JPH0281997A - Fluid pressure generating device and operating method thereof - Google Patents

Abstract

PURPOSE:To prevent generation of noise and vibration by providing a rotary shaft forming in its circumferential surface a grooved part consisting of many grooves tilting with respect to a direction of the axial center, stationary cylindrical surface part arranged being opposed to the peripheral part of this grooved part with a narrow space, suction port of fluid and its delivery port. CONSTITUTION:A stationary circumferential surface part 10 is formed being opposed to a grooved part 4 on a rotary shaft forming many grooves 3, in the inside of a main unit 1. Now in a condition that a valve 7 is closed, when the rotary shaft 2 is rotated in the counterclockwise direction as viewed from the right side, a pressure of fluid is generated in groove space 11, supporting the rotary shaft 2 in its own weight by a dynamic pressure effect of fluid while allowing the fluid, while its pressure is gradually increased, to flow from the side of a reservoir part 9 toward the side of a delivery port 6 into the groove space 11 reaching a steady condition. Next the fluid, when the valve 7 is opened, is accumulated once in the reservoir part 9 from a suction port 5 via a communication hole 8, and next the fluid passes through the groove space 11 generating a flow of the fluid toward the delivery port 6.

Description

DETAILED DESCRIPTION OF THE INVENTION [Aspects of the Invention] (Field of Industrial Application) The present invention relates to a fluid pressure generating device based on fluid lubrication theory and an IJ method for operating the same.

(Prior Art) Conventional fluid pressure generating devices, such as centrifugal compression type devices, cause a loss phenomenon when operated at a compression ratio greater than the design point compression ratio, making operation impossible. In other words, cold! II] Even if the condensing pressure is maintained at the design value, a surging phenomenon occurs when the condensing pressure becomes higher than the nominal pressure. When the pressure increases, the discharge pressure of tI6m increases accordingly, eventually causing damage to the compressor or overload of the electric motor. If a positive displacement compressor is operated with the valve of the discharge side piping system in the fully open state by mistake, the discharge pressure will become abnormally high, which may cause a serious accident.

This phenomenon is exactly the same in pumps that handle liquids.

In addition, all centrifugal and positive displacement compressors and pumps generate noise and vibration, which cannot be completely eliminated.

(Problem to be solved by the invention) The prior art has various problems as described above.

The present invention aims to eliminate the above-mentioned problems by using a fluid pressure generating device based on fluid lubrication theory.

[Structure of the invention]

(Means for Solving the Problems) The fluid pressure generating device of the present invention has the following configurations A to E in order to achieve the above object.

(△) A rotating shaft in which a groove formed by a large number of vortices inclined with respect to the axial direction is formed on the circumferential surface, a stationary cylindrical surface part disposed opposite to the outer periphery of the groove with a narrow gap, and a fluid inlet. , has a discharge port, supports the weight of the rotary shaft by utilizing the dynamic pressure effect of the fluid induced in the full space between the groove and the stationary cylindrical surface by the rotation of the rotary shaft, and also supports the groove space. The fluid is caused to flow from one end to the other end, and the fluid is sucked through the suction port, pressurized, and discharged from the discharge port.

In the above device, instead of the groove on the circumferential surface of the rotating shaft, the groove may be formed on the circumferential surface of the opposing stationary cylindrical surface so as to be inclined with respect to the axial direction of the cylindrical surface. In the device, a stationary shaft can be provided in place of the rotating shaft, and a rotating cylindrical surface can be provided in place of the stationary cylindrical surface.

(B) A rotating shaft having a circumferential surface formed with a groove portion consisting of a large number of grooves inclined with respect to the axial direction, a stationary cylindrical surface portion disposed facing the outer periphery of the groove portion with a narrow gap, and a fluid inlet. , having a discharge port, a collar portion provided on the rotating shaft, and a groove portion consisting of a large number of spiral grooves or linear bays inclined with respect to the radial direction formed on the surface of the collar portion adjacent to the groove portion. , a stationary plane part is arranged opposite to the surface of the groove part of the collar part with a narrow gap therebetween, and the rotation shaft is rotated by the rotation of the rotary shaft; 2! Using the dynamic pressure effect of the fluid induced in the groove space between the groove and the stationary cylindrical surface part and the groove space between the groove of the collar part and the stationary plane part, the dead weight of the rotating shaft is reduced by the Supported by a stationary cylindrical part,
Further, the thrust in the axial direction is supported by the stationary plane part, and the fluid is made to flow through the groove space of the rotating shaft part and the groove space of the collar part, and the fluid is sucked from the suction port and pressurized, and then the fluid is forced to flow from the discharge port. To exhale.

In the above device, the groove of the rotating shaft is replaced with the circumferential surface of the rotating shaft, and a groove is formed on the inner circumferential surface of the opposing stationary cylindrical surface so as to be inclined τ1 with respect to the axial direction of the cylindrical portion, and the collar is Instead of the surface of the collar part, the groove part of the part can also be formed on the surface of the opposing stationary plane part, and in these devices, a stationary shaft and collar part are provided instead of the rotating shaft and collar part, Providing a rotating cylindrical surface section and a rotating plane section in place of the stationary cylindrical surface section and stationary plane section t)C.

(C) The multilayer cylinder part of the rotating cylinder body and the multilayer cylinder part of the stationary cylinder body are concentrically combined and arranged opposite to each other with a narrow gap in the intersection H to form a cylindrical narrow space of two or more layers, facing each other. On either the outer surface or the inner surface of the cylindrical portion, a groove portion consisting of a large number of grooves inclined with respect to the axial direction of the cylindrical portion is formed, and a fluid inlet and discharge port are formed. h the outlet, and the rotation of the rotating cylindrical body fills the space between the groove and the cylindrical surface of the opposing cylindrical part; using the dynamic pressure effect of the induced fluid, the dead weight of the rotating cylindrical body is reduced. While supporting the fluid, the fluid is allowed to flow through the plurality of groove spaces, and the fluid is sucked through the suction port, pressurized, and discharged from the discharge port.

(D) Two or more grooves formed in the circumferential surface of the rotary shaft on both sides of a sealed electric motor rotor with a large number of grooves inclined with respect to the axial direction are arranged in series at appropriate intervals. On the other hand, two or more stationary cylindrical surfaces are arranged in series at an appropriate interval so as to face the groove with a narrow gap between them and the outer periphery of the groove, and the fluid outlet of the groove is connected to the intercooler. The fluid outlet of the intermediate cooling unit is connected to the fluid inlet of the next groove, and the fluid in both grooves is connected to the circumferential surface of the rotating shaft between the grooves. To form a bypass prevention groove section consisting of a large number of grooves having an inclination that induces a flow in a direction opposite to that of the flow direction.

(E) On the rotating shaft on both sides of the motor rotor of the sealing ring 1, a groove portion having a large number of grooves inclined with respect to the axial direction is arranged on the circumferential surface, followed by a collar portion.
A groove portion consisting of a large number of helical grooves or linear grooves inclined with respect to the radial direction is formed on both surfaces of the collar portion, and an outer peripheral portion of the groove portion provided on the -1 axis of rotation is formed. A stationary cylindrical surface part is arranged with a narrow gap from the surface, and a stationary flat part facing the grooves on both sides of the collar part with a narrow gap, respectively, and the rotating shaft and collar part pair and stationary part are arranged as described above. Two or more sets of a cylindrical surface part and a stationary plane part are arranged in series on the rotating shaft, and the fluid outlet of the groove part of the collar part is connected to the fluid inlet of the intermediate cooling FJl vessel, and the fluid of the intermediate cooling FII vessel is connected to the fluid outlet of the groove of the collar part. The outlet is connected to the fluid population of the groove of the next collar part, and the outer peripheral surface of each collar part is further provided with an inclination that induces a flow in a direction opposite to the flow direction of the fluid in each groove of the rotating shaft. To form a bypass prevention groove portion consisting of a large number of grooves.

In the multi-stage fluid pressure generating device of (D) or (E), the groove for bypass prevention IL is opposed to the outer peripheral surface of the rotating shaft or the collar instead of the outer peripheral surface of the rotating shaft or the collar. It can also be formed on a stationary cylindrical surface.

Furthermore, the method of operating a fluid pressure generating device of the present invention has the following configuration in order to achieve the above object.

In the fluid pressure generating devices A to E described above, constant speed operation is performed using a sacrificial fluid, and the discharge port of the fluid is connected to a condenser, and the cooling medium flow 8 or condensation of the condenser is connected to the condenser. The condensing temperature of the fluid is adjusted by increasing or decreasing the effective heat transfer area of the vessel, and the pressure and flow rate of the fluid discharged from the discharge port are controlled by increasing or decreasing the condensing temperature.

(Function) When the rotating shaft is rotated by a rotating shaft in which a groove formed of a large number of inclined grooves is formed on a circumferential surface, and a stationary cylindrical surface portion facing the outer circumference of the groove with a narrow gap, A dynamic pressure effect is induced in the groove space between the groove part and the stationary cylindrical surface part, and this effect is used to support the weight of the rotating shaft and to cause fluid to flow from -d5 to the other end of the groove space. It can be discharged under pressure.

A rotary shaft having a plurality of inclined grooves formed on its circumferential surface, a stationary cylindrical surface portion facing the outer circumferential portion of the groove portion with a narrow gap, and a collar portion provided on the rotary shaft. A groove consisting of an inclined linear groove is formed on the adjacent surface, and a narrow gap is formed between the surface of the groove of the collar part and the stationary plane part is placed between the opposite sides 6, so that the rotating shaft can be rotated. When rotated, a dynamic pressure effect is induced in the groove space between the groove of the rotating shaft and the stationary cylindrical surface part and in the 1 m full space between the groove of the collar part and the stationary plane part, and the dynamic pressure effect is utilized. The dead weight of the rotating shaft can be supported by the stationary cylindrical part, and the thrust in the axial direction can be supported by the stationary flat part, and through the 6iJ groove space of the rotating shaft part and the groove space of the collar part. 9□ The multi-layer cylinder part of the rotating cylinder body and the multi-layer cylinder part of the stationary cylinder body are combined so that they are arranged concentrically and alternately facing each other with narrow gaps between them. A narrow cylindrical space with two or more layers is formed.
Furthermore, by forming a groove portion consisting of a large number of inclined grooves on the surface of one of the opposing cylindrical portions,
When the rotating cylinder rotates, a dynamic pressure effect is induced in the groove space between the groove and the cylindrical surface of the opposing cylinder, and the dynamic pressure effect is used to support the weight of the rotating cylinder. , the fluid can be made to flow through the plurality of groove spaces, and can be pressurized and discharged.

Two or more grooves each having a large number of inclined grooves formed in the circumferential surface of the rotating shaft on both sides of a sealed electric motor rotor are arranged in series at an appropriate interval, and a narrow gap is formed between the outer circumference of the groove and the groove. Two or more stationary cylindrical surface portions are arranged in series at appropriate intervals so as to face the groove portions, and the groove portions shown in @ are connected via an intercooler, and the groove portions and the groove portions are The fluid can be sufficiently intermediately cooled by forming a bypass-preventing groove section consisting of a large number of grooves inclined to the rotation axis between the two.

A groove section in which a large number of inclined grooves are formed on the circumferential surface of the rotating shaft on both sides of a closed type electric motor rotor, and a collar section is arranged next to this, and a large number of inclined vortices are formed on both sides of the collar section. A stationary cylindrical surface part is formed with a groove part formed on the rotating shaft with a narrow gap from the outer peripheral surface of the groove part, and a stationary flat part faces the groove parts on both sides of the collar part with a narrow gap therebetween. are arranged in series on the rotation shaft, and two or more pairs of the rotating shaft and the collar part and the stationary cylindrical surface part and the stationary plane part are arranged in series on the rotation shaft, and furthermore, the phase between the both sides of the collar part is The grooves are connected via an intercooler, and a bypass prevention groove consisting of a large number of inclined grooves is formed on the outer circumferential surface of each collar, so that the fluid can be sufficiently intercooled. can.

The fluid discharge port of a fluid pressure generator using a rhombic fluid is connected to a condenser, and the condensed humidity of the fluid can be adjusted by increasing or decreasing the cooling medium flow E of the condenser or the effective heat transfer area of the condenser. The pressure and flow of the fluid discharged from the discharge port can be controlled by adjusting the condensation humidity and increasing or decreasing the condensed humidity.

(Example) Before entering into the description of the example, the theory on which the present invention is based will be explained.

FIG. 16 is a model of a normal hydrodynamic bearing system consisting of a rotating shaft 111 and a bearing 112. A negative phase of the axial load W is applied to the rotating shaft 111, and its axial center is eccentric by a distance ε with respect to the center of the bearing, and due to this eccentric action, a bearing reaction force F based on the fluid lubrication theory is generated within the bearing, and the axial load W is Balance with. Normally, the shaft surface within a bearing is a smooth cylindrical surface, but in some special shaft/bearing systems, the shaft surface may not be smooth as shown in FIG.

That is, in FIG. 17, β1.
A large number of shallow grooves 113 having an inclination angle of β2 are formed.

Usually β1+β2=180', and the fluid force is often generated symmetrically with respect to the axis-perpendicular cross section of the center of the bearing. Such a bearing is called a herringbone journal bearing (hereinafter abbreviated as rHJBJ).

Next, I will explain HJB's lubrication theory to Buko. When the rotating shaft 111 is rotated in the direction of the arrow, the inner peripheral surface 11 of the bearing 112
Fluid pressure is generated in a narrow space (referred to as a "groove space") 115 between the rotary shaft 4 and the outer surface portion of the rotating shaft in which a large number of shallow grooves 113 are formed. The state in which this fluid pressure is generated will be explained with reference to FIG.

According to FIG. 18, the pressures generated in the groove spaces of the grooved portion B and the smooth cylindrical portion A of the rotary shaft 111 are as shown in (■) in the figure. Note that (2) and 0 are drawn so as to correspond vertically.

The pressure actually generated in the groove space is the total pressure pt, and HJ
It forms a mountain shape that is highest at the center of B. According to fluid lubrication theory, when Pa is the first perturbation pressure and Pε is the second perturbation pressure, Pt = Po + pε. Pε is the pressure mainly caused by the eccentricity ε of the rotating shaft and the value of PO, and Po is determined by the shape and rotational speed of 1''JB, the viscosity of the fluid, and the ambient pressure, regardless of ε.

The presence of this Po is a characteristic of 1-IJ L3, which does not exist in ordinary cylindrical smooth surface bearings. Theoretical basis 1 of the present invention also lies in the existence of this Pa. Although P0 has a value greater than the ambient pressure, Pa becomes equal to the ambient pressure, and the load capacity of the b bearing exists. When Pa decreases for the same load, the eccentric distance ε increases and the load can be supported. This is because although the load capacity is determined only by the value of Pa, Pa is a function of both Pa and ε.

The present invention is based on this theory and aims to utilize Pa effectively. That is, Pa is intended to be used as the pressure of the fluid flowing between the sinus cavities.

Next, in order to facilitate the beating of the embodiment of the present invention, a hydrodynamic thrust bearing will be briefly explained.

FIG. 19 shows a typical hydrodynamic thrust bearing.

7. The rotating shaft 121 and the collar part 122 have a body structure,
A bearing portion 123 is arranged as a surface facing the collar portion 122,
A large number of helical grooves 124 are formed on the surface. One end of the helical groove 124 is closed within the bearing surface, and only the other end is open to the inner periphery. When the rotating shaft is rotated counterclockwise when viewed from above, fluid is sucked from the inner diameter portion and released from the outer periphery of the outer diameter portion as shown by the arrow. In the narrow space 125 formed by the facing surfaces of the collar part 122 and the bearing part 123, pressure is generated in a distributed shape as shown in FIG.
direction distance). This generated pressure generates a thrust load capacity on the bearing surface.

Similar to FIG. 19, FIG. 20 shows a normal thrust bearing, but differs from FIG. 19 in that only the other end of the helical groove 124 is open to the outer periphery. When the rotating shaft is rotated in a counterclockwise direction when viewed from the top, fluid is sucked from the outer diameter part as shown by the arrow and flows to the inner diameter part, and the fluid flows into the space 125 as shown in FIG. Generates pressure with a similar distribution shape, and generates the ability to apply force.

The bearings shown in Figs. 19 and 20 are called spiral groove thrust bearings (hereinafter referred to as r S G T
(abbreviated as B j).

The aforementioned HJB and 5GTB are based on exactly the same fluid lubrication theory. The present invention attempts to flow and pressurize fluid in a thrust bearing (even in one structure) using the fluid theory described above.The principle of the present invention will be explained with reference to FIG. 21.

The rotating shaft 121 integrally formed with the collar portion 122 is the bearing 1
29, with a narrow space (groove space) 125 between them.
This space communicates with the outside via a discharge pipe 121. A valve 128 is provided in the discharge pipe 127.

In addition, the inner surface of the bearing 129 facing the lower surface of the collar portion 122 has a spiral shape as shown in the right half of FIG. A large number of grooves 126 are formed, and both ends of these grooves 126 are open to both the inner diameter portion and the outer diameter portion.

When the rotating shaft 121 is rotated in the counterclockwise direction when viewed from above with the valve 128 fully open, a pressure as shown by the curve m in FIG. The pressure pd is the pressure at the outer periphery and is the outlet pressure. As the valve 128 is gradually opened, the outlet pressure Pd decreases and the flow IQ increases, as shown in FIG. When the valve 128 is fully opened, the flow ff1Q reaches the maximum value Qmax, the inlet pressure and the outlet pressure of the fluid both become equal to the ambient pressure (atmospheric pressure) as shown in FIG. shows the minimum (1α).

Therefore, when the valve 128 is fully opened, the 11 force Q load capacity becomes the minimum. If a historically large thrust load capacity is required when the valve 128 is fully open, the outlet portion of the groove may be closed, and Δr in FIG. 19(c) may be set to an appropriate amount.

The present invention uses the structure shown in FIG. 21 to maintain the required thrust load capacity while allowing fluid to flow in a full space and increasing the pressure.

In a fluid pressure generating device, it is necessary to maintain the gap between the groove spaces of the component parts of HJ[3 within approximately 1/100 of the shaft diameter, and the gap of the full space of the component parts of 5GTL3 is equal to the outer diameter of the collar. It is necessary to maintain it within approximately 1/100 of the above. If the dimensions of the gaps are larger than those mentioned above, sufficient pressure will not be generated.

A first embodiment of the present invention will be explained with reference to FIG.

In the same figure (2), 1 is the main body of the fluid pressure generator at 5A,
2 is a rotating shaft, 3 is a groove formed on the circumferential surface of the rotating shaft 2,
4 is a groove portion of the rotating shaft 2 in which a large number of grooves 3 are formed; 5 is a fluid intake port; 6 is a fluid discharge port; 7 is a valve provided on the discharge port 6 side; 8 is a fluid communication hole; 9 10 is a stationary cylindrical surface formed inside the main body 1 facing the groove 4; 11 is a narrow groove space between the groove 4 and the stationary cylindrical surface 10; and 12 is a sealing. The groove space 11 is a narrow gap within 1/100 of the diameter of the rotating shaft. The groove 3 is formed in a herringbone shape on the circumferential surface of the rotating shaft 2 so as to be inclined with respect to the axial direction.

Now, with the valve 7 closed, when the rotating shaft 2 is rotated from the right side in the drawing in the opposite direction 6 ↑, fluid pressure is generated in the groove space 11, and due to the dynamic pressure effect of the fluid, the rotating shaft 2 is rotated. While the own weight is supported, the pressure of the fluid in the groove space 11 is gradually increased from the side of the reservoir 9 toward the side of the discharge port 6 and reaches a steady state. Next, when the valve 7 is opened, the fluid passes through the communication hole 8 from the suction port 5 and is temporarily stored in the reservoir 9, and then the fluid flows into the groove space 11.
A flow of fluid is generated through the discharge port in six directions.

The relationship between the fluid pressure P induced in the full space and the fluid flow mQ discharged from the discharge port 6 is as shown in FIG. That is, as the valve 7 gradually begins to be heard, the pressure P in the groove space 11 gradually begins to decrease, and conversely, the flow rate Q increases. When the valve 7 is fully opened, the pressure at the suction port 5 and the discharge port 6 becomes equal to the surrounding pressure (Popular I]-). Therefore, by appropriately selecting the pressure of the valve 70, a predetermined amount of fluid under pressure can be discharged.

In this way, according to the first embodiment, the rotating shaft 2 is arranged in the full space 11.
Since it is supported by dynamic pressure by the stationary cylindrical surface part 10 via
It can be seen that in addition to having the function of a dynamic pressure bearing (radial bearing), by selecting the opening degree of the valve 7 to be closed, it can also have the function of a fluid pump. In other words, this embodiment can be said to be a fluid pressure generating device that also has the function of a dynamic pressure bearing.

A second embodiment will be explained with reference to FIGS. 1 and 2.

15 is a collar portion formed on the rotating shaft 2; 16 is a groove portion formed on both sides of the collar portion adjacent to the groove portion 4 and consisting of a large number of helical grooves or linear grooves inclined with respect to the radial direction; Reference numeral 17 indicates a stationary plane portion formed inside the main body 1 facing the groove portion 16, and 18 indicates the groove portion 16 and the stationary plane portion 17.
This is the narrow gap between the grooves. The gap in the groove space has a size within 1/100 of the outer diameter of the collar portion 15. Portions with the same reference numerals as those in the first embodiment (FIG. 3) have the same configurations, so description thereof will be omitted.

When the rotating shaft 2 is rotated counterclockwise when viewed from the right side in the drawing, pressure is gradually increased by the groove 4 of the fluid rotating shaft 2 and reaches the collar 15. Since the groove portion 16 is formed on the surface, fluid pressure is generated between the groove portion 16 and the stationary plane portion 17, and the fluid is caused to flow from the center of the collar portion 3 in the circumferential direction, and further pressure is applied. It is raised and reaches the discharge port 6.

According to FIG. 2, when the rotating shaft 2 is rotated in the direction of the arrow,
The pressure of the fluid is gradually increased as it flows from the shaft end to the center of the collar and then toward the outer periphery of the collar. Therefore, the fluid flows from the suction port 5 to the passage communication hole 8 and the reservoir 9 to the groove space 11 to the full space 18 to the leaf outlet 6.

According to the second embodiment, the rotation +
The thrust in the axial direction of 1'1l12 is supported by the stationary plane part 17, and the stationary plane part 17 performs the function of an lIl pressure bearing (thrust bearing). Therefore, in addition to the radial bearing function of the stationary cylindrical surface portion 10, this embodiment can be said to be a fluid pressure generating device that has two bearing functions.

FIG. 4 shows a third embodiment.

In the first embodiment (Fig. 3), the rotating shaft 2 rotates and the main body 1 remains stationary, but since this has no relative structure, the main body 23 is rotated and the shaft is moved as shown in Fig. 4. Stationary axis 2
4 can also be used as a fluid pressure generating device. However, in this case, if the direction of inclination of the many grooves 3 with respect to the stationary shaft 24 is the same as in the first embodiment, the direction of rotation of the main body 23 is opposite to that in the case of rotation @2 in the first embodiment.

21 and 22 are supports for fixing the stationary shaft; 25 is an inlet;
26.2rG communication hole 2 in the axial direction communicating with the suction port 25
9 is a hole that communicates with the reservoir 9; 28 is a hole that communicates with a single-layer communication hole 30 facing Ir117'J that communicates with the discharge port 31;
32 is a rotating cylindrical surface portion.

When the main body 23 is rotated, fluid flows in from the suction port 25, passes through the communication hole 29, flows through the holes 26 and 2γ into the reservoir portions 9 and 9, and from there flows through the reservoir portions 9 and 9 while being gradually increased in pressure by the herringbone. It reaches the center of the stationary shaft 24, flows into the hole 28 from here, and then passes through the communication hole 30 to the discharge port 31.
It is discharged from.

Therefore, this embodiment also becomes a fluid pressure generating device having the function of a radial bearing.

FIG. 5 shows a fourth embodiment.

In the second embodiment (Figs. 1 and 2), the rotation @ 2 rotates and the main body 1 stands still. The shaft 24 can also be a fluid pressure generating device. In this case too, still @
If the direction of the large number of inclinations ♀1 with respect to 24 is the same as in the second embodiment, the rotation direction of the main body 23 is opposite to that of the rotating shaft 2 in the second embodiment.

33 is a hole provided on the circumferential surface of the collar portion 15 and communicates with the communication hole 30, and 34 is a rotating plane portion. Third example (fourth example)
Since the parts with the same reference numerals as in FIG.

When the main body 23 is rotated, fluid flows from the suction port 25, passes through the communication hole 29, and once flows into the reservoir 9 from the holes 26 and 27.
From here, the pressure is gradually increased by the herringbone, and it flows through the groove space in the @h direction, then through the groove space in the Y direction, reaching the circumferential surface of the collar part 15, from where it flows into the hole 33, and then into the communication port 30. After that, it is discharged from the outlet 31.

Therefore, this embodiment is also a fluid pressure generating device having the functions of radial and linear bearing links.

FIGS. 6 and 8 show the fifth embodiment.

This embodiment improves the L1-capacity per shell volume of the device and improves pressurization.

37 is a stationary cylindrical body, 38 is a rotating cylindrical body, 39 is a rotating shaft integral with the rotating cylindrical body 38, and 40 is a stationary cylindrical body 37
41 is a multilayer cylindrical portion of the rotation side cylindrical body 38,
42 is a groove space formed when the multilayer cylindrical parts 40 and 41 are stacked alternately; 43 to 46 are the multilayer cylindrical parts 4;
A large number of grooves are formed on one of the opposing surfaces of the 0.41 cylinder surface at an angle with respect to the cylinder axis, 47 is a fluid intake port, 48 is a fluid discharge port, and 49 is a communication hole. .

In addition, since it is easy to form a large number of grooves on the cylindrical surface portion on the outer circumferential surface of the cylinder, in this embodiment, all of them are formed on the outer circumferential surface as shown in FIG. 8(2)(c).

The stationary side cylindrical body 37 and the rotating side cylindrical body 38 have multilayered cylindrical parts 40 and 41 stacked on top of each other alternately to form a large number of concentric narrow grooves 42, and on opposing surfaces of the cylindrical parts. is provided with a large number of inclined grooves 43 to 46, so when the rotating shaft 39 is rotated counterclockwise when viewed from the right side in the drawing, the fluid flowing into the reservoir 3G from the suction port 47 flows into a multilayer narrow groove. The groove space 42 is indicated by the arrow in FIG.
As shown by the arrow in Figure (C), the gas flows sequentially from the outside to the inside to the outside (repeating a no-turn), and after gradually increasing the pressure (multi-stage addition ITl-), it is discharged to the outside from the discharge port 48. Ru.

Due to the rotation of the rotating cylindrical body 38, a large number of 43 to 46
Circumferential surface of the cylindrical part formed with (outer peripheral surface forming the groove)
Dynamic pressure of the fluid is induced in the full space 42 between the rotor and the circumferential surface (circumferential surface) of the cylindrical portion facing it, and the dead weight of the rotation-side cylindrical body 38 is supported by this dynamic pressure effect. Therefore, it is a "multi-stage BN pressure fluid pressure valve" device that also has a bearing 15Il function that utilizes dynamic pressure.

FIGS. 7 and 9 show a sixth embodiment.

This embodiment improves the fluid flow rate per unit volume of the device.

50 is a communication hole formed in the multilayer cylindrical part 40 of the stationary side cylindrical body 37, 51 is a communication hole formed in the multilayer cylindrical part 41 of the rotating side cylindrical body 38, and 52 to 55 are cylindrical parts of the multilayer cylindrical part 40 and 41. A large number of grooves are formed on either one of the opposing surfaces at an angle with respect to the cylinder axis. Portions with the same reference numerals as those in the fifth embodiment (FIGS. 6 and 8) have the same configuration. Therefore, the explanation will be omitted.

When the rotating shaft 39 is rotated in the opposite cutting direction when viewed from the right side in the drawing, fluid pressure is generated in the multilayer narrow groove space 42, but the communication hole 50. Since the pressures on the and outlet sides are kept at the same level, the fluid sucked from the suction port 47 simultaneously enters the plurality of groove spaces 42 of the multilayer cylindrical portion from the inlet side at the same suction pressure, as shown in FIG. 9(c). While flowing and moving as a parallel flow, the pressure increases and reaches the outlet side, where they merge and are then discharged from there through the communication hole 49 and from the discharge port 48 to the outside.

Like the fifth embodiment, this embodiment is also a fluid pressure generating device that also has a bearing function using dynamic pressure.

FIG. 10 shows a seventh embodiment.

This embodiment can also be said to be an application example of the fifth embodiment (Figs. 6 and 8), in which the stationary side cylindrical body of the fifth embodiment holds the motor fixed winding 60 at /v. Two cylinders are provided to form a main body 58, and two rotation-side cylindrical bodies of the fifth embodiment [however, the rotation shaft 39 is missing] are installed inside the main body 58? The L-motor rotating body 61 is integrally provided to form five rotating bodies. As in the fifth embodiment, the multilayer cylindrical portions 40 and 41 each have a large number of vortices formed on their cylindrical surfaces, and are fitted together concentrically, forming the groove space 4 as a large number of spaces.
2 is formed.

When the electric power was applied to the machine, the rotating body 59 rotated, and the fluid sucked from the suction port 4I was introduced into the fluid 42 for nine minutes through the passage 62, and the pressure was gradually increased while flowing in series through a large number of groove spaces. Thereafter, it is discharged to the outside from the discharge port 48 via the passage 63. The weight of the five rotating bodies is supported by the dynamic pressure induced in the large number of filled spaces 42.

FIG. 11 shows the eighth embodiment.

This embodiment can be said to be an applied example of the sixth embodiment (Figs. 7 and 9), and the main body is formed by combining two stationary cylinders of the sixth embodiment. A fixed winding 60 is provided at the center of the main body 58, and two rotating cylinders of the sixth embodiment [however, the rotating shaft 39 is missing] are provided with an electric motor rotor 61. A rotary body 59 is formed integrally with the rotor 59 at the center.

As in the sixth embodiment, the multi-layered cylindrical portions 40, 41 have a large number of grooves formed on their circumferential surfaces and are combined concentrically with each other to form groove spaces 42 as a large number of spaces. 64 is a groove space where a part of the fluid is pressurized, and a helical groove or an inclined linear groove as shown in FIG. 21 is formed in either the rotating plane part or the stationary plane part -h which faces each other. 65 and 66 are fluid passages.

When the power supply 11111 is energized, the rotating body 59 rotates, and the fluid sucked from the suction port 47 is introduced into the groove space 42 through the passage 62. Since the multilayer full space is communicated with the beans through the communication holes 50 and 51, as in the case of the sixth embodiment,
The same suction pressure flows from the inlet side (the side where the communication hole 50 is located) through a large number of concentric groove spaces as a parallel flow toward the center of the main body 58, and the pressure rises, and the pressure increases and the pressure increases. 51], the liquid flows through the communication hole 49, then through the passage 63, and is discharged from the discharge port 48 to the outside.

Further, as described above, a part of the fluid whose pressure has been increased by flowing to the outlet side (fluid flowing through the outermost layer) is diverted to the groove space 64 and the pressure is further increased, and then the motor rotor 61 The fluid flows through a passage 65 on the circumferential surface, passes through a passage 66, merges with the fluid passing through the passage 63, which is the main peak passage, and is discharged from the discharge port 48.

As described above, the fluid flowing in the groove space 64 induces dynamic pressure and serves the 1q-th function of supporting the thrust force acting on the rotating body 59. In addition, the weight of the five rotating bodies is induced in a large number of full spaces 42!
1II3-.

FIG. 12 shows a ninth embodiment.

In this embodiment, the multi-stage pressure f! This is an example of the type. 70 is a main body, 71 is a motor fixed winding provided in the center of the main body 70, 72 is a rotor of the motor, 73 is a fluid inlet, 74 is a fluid outlet, 76 is a rotation on the motor rotor side. Grooves 78 provided in multiple stages and at intervals on the cylindrical surface of the shaft.
Similarly, numeral 79 indicates a plurality of grooves for bypass prevention provided in the cylindrical surface of the rotary shaft portion at the above-mentioned intervals, numeral 79 indicates a large number of grooves in the groove portion 78, numeral 75 indicates the motor rotor 72, the groove portion 7G on the rotary shaft portion, and A rotating body with a groove 78 integrally formed therein, 7
7 is an electric motor (fluid passage formed around the rotating ring T72; 80 is a stationary cylindrical surface portion 87 formed inside the main body 7o);
81 is a fluid outlet of the groove 76, 83 is an intercooler, 84 is a cooling fluid pipe system, 82
85 is a fluid inlet of the intercooler 83, 85 is a fluid outlet of the intercooler 5, and 86 is a fluid inlet of the groove 7G in the next stage. The fluid outlet 81 of each groove 76 of each stage is connected to the fluid inlet 82 of the intercooler 741 of each stage, and the fluid outlet 85 of the intercooler of each stage is connected to the fluid inlet 8 of the groove 76 of the next stage.
Connected to 6.

Intermediate cooling 583 is for removing compression heat of the fluid during the compression stage, and is intended to prevent the temperature of the compression groove space from exceeding a certain temperature and to reduce the power required for compression. By the way, when fluid passes through the intercooler 83, a pressure drop occurs, and due to the presence of this pressure drop, the fluid flows from the fluid outlet 81 of one groove 76 to the fluid inlet 86 of the next groove 76 through the gap 80 and bypasses it. It will end up being put away. For this reason, a bypass prevention groove 18 is provided to ensure that the fluid flows toward the intercooler 83. The circumferential surface of the groove 78 on the other hand has an inclination h opposite to that of the groove 1G.
Form a large number of 79. This reversely inclined groove 79 creates a pressure gradient opposite to that of the groove 76, and the intercooler 8
3 to induce a pressure difference in the opposite direction that is approximately equal to the raw f6 pressure loss.

When the device is energized, the rotating body 75 rotates in the clockwise direction when viewed from the right side in the drawing, and the fluid is introduced from the suction lower 3 into the suction port, passes through the passage 17, and is introduced into the first stage groove 76 where it is compressed. After that, it flows through the fluid outlet 81, the fluid population 82, the intercooler 83, and the fluid outlet 85 to be cooled by 1J, and then flows from the fluid inlet 86 to the second
It is introduced into the groove 7G of the step. After repeating this process, the fluid is discharged from the discharge lower 4 to the outside through the passage 88. The top of the rotating body 75 is supported by dynamic pressure as in other embodiments.

Fig. 12(f) is a diagram showing the process of fluid pressure build-up within the device in a manner that corresponds vertically to Fig. 12(2), in which the suction pressure ps is compressed in the groove 7G region and the It can be seen that the discharge pressure becomes Pd.

Note that there is no upper radius of fluid pressure in the cavity 78 for bypass prevention.

Furthermore, the bypass prevention groove 78 can be formed not on the rotating shaft but on the stationary cylindrical surface portion 87 facing the rotating shaft.

FIG. 13 shows a tenth embodiment.

This embodiment can obtain a higher compression ratio than the ninth embodiment for the same dimensions.

91 is a collar portion, 92 is a groove portion consisting of a large number of helical grooves on both sides of the collar portion 91 or a straight groove having a C inclination with respect to the radial direction, 93 is a stationary cylindrical surface portion, and 94 is a groove portion 9.
A static plan view facing 2, 95 shows the groove 9 of the collar part 91.
No. 2 fluid outlet, 9G is a groove portion 92 on the other side of the collar portion 91.
The fluid inlet 97 is a bypass prevention groove formed of a large number of grooves on the outer circumferential surface of the collar portion 91 with an inclination that induces a flow in a direction opposite to the flow direction of the fluid in the groove 76. Portions with the same reference numerals as those in the ninth embodiment (FIG. 12) are structural portions that are the same, so a description thereof will be omitted.

In this embodiment, in the rotating shafts on both sides of the motor rotor 12, a hollow portion 76 and a groove portion 92 of a collar portion 91 are provided on the cylindrical surface of the rotating shaft portion, and a groove portion 92 of a collar portion 91 is provided on the inner surface of the main body 70 opposite to the groove portion 76. A stationary cylindrical surface portion 93 is provided, and a stationary cylindrical surface portion 94 is provided opposite the groove portion 92. Then, two or more sets of the above-mentioned navy blues are arranged in series on the rotating shaft. Also, the bay part 92 of the collar part 91
A fluid outlet 95 from the intercooler 83 is connected to the fluid outlet 82 of the intercooler 83, and a fluid outlet L396 to the groove 92 is connected to the fluid outlet 85 of the intercooler 83, respectively.

In this embodiment, the fluid compressed by the groove 7GU on the cylindrical surface of the rotating shaft is further compressed by the cavity 92 of the collar 91, so the compression ratio can be reduced accordingly. The functions of the groove part 91 of the collar part 91 and the intercooler 83 are the same as those of the bypass prevention 1 part 18 and the intercooler 83 in the ninth embodiment.

In this embodiment, it occurs in the groove space between the groove portions 92 on both surfaces of the collar portion 91 and the static plan view 94! The rotating body 75 is stably supported in the thrust direction by J+ tt'.

Note that the bypass prevention groove 97 can be formed not on the outer peripheral surface of the collar portion but on the stationary cylindrical surface portion facing thereto.

FIG. 14 is an embodiment of a method of operating the fluid pressure generating device of the present invention.

This embodiment is an example in which a fluid pressure generation device is applied to a refrigeration system that uses condensable fluid under constant rotation. The condensate is cooled and becomes a condensate, which reaches the expansion valve 105. Here, the isenthalpically expanded refrigerant liquid reaches the evaporator 106, absorbs heat from the cooling load 107, evaporates, and is sucked into the compressor 101 again. The compressor 101 always rotates at a constant speed, and capacity control is performed as follows. F) valve 10 in cooling fluid piping system 103 to condenser 102;
4 is provided to adjust the opening degree of this valve. For example, valve 10
If the opening degree of 4 is made small, the water amount of the cooling fluid decreases, the leakage of the condenser 102 becomes worse, and the discharge pressure of the compressor 101 increases. This makes the 8 skewers of the refrigerator smaller.

To explain the performance of the compressor of this embodiment with reference to FIG. 15, P is the pressure, KWth is the theoretical required power, KWs is the shaft power, and Q is the flow rate. When the discharge valve 108 is fully opened, the pressure is The flow FJQ increases as the valve opening increases, and the discharge pressure decreases.3.The point at which the theoretically required movement horn is approximately at its maximum is set as the 51st point.

This compression is characterized by a constant torque characteristic, and at constant speed rotation, the force KWs is approximately constant. Therefore, the value of (KWs - KWth) is positive at points other than the setting point, This vIh amount becomes a friction loss. Therefore, as it deviates from the design point, this friction loss increases, but it does not cause any problems in operation. Since there are no contact parts in the moving parts, the R life is infinite. In addition, it is considered optimal to operate this B condenser continuously at all times and to control the capacity steplessly from O to 100% as necessary.Also, the above-mentioned cooling control is used to raise and lower the condensing temperature of the refrigerant. In addition to adjusting the flow rate of the medium, it is also possible to increase or decrease the self-effective heat transfer area of the condenser, or in the case of air cooling, it is also possible to adjust the wind blade. The emission of heat from the condenser into outer space, that is, the emission heat (width heat) can be controlled by a shutter or the like that adjusts the heat transfer area of the condenser.

〔Effect of the invention〕

The effects of the present invention are as follows.

(1) When used as a compressor, a completely oil-free compressor can be realized.

Normal compression (some use oil lubrication for bearings, so
Great care must be taken to prevent the compressed fluid and oil from mixing or to separate them. Since this compressor uses a gas bearing system using the circulating pressurized fluid itself, there is no problem with lubricating oil.

(2) There is no vibration noise.

All centrifugal and positive displacement compressors and pumps
I-motion is inevitable, and it is almost impossible to completely eliminate it. In the present invention, since there is no cause for generating imaging noise in the fluid pressurization process, there is no vibration noise at all.

(3) Extremely stable operation is possible against fluctuations in pressure ratio.

There are no problems such as surging phenomenon in turbo-type machines or stable high pressure due to discharge valve blockage in positive-displacement machines, and extremely stable operation is possible under constant continuous operation.

(4) Lifespan is permanent.

Since the movable parts are completely non-contact, there are no wear parts, and qQ
J is permanent.

(5) A completely sealed structure is optimal, and fluid leakage can be completely prevented.

(6) It is possible to realize an extremely small capacity machine.

(7) Capacity can be effectively controlled in continuous operation without stopping the machine. Therefore, there is no need to stop the machine, and it is possible to prevent problems that frequently occur when starting and stopping the machine.

[Brief explanation of the drawing]

Fig. 1 is a sectional view of a second embodiment of the fluid pressure generating device of the present invention, Fig. 2 is a partially omitted perspective view excluding the main body of the pressure generating device, and Fig. 3(a) shows the present invention. A sectional view of the first embodiment of the fluid pressure generating device shown in FIG.
Figures 4 to 7 are cross-sectional views of the third to sixth embodiments of the fluid pressure generating device of the present invention, and Figure 8 is an explanatory diagram of the fifth embodiment. FIG. 9 is a perspective view of a defect in some cylinders in the multilayer cylinder part; 0 is a perspective view of a defect in a part of the cylinder in the multilayer cylinder part on the rotating side; FIG. The figure is an explanatory view of the sixth embodiment ((support) is a perspective view of a part of the cylinder in the multilayer cylinder part on the stationary side, and (c) is a perspective view of a part of the cylinder in the multilayer cylinder part on the rotating side. (c) is a fluid distribution route explanatory diagram, No. 10
11 are seventh and eighth embodiments of the fluid pressure generating device of the present invention, FIG. 12 is a ninth embodiment of the fluid pressure generating device of the present invention, and (2) is a partial partial view thereof. (c) is P-shi)
)A force distribution diagram, FIG. 13 is a partial sectional view of the 10th embodiment, and FIG. 14 is a force distribution diagram of the present invention.
Flow sheet diagram of an example of the 15th method
The figure is a curve diagram of P and KW-Q of the embodiment shown in Fig. 14.
Figure 6 is normal! 7IIEl: Explanatory diagram of type bearing system, No. 17
The figure is a partially omitted perspective view of ``J [3], Figure 18 t4 is an explanatory diagram of a normal HJB, (2) is a pressure distribution diagram with respect to the position in the rotational axis direction, and (c) is a structural explanatory diagram of 11 J B. , 19th
The figures relate to a normal hydrodynamic thrust bearing. 2) is a partially omitted sectional view, a (a) is a plan view of the bearing part, (c) is a P-r curve diagram, and Fig. 20 is a normal hydrodynamic thrust bearing. In other examples, (c) is a partially omitted sectional view, (c) is a plan view of the receiving part, and (c) is a p-
The r curve diagram and FIG. 21 are for explaining the fluid pressure light/i:\i position drum strike of the present invention using a model. (a) t is a cross-sectional view of the model, and A-A sectional view, (c
) is a p-r curve diagram, and ) is a P-Q[tll diagram. 2...Rotating shaft, 3...Groove, 4...Groove portion, 10...Stationary cylindrical surface portion, 11...Groove space, 15...jJra part, 17...
- Stationary plane part, 18...Groove space, 37...Stationary side cylindrical body, 38...Rotating side cylindrical body, 40.41...Multilayer cylinder part,
42... Groove space, 72... Electric VJ machine rotation complete, 76... Vortex part, 79... Vortex, 83... Intercooler, 87... Stationary cylindrical surface part, 91... Empty part, 93...・Stationary cylindrical surface part,
94...Stationary plane part, 97...Groove part, 101...Compressor as a fluid pressure generating device, 102...Condenser. (b) (■ CC) Cb) C(L) (b) Den SushiΔ P4. I3z b=9 P8 MUCHTBtmkf9 I stand 1 [) (αji(b) Rod 18 figure Rod 20 figure

Claims (11)

[Claims] (1) A rotating shaft with a groove formed on its circumferential surface consisting of a large number of grooves inclined with respect to the axial direction, a stationary cylindrical surface portion facing the outer periphery of the groove with a narrow gap, and a fluid inlet , has a discharge port, supports the weight of the rotary shaft by utilizing the dynamic pressure effect of the fluid induced in the groove space between the groove portion and the stationary cylindrical surface portion by the rotation of the rotary shaft, and also supports the groove space. A fluid pressure generating device characterized in that the fluid is caused to flow from one end toward the other end, and the fluid is sucked through the suction port, pressurized, and discharged from the discharge port. (2) In the fluid pressure generating device according to claim 1, the groove is provided on the inner circumferential surface of the opposing stationary cylindrical surface section in place of the circumferential surface of the rotating shaft so that the groove is inclined with respect to the axial direction of the cylindrical surface section. Formed fluid pressure generating device. (3) The fluid pressure generating device according to claim 1 or 2, wherein a stationary shaft is provided in place of the rotating shaft, and a rotating cylindrical surface portion is provided in place of the stationary cylindrical surface portion. (4) A rotating shaft with a corner formed on its circumferential surface consisting of a large number of grooves inclined with respect to the axial direction, a stationary cylindrical surface disposed facing the outer periphery of the groove with a narrow gap, and a fluid suction A collar portion is provided on the rotating shaft, and a groove portion consisting of a large number of helical grooves or linear grooves inclined with respect to the radial direction is formed on the surface of the collar portion adjacent to the groove portion. A stationary plane part is arranged opposite to the surface of the groove part of the collar part with a narrow gap therebetween, and rotation of the rotating shaft causes the groove space between the groove part of the rotating shaft and the stationary cylindrical surface part and the surface of the collar part to be closed. Utilizing the dynamic pressure effect of the fluid induced in the groove space between the groove and the stationary plane part, the weight of the rotating shaft is supported by the stationary cylindrical part, and the thrust in the axial direction is transferred to the stationary plane part. A fluid pressure generator characterized in that the fluid is supported by the rotating shaft portion and the groove space of the collar portion, and the fluid is sucked through the suction port, pressurized, and discharged from the discharge port. Device. (5) In the fluid pressure generating device according to claim 4, the groove of the rotating shaft is replaced with the circumferential surface of the rotating shaft, and a groove is provided on the inner circumferential surface of the opposing stationary cylindrical surface section, which is inclined with respect to the axial direction of the cylindrical section. A fluid pressure generating device in which the groove portion of the collar portion is formed on the surface of the opposing stationary flat portion instead of the surface of the collar portion. (6) In the fluid pressure generating device according to claim 4 or 5, a stationary shaft and collar section are provided in place of the rotating rotating shaft and collar section, and a rotating cylindrical surface section and a rotating section are provided in place of the stationary cylindrical surface section and stationary flat surface section. A fluid pressure generating device with a flat section. (7) The multilayer cylinder part of the rotating cylinder body and the multilayer cylinder part of the stationary cylinder body are concentrically combined and alternately arranged facing each other with a narrow gap to form a narrow cylindrical space of two or more layers and facing each other. A groove portion consisting of a large number of grooves inclined with respect to the axial direction of the cylindrical portion is formed on either the outer surface or the inner surface of the cylindrical portion, and a fluid inlet;
It has a discharge port, and uses the dynamic pressure effect of the fluid induced in the groove space between the groove and the cylindrical surface of the opposing cylindrical part by the rotation of the rotating cylindrical body to reduce the weight of the rotating cylindrical body. A fluid pressure generating device characterized in that the fluid is supported, and is made to flow through the plurality of groove spaces, and the fluid is sucked through the suction port, pressurized, and discharged from the discharge port. (8) On the rotating shafts on both sides of the sealed motor rotor,
two or more grooves formed in the circumferential surface thereof with a large number of grooves inclined with respect to the axial direction are arranged in series at appropriate intervals,
On the other hand, two or more stationary cylindrical surfaces are arranged in series at an appropriate interval so as to face the groove with a narrow gap from the outer periphery of the groove, and the fluid outlet of the groove is connected to the fluid inlet of the intercooler. The fluid outlet of the intercooler is connected to the fluid inlet of the next groove, and the fluid flow in both grooves is connected to the circumferential surface of the rotating shaft between the grooves. 1. A multi-stage fluid pressure generating device, characterized in that a bypass-preventing groove portion is formed with a large number of grooves having an inclination that induces a flow in the opposite direction. (9) On the rotating shafts on both sides of the sealed motor rotor,
A groove section having a large number of grooves inclined with respect to the axial direction is arranged on the circumferential surface, followed by a collar section, and a large number of helical grooves or radial grooves are arranged on both sides of the collar section. forming a groove portion consisting of a linear groove inclined to the
On the other hand, a stationary cylindrical surface part is arranged with a narrow gap from the outer peripheral surface of the groove part provided on the rotating shaft, and a stationary plane part is arranged opposite to the groove part on both sides of the collar part with a narrow gap, Two or more sets of a rotating shaft and a collar part and a set of a stationary cylindrical surface part and a stationary plane part are arranged in series on the rotating shaft, and the fluid outlet of the groove of the collar part is connected to the fluid inlet of the intercooler. and connecting the fluid outlet of the intercooler to the fluid inlet of the groove of the next stage collar part,
Furthermore, bypass prevention grooves are formed on the outer circumferential surface of each collar portion, consisting of a large number of grooves having an inclination that induces a flow in a direction opposite to the flow direction of the fluid in each groove of the rotating shaft. A multi-stage fluid pressure generating device with special features. (10) In the multi-stage fluid pressure generating device according to claim 8 or 9, the bypass prevention groove portion is provided at a stationary portion facing the outer circumferential surface of the rotating shaft or the collar portion instead of the outer circumferential surface of the rotating shaft or the collar portion. A multistage fluid pressure generator formed on a cylindrical surface. (11) In the fluid pressure generating device according to any one of claims 1 to 10, constant speed operation is performed using a condensable fluid, and a discharge port of the fluid is connected to a condenser, and the flow rate of the cooling medium of the condenser is A fluid pressure generator characterized in that the condensing temperature of the fluid is adjusted by increasing or decreasing the effective heat transfer area of the vessel, and the pressure and flow rate of the fluid discharged from the discharge port are controlled by increasing or decreasing the condensing temperature. How to operate the equipment.