JPS5843587B2 - Jinetsufukaido Pump Souch - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION This invention relates generally to a coherent and efficient means of generating electricity using the energy of geothermal sources, and more specifically, to the use of hot water to transfer thermal energy to the earth's surface. The present invention relates to a device that is used in deep wells and includes a device that efficiently generates and pumps superheated steam.

Although geothermal energy sources have been developed to some extent for power generation, conventional devices commonly known have low operating efficiency and significant drawbacks.

In the few installations where dry steam is supplied to the surface from a well, the steam can be supplied directly to the turbine from the well head after solids removal.

On the other hand, most geothermal wells are characterized by the fact that a mixture of steam and hot water with corrosive solutes is obtained at the surface, so that the water must be separated from the steam before it is used in a turbine. There must be.

Both types of equipment typically produce steam at low pressures, resulting in relatively low power generation efficiency compared to power generation using traditional fuel or nuclear-powered power generation equipment. .

In only a few cases, geothermal wells produce truly superheated steam, with small amounts of undesirable gases, and with virtually no liquid water.

The presence of significant amounts of liquid water in wells used in conventional geothermal devices creates problems in addition to separation.

If the water is only moderately hot, extracting thermal energy from it is expensive, or at least inefficient.

Water must be treated with or without heat.

Normally, water carries significant concentrations of quartz and alkaline salts, including chlorides, sulfates, carbonates, borates, and similar ions, and all such dissolved salts are Precipitation problems arise in that even a portion of the water suddenly flashes off to steam.

The release of alkaline water at the facility results in significant chemical and thermal pollution of the river.

Finally, there is evidence that withdrawing large amounts of water from geothermal storage sources has the potential to lead to undesirable ground subsidence in the vicinity of thermal well installations.

Technological advances in the field of extracting and utilizing geothermal energy are described in US Pat. No. 3,824,793.

This U.S. patented invention efficiently generates electricity by generating dry, superheated steam from an underground geothermal source that operates underground equipment that pumps highly pressurized and extremely hot well water to the surface. The means by which it occurs is described.

Clean water is injected into a deep well from a first site, a site on the surface of the earth, and the thermal energy stored in the high temperature deep well water carrying solutes is transferred to a second site, a site in the deep well, to clean the well. Used to generate superheated steam from water.

The resulting dry superheated steam is used at the bottom of the well,
A turbine-driven pump is activated to force the hot well water carrying solutes to a first site at the surface of the earth.

Water is pumped at all times and everywhere within the device at a pressure that prevents flash steam generation.

High-energy water is used in a binary fluid system in a first section to transfer its thermal energy to a closed-loop boiler-turbine system at the surface of the earth to drive a generator.

The cooled, clean water is regenerated by equipment on the surface and injected back into the well to operate the steam turbine located within the well.

Unwanted solutes are pumped into the ground through separate wells in the form of concentrated brine.

Compared to the relatively poor performance of other conventional devices, the invention described in this patent is highly efficient and has many other advantageous features.

Its applications are not limited to only rare dry steam sources;
Moreover, there is no problem of water and steam separation associated with conventional conventional equipment used in wells that supply a mixture of steam and hot water.

Because this new power plant operates on dry, highly superheated steam, existing efficient heat transfer elements as well as efficient high-pressure turbines can be readily employed at surface sites.

The extremely large amount of heat from the high-pressure, high-temperature water is efficiently utilized.

The use of a high pressure liquid as the heat transfer medium prevents unwanted vapor flash formation and the attendant problems of deposits of molten material.

Because the molten salt is efficiently pumped deep into the earth as far away as necessary from the geothermal source, contamination of the ground surface is avoided and there is little risk of ground subsidence in the vicinity of the geothermal source. .

This invention is an improvement on deep well geothermal devices of the type described in U.S. Pat. No. 3,824,793, supra.

The invention provides an efficient means of generating electricity at the surface of the earth using energy extracted from geothermal sources.

The equipment includes an efficient means of generating superheated steam and a novel steam-driven pumping device located at the bottom of the well that transfers the hot water to the surface where its energy content is advantageously utilized for the generation of electricity. including.

One feature of the invention is to utilize equipment installed on the surface of the earth that enables the efficient continuous operation of power generation equipment, and to control the start-up and shutdown of steam turbine pump equipment located underground.

Another aspect of the invention is the ability to efficiently generate steam within a confined annular volume between concentric vertical tubes.

This feature allows the steam to flow downward in a spiral pattern while the proportion of water droplets gradually decreases so that both flow in close proximity to the hotter end of the two tubes, thus improving steam production efficiency. .

In particular, the invention relates to features of a coherent and efficient steam turbine system suitable for use within the hostile environment of deep hydrothermal wells.

In this device, superheated steam passes downward and impinges on the turbine blades at the periphery of the turbine impeller.

Another feature is that the expanding steam then slightly reverses its flow direction, allowing the steam to flow back along the axis of the turbine impeller and back to the surface, recovering even more energy. to be done.

The arrangement of passing the exhaust steam through the turbine impeller eliminates the restriction of the passage of pumped well hot water within the confined space inside a conventional well casing.

Figure 1 shows a deep well extending far below the surface of the earth.
The general construction of a portion of the geothermal energy extraction device of the invention that is immersed in a deep well, preferably below the earth's surface, at a depth such that an abundant source of extremely hot water at high pressure is naturally available. and characteristics are shown.

The working pump structure is located on the side of the hot water source and is generally located within a conventional well casing pipe 10.

In the embodiment shown in FIG.
It can be seen that the main well portion 2 extends from the well head 1 to below the ground surface 11.

The main well section 2 is coupled to the input section 3 of the steam generator with an underground high pressure hot water source.

A steam generator section 4, a steam turbine section 5, a power station rotation bearing section 6 and a hot water pumping section 7 are arranged one after another at progressively deeper depths.

A well casing pipe 10 extends downward from the well head 1 at the ground surface 11, the purpose of which will be explained later, to provide a flow of relatively cool and relatively pure water to the bottom of the well. It preferably concentrically surrounds a tube or conduit 8 of steel or other high quality alloy steel.

Also provided within the well casing 10 is a second relatively large pipe or conduit 9 of similar quality surrounding the pipe 8 and extending from the well head 1 to the energy conversion and pumping equipment at the bottom of the well and later on. As described, the turbine exhaust steam is allowed to flow to the surface.

It can be seen from FIG. 1 that relatively clean and cool water is pumped from a location at the surface 11 to the area of the pipe T-joint 12.

At the T-joint 12, the water flowing downward is divided into two branches.

As will be explained later, the first branch delivers clean lubricating water to the pipes 13 and 17 to lubricate the bearing arrangement in the bearing section 6.

The second branch carries clean water to the pressure regulator 15 and via distribution pipe(s) 16 to a steam generator 18 formed between the generally concentric walls of the alloy tubes 9 and 9a.
input manifold 22.

For this purpose, high pressure steam is generated and sent to a steam turbine provided inside the turbine section 5.

The action of the turbine located at 5 and supported on bearings in bearing section 6 is to drive a hot water pump provided in section 7 .

To this end, high-pressure hot water is propelled upward by a rotating pump vane 20 between the rotating conical end 23 of the pump and an associated rotating or stationary shroud 19.

The hot water is pumped upwards at high speed in the annular conduit between tubes 9, 10, thus making the thermal energy contained in the hot water available for use at the surface, as will be explained later.

More importantly, the pressure when pumping the hot water upwards to the earth's surface causes the hot water to flash into steam.
The value should be such that undesirable deposition of dissolved salts at the flash point does not occur.

Therefore, it can be seen that the extremely high temperature and high pressure well water is forced upward and flows within the annular region defined by the alloy tubes 9 and 10.

The heat provided by the well's hot water immediately converts the clean water flowing into the manifold 22 of the steam generator 18 into high energy dry superheated steam.

The clean 7A is at a very high pressure before passing through the tee 12 and pressure regulator 15 due to the hydrostatic head and because the pressure is usually supplemented by a surface pump, which will be explained later, so that it It does not turn into vapor due to flash operation.

The pressure regulator 15 controls the pressure of the clean water passing therethrough so that it is evaporated and superheated within the volume of the steam generator 18.

The high-energy steam drives a steam turbine and after expansion is redirected to flow upward to the surface 11 as relatively cool steam flowing in an annular conduit confined between alloy tubes 8 and 9. .

As will be explained later, at the earth's surface 11, thermal energy is mainly recovered from high-pressure hot water, but it can also be recovered from exhaust steam from a turbine.

FIG. 2 shows details of the input section 3 and the steam generator section 4 of a preferred type of steam generator.

It can be seen that the overall shape is similar to that described with respect to FIG.

However, in FIG. 2, T-joint 12 is utilized to supply two pressure regulating devices: a pressure threshold valve 15a and a differential pressure valve 15b in series therewith.

Both valves may be conventional or may be modified as explained later in FIG. 16.

The operation of the threshold valve 15a is to sample the pressure of the hot water flow rising between the pipes 9 and 10;
A hollow tube 21 for connection is provided.

Also shown in FIG. 2 is a symmetrical input device to the steam generator 18.

For this purpose, an array of radially oriented distribution pipes 16 is provided which directs the pressure-regulated water of the differential pressure valve 15b into the volume of the generator 18 through an opening provided in the end plate 29 of the steam generator. pass to.

In this way, clean water is distributed symmetrically to the annular steam generator 18, in which a significant portion of the heat is transferred from the pumped hot water through the walls of the tubes 9, producing dry superheated steam. Occur.

The alloy tubes 9,9a are separated from each other and supported in a fixed relationship by an array of radial spacers, such as typical spacers 31,31.

It will be appreciated that the spacers 31.31 may be vertically aligned and it is preferred to use several such arrays of spacers spaced along the steam generator wall.

A preferred form of spacer is shaped to perform a different function.

As previously mentioned, fresh water supplied from manifold 22 is converted to superheated steam as it descends within steam generator 18.

It has been found that in some applications, an undesirable proportion of water droplets fall within the volume of the steam generator 18 without being completely steamed.

Since such water droplets are denser than dry steam, they fall much faster than the already evaporated part of the stream and therefore tend to remain more or less in the center of the stream, resulting in greater heat transfer in the tube 9. Do not hit the heating surface.

In the steam generator 18, a two-phase flow flows downward within the annular volume, and the inner surface of the annular volume (alloy tube 9a) tends to absorb heat rather than supply thermal energy to the steam generation process. In that sense, there is another problem.

The mechanism of this heat absorption is that the fluid rising in the pipe 9a is relatively cold turbine exhaust steam.

To overcome this undesirable result, an arrangement of spacers as shown at 32 can be used.

Spacer 32 is not vertical, but has a finite angle to the vertical.

Typically, several such arrays of spacers 32 are used, spaced apart along face 9a.

Although its shape and average inclination angle are related to the overall design, the curved spacer is arranged to swirl the descending two-phase fluid into a generally helical path as shown by arrow 33.

The action of centrifugal force thus directs both the water droplets as well as the steam already converted away from the heat absorption represented by the continuous surface of the cooling tube 9a and towards the heat source represented by the continuous surface of the tube 9.

As a result, the already converted steam is further heated and any water droplets are converted to steam and further heated as they pass through the volume of the steam generator 18 towards the steam turbine. It is advantageous because

A major problem to be solved in determining the practical form of this invention is to create a form that is both compact and efficient, especially since the structure is preferably inserted within a well casing of standard dimensions. It will be understood that this is true.

Compactness of construction and high efficiency of operation are therefore the main features of the device of FIGS. 3 to 6, which is installed in the turbine section 5 of FIG.

Referring to FIG. 3, it can be seen that the conduits of FIG. 2 enter the steam turbine section 5.

For example, the passage of hot water to be pumped is between the tubes 9, 10, and the opposite sides of the tubes 9, 9a define the steam output passage 18 of the steam generator.

Between the tubes 9a, 17 there is a passage for exhaust steam flowing upwardly from the turbine.

Pipe 17 is effectively extended so that clean water flows downwardly to and past steam turbine section 5 via channels 40,41.

A series of spaced apart radial wings 34 welded between tubes 9a and 17 provide support.

These vanes allow the exhaust steam to flow vertically in the rising exhaust steam chamber with virtually no rotational motion.
There is also a tendency to redirect exhaust steam.

To operate the steam turbine of FIG. 3, steam from a steam generator 18 located between tubes 9, 9a is fed into an annular manifold 42 and thence into an array 43 of steam injection nozzles of generally conventional design.

Nozzles 59 are shown in greater detail at 43 in the exploded view of FIG. 6 and are used in the conventional manner to direct high velocity steam to the blades of each stage of the turbine.

Various known types of single-stage or multi-stage turbine blade systems can be used in the apparatus of the present invention.

However, a multi-stage device is shown in the drawings. The first and second stages each consist of a plurality of wings 44,46 extending from a circular base ring 47 in a circular arrangement.

A rotor arrangement of wings 44 and 46 cooperates with a conventional arrangement 45 of stator fixtures therebetween.

The stator is fixed to a body block 74 common to the turbine section 5 and the bearing section 6.

A ring 47 supporting the vane arrays 44 and 46 is fixed to the impeller rim 48 in a conventional manner.

Rim 48 is part of an impeller having a set of spokes 54 and a hub 49.

When the rotor device rotates, the hub 49 rotates at the shaft portion 50°58
Also rotate.

Hub 49 is secured to threaded extension 53 of shaft portion 50 by washer 51 and nut 52.

A feature of the invention that allows for a compact design concerns the disposal of the expanded steam that has imparted useful energy to the rotor of the turbine.

This feature solves the problem of redirecting exhaust steam without using space-consuming elements.

To this end, the turbine body block 74 is provided with a smoothly curved annular Torocida/11 passage 56 which redirects the steam coming from the rotor blade arrangement 46 radially inward towards the shaft section 58 while at the same time Change its direction so that it flows upward.

An annular passage 56 is defined by a suitably curved surface 60 cast into the body block 74 and an opposing surface of the annular ring or guide 55 .

The annular guide 55 may be supported by an array of radially extending vanes 57 which, in addition to supporting the annular guide 55 on the turbine body block 74, redirect the exhaust steam to increase its velocity. There is a tendency for the rotational motion component to have a small amplitude, mainly in the vertical direction.

This creates a smooth-sided toroidal steam expansion path that directs the steam from the time it exits the annular blade arrangement 46 until it passes again through the turbine impeller.

By arranging the spokes 54 of the turbine impeller specifically as shown in FIGS. 4 and 5, the spokes 54 allow the steam to pass through the impeller in an unobtrusive manner. becomes especially easy.

The spokes 54 are individually tilted with respect to the direction of rotation of the rim 48 so that their influence on the selected operating rotational speed of the rotor is completely neutral.

In fact, the spokes 54 are shaped to have an angle of incidence relative to the direction of steam flow such that there is desirably no exchange of energy with the upwardly flowing steam.

Furthermore, no steam passages are required beyond the periphery of the rotating elements of the steam turbine, so that the flow of hot pumped well water is not interrupted.

As previously mentioned, it will be apparent to those skilled in the art that other features of known steam turbines may be used without departing from the scope of this invention.

As an example, a turbine with a single array of blades may pass steam downward through one set of nozzles and then reverse to flow upward through a second set of nozzles and the same turbine blades. Staged reentry turbines can be used.

The spent steam is also discharged in the direction shown in FIG.

FIG. 7 particularly shows the relationship of the elements of the bearing part 6 and the hot water pump part 7.

If you look at Figure 3, you will see that there is a well casing 1 in the equipment shown in Figure 7.
0 and a bearing block or body block 74, from which a generally conical casting 75 is inserted into the bolt 69.
It can be seen that it is supported by bolts like this.

This casting supports the pumping device described later.

The castings or blocks 74, 75 include a casing that houses a bearing arrangement that cooperates with and surrounds the shaft for the steam turbine to directly drive the hot water pump.
It has several main functions.

However, for clarity of illustration, the bearing assembly will be described separately, particularly with respect to FIG.

From the explanation at that time, clean lubricating water was added to the main body block 74.
, passage 41, annular manifold 73 and passage(s) 73a to the bearing arrangement.

Furthermore, coupling members such as those shown at 72 and 76 position the bearing elements relative to the cast blocks 74,75.

A hardened casing is provided to integrate blocks 74, 75 and protect them from impact and corrosion, and includes a cylindrical portion 70 and a frusto-conical portion extending concentrically downwardly into the conical end of block 75. It is in the form of a circular element with a hollow shell portion 71 in the form of a circular element.

The pump end of the shaft portion 68 projects beyond the generally coplanar ends of the conical shell portion 71 and the conical block 75 and supports a rotor 77 with a conical end.

The conical side surface of this rotor is effectively an extension of the conical surface 89 of the conical shell element 71.

A nose cone rotor 77 connects a plurality of pump implements such as vanes 20 and rotatable portions 8 of the pump shroud.
4 to support other rotating elements of the pump.

Several shroud elements that are stationary cooperate with the rotatable shroud element 84.

Therein is a generally cylindrical shroud element 93 whose upper conical surface 82 is of approximately the same profile as the conical surface 89 .

An annular shroud element 93 is supported directly from surface 89 by a plurality of fixed steam steering vanes 80 .

The vanes 80 support the shroud element 93 and also serve to direct the flow of the pumped hot water.

Although the blades 80 are shown in FIG. 7 as generally in the plane of the drawing, the blades 80 efficiently convert any rotational motion component of the pumped hot water into upward translational motion, thus as it ascends. It is preferable to increase the pressure of the hot water.

The stator portion 93 of the shroud is completed by a throat member 85 having an annular configuration held in place against the shroud element 93 by an array of bolts such as bolts 87 .

Thus, the pump mouth 88 is bounded by the inner curved surfaces of the shroud throat element 85 and the shroud rotatable element 84, as well as the conical surfaces 82, 89, which cause the flow within the casing to be at a considerably high velocity. This serves as a passageway for sending high-pressure hot water.

As previously mentioned, the rotating element 8 of the shroud allows the plurality of wings 20 to rotate at high speed by the shaft portion 68.
4 is supported from the nose cone 77.

The impeller blade 20 is shown in the drawing as having a generally flat planar surface, but in order to work most efficiently with the fixed blade 80, it is shown as 20 in the exploded view of FIG. Preferably, it has a hydrodynamic but normal curved shape.

Hot water from the well can be pumped into the casing pipe 1 by any convenient method, such as by using an annular seal 90 near the pump mouth 88.
0 and the stator portion 93 of the pump shroud.

As a novel feature of this invention, the hot water pump is provided with a thrust balancing mechanism.

As the pump generates an increase in pressure drop when pumping hot water upward, a significant downward axial thrust is applied to the turbine pump shaft.

This thrust is approximately proportional to the total dynamic pressure.

Typically, in systems where significant space is available, larger thrust bearings are used to withstand the maximum anticipated loads.

However, it is certain that when such bearings are used in such disadvantageous environments, significant power losses occur and long life and efficiency are not expected.

The need to find a mechanism to balance large axial downward thrusts may be generally illustrated by a specific example.

The specific examples listed below are merely illustrative, and the numerical values listed therein are not necessarily the same as those actually used.

For example, assume that the hot water pressure at the pump throat mouth 88 is approximately 800 pounds per square inch.

In operating conditions of the pump, the pressure within the volume occupied by the impeller blades 20 increases to, for example, 1050 psi.

A stator or diffuser vane 80 connects the casing 10 and the cylindrical part 7
Where it hits the annular volume 81 between 0 and 0, the pressure is 11
It is expected to be 50 psi.

When the turbine or pumping device is rotating at the intended operating speed, a strong downward thrust is generated on the shaft portion 58;
Correspondingly, typically 800 psi for the equivalent area of the shaft.
is added to the upward thrust of hot water.

A significant net downward force then remains, which must be absorbed by the large thrust bearing.

The pressure balance device of FIG. 7 reduces undesirable net downward thrust, thus allowing the use of smaller sized thrust bearings.

This bearing will be explained with reference to FIGS. 9, 12, 13, and 14.

The first aspect of the device that reduces the net downward force on the shaft is that
It is in the form of a conical rotor or hub end 77.

The rotor hub 77 has a relatively large axial bore 78 and a mating labyrinth sealing element at the generally horizontal end of the stationary conical cast block 75 in close proximity and in a generally horizontal plane. A labyrinth closure 79 is provided.

The elements of the seal 79 are concentric with the shaft end 68 and can be constructed of a number of concentric ring-shaped labyrinth elements, as is well known.

Only one stage is shown in the drawing for clarity.

Therefore, the hot water can flow axially into the hollow hole 78 and radially through the narrow passage of the labyrinth seal 79.

If the bore 78 and the labyrinth seal 79 are not in a cooperating relationship, there will be approximately 1050 psi of pressure on the top of the rotor conical end 77, or as described in the previous example, or the shaft and rotor Taking into account the difference in area of the end portion 77, 600
There is 0 pounds of downward thrust.

In the format shown in FIG. 7, the labyrinth seal 79 is 1050
Only a small amount of hot water flows radially inward from the psi annular region 80 to the central top of the rotor hub 77.

The high impedance passage in the seal 79 and the low impedance in the bore 78 cooperate to
The pressure at the top of hub 77 is now approximately 8000 psi instead of the previous 1050 psi, reducing the net downward thrust by 920 pounds.

For example, the labyrinth sealing area 79 is from SOO to 1050
It is observed that the pressure is in the middle of psi.

A second aspect of the apparatus for reducing the downward thrust on the shaft includes a shroud stator element 85, 93 and a shroud rotor element 84 which is fixed to and rotates with the pump impeller vanes 20. Incorporated into pump shroud equipment.

A pair of cooperating annular labyrinth sealing elements 91.92 are housed at the interface of the shroud rotor portion 84 and the shroud stator element 85.93.

115 in the tube 10 between the separate sealing parts 91,92.
There is an opening to a passage 83 that connects with the annular passage just inside the casing tube 10 at a connection point that connects to a pressure of 0 psi.

Labyrinth seal 91 is considerably larger in diameter than labyrinth seal 92.

The separate labyrinth closure elements 91,92 are usually composed of a plurality of cooperating ring-shaped labyrinth elements.

Due to the presence of passageway 83, a significant pressure differential across seal 91, for example 100 psi, is created.

This differential pressure acts upwardly on the difference in area of seals 91, 92, creating an upward thrust of, for example, 380 pounds, which acts to balance the downward thrust of the pump during operation.

Thus, the first and second parts of the thrust compensator significantly reduce the forces on the thrust bearing arrangement that will be described, so that relatively small diameter thrust bearings can be used.

By utilizing these two balancing features, reliability of operation is guaranteed and losses are minimized.

Both the axial thrust and the counterbalance force are proportional to the pump discharge pressure and thus remain balanced over a range of speeds and flow rates.

As previously mentioned, the steam turbine and pump apparatus of FIGS. 3 and 7 rotate on a shaft, and the details of this shaft are
This is shown in more detail in Figures 1-13.

Referring now particularly to FIG. 9, this shaft is mounted between a steam turbine having its rotor fixed to shaft portion 50 and a water pump having its rotor mounted to shaft portion 58 at bearing portion 6.
It turns out that it can pass through.

In general, the bearing support structure in the bearing section 6 has four main elements, which are a first radial bearing arrangement that cooperates with the thickened shaft section 61 and a thickened and tapered section 125. The shaft bearing section 154 includes a working thrust bearing section, a ball bearing section 154 provided for intermittent use, and a second radial bearing arrangement cooperating with the thickened shaft section 94.

It will be appreciated that the turbine and pump shaft bearings are constantly immersed in clean water, which is injected via passage 73a, which is also shown in FIG. 7 as being connected to annular manifold 73.

By applying high pressure clean water to all surfaces of the bearing, the presence of corrosive as well as contaminated hot water is prevented.

Generally, the radial loads due to the shaft are relatively small and can be accommodated by tilting the pad-shaped hydrodynamic bearings associated with the shaft portions 61,94.

Large downward thrusts, such as those encountered during pump operation, are accommodated by tilting a pad-shaped hydrodynamic thrust bearing attached to the tapered enlarged portion 125, as will be discussed in more detail with respect to FIG. 12 below.

As shown in FIG. 14, a hydrostatic thrust bearing may be used instead of a hydrodynamic thrust bearing.

It will be appreciated that the ball bearing arrangement 154 is only active when the shaft thrust is upward when the rotational speed is zero or low, ie after starting or stopping.

If a hydrostatic bearing similar to that shown at 125 is provided to receive this upward thrust, the rotational speeds present during this condition will not be sufficient to create a separating fluid film between the surfaces of the bearing. sufficient that damage or destruction may occur.

In extreme cases, the steam turbine may not be able to provide the torque necessary to initiate rotation of the device against the frictional effects at the thrust pad bearing interface.

For this reason, the main action of the ball bearing device is when the device starts up and immediately before its rotation completely stops.

It will be appreciated that clean water enters all the passages in and around some of the bearings via passage 73a, constantly bathing the bearing surfaces in clean, cold water.

For example, the water that has flowed into the thrust bearing is
2, 133 and then upwardly through passages such as 123 and 122 into the radial bearing attached to bearing surface 61.

There, the bearing elements are lubricated and a high impedance seal 10
6 and finally into the flow upwardly through the turbine discharge section 56
released from.

The annular seal 106 is held in a localized position by a retainer 105, which is preferably a seal with a very small clearance to the cylindrical surface of the shaft portion 50.

Such clearance closures are well known and commercially available.

For example, it is made of tungsten carbide or aluminum oxide.

The water injected into the thrust bearing from the passage 73a
It also flows downwardly into the passage 144 surrounding 28 and thus between the races 146 and 147 of the ball bearing arrangement 154.

Thus, the bearing surfaces of the balls and races 146, 147 are continuously lubricated by clean water flowing downwardly into the radial bearings associated with the shaft portion 94.

The bearing surfaces associated with this radial bearing are also continuously lubricated with clean water, after which the water passes through the annular high impedance seal 164 and is pumped upward into the well heat as described with respect to FIG. flows into the water.

9 and 10, the structure of the two radial bearings associated with the shaft portion 61.94 will now be described.

With particular reference to Figure 10, it can be seen that the radial bearing is generally of a conventional tilted pad type construction, with the shaft portion 61 being surrounded by an aluminum oxide cylinder 95 secured to the shaft.

In the normal case, three angled pad surfaces cooperate with the aluminum oxide cylinder 95.

A typical construction uses a coupling member 72 with a pad positioning axis 101.

This pad positioning shaft enters a hollow hole in the main body block 74.

Pad positioning axis 101 is positioned according to the set position of threaded portion 102 and is radially adjustable within body 74 .

The shaft 101 has a hardened steel ball 99 at its opposite end, a portion of which enters the countersink 100.

The balls 99 enter the water-filled interior of the cylindrical wall 97 of the body block 74 where they plunge into corresponding recesses in the bearing support block 96.

An arcuate sector 98 made of aluminum oxide is fixed to its inner arcuate surface by brazing or other conventional methods.

The sector 98 and cylinder 95 have abutting surfaces with a very thin clean water lubricating film between them.

A cylindrical element 95 of aluminum oxide may also be soldered or attached to the annular flange 10 seen in the upper part of FIG.
Mechanical attachment like 4 can be fixed to the shaft 61 using a tool.

In practice, three or more similar tilt pad type radial bearings are used to perfectly set the position of the shaft portion 61.

It will be apparent that the radial bearing in shaft portion 94 of FIG. 9 can be similarly constructed and operated.

A thrust bearing arrangement is arranged in FIG. 9 between the two radial bearings associated with the shaft portions 61, 94;
This is shown in detail in FIGS. 2 and 13.

As can be seen in particular from FIG. 9, the tilt pad thrust bearing arrangement includes an enlarged tapered portion 125 defining a horizontal interface 126.

The interface 126 may be bonded with a commercially available fluorocarbon Viton bond, or by brazing or other methods, with a flat ceramic material generally concentric with the shaft portion 128.
A ring 129 is attached.

Ceramic ring 129, which may be constructed of alumina, has an exposed flat annular surface 127 that forms the thrust bearing surface.

As with radial bearings, the alumina used is purity 9.
It may be of the quality known under the name C00R8995, which is 9.5% alumina oxide.

As best seen in FIGS. 12 and 13, a flat bearing surface 127 cooperates with a plurality of bearing surfaces, such as the surface of bearing 130.

Each bearing 130 is associated with a tilt pad type thrust bearing element.

Each inclined bearing pad has a sector-shaped frusto-conical metal substrate 13.
1 and an associated sector-shaped ceramic bearing 1
30 may be permanently secured at interface 135 by brazing or other methods.

The surface of the ceramic bearing 130 is inserted into the annular ceramic ring 1 by means of a mechanical device which will now be described, cooperating with a spherical recess 170 provided in the center of the lower surface of the metal substrate 131.
It is possible to closely follow the surface 127 of 29.

When surface 127 rotates, a plurality of ceramic bearings 130
A pair of inclined support plates 132 and 133 are used to make it easier to incline with respect to the annular support plate 134.

The inclined support plate 132 has a circular array of hardened balls 171, one for each recess 170, forming a hemispherical support surface.

The ceramic bearing 130 cannot rotate around the balls 171 because the inner part of the bearing 130 is in close proximity to the shaft part 128; It has the degree of mechanical restraint necessary to enable it to follow.

Further undesirable restraint is the inclined support plate 132°13
removed by 3.

For this purpose, a pair of diametrically disposed hemispherical recesses 172 , 172 are provided on the underside of the upper inclined support plate 132 .

These recesses align with the positions of the hardened balls 173, 173 fixed to the upper surface of the lower inclined support plate 133, so that the upper inclined plate rotates slightly around the line connecting the balls 173, 173, or It is designed so that it can be tilted.

Similarly, a hemispherical recess 174 is formed on the lower surface of the lower inclined plate 133.
, 174, which are spaced apart along a diameter perpendicular to the line connecting the recesses 172, 172.

To this end, the former cooperates with hardened balls 175175 (one of which is shown in FIG. 12) fixed to the upper surface of the support plate 134.

As seen in FIG. 9, the support plate 134 is clamped in place between the body block 74 and the conical casting block 75.

It is further seen that the elements 132, 133134 are provided with a central opening through which the shaft rotates and through which clean water for bearing lubrication flows.

In this way, the inclined support plates 132, 133 act to a limited extent as elements of the gimbal arrangement, with the bearing surface of each of the several ceramic bearings 130 shown in FIG. It is possible to follow the annular surface, and the accuracy of the tracking is precisely maintained by a clean water film in the gap between the bearing surfaces.

9 and 11 illustrate the arrangement of parts required by tapering portion 125 to facilitate assembly of the elements of the invention.

The annular element is constructed in halves 121, 121a and is held in place by a pin or other coupling member 120 threaded at 150 into a threaded hole 151 in the cast block 74 of the body.

Elements 121, 121a fill most of the space within the body casting block 74 where undesirable turbulence of clean water for lubrication may occur.

Passages 122 and 123 are roughly the same shape as the surrounding walls.
is made narrower by the annular element 121.121a.

When the pump is activated, the pressure of the hot water in the well is high, exerting several hundred pounds of upward thrust on the main shaft.

Although the activation cycle only lasts for example on the order of one minute, the effect of the reverse thrust present in the activation or deactivation condition must be reduced or eliminated.

For this purpose, a ball bearing arrangement 154 according to FIG. 9 is interposed, for example, between the tapered shaft section 125 of the thrust bearing and the radial bearing on the shaft section 94.

In FIG. 9, the ball bearing assembly 154 is shown in an actual operating state, for example during start-up or shutdown of the entire system.

In this state, the pressure of the hot water in the well pushes the shaft upward, so that the upper surface 148 of the thickened shaft portion 94 touches the cage 1.
50 faces.

The outer race 146 is fixed to the outer annular retainer 145, and the inner race 147 is integral with an annular flange retainer 150.

For this reason, the balls 149 of the ball bearing device 154 are connected to the race 146,
147 to absorb the transient upward thrust and generally position the shaft.

When the entire device is in operation, the shaft is in the lower position and the retainer 150 does not rotate.

There is a gap between it and surface 148.

Usually, the start-up cycle is different for ball bearing devices 15
This is a very small portion of the expected lifespan of 4.

As the rotational speed of the device increases, the downward thrust of the pump becomes greater than the upward thrust of hot water in the well, reversing the orientation of the thrust relative to the axis.

Those skilled in the art will appreciate that at this time, the shaft and the rotor of the turbine and pump attached thereto are lowered, the contact between the end face 148 of the shaft portion 94 and the retainer 150 is broken, and the ball bearing arrangement 154 is disengaged. It will be appreciated that there is sufficient axial clearance to

Therefore, under normal operating conditions, no load is applied to the bearing 154, and the friction ring 153 is connected to the inner race 147 and the ring 1.
50 acts to prevent incidental rotation.

As previously mentioned, a hydrostatic thrust bearing such as that shown in FIG. 14 may be used in place of the hydrodynamic thrust bearing shown in FIG.

Such a hydrostatic thrust bearing can be used in conjunction with a pair of radial pad type bearings of the type shown in FIG.

Only this one bearing is shown at shaft portion 58 in FIG.

The hydrostatic thrust bearing of FIG. 14 is also lubricated by clean water passing through passageway 73a and has a generally cylindrical cavity 152.
It consists of a stator and a rotor part installed inside the rotor.

A stator 158 encircles the shaft portion 142 through a small clearance passage 160 having a width of, for example, 0.002 inches and balances the pressure with the non-rotating body cast block 74.

Although rotation is not actually prevented, due to the friction between the stator 158 of the bearing and the block 74, the stator 158
2 and cannot be rotated.

The rotor 159 of the bearing is connected to the hub 4 of the impeller of the steam turbine.
Although the pressure is balanced with the hub 49, it rotates roughly together with the hub 49.

Stator 158 and rotor 159 are allowed to move slightly axially relative to shaft portion 142.

Thus, the stator 158 and rotor 159 may move axially relative to each other by an amount sufficient to naturally align their spherical bearing surfaces to support the lubricating water film 141. .

The water in this membrane flows from the passage 73a to the annular passage 162, 163,
157°160, 161.

Any hydrostatic imbalance caused by misalignment of the bearing stator 158 and rotor 159 forces the parts into alignment.

Passageway 157 includes an annular pressure drop seal 156 held in place by retainer 155 .

In operation, high pressure water for lubrication passes through the pressure drop seal 156 and the spherical bearing surface to form a film 141, which is normally conveniently disposed of in the exhaust passage region 56 of the low pressure steam turbine.

The pressure of the lubricating water approaching the seal 156 is, for example, 140
At 0 psi, a portion of the pressure drop will be across the seal 156 and most of the remaining drop will occur at the bearing interface within the membrane 141.

The bearings 15B, 159 are driven by the average effective pressure of the spherical membrane 141 acting to separate the sections 158, 159.
Selected operating bearing clearance of membrane 141 (e.g. 0.000
5 inches) and is designed to generate an upward force roughly commensurate with the downward thrust of the pump.

The thickness of this membrane changes to suit changing loading conditions, increasing slightly as the load decreases and decreasing slightly as the load increases.

This effect is achieved because the seal 156 has a substantially constant impedance, the pressure drop across it being proportional to the flow rate, and as the thickness of the membrane 141 changes, the impedance of the bearing changes.

The pressure drop across the spherical bearing when the flow rate is constant is the membrane 141.
is inversely proportional to the cube of its thickness.

Therefore, if the bearings 158°159 are operating stably in a steady state and the load increases, a) the increased load will be greater than the hydrostatic force generated by the thrust bearing, and the bearing clearance will decrease. As the clearance decreases, the impedance of the thrust bearing increases and the water flow rate through the seal 156 decreases accordingly, and as the water flow rate decreases, the pressure drop across the seal 156 decreases. and the drop across the bearing increases until 2) the pressure across the bearing rises to the point of supporting the increased load;
Closed sequentially from the bearing.

When the load decreases, the opposite is true and the bearing reaches equilibrium with increased clearance and an increased flow rate of lubricating water.

To explain the device of FIG. 15, the purpose of the deep well device of FIGS. 1 to 14 is to provide a generally ordinary It will be appreciated that a steam turbine and a generator may be used to act as part of a system that generates a large amount of electrical power at power output terminal 262.

For this purpose, hot water pumped to the surface is supplied by pipe 10 and its extension (tube 10a) via a normally open valve 264 to an element 266 of a conventional boiler heat exchanger arrangement 265.

The device 265 is in the form of a conventional closed tank and is designed to exchange heat between the heat exchanger elements 266, 271 contained therein.

The elements 266, 271 may be in the form of sector-shaped or coiled pipes and transfer thermal energy by direct heat conduction through their metal walls or by intervening suitable fluids, as is well known. Exchange.

Heat from the hot water in tube 10a is the main heat source supplied to device 265.

A small portion of this hot water, after being reduced in temperature in a boiler heat exchanger 265, is sent via pipe 267 from a normally open valve 268 to a conventional evaporator 269.

Valve 268 may be a throttle valve that is adjusted to reduce the pressure of the fluid passing therethrough, allowing the fluid to easily flash evaporate at a lower temperature when supplied to evaporator 269.

Evaporator 269 is conventional and typically includes a conventional vacuum pump 270 which serves to remove non-condensable gases.

An evaporator 269 generates clean steam, which is condensed by a conventional condenser 273 and fed to a connection 274 via a water pump 272 to provide an additional supply of clean water.

Most of the water that initially flows upwardly through well casing tube 10 is returned via tube 275 to the well formed by tube 277.

For this reason, most of the dissolved mineral salts dissolved in the hot water in the pipe 10 and pumped to the earth's surface are returned to the earth.

The well formed by tube 277 can be located quite far from the well of the heat transfer device, and there may be more than one.

This also pumps liquid into a different geological formation or into the same formation as the water source of the original thermal well.

Although a pressure accumulator or variable capacity storage tank 185 is added to the branch pipe 8a connected to the clean water return line 8,
Its purpose will be explained later.

A second energy source is supplied to the boiler heat exchanger arrangement 186, which is steam discharged from the deep well turbine 5 via pipe 9.

This steam can flow through pipe 9a and normally open valve 278 to heat exchanger element 187 of boiler heat exchanger arrangement 186.

Element 187 is subjected to heat exchange with the steam therein at the coldest end of device 186 (near the cold clean water input to heat exchanger element 188).

Therefore, the exhaust steam from the pipes 9 and 9a is transferred to the heat exchanger 186.
It is condensed within.

The condensate thus obtained is supplied to the aforementioned connection 274 via a pipe 279 and a normally open valve 280.

Water from pipe 279 and condenser 273 reaches connection 274 in a relatively pure state and can therefore be supplied directly to cold water input pipe 8 of the deep well installation.

When the valve 281 of the branch pipe 282 is closed, the connection part 274
of water is pumped into line 8 by a conventional feed pump 283 via a normally open valve 284 and line 8a.

By opening valve 281, makeup water can be supplied from any available source coupled to terminal 297.

Additionally, condenser 273 transfers cold water from a cooling tower (not shown) to heat exchanger element 286 in heat exchanger 273.
It will be understood that water cooling can be achieved by, for example, supplying water to water.

Alternatively, element 273 can be cooled at several points simply by forced air flow.

Feed pump 283 is effectively converted into a variable flow pump by using an adjustable valve 305 placed in parallel with the pump or other known means.

For this reason, the amount of clean water passing through the clean water return pipe 8a is determined by reading the readings on the indicators 180 and 181 that indicate the pressure and temperature of the hot water being pumped in the pipes 10, respectively, and checking the valve 284.
and 305 can be adjusted to optimal values by manually adjusting them according to a table prepared in advance.

A servo system may be used to make this adjustment, if desired.

During normal turbine and pump operation, the feed pump 283
but sufficient pressure, taking into account the gravitational head, that the clean water for lubrication reaches the input of the underground steam generator 18 at a pressure several hundred pounds per square inch higher than the pressure of the hot water in the well. Then, clean water is sent to the descending water supply pipe 8.

At this time, the pressure accumulator 185 acts to smooth out any pressure fluctuations that may occur at the input of the steam generator 18 due to the pump 283.

The threshold valve 15a of FIG. 2 is shown in detail in FIG.
It is set to open when the pressure is high (00 psi), and for this reason it is normally left open.

The differential pressure valve 15b shown in FIGS. 2 and 16 is preset to automatically maintain a constant difference between the pressure of the feed water and the pressure of the water entering the steam generator 18.

The pressure of the water supplied to the input of the steam generator must be less than the saturation pressure of the water at the temperature of the well in order to allow this water to evaporate within the steam generator 18.

Under proper operating conditions, the water pressure at the input of the steam generator determines the pressure inside the steam generator 18.

Furthermore, the pressure of the steam determines the mass flow rate through the nozzle 59 of the turbine.

Therefore, in this invention, from the supply pump 283 to the pipe 8a,
By varying the output pressure to 8, the water supply pressure is controlled at the surface.

For this control operation, only one simple element has to be installed near the deep well installation.

As can be seen, the steam discharge pressure of the turbine 5 is controlled at the surface by adjusting its condensing temperature.

Through this control, the degree of dryness of the steam within the turbine 5 is controlled.

The turbine pump device is a clean water supply pump 28
3 to a pressure sufficient to close the threshold valve 15a, but to ensure that the turbine bearings are lubricated while the energy stored in the steam generator 18 is dissipated and the turbine rotation ceases. It can be stopped by lowering it.

This intermediate pressure is still higher than the hot water pressure in the well;
It can be kept continuous during shutdown of the rotating equipment so as to completely eliminate contaminated hot water of the well from inside the turbine pump equipment, especially all bearings.

Valve 284 may include a check valve mechanism and conventional flow control components.

In the event of a failure of the feed pump 283, this backflow check valve closes, preventing flow from being lost through the feed pump 283, and the pressure within the accumulator 185 rapidly drops to the level at which the threshold valve 15a closes. .

Therefore, the turbine 5 can be safely decelerated and stopped.

However, the accumulator 185 continues to supply the small amount of clean water required by the pump-turbine system bearings to lubricate all bearings during the shutdown procedure.

FIG. 16 shows the threshold valve 15a of the regulator 15 and the differential pressure valve 1.
5b is shown in detail.

As previously mentioned, the pressure regulating device may be constructed of conventional elements.

These elements can be enclosed in an integral extension of the clean water input tube 14, coupling the pressure under the extension to the distribution tube 16 previously described with respect to FIG.

A pipe 21 is also provided which couples the rising well hot water pressure to the threshold valve 15a.

It can be seen that the threshold valve 15a utilizes an armature valve element 202 that can seat in an annular conical valve seat in a septum 201.

The guide includes a guide 200 and a valve stem 20 which is free to move vertically in a cavity 206 provided for braking if desired.
5.

Armature 202 of valve 15a is further supported by spring bellows 203.

The bellows are sealed to the bottom of the armature 202 and to the top of the bowl-shaped element 204 surrounding the braking element 206.

A tube 21 supports a bowl-shaped element 204 and a bellows 20
3. Provides an input to the cavity formed in the bowl-shaped element 204 and the damping cavity 206, so that a pressure corresponding to the rising hot water of the well is maintained therein.

When threshold valve 15a opens, the pressure above armature element 202 communicates via cavity 207 to the top of second armature 210 within differential pressure valve 15b.

Armature 210 is arranged to sit on a conical surface in bulkhead 209 and is guided by guide portion 208, valve stem 212 and piston 213 relative to the opening in bulkhead 209.

The piston 213 has a small hole 21 between the opposite sides of the piston 213 with a suitable damping fluid in the cavity 214.
By communicating at 3a, it can act as a braking element.

The operation of the differential pressure valve 15b is the same as that of the threshold value valve 15a.
11 by using an appropriate spring constant.

This spring tends to urge armature 210 to seat against the conical valve seat of septum 209.

Its operation will be apparent to those skilled in the art since the elements of this regulating device 15 are generally conventional and their operation during operation within the apparatus of the invention is as previously described. .

The main elements that provide heat to the boiler heat exchanger device 265 have been described above.

This heat is extracted and used in the conventional manner to operate a steam turbine 260 located at the surface of the earth.

For this purpose, the heat exchanger element 271 of the boiler-heat exchanger 265 is supplied via a pipe 289 from a conventional feed pump 288 to the heat exchanger element 271 of the boiler heat exchanger 265.
supply liquid to.

The flow of liquid is opposite the direction of heat flow to device 265 within element 266.

The liquid evaporates, thereby generating hot steam, which is coupled via tube 290 to the input stage of turbine 260.

After doing useful work, the turbine exhaust steam exiting from pipe 291 flows to a conventional condenser device 293.

This device has heat exchanger elements 292 and 294, after which a feed pump 2 is supplied again as a liquid via a line 296.
Flows to 88.

Condenser 292 may be cooled by water flowing through heat exchanger element 294 from a cooling tower (not shown).

Exchanger 293 may alternatively be air cooled in the conventional manner.

Although fluids such as water can be used to generate hot steam in the boiler heat exchanger 265 and associated surface-based loops, alternatively, fluids such as water can be used in Organic fluids may also be used.

Referring again to FIG. 15, a variable valve 190 is provided between feed pump 288 and condenser element 274 in parallel with heat exchanger element 188.

Valve 190 observes temperature indicator 189 which produces a reading responsive to the temperature of the turbine exhaust steam in pipe 9a.
It can be adjusted manually.

Alternatively, an automatic servo link, indicated by dashed line 191, may be used.

The bypass valve 190 is continuously adjusted depending on the temperature of the steam in the pipe 9a.

That is, the pressure inside the pipe 9a (back pressure of the underground turbine 5) is
It is adjusted to control the dryness of the steam in the turbine 5.

This desired control can easily be achieved at the surface by simply adjusting the temperature of condenser 186.

From the above description, the overall operation of the invention will be clear.

The geothermal energy deep well device is composed of a superheated steam generation section 4 located deep underground, a turbine section 5 driven by the superheated steam, and a hot water pump section 7, all of which are capable of generating a relatively large amount of melted water. It is located within a hot water source region where there is a large amount of hot water that may also contain materials.

Clean water, formed by condensing clean steam at the earth's surface, is supplied to the steam generation section 4 to generate the turbine 5.
It drives the engine and reliably supplies bearings in the turbine and pump parts.

The hot water pump section 7 increases the pressure level of the hot water so that it reaches the surface at a pressure well above the saturation pressure.

The pressure of the well water entering the hot water pump is high enough to prevent cavitation damage to the pump and any resulting loss of performance to the pump.

Generally, the actual pressure of the hot water is kept above the flash point by a sufficient margin at all points in the system through which the hot water flows inside the well.

This is one of the features that is particularly important to the success of this invention because when the hot water is kept above its flash pressure at all times and everywhere, it does not flash into steam.

Flashes of hot water into steam can be prevented because this can disrupt, if not actually destroy, the equipment, or at least deposit large amounts of mineral scale in the area where the flash event occurs. Should.

Devices on the surface can easily extract heat from extremely hot water and use it to generate electricity or for other useful purposes.

The energy remaining in the steam used to drive the deep well turbine in section 5 is also sent to the surface and recovered by surface-based equipment.

Although preferred embodiments of this invention have been described, the terms used here are descriptive terms and are not intended to limit this invention, and it goes without saying that various changes can be made within the scope of this invention.

[Brief explanation of the drawing]

Fig. 1 is a side view showing most of the geothermal deep well pump device in cross section, Fig. 2 is a detailed side view showing a part of the device in Fig. 1 in cross section, and Fig. 3 is the pump drive of this invention. 4 is a plan view of novel elements of the apparatus of FIG. 3, and FIG. 5 is taken along line 5-- of FIG. 4. 5 is a detailed cross-sectional view taken at point 5, FIG. 6 is a developed view showing a part of the device shown in FIG. 3 in cross section, and FIG. 7 is a sectional view of the lower part of the device shown in FIG. FIG. 8 is a partially exploded view of the device shown in FIG. 7;
9 is a cross-sectional view of a hydrodynamic bearing device used in the device shown in FIG. 3, FIG. 10 is a cross-sectional view taken along line 10-10 in FIG. 9, and FIG. 11 is a cross-sectional view taken along line 11-11 in FIG. 9. 12 is an exploded view showing a section of a part of the bearing device in FIG. 9, FIG. 13 is a plan view taken along line 13-13 in FIG. 9, and FIG. 14 is a diagram in FIG. 9. 15 is a schematic diagram of a surface-based device that cooperates with the deep well device of FIG. 1; FIG. FIG. 3 is a side view showing a part of the adjustment device in cross section. Explanation of main symbols, 9, 9a: pipe, 10: well casing pipe, 18: steam generator, 44, 46: rotor blade, 5
0, 58, 68: shaft, 55: annular ring, 60:
Curved surface.

Claims (1)

[Scope of Claims] 1. A geothermal energy exchange means provided in an underground geothermal well fluid source to supply a working fluid, and a geothermal well fluid having an energy exchange relationship with the geothermal energy exchange means so as to flow to the surface of the earth. In a geothermal deep well pumping device of the type having a pumping means that always pumps in a liquid state, a rotor means coupled by shaft means to drive the pumping means and a working fluid from the geothermal energy exchange means to the first an annular conduit means disposed in the rotor means opposite the annular conduit means for directing the flow in the direction of the rotor means to exchange energy with the rotor means; and an annular working fluid redirecting conduit means for generally reversing orientation, the rotor means having rotor passage means about the shaft means such that the working fluid changes direction after energizing the rotor means. A geothermal deep well pumping apparatus adapted to allow diverted working fluid to pass through said passageway means as a discharge fluid in a second direction generally opposite to the first direction. 2. In the geothermal deep well pump apparatus according to claim 1, the rotor means includes a hub means mounted on the shaft and a rim means supported by spoke means to be separated from each other, and thus the shaft means A geothermal deep well pump apparatus, wherein said rotor passage means is formed between spoke means around said rotor. 3. In the geothermal deep well pump device according to claim 2, the spoke means has a generally planar wide surface inclined with respect to the main plane of the rotor means, and the direction is changed. A geothermal deep well pumping apparatus having an angle of incidence with respect to the general direction of fluid flow such that there is substantially no energy transfer to or from the rotor means at operating speeds. 4. In the geothermal deep well pump device according to claim 2, the rim means is provided with a plurality of energy extraction turbine blade means to perform heat exchange with the working fluid at the annular conduit means, A geothermal deep well pumping apparatus wherein the annular conduit means includes a working fluid directing nozzle means. 5. In the geothermal deep well pump apparatus as claimed in claim 4, stator means are provided for supporting bearing means for rotating the shaft means therein, the stator means cooperating with said annular conduit means. and a plurality of redirecting stator turbine vane means in an annular arrangement forming the wall of the working fluid redirecting conduit means and adjacent to the plurality of energy extraction turbine vane means in said wall of the stator means. Deep well pump equipment. 6. In the geothermal deep well pump system as claimed in claim 1, a plurality of radially oriented vane means are provided in the annular working fluid diversion conduit means to effect rotation of the working fluid therein. At least one geothermal deep well pump apparatus, wherein the annular working fluid diversion conduit means is generally semi-toroidal to permit expansion of the diverted working fluid as it flows toward the rotor passageway means. 7. In the geothermal deep well pump device according to claim 1, the discharge fluid that has passed through the rotor passage means flows through the discharge conduit means having a first wall common to the annular conduit means. Device. 8. In the geothermal deep well pumping apparatus as claimed in claim 7, a plurality of radially oriented vane means are provided within the discharge conduit means to reduce rotation of the discharge fluid therein. Geothermal deep well pump device 9. In the geothermal deep well pump device according to claim 7, geothermal well fluid conduit means arranged approximately symmetrically around the annular conduit means is provided, and the conduit A geothermal deep well pumping apparatus, wherein the means has a second wall in common therewith, allowing geothermal well fluid to flow substantially unimpeded from the pumping means toward the surface of the earth. 10 In the geothermal deep well pump apparatus of claim 9, deflection means is provided in the working fluid conduit means to direct the working fluid away from the first common wall means and away from the second common wall means. the extruded geothermal well fluid is at a higher temperature than the working fluid so as to efficiently exchange thermal energy in close proximity with the means;
A geothermal deep well pump device in which the working fluid is at a higher temperature than the discharge fluid. 11. In the geothermal deep well pump device according to claim 10, the deflection means is constituted by curved wing means depending from at least one of the first or second common wall means, imparting a rotational motion component to the fluid and increasing its proximity to the second common wall means, thus increasing heat exchange between the first common wall means and the working fluid as it passes through the annular conduit means. A geothermal deep well pumping apparatus adapted to improve heat exchange between a second common wall means and a working fluid while reducing heat exchange.