with both ends closed has a radius that gradually increases from the inlet tube to the outlet tube. (19) The centrifugal compressor according to claim 17 or 18, wherein the cylindrical tube with both ends closed is doubled to form an annular tube with both ends closed. (20) The centrifugal compressor according to any one of claims 9 to 19, wherein both the centrifugal compression path and the centripetal path are constructed from pipe bodies. (21) The centrifugal compressor according to any one of claims 9 to 20, wherein the circumferential diffuser and/or the central diffuser are both made of pipe bodies. (22) The centrifugal compressor according to any one of claims 9 to 21, wherein the outside of the casing is covered with a heat insulating material. (23) The centrifugal compressor according to any one of claims 9 to 22, wherein a reflective material that reflects radiant heat is provided on the inside of the casing or (and) the outside of the rotor. (24) The centrifugal compressor according to any one of claims 17 to 23, wherein the outside of the centrifugal speed reduction and pressure increase device is covered with a heat insulating material.