JP2015135097A - Volume variable axial flow screw pump, fluid engine and heat engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly thermodynamically handle compressive fluid by moving a cavity in an axial direction while changing a volume with rotation of a rotor of an axial flow screw pump (a uniaxial eccentric screw pump and a uniaxial screw pump).SOLUTION: An eccentric radius e, a shape constant T (a diameter Dr in a case of a mohno type) and a wavelength λ (a pitch) of a rotor, which defines the volume of a cavity of an axial flow screw pump (a uniaxial eccentric screw pump and a uniaxial screw pump), are changed in an axial direction, and thereby the volume can be changed while the cavity is moved in the axial direction, and the volume can be changed during operation.

Description

  The present invention relates to a single-shaft eccentric screw pump and a variable-volume axial flow screw pump, a fluid engine, and a heat engine that can change the volumes of the single-shaft screw pump.

  There are gear pumps, screw pumps, and the like as rotary displacement pumps, and uniaxial eccentric screw pumps are particularly suitable for quantitative transportation of fluids with high viscosity, and their applicability has been recognized in a limited field and are becoming popular in recent years. The single-shaft eccentric screw pump has a unique structure not found in other pumps, in which it moves in the axial direction while maintaining a constant volume of the cavity generated between the rotor and the stator as it rotates. However, since everyone assumes that the volume cannot be changed, a method of using the compressible fluid effectively has not been proposed.

JP 2013-53601 “Uniaxial Eccentric Screw Pump and Fluid Motor” Dainippon Screen Mfg. Co., Ltd. JP 2007-278276 “Continuous axial flow volume transfer type worm pump” General Electric Company

Hyoji Equipment Co., Ltd. “Structure and principle of MONO pump” http://ebw.eng-book.com/pdfs/b3f41bbbebc8912f99534B5a8e2185ea. pdf seepex international http: // www. seepex. jp / products_basic_information_geometrics. html Drills for drilling n-square holes (part 29) http: // geocites. jp / ikuo_kotaro / koramu / 475_d29. htm Drills for drilling n-square holes (part 22) http: // geocites. jp / iku_kotaro / koramu / 464_d22. htm Drill for drilling n-square holes (19) http: // www. geocities. jp / icuro_kotaro / koramu / 449_d19. htm Drill for drilling n-corner holes (Part 48) http: // www. geocities. jp / icuro_kotaro / koramu / 563_d48. htm Sanwa Enterprise Co., Ltd. “About Voltech Tube” http: // www. sanwa-ent. co. jp / sanwahps / colder / coldertop3catalog. htm

  The problem to be solved is to handle the thermodynamic phenomenon appropriately by moving the cavity in the axial direction while changing the volume with the rotation of the single-shaft eccentric screw pump or the rotor of the single-screw pump.

In the present invention, the uniaxial eccentric screw pump or the three factors that determine the volume of the cavity of the single screw pump, the eccentric radius e of the rotor, the diameter Dr, and the wavelength λs are changed in the axial direction to change the volume of the cavity. It is in discovering that it can rotate.
Non-patent document 1 explains the “structure and principle of the MONO pump” in detail, which is for reference.
A volume Q _M discharged per one rotation of the rotor of a uniaxial eccentric screw pump called a MONO pump is expressed by the following equation.
Q _M = 4e · Dr · λs
Here, e: eccentric radius of the rotor Dr: diameter of the rotor λs: wavelength of the stator, λs = 2λr (when the rotor makes one revolution, the cavity advances by λs)
It can be seen that the volume Q of the cavity changes as the eccentric radius e, the rotor diameter Dr, and the stator wavelength λs change.
The inside of the stator is an oval hole that rotates once with a major axis 4e + Ds, a minor axis Ds, and a wavelength λs.
Further, Ds> Dr and Ds≈Dr.

FIG. 1 is a longitudinal sectional view (a) and sectional views (b1) to (b5) on a spherical surface of a variable volume uniaxial eccentric screw pump in which the eccentric radius e is linearly changed.
Each circle 63 centering on the intersection of the central axis 60 of the stator 2 and the eccentric shaft 61 of the rotor 1 shows the state of the cross section on the spherical surface at each position in the longitudinal sectional view (a) from (b1) to (b5). Represents. Although it is a spherical surface, it cannot be represented correctly on a plane, but the rotor 1 having a diameter Dr reciprocates a distance of 4e along the spherical surface, and the stator 2 has an elliptical shape having a major axis 4e + Ds and a minor axis Ds. It shows that there is a hole.

  By increasing the eccentric radius e linearly in the axial direction, the volume Q increases monotonously. In the example of FIG. 1, the eccentric radius e is changed 10 times. In order for the closed cavity to exist, the length of the wavelength λs of the stator is necessary, and the effective volume ratio is about 2.4 excluding the section in which the cavities at both ends are released. It is possible to increase the length and further increase the volume ratio.

Further, along with the rotation of the rotor 1, the rotation shaft 61 precesses with respect to the central shaft 60 of the stator 2. The rotor 1 can be driven or can be driven through a universal joint 151, a drive shaft 152, not shown in the drawing, but a universal joint or other drive components.
As for assembly, the rotor 1 can be inserted from the direction in which the diameter of the stator 2 is large, and assembly and removal can be performed. It is necessary to take measures to prevent the rotor 1 from moving in the axial direction during operation.

FIG. 2 is a longitudinal sectional view (a) and transverse sectional views (b1) to (b5) of a variable volume uniaxial eccentric screw pump in which the diameter Dr of the rotor 1 is linearly changed.
The central shaft 60 of the stator 2 and the eccentric shaft 61 of the rotor 1 are parallel. Cross sections at respective positions in the longitudinal sectional view (a) are shown in (b1) to (b5). It is shown that the rotor 1 having a diameter Dr reciprocates a distance of 4e along each cross section, and an oblong hole having a major axis 4e + Ds and a minor axis Ds is opened in the stator 2.

The volume Q _M can be changed by increasing or decreasing the diameter Dr of the rotor 1 in the axial direction. In the example of FIG. 2, the diameter Dr is changed 10 times. In order for the closed cavity to exist, the length of the wavelength λs of the stator is necessary, and the effective volume ratio is about 2.4 excluding the section in which the cavities at both ends are released. In the example of FIG. 2, the length is the length of the four wavelengths of the rotor, but it is possible to further increase the volume ratio, so it is possible to increase the volume ratio.

Further, along with the rotation of the rotor 1, the rotation shaft 61 rotates in parallel with the central axis 60 of the stator 2. The rotor 1 can be driven or can be driven through a universal joint 151, a drive shaft 152, not shown in the drawing, but other drive components.
As for assembly, when the diameter Dr of the rotor monotonously increases, the rotor 1 can be inserted and assembled or removed from the direction in which the diameter of the stator 2 is large. It is necessary to take measures to prevent the rotor 1 from moving in the axial direction during operation.

FIG. 3 is a longitudinal sectional view (a) of the variable volume uniaxial eccentric screw pump in which the eccentric radius e and the rotor diameter Dr are linearly changed, and sectional views (b1) to (b5) on the spherical surface.
Each circle 63 centering on the intersection of the central axis 60 of the stator 2 and the eccentric shaft 61 of the rotor 1 shows the state of the cross section on the spherical surface at each position in the longitudinal sectional view (a) from (b1) to (b5). Represents. Although it is a spherical surface, it cannot be represented correctly on a plane, but the rotor 1 having a diameter Dr reciprocates a distance of 4e along the spherical surface, and the stator 2 has an elliptical shape having a major axis 4e + Ds and a minor axis Ds. It shows that there is a hole.

  The volume Q can be greatly changed by changing the eccentric radius e and the diameter Dr of the rotor 1 in the axial direction. The eccentric radius e must be changed linearly, but the diameter Dr can be changed arbitrarily. In the example of FIG. 3, the eccentric radius e is changed 10 times and the rotor diameter Dr is changed 10 times. In order for the closed cavity to exist, the length of the wavelength λs of the stator is necessary, and the effective volume ratio excluding the section where the cavities at both ends are released is 5.7, as shown in FIGS. It is bigger than the ones. In the example of FIG. 3, the length is equivalent to the four wavelengths of the rotor, but the length can be further increased, so that the volume ratio can be increased.

Further, along with the rotation of the rotor 1, the rotation shaft 61 precesses with respect to the central shaft 60 of the stator 2. The rotor 1 can be driven or can be driven through a universal joint 151, a drive shaft 152, not shown in the drawing, but other drive components.
As for the assembly, when the eccentric radius e and the diameter Dr of the rotor monotonously increase, the rotor 1 can be inserted and assembled or removed from the direction in which the diameter of the stator 2 is large. It is necessary to take measures to prevent the rotor 1 from moving in the axial direction during operation.

FIG. 4 is a longitudinal sectional view (a) and lateral sectional views (b1) to (b5) of the variable volume uniaxial eccentric screw pump in which the wavelength λs is linearly changed. The central shaft 60 of the stator 2 and the eccentric shaft 61 of the rotor 1 are parallel. Cross sections at respective positions in the longitudinal sectional view (a) are shown in (b1) to (b5).
It is shown that the rotor 1 having a diameter Dr reciprocates a distance of 4e along each cross section, and an oblong hole having a major axis 4e + Ds and a minor axis Ds is opened in the stator 2.

It can be seen that the volume Q _M can be changed by changing the wavelength λs in the axial direction. When the wavelength λs is changed 10 times, and excluding the sections at both ends where the cavity is released, the effective volume ratio is about 1.7. The length of FIG. 4 is for the four wavelengths of the rotor, but can be further increased, so that the volume ratio can be increased.
Further, along with the rotation of the rotor 1, the rotation shaft 61 rotates eccentrically in parallel with the central axis 60 of the stator 2. In order to prevent the rotor 1 from moving axially in the operating state, the rotor 1 is driven through the universal joint 151, the drive shaft 152, other drive parts not shown in the figure, or the drive is driven. Can receive.
For assembly, the rotor 1 cannot be inserted unless the stator 2 is divided into two parts.

FIG. 5 is a longitudinal sectional view (a) and spherical sectional views (b1) to (b5) of the variable volume uniaxial eccentric screw pump in which the eccentric radius e, the diameter Dr of the rotor, and the wavelength λs are changed.
Each circle 63 centering on the intersection of the central axis 60 of the stator 2 and the eccentric shaft 61 of the rotor 1 shows the state of the cross section on the spherical surface at each position in the longitudinal sectional view (a) from (b1) to (b5). Represents. Although it is on the spherical surface, it cannot be represented correctly on the plane, but the rotor 1 having a diameter Dr reciprocates a distance of 4e along each spherical surface, and the stator 2 has a long diameter 4e + Ds and a short diameter Ds. It shows that there is a circular hole.

  By changing the eccentric radius e, the diameter Dr of the rotor 1 and the wavelength λ in the axial direction, the volume Q can be greatly changed. In the example of FIG. 5, the eccentric radius e is changed 10 times, and the rotor diameter Dr and wavelength λ are changed 10 times. In order for the closed cavity to exist, the length of the wavelength λs of the stator is necessary. Therefore, the effective volume ratio excluding the section where the cavity is released is 11 times. Since the length can be further increased, the volume ratio can be further increased.

Further, as the rotor 1 rotates, the rotating shaft 61 precesses with respect to the central shaft 60 of the stator 2, and measures are taken so that the rotor 1 does not move in the axial direction in the operating state. Can be driven through the universal joint 151, the drive shaft 152, not shown in the drawing, or can be driven and act on the compressible fluid.
Depending on the combination of each of the eccentric radius e, diameter Dr, and wavelength λs, the rotor 1 may not be inserted unless the stator 2 is divided into two parts in the longitudinal section.

  FIG. 6 is a longitudinal sectional view (a) of a variable volume uniaxial eccentric screw pump having a Tricam type cross section, and its cross sectional views (b1) to (b5), and a cross sectional view (c1) to (c4) of a similar Tricam type shape. ), A longitudinal sectional view (d) of a variable volume uniaxial eccentric screw pump having a cardioid type cross section, and (e1) to (e5), a longitudinal sectional view of a variable volume uniaxial eccentric screw pump having a Wankel type cross section ( f) and its cross-sectional views (g1) to (g5), cross-sectional views (h1) to (h5) of a cross-section similar to these, a cross-sectional view (i1) of a hypocycloidal shape, and a trochoidal shape Explanatory drawing showing the relationship (i2), a transverse sectional view of the trochoid pump (l), a longitudinal sectional view of a constant volume uniaxial eccentric screw pump having the same section (m), and a longitudinal sectional view of a variable volume uniaxial eccentric screw pump having the same section (N Is a cross-sectional view of a multi-rotor trochoid shape (o) and longitudinal sectional view of a variable volume monoaxial eccentric screw pump having the same cross section (p).

Non-Patent Document 2 introduces a Tricam type single-shaft eccentric screw pump as a replacement part capable of increasing the capacity of a Mono pump. In the Tricam type single-shaft eccentric screw pump, a double helical rotor having an elliptical cross section rotates eccentrically in a triple helical stator having a cross sectional shape with rounded triangular corners.
Non-Patent Document 3 discusses a rotor composed of a combination of elliptical adjoint curves (represented as an elliptical arc) that rotates inside an equilateral triangle with rounded corners. (Since sufficient data cannot be obtained for the shape of Non-Patent Document 2, it is unclear whether the shape is exactly the same.)
By changing the eccentric radius e of the tricam type uniaxial eccentric screw pump in the axial direction, the volume of the cavity can be varied while being transferred in the axial direction as shown in the longitudinal sectional view of FIG. Each circle 63 centering on the intersection of the central axis 60 of the stator 2a and the eccentric shaft 61 of the rotor 1a shows the state of the cross section on the spherical surface at each position in the longitudinal sectional view (a) from (b1) to (b5). Represents. Although it is a spherical surface, it cannot be represented correctly on the plane, but the elliptical arc-shaped rotor 1a is eccentrically rotated along each spherical surface 63 in a triangular hole with rounded corners of the stator 2a. Is shown. Similar to the MONO type, the volume of the cavity can be varied by changing the eccentric radius or wavelength.
Note that the straight figure (C1) inscribed in the triangular hypocycloid and rotating eccentrically cannot be created because the rotor has no thickness, but it is not correct because the side is not a straight line as described in Non-Patent Document 3. Figure (c2) that can be used as a rotary pump that is not inscribed in a triangle but replaces a straight line with an ellipse, and a figure of an elliptical rotor that is inscribed in a regular triangle with rounded corners and is rotated in the form of Non-Patent Document 4. (C3), a triangular figure (c4) composed of an elliptical arc rotating inscribed in a square with rounded corners, and the like are shown.

Non-Patent Document 5 discusses a rotary pump having an elliptical arc type rotor that rotates inscribed in a stator having a cardioid type cross section. About this shape, by extending while spirally twisting in the axial direction, by changing the cross-sectional area etc. in the constant volume or axial direction, the uniaxial eccentric screw pump (if the eccentric shaft is fixed, Single screw pump).
As shown in the vertical cross section (d) and its cross sections (e1) to (e5) of a variable volume uniaxial eccentric screw pump having a cardioid stator cross section, the shape of the cross-sectional area through which the fluid passes is extremely high. It has a shape suitable for handling a large amount of compressible fluid.
In addition, since both ends of the rotor in the cross-sectional shape and the convex part in the stator are always in contact with other parts, it is advantageous to improve the airtightness of the cavity by attaching a flexible material in a spiral shape. Shape.

Japanese Patent Application Laid-Open No. 2013-53601 “Uniaxial Eccentric Screw Pump and Fluid Motor” in Patent Document 1 proposes a constant volume uniaxial eccentric screw pump having a Wankel type cross section.
The uniaxial eccentric screw pump having a Wankel-type cross section is a variable volume uniaxial eccentric screw pump that can rotate while changing the volume as shown in the longitudinal sectional view of FIG. 6 (f) by changing the eccentric radius in the axial direction. Become. Each circle 63 centering on the intersection of the center axis 60 of the stator 2b and the rotation axis of the rotor 1b, that is, the eccentric shaft 61, shows the state of the cross section on the spherical surface at each position in the longitudinal sectional view (f) from (g1) ( g5). Although it is a spherical surface, it cannot be represented correctly on a plane, but the rotor 1b projected onto the spherical surface rotates eccentrically along each spherical surface 63 and is a stator defined by a peritrochoidal curve expanded on the spherical surface. It shows that the reciprocating motion is reciprocating in the bowl-shaped hole 2b. The volume can be varied by changing the wavelength λs (pitch) in addition to the eccentric radius e.
Non-Patent Literatures 5 and 6 introduce a cardioid type (h1), a Wankel type (h2), a higher order (h3), and a shape closer to a circle than the cardioid type (h4).
Japanese Patent Application Laid-Open No. 2007-278276 “Continuous Axial Volumetric Transfer Warm Pump” in Patent Document 2 introduces a Wankel-type shape (h5).

In Patent Document 2, the ratio of the radius of the constant circle to the rotating circle shown in FIG. 6 (i1) is 3 (triangular) for the rotor and 4 (square) for the stator. There is a description.
FIG. 6 (i2) shows the relationship between the hypocycloid shape and the trochoid shape. It shows the shape of a small circle envelope with a constant diameter.
In FIG. 6 (j), the trochoid pump 50c is known as a rotary pump in which a trochoidal stator (outer rotor) 2c and a trochoidal rotor (inner rotor) 1c rotate together.
Normally, it is not used as an axial pump, but when this cross-sectional shape is extended while being spirally twisted in the axial direction, a single-screw pump is obtained as shown in the longitudinal sectional view of FIG. When the outer rotor 2c is fixed so as not to rotate and handled as a stator, a uniaxial eccentric screw pump is obtained. Further, when the eccentric radius is changed in the axial direction, the variable volume uniaxial eccentric screw pump 3c or the variable volume uniaxial screw pump 3c is obtained as shown in the longitudinal section (l).
In addition to the eccentric radius e, the volume Q of the cavity can be varied by changing the axial screw pitch (wavelength λs).
In addition, this type of internal gear pump has many variants with different numbers of teeth.
A trochoidal rotor whose transverse cross section is shown in FIG. 6 (m) and whose longitudinal cross section is shown in (n) is used for multiple (the number of teeth of the outer rotor is one more than the number of teeth of the inner rotor). and so on. In the case where the trochoidal rotor is multiplexed, the ratio of the cross-sectional area through which the compressive fluid can pass can be increased by multiplexing.

Table 1 shows a hypocycloid shape with a number of stators up to 5 and Table 2 shows an epicycloid shape with a number of stators up to 3 in a list. Each of them has a larger number of articles.
Table 1 shows a hypocycloid-shaped stator that is reduced so that a hypocycloid-shaped rotor is inscribed by one less than the number of stators.
Line A indicates the basic shape, and it is difficult to create a shape without a thickness indicated by only a line or a shape with a sharp corner.
The shape that can be produced is a B-line shape corrected to an envelope formed by rolling a circle into a basic shape, and the Monono type and the Trochoid type are classified therein.
Line C is a shape in which each side of the rotor of the basic shape is replaced with an arc, an elliptical arc, a part of a hypocycloid curve, etc., and the center part is expanded, and is adjusted so as to be inscribed in the regular polygonal stator. It is a modified envelope that can be rotated, and the Tricam-type shape is classified in this. Although not listed in this table, depending on the shape of the elliptical arc, it cannot be inscribed in a regular polygon with rounded corners, but as shown in the figures of (c2) and (c3) in FIG. There are shapes that can be used as single screw pumps.
Lines D to F in Table 2 use epicycloid-shaped stators, and are reduced so that a hypocycloid-shaped rotor, one more than the number of stators, is inscribed. The basic shape of the D row is a shape that is difficult to create as it is, such as one having no thickness and sharp corners.
The shape that can be produced is an E-line figure corrected to an envelope formed by rolling a circle into a basic shape. In the F row, a shape in which the corners of the rotor of the basic shape are replaced with an elliptical arc or the like so as to swell the central portion is classified, and the Wankel type is classified in this shape. A suitable shape is selected and replaced from various arcs, elliptical arcs, hypocycloid curves, and the like, and the shape of the stator is adjusted according to the envelope of the rotor that rotates eccentrically.

The graphics categorized in Tables 1 and 2 can be extended to constant-volume axial flow pumps (uniaxial eccentric screw pumps and uniaxial screw pumps with variable volume) by twisting them in the axial direction in a spiral manner. The area S obtained by subtracting the cross-sectional area of the rotor from the opening area of
S = T · e ²
Can be described.
Here, e is an eccentric radius, T is a shape constant determined by the shape, number of stripes, and combinations of the stator and rotor, and there are a number of factors such as whether or not an elliptical arc is used and the diameter of the circle that generates the envelope. Change.
When used as a uniaxial eccentric screw pump, the volume Q discharged per one rotation of the rotor of wavelength λr is expressed by the following equation.
Q = S · Ns · λr
= T ・ e ²・ Nr ・ λs
Here, Nr: number of rotor stripes, Ns: number of stator stripes, λs: length of one wavelength of the stator.
The MONO type shape constant T _M is such that the direction in which the rotor moves eccentrically and the direction in which the diameter Dr contributes are orthogonal,
T _M = 4 · Dr / e
If so, the MONO-type discharge volume Q _M has Nr of 1, so
Q _M = 4 · e · Dr · λs
Which is consistent with the equation for volume Q _M listed in paragraph 0006.

The length of the closed cavity is one wavelength for a hypocycloid stator and two wavelengths for an epicycloid stator (more than two wavelengths for two or more epicycloid basic figures. The length of the stator is required depending on the method.
The discharge volume Q of the uniaxial screw pump that rotates the stator together with the rotor corresponds to the case where the difference between the rotation speeds of the stator and the rotor is 1.
The graphics classified in Table 1 and Table 2 and the graphics not arranged in the table are extended while spirally twisting in the axial direction, and the eccentric radius e, the shape constant T, and the wavelength λs ( By changing the (pitch), it can be expanded to a uniaxial eccentric screw pump and a uniaxial screw pump with variable volume.
There are no other proposals regarding axial flow screw pumps (volume variable uniaxial eccentric pump and volume variable uniaxial screw pump) that vary the volume of the cavity in the axial direction.

  As the rotor rotates, the cavity can be transferred in the axial direction and its volume can be changed continuously, so the physical state of the compressible fluid (liquid, gas), pressure (density), temperature, etc. Many events including chemical changes such as chemical changes and combustion can be handled appropriately.

  In addition to being used as a compressor for air conditioners, refrigerators, and freezers, by increasing the number of cavities, it is possible to handle large pressure differences that cannot be handled by conventional pumps. Since it is a positive displacement pump, it is possible to operate with high efficiency at a very slow rotation speed and to perform compression and expansion of a thermodynamically ideal gas, so that it can be used as an efficient heat engine. In addition to bringing about thermodynamic reforms, it can be applied in a variety of fields, such as being able to be applied to the collection of natural energy and resources in a completely new way different from conventional methods.

It is explanatory drawing of the variable volume uniaxial eccentric screw pump which changed the eccentric radius e linearly. It is explanatory drawing of the volume variable uniaxial eccentric screw pump which changed the diameter Dr of the rotor linearly. It is explanatory drawing of the volume variable single axis | shaft eccentric screw pump which changed the eccentric radius e and the diameter Dr of the rotor linearly. It is explanatory drawing of the volume variable uniaxial eccentric screw pump which changed wavelength (lambda) (pitch) linearly. It is explanatory drawing of the volume variable uniaxial eccentric screw pump which changed the eccentric radius e, the diameter Dr of the rotor 1, and wavelength (lambda) r (pitch). It is explanatory drawing regarding the shape which can be used as a variable volume pump, such as a tricham type, a cardioid type, a Wankel type, a trochoid type, and other similar shapes, and an explanatory diagram regarding a multiple rotor. It is a basic explanation about the shape of a rotor and a stator, and a cavity, and an explanatory view about a connecting method. It is explanatory drawing which showed the implementation method as a vacuum pump (Example 1). It is explanatory drawing which showed the implementation method as a compressed air engine (Example 2). It is explanatory drawing which showed the implementation method as an air liquefying apparatus (Example 3) and an air conditioner (Example 4). It is explanatory drawing which showed the implementation method as a water vapor expander (Example 5). It is explanatory drawing which showed the implementation method as an internal combustion engine (Example 6). It is explanatory drawing which showed the implementation method as a remote drive pump (Example 7), a seabed resource extraction pump (Example 8), and a multiple trochoid pump (Example 9). It is explanatory drawing which showed the implementation method as a thermal energy recovery device (Example 10) and a cold energy recovery device (Example 11). It is explanatory drawing which showed the implementation method as a solar energy recovery device (Example 12). It is explanatory drawing which showed the implementation method as a geothermal energy recovery device (Example 13). It is explanatory drawing which showed the implementation method as a high pressure air utilization system (Example 14), a heat exchange expander (Example 15), and a compressible fluid pressure regulator (Example 16). It is explanatory drawing which showed the implementation method as a temperature difference drive generator (Example 17), a compressed air drive generator (Example 18), and a heat recovery panel type generator (Example 19).

The variable volume uniaxial eccentric screw pump shown in FIGS. 1 to 5 can be expanded by rotating the rotor 1 in an opposite direction by rotating the rotor 1 (eccentric rotation). The ratio can be designed from 1.01 to several hundred times.
Also, the eccentric shaft can be fixed, and both the rotor 1 and the stator 2 can be rotated to be used as a variable volume uniaxial pump. (In this case, the stator 2 is called an outer rotor.)
As shown in FIG. 6, various shapes such as Tricam type, Wankel type, trochoid type, cardioid type, etc. can be expanded while twisting in the axial direction, and a constant volume or variable volume uniaxial eccentric screw pump and It was shown that it can be used as a variable volume single screw pump.
Needless to say, it can be used in place of conventional refrigerators and air conditioner compressors, but by combining multiple pumps and adding a function to adjust the pressure in the cavity by adding a valve, The ability can be greatly improved.

FIG. 7 shows a longitudinal sectional view (a) in which the length of the variable volume uniaxial eccentric screw pump 3 is set to 12 wavelengths, an external view (b) of the rotor 1 and an external view of the stator 2 modeled with a certain thickness ( c) Longitudinal sectional view of a physical / chemical reactor 33 in which a variable volume uniaxial eccentric screw pump is coupled on the short diameter side, and a longitudinal sectional view of a compressible fluid pressure transducer 35 in which the rotational direction of the screw is reversed at the central portion. It is the longitudinal cross-sectional view (f) of the physical-chemical reactor (the 2) 38 couple | bonded by (e) and the long diameter side of the volume variable single screw pump.
FIG. 7A shows the effective volume of a closed cavity by changing the eccentric radius e and the diameter Dr of the rotor 1 10 times, changing the wavelength λ 5 times, and changing the length to 12 wavelengths of the wavelength λr of the rotor 1. A ratio of 90 is obtained.
By reducing the length of the wavelength λs, the number of cavities can be increased and the effective volume ratio can be increased.
The eccentric radius e must change linearly in the axial direction, but the shape constant T can be arbitrarily set, and various designs such as changing the volume of the cavity in a geometric series are possible.
Comparing the case where high pressure air is put into the cavity A and the case where high pressure air is put into both A and B, both the consumption amount and the rotational force of the high pressure air become larger. By providing a suction valve in each of the cavities A to G and changing the suction point of the high-pressure air, it is possible to operate with a different volume ratio.
Similarly, an appropriate expansion volume ratio can be selected by providing a valve in each of the cavities H to M.

FIG. 7B shows the appearance of the rotor 1, and FIG. 7C shows the appearance of the stator 2 modeled with a constant thickness.
In either case, the rotor 1 and the stator 2 in the longitudinal sectional view of FIG. 7A are modeled as three-dimensional shapes, and it is understood that the rotor 1 is a single screw and the stator 2 is a double screw.

FIG. 7D shows a physical / chemical reactor 33 in which two volume-variable uniaxial eccentric screw pumps 31 and 32 are arranged on the left and right sides, and the central shaft 60 and the eccentric shaft 61 are joined together and combined on the short diameter side. It is a longitudinal cross-sectional view. The rotor 1 rotates and the air that has entered from the left opening 241 is compressed by the compressor 31, then expanded by the expander 32, and discharged from the opening 240.
This configuration can be used as a physicochemical reactor 33 that performs a reaction such as a physical change or a chemical change in a high pressure at the center. The energy required for compression can be recovered during the expansion process. It can be used in many fields, including combustion in high-pressure air and continuous chemical reactions in high-pressure and high-temperature supercritical fluids.

FIG. 7E is a longitudinal sectional view of a variable volume uniaxial eccentric screw pump that can be used as the pressure transducer 35 in which the screw rotation direction is reversed at the center.
High pressure air of 4 atm is added to the left opening 241, and the rotor 1 is rotated by the pressure, and discharged from the opening 240 at the center. As the rotor 1 rotates, 1 atm of air is sucked from the opening 241 on the right side, and approximately 2 atm of air is discharged from the opening 240 at the center.
When the pressure is reduced by the throttle valve, the air amount does not change, but in the pressure converter 35, the amount of air sucked from the right opening 241 is added, so it can be understood that the loss is small. Heat and cold generated with pressure changes are averaged.
Further, when used in the reverse direction, it operates as a booster, and by applying pressure to the central opening 240 of the pressure transducer 35, air flows toward the right opening and the rotor 1 rotates. Since the direction of the spiral is reversed, air with increased pressure can be obtained in the left opening 241. Since the generated heat and cold heat are not averaged, heat exchange may be performed as necessary.
A method is also conceivable in which the interior of the rotor 1 is hollow, or the periphery of the stator 2 is covered with an outer shell to form a spiral flow path, and the inside of each is a heat pipe, thereby performing heat exchange.

FIG. 7F shows a physical / chemical reactor in which two volume-variable uniaxial eccentric screw pumps 31 and 32 are arranged on the left and right sides, and the rotor rotation shaft (eccentric shaft) 61 is aligned, and the rotor is coupled on the longer diameter side. (No. 2) FIG. The air that has entered through the opening 241 is compressed by the compressor 31, expanded through the pipe by the expander 32, and discharged from the opening 240.
Although it can be used in the same manner as the physical-chemical reactor 33, which can carry out reactions such as physical changes and chemical changes under high pressure, the stator (outer rotor) also rotates as the rotor rotates. It is necessary to ensure the airtightness of the rotating connection part, such as using a magnetic fluid.
When connecting by using a universal joint or the like to connect the rotor, it is not necessary to rotate the stator.

Although not shown in the figure, four uniaxial eccentric screw pumps are arranged in parallel, and the phase of the eccentric rotation of the rotor is adjusted and coupled by gears, and the two units are rotated in the opposite direction to cause eccentric motion (precession). An arrangement that cancels the displacement of the center of gravity due to movement) is also conceivable.
By adjusting the amount of change in the eccentric radius e, shape factor T, and wavelength λ (pitch), which are the factors that determine the volume of the cavity, and increasing the diameter, the wavelength is designed to be longer, making it a substantially constant volume. The following design is also possible. Even when the incompressible fluid is discharged at a high pressure, it is possible to design so that the pressure does not concentrate in one cavity in consideration of the compression characteristics. In applications where only air is blown without pressure or where incompressible fluid is transferred to a height of several tens of centimeters, even if there is a slight gap between the rotor and the stator, there is less than one closed location. Even so, it is possible to transfer the fluid and there are applications that can be used as such.
In applications where high pressure is handled, the degree of sealing of the cavity becomes important, and therefore the rotor and stator need to be precisely processed in consideration of deformation due to temperature changes.

  FIG. 8 is a longitudinal sectional view showing the vacuum pump 312 (Example 1). The variable volume uniaxial eccentric screw pump 3 composed of 12 stages of cavities with a volume ratio of 50 times and a plurality of matching valves 28 are configured. A motor as a power source is arranged on the normal pressure side where maintenance can be easily performed, and is connected by a universal joint 151. (Because it is an explanatory diagram, the vacuum vessel 53 is drawn quite small.)

  At the start of operation, when the operation is started from the state where the pressure in the vacuum vessel 53 is normal pressure, the pressure in the cavity at the rear stage of the variable volume uniaxial eccentric screw pump 312 transiently exceeds the atmospheric pressure. . In order to avoid excessively compressing the air to be exhausted, a matching valve 28 is provided, and the check valve 283 of the cavity whose pressure is higher than that of the air chamber 255 is opened to exhaust the excess air. (The check valve 284 expresses that it is open.)

If the incompressible fluid fills the cavity due to condensation of moisture contained in the air, the rotation of the rotor 1 is stopped. The check valve 28 of the cavity whose pressure is increased due to the incompressible fluid is opened and discharged to the air chamber 255. In the air chamber 255, the air 95 and the incompressible fluid 99 are discharged from the discharge port 240 by being separated by gravity.
The volume ratio can be designed to be larger. By reverse rotation, air can be returned gently.

  FIG. 9 is a longitudinal sectional view (a) of a compressed air engine 323 (Example 2), an in-vehicle image (b), and a transverse sectional view (c) including a control valve. FIG. 9A shows a compressed air engine 323 constituted by a variable volume single-shaft eccentric screw pump 3 having a real volume ratio of 60 times and comprising a 12-stage cavity integrated with a high-pressure air chamber 155 and a plurality of matching valves 28. is there. The rotational force is transmitted via the universal joint 151 and the drive shaft 152. In addition to vehicles, it can be used as a power source for tools and the like.

A throttle valve is generally used to adjust the air pressure. However, since the pressure loss when passing through the throttle valve is large, the energy of the compressed air cannot be fully utilized.
In the embodiment of FIG. 9A, a truncated cone-shaped cylindrical valve 281 is used, and the opening 24 is opened in order from the smallest of the cavities for each rotation angle, and high-pressure air is filled.
In order to obtain the required torque, the cylindrical valve 281 is operated and adjusted so that the cavity corresponding to the load is filled with high-pressure air.

The frustoconical cylindrical valve 281 needs to have a structure that can be adjusted from the outside without being affected by the pressure of the high-pressure air chamber 255.
When the pressure in the high-pressure air chamber 255 is reduced, the truncated cone-shaped cylindrical valve 281 is rotated and opened by several steps to compensate for the reduction in rotational force.
A frustoconical cylindrical valve 280 is also provided on the discharge side, and can be adjusted so as to appropriately expand the compressed air.

A plurality of holes 24 are spirally formed along the projecting portion of the double thread of the stator 2 and are opened and closed by an opening 24 provided in a truncated cone cylinder 28.
FIG. 9C shows a cross-sectional view including the opening 24 of the truncated conical cylinder valve 28. The frustum-shaped cylindrical valve 28 is rotated, and the cavity is opened when the opening 24 overlaps the opening 24 of the stator 2. The shapes of the opening 24 arranged in a spiral shape of the stator 2 and the truncated cone-shaped cylindrical valve 28 are similar to those in FIG. 9C (the opening angle of the opening 24 of the truncated cone-shaped cylindrical valve is different). .

Since the temperature of the discharged air decreases during the expansion process, it can be used for indoor cooling.
By closing all the frustoconical cylindrical valve 281, the inside of the cavity gradually becomes negative pressure and rotation is suppressed, so that a braking operation can be performed. The regenerative operation can be performed by rotating the rotor 1 of the compressed air engine 323 in the reverse direction by sucking and compressing air and filling the high-pressure air chamber 255 by turning the transmission gear in the reverse rotation state during traveling. it can. The amount of braking is adjusted by the truncated cone-shaped cylindrical valves 280 and 281.

  FIG. 10A is a longitudinal sectional view of an air liquefying apparatus 332 (Example 3) comprising a heat exchange air compressor 315 and a heat insulating expander 321 in which two rotors with variable volume are connected to a rotor on the short diameter side. It is. After driving through the universal joint 151 and compressing the air 900 taken from the opening 241 while exchanging heat, it is adiabatically expanded by the expander 321.

  An incompressible fluid trap 285 is provided below the heat exchange air compressor 315 and the heat insulating expander 321 to capture dew condensation water 991, liquid carbon dioxide 992, and the like. The incompressible fluid trap 285 is discharged by opening the valve as appropriate. As the expansion proceeds, the temperature is decreased and separated into liquefied oxygen 993 and a low-temperature gas 904 mainly composed of nitrogen. The low-temperature gas 904 circulates in the spiral flow path 243 outside the stator of the heat exchange compressor 315, performs opposed heat exchange, and is discharged from the discharge port 240.

  The return pipe 244 connecting the cavities provided in the stator 2 of the heat exchange air compressor 315 moves air from a cavity having a high pressure to a cavity having a low pressure. The air ejected into the cavity generates convection and improves the efficiency of heat exchange. Since air moves in the direction opposite to the direction of movement of the cavity, heat exchange efficiency is improved at the expense of transfer efficiency. By providing a throttle valve on the return pipe 244, adjustment can be performed during operation. The return pipe can also be provided in the rotor 1. By directly connecting the heat exchange air compressor 315 and the rotor of the adiabatic expander 321, part of the energy required for compression can be recovered.

FIG.10 (b) is a longitudinal cross-sectional view of the air conditioner 331 (Example 4) which does not use a refrigerant | coolant.
Air 900 is taken in from the suction port 241 and compressed by the adiabatic compressor 311. Although the compressed air becomes a high temperature, heat is exchanged with the air branched in the middle of compression with the counter-flow heat exchanger 571, and then adiabatic expansion is performed with the adiabatic expander 321, thereby forming the cooling air 930.
High-temperature air 910 and cooling air 930 can be simultaneously formed in the two discharge ports 240. One is blown indoors and used for heating or cooling, and the other is discharged outdoors. (The efficiency can be further improved using the thermal energy recovery device of FIG. 14 (a) or the cold energy recovery device of FIG. 14 (b).)
The combined variable volume single-shaft eccentric screw pump 33 is driven by a motor 161 through a gear 154 at the center. Considering that the rotor 1 rotates eccentrically, the gear 154 needs to be manufactured.

FIG. 11 is a longitudinal sectional view (a) of the water vapor expander 322 (Example 5) and an explanatory view (b) of the joint portion of the rotor 1 and the gear 154.
FIG. 11A shows a steam expander 322 for power generation constituted by a variable volume uniaxial eccentric screw pump 3 having an actual volume ratio of 3.5 times and a generator 165.
The stator 2 is rotatably installed by two sets of bearings 151 and is rotated at a speed that is half of the rotational speed of the rotor 1 inserted therein.

  High-temperature and high-pressure steam 911H is introduced from the steam generator into the dilator inlet 241. The rotor 1 and the stator (outer rotor) 2 are rotated in the direction in which the volume of the cavity is increased by the high pressure and expansion force of the high-temperature and high-pressure steam 911H. The high-temperature and high-pressure steam 911H is adiabatically expanded to convert heat energy into rotational force. The rotational force drives the generator 165 connected to the gear 154 and the drive shaft 152 to obtain electric power. The low-pressure steam 901 whose temperature has been lowered is led to the condenser.

  FIG. 11B shows a state of the cross section 63 of the joint portion between the rotor 1 and the gear 154. The pitch circle 65 of the internal gear 254 of radius 2e fixed to the stator 2 and the gear circle 154 of diameter 2e fixed to the rotor 1 is meshed at the upper portion as indicated by broken lines, and the stator 2 is centered on the central axis 60. The rotor 1 rotates at a ratio of 1: 2 around the rotation axis 61 of the fixed rotor.

Although the stator 2 rotates, since the rotor 1 can rotate without precession (eccentric movement), there is a feature that there is little vibration.
Both the stator 2 and the rotor 1 need to be balanced against the rotation axis. Particularly, since the mass of the end portion of the rotor 1 is large, adjustment such as making the inside hollow is necessary.

FIG. 12 is a longitudinal sectional view (a) and an in-vehicle image (b) of the internal combustion engine 335 (Example 6).
Two volume-variable single-shaft eccentric screw pumps are arranged as rotation targets as a compressor 31 and an expander 32, and are coupled on the short diameter side to form a high-pressure air chamber 255 at the center. The rotating shaft of the rotor 1 and the center line of the stator 2 are arranged in a straight line and are directly connected. Power is transmitted from the long diameter side of the dilator 32 to the drive shaft 152 via the universal joint 151.
A plurality of matching valve openings 24 are provided in a spiral projecting portion of the stator 2, and truncated cone-shaped cylindrical valves 280 and 281 are arranged. The frustoconical cylindrical valves 280 and 281 have a structure in which the opening 24 is opened in order from the larger cavity by rotation thereof. FIG. 12A shows a state where approximately half is open.

  In starting, the start valve 288 is opened, the compressed air accumulated in the high-pressure air chamber 155 is introduced into the expander 32, and the rotor 1 is rotated by the pressure. Further, fuel is injected from the fuel supply tube 261 and ignited by the ignition device 263. Combustion proceeds in a cavity filled with high pressure air. As the rotor 1 rotates, the volume of the cavity gradually increases, burns over a sufficient time, and adiabatic expansion of the combustion gas. The thermal energy of combustion gas is efficiently converted into rotational force as expansion force. Unlike the piston engine, there is no part that reciprocates between the low temperature part and the high temperature part, and combustion is always performed in the same part. After starting, the air taken in from the suction port 241 is compressed by the compressor 31 and reaches the expander 32. Then, the starting valve 288 is closed, and a steady operation state is obtained.

  Unlike a piston engine, the cavity volume increasing rate is small, and a pressure relaxation chamber 264 is provided to relieve a rapid pressure increase in the cavity caused by combustion. Arranged in the moving direction of the cavity where combustion starts, a part of the wall surface of the stator is pushed into the pressure relaxation chamber as a piston as the pressure increases due to combustion, and a sudden pressure rise is alleviated. When the volume increases with the movement of the cavity and the pressure decreases, the combustion gas is pushed back into the cavity by the force and back pressure of the spring built in the pressure relaxation chamber 264.

  The compression stroke of air is adjusted by rotating the truncated cone 281 attached to the compressor 31. By rotating the frustoconical cylinder 280 attached to the dilator 32, the expansion stroke can be adjusted. Since the amount of compressed air, the amount of fuel input, and the expansion stroke can be changed in a wide range, the rotational speed and the generated torque can be adjusted in a wide range. During operation, the control valve 287 is opened, and the high-pressure air chamber 155 is filled with compressed air. By stopping the fuel supply and opening the control valve 287, braking and regenerative operations can be performed. In the stop state, the control valve 287 is opened, high-pressure air is sent to the compressor 31 and operated as an expander, so that it can be rotated in reverse and the vehicle can be moved backward.

The rotor 1 is manufactured so that the center of gravity of the rotor 1 is on the rotation axis and the center of gravity of the stator 2 is on the center axis. When two single-shaft eccentric screw pumps are integrated, the center of gravity exists substantially at the center, but rotational blur due to precession of the rotor becomes a problem. Vibration can be canceled by supporting on a straight line that is a mass ratio between the eccentric shaft and the central shaft. (To counteract the precession of the rotor by hanging the stator in the opposite direction.)
An anti-vibration crank 151 shorter than the eccentric radius e, and an anti-vibration support 253 that supports the stator 2 so as not to be affected by blur due to precession and so that the stator 2 does not rotate around the central axis. By shortening the length, vibration transmitted to the vehicle body can be reduced.

FIG. 13 is a longitudinal sectional view (a) of a remotely driven pumping pump 341 (Example 7) and an explanatory diagram (b) of the utilization method, an explanatory diagram (c) of a submarine resource collection pump 342 (Example 8), and It is the cross-sectional view (d) and longitudinal cross-sectional view (e) of the multitrochoid compressor 31c (Example 9).
FIG. 13 (a) uses a variable volume uniaxial eccentric screw pump 3 to form a remotely driven pumping pump 341 having a head exceeding 10 m as shown in FIG. 13 (b). A part of the pumped water is supplied to the drive fluid supply port 242 of the remote drive pump 34 by the pump 501. Since the force which expands a cavity by the applied water pressure acts, the rotor 1 is rotated while sucking water below the water surface 75 and pumped.

  In the case of a Mono pump, the length of the cavity is equivalent to one wavelength of the stator, that is, two wavelengths of the rotor, and the distance between the cavities is one wavelength of the rotor. If so, there will always be only one closed cavity. When the wavelength is shorter than 3 wavelengths, the cavity in the water supply may be in a released state, and when the wavelength is longer than 3 wavelengths, the water is not supplied to the cavity. In this embodiment, the length is longer than three wavelengths and two check valves 283 are arranged to avoid the occurrence of dead center.

  When the effective volume ratio of the closed cavity is 2, the amount of pumped water can pump twice as much water as the amount pumped from the pump 501. When the pump 501 is not filled with water at the time of starting, it is necessary to send out air at a high pressure and start pumping. The pump 501 is suitably a uniaxial eccentric screw pump having a constant cavity volume.

FIG. 13C is an explanatory diagram of the seabed resource extraction pump 342 (Example 10) that pulls up the seabed resource mud 76 from the offshore resource drilling ship 513 by using the remote drive pump 34. The multiple trochoid compressor 31c and the air compressor 311 installed in the resource excavation ship 513 send high-pressure air corresponding to the water pressure of the seabed through the tube 841 to the driving fluid supply port 242 of the seabed resource extraction pump 342 on the seabed.
The multiple trochoid compressor 31c uses a 5-fold trochoidal rotor and has a two-to-one relationship by setting the number of teeth to the innermost circumference 4 and the outermost circumference 8. Since the eccentric shaft can be shared with the air compressor 311 which is a Mono type uniaxial eccentric screw pump, and the cross-sectional area through which the compressive fluid can pass can be increased, a large amount of air can be taken in. (The driving method and the like are omitted in the figure.)
In order to use it as a compressor, it is an indispensable condition to form a closed cavity. However, when the flow rate is restricted in the subsequent stage, if there is one closed part, the compressive fluid is compressed. I can do it. (When used for applications where compression is not intended, such as a blower, there is a feature that if one place is closed, the reverse wind can be cut off, stable blowing can be performed, noise can be cut off, etc.) In consideration of this, appropriate design is possible, such as changing the passage area and wavelength (pitch).)
The submarine resource collection pump 342 has a fin 166 attached to the tip of the rotor 1 of the remote drive pump 34 in FIG. 13 (a), scoops off the seabed resource mud 76, and sucks it into the submarine resource collection pump 342. ing.

  Note that the check valve 283 does not need to be provided in a situation where the rotor 1 is rotated by high water pressure at the sea bottom even when driven by high-pressure air and the inside of the cavity is in a vacuum state. A mechanism for increasing the number of cavities, increasing the expansion ratio, rotating the rotor 1 at a low speed under high water pressure, and a mechanism for stopping the rotation of the rotor as necessary are necessary.

  When the rotor 1 rotates, in the cavity of the seabed resource extraction pump 342, the resource mud, the seawater, and the high-pressure air fed from the sea are sequentially layered and pushed up. When the top of the cavity is opened, air is first sent to the tube 840. Next, seawater and resource mud are pushed into the tube 840. When the rotation of the rotor 1 proceeds and the next cavity is released, high-pressure air is ejected, so that the seawater and the resource mud 76 are pushed up by the pressure of the high-pressure air.

  The resource mud 76 having a high viscosity rises as the bullet advances in the barrel of the air gun while maintaining its shape. Since it repeats every time the cavity opens, high-pressure air and resource mud rise alternately. Since the weight of air is small, the load required for operation is reduced. The submarine resource mud 76 reaches the resource excavation ship 513 in a short time and is separated from the air in the ship. The seabed resource mud 76 is often mixed with a large amount of seawater and pumped out. However, separating the seawater and the resource mud requires a very difficult operation. Since air and mud can be easily separated, environmental destruction caused by resource mining can be reduced.

FIG. 14 is a longitudinal sectional view (a) of the thermal energy recovery device 351 (Embodiment 10), an explanatory view of application to wind power generation (b), and a longitudinal sectional view (c) of the cold energy recovery device 345 (Embodiment 11). It is.
FIG. 14A shows a thermal energy recovery device 351 configured by a pressure transducer 35 in which the compressor 31 and the expander 32 are integrated by sharing an eccentric shaft. The direction of the spiral of the stator 2 and the rotor 1 is reversed on the left and right from the position of the arrow 900. (Direction of rotor side 2s is different)
The pressure transducer 35 shown in FIG. 7 (e) has a structure capable of exchanging heat from an external heat source fluid.

The heat source fluid 92 is sucked from the suction port 141A, travels around the spiral flow path 243 around the stator 2 of the dilator 32, transfers heat to the stator 2, and exhausts the heat source fluid from the discharge port 240A at a temperature close to the outside air temperature. 95. When the stator 2 is heated and the air in the cavity expands, the rotor 1 starts to rotate. The air 900 taken from the central suction port 241B is divided into right and left, and the air that has advanced to the right is heated and expanded to become high-temperature air 910, and then turns around the spiral flow path from the center of the dilator 32. Then, the heat is returned to the stator 2, and the low-temperature air is exhausted 95 from the discharge port 240B. On the other hand, the air that has advanced to the left is compressed by the compressor 31 to produce high-temperature high-pressure air 910H, and is discharged from the discharge port 240C through the check valve 283.
Both the heat source fluid 92 and the hot air 910 travel around the spiral flow path 243, but the paths are different and do not mix. In consideration of the temperature distribution of the dilator 32, the position where the hot air 910 is folded is determined.
The inner surface of the stator 2 of the dilator 32 and the surface of the rotor 1 are not smooth, but have a stepped shape that rotates every 30 degrees. Its shape does not hinder the rotation of the rotor, increases the surface area of the heat exchange, and stirs the air inside the cavity to make the heat exchange efficient. The heat exchange expander 325 is an external combustion engine such as a Stirling engine, but is an open type heat engine that does not require a heat exchanger on the cold heat source side.

FIG. 14B is an explanatory diagram for effectively using the thermal energy recovery device 351 in the wind energy utilization system. The compressor 31 is driven by a wind turbine propeller 262 to generate high-pressure air. At this time, a large amount of heat is generated due to adiabatic compression. Although high-pressure air can be stored in the compressed air tank 551, it is one of the factors that hinder the efficient use of natural energy because it is difficult to store heat.
The high-temperature and high-pressure air produced by the wind turbine compressor 31 is sent to the suction port 241A of the thermal energy recovery device 351 as the heat source fluid 92H, and discharged to the discharge port 240A through the spiral flow path 243. Heat exchange is performed with the air 900 taken from the suction port 241B, and the expansion force of the air is changed to a rotational force. High-pressure air 910H is produced by the compressor 31 from this rotational force. Since this high-pressure air 910H also contains heat, it is mixed with the heat source fluid 92H, recovered again, and then sent from the discharge port 240A to the high-pressure air tank 551 for storage. In order to store high-pressure air, a high-pressure air tank is sufficient, and it is not necessary to use scarce and expensive resources like a secondary battery, so an economically large-scale system can be constructed.

FIG. 14C shows a cold energy recovery unit 345 composed of heat exchange compressors 315A and 315B sharing a central axis and an eccentric axis.
The cold heat source fluid 930 is sucked from the opening 241A, travels around the spiral flow path 243A in the heat exchange compressor 315A, cools the air in the cavity, and exhausts 95 from the opening 240A. The air in the cavity is cooled to reduce the volume, thereby rotating the rotor 1. The air whose temperature has dropped from the cavity passes through the path C, circulates through the spiral flow path 243A, is used for precooling the cavity, and then exhausts 95 from the discharge port 240C.
By rotating the rotor of the compressor 315B, the air 900 taken in from the opening 141B is compressed, and after passing through the counterflow heat exchanger 571, the high-pressure air 910H is discharged from the discharge port 240B. The air 900 taken from the opening 241C is passed through the counterflow heat exchange 571 to recover the heat, and a temperature difference is ensured and returned to the heat exchange compressor 315A.
A partition plate 171 is provided between the heat exchange compressor 315A and the compressor 315B so that the working fluid is not mixed.

FIG. 15: is the longitudinal cross-sectional view (a) of solar energy recovery device 352 (Example 12), explanatory drawing (b) of a utilization method, and explanatory drawing (c) of the utilization method in outer space.
FIG. 15A shows a structure in which the stator 2 is exposed in order to recover solar energy by modifying the thermal energy recovery unit 351 of FIG. By concentrating sunlight 71 on the exposed portion of the stator 2 to a high temperature, the air inside the heat exchange expander 325 is expanded and the rotor 1 is rotated. Air 900 is sucked from the suction port 241A, and the cavity of the dilator 325 is expanded. The discharged hot air 910 is turned back and used for preheating the expander 325, and the temperature is lowered to exhaust 95 from the discharge port 240A.

  The air 900 sucked into the compressor 31 from the suction port 241A is compressed by the rotation of the rotor 1 to become high-temperature and high-pressure air 910H, and is discharged from the discharge port 240B. The efficiency can be increased by sending it again to the heat exchange expander 325 and using it for preheating, but this illustration is omitted because the explanatory diagram becomes complicated. In addition, the surface of the heat collecting part of the heat exchange expander 325 is made into a small pyramid shape, and the surface is processed black so that the sunlight 71 can be efficiently absorbed and the sunlight is not taken away by the atmosphere. It is desirable to protect with a heat insulating material that permeates.

  FIG. 15B is an overall explanatory diagram of the solar energy utilization system. A concave reflector 514 capable of tracking the sunlight 71 and a solar energy recovery device 352 are disposed at the focal point thereof. There is also a light collecting method in which the solar energy recovery device 352 is in the shape of an upright tower and a large number of movable mirrors that can be tracked are arranged around the periphery. The high-pressure air is sent to a high-pressure air tank 551 disposed nearby and stored. Compared with solar panels using semiconductors, the present solar energy utilization system has the feature that energy can be stored as high-pressure air at a low cost and can flexibly respond to fluctuations in demand. Electric power can be obtained from the accumulated high-pressure air by the compressed air drive generator 324 configured by the variable volume uniaxial eccentric screw pump 32 and the generator 165.

  FIG. 15C illustrates a method of using the solar energy recovery device 352 in outer space. Since the atmosphere cannot be used, it is necessary to prepare a radiator 573 and a large-sized low-pressure air tank 550 on the cold heat source side. It arranges behind the reflector 514 where sunlight does not hit. Using the pressure difference between the compressed air tank 551 and the low pressure air tank 550, electric power is obtained by the compressed air drive generator 324 configured by the variable volume uniaxial eccentric screw pump 32 and the generator 165.

FIG. 16: is a longitudinal cross-sectional view (a) of geothermal energy recovery device 353 (Example 13), and explanatory drawing (b) of the usage method.
In FIG. 16A, the thermal energy recovery device 351 is deformed to have a structure in which the stator 2 is exposed, and a spiral flow path 143 is provided inside the rotor 1 as a return path for the high-temperature air 910.
The rotor 1 is rotated by the expansion force of the air in the cavity heated to geothermal heat, and the heated air 910 exchanges heat with the cavity through the spiral flow path 143 inside the rotor 1. The air is exhausted 95 from the discharge port 240A and led to the ground with a tube.
On the other hand, high-pressure air 910H produced by the compressor 31 is discharged from the discharge port 240B by the rotation of the rotor 1 and led to the ground.

FIG. 16B is an overall explanatory diagram of the geothermal utilization system. The ground 73 where geothermal heat can be expected is bored to make a hole, and the thermal energy recovery device 353 is inserted into the ground. Air 900 is sent from the ground to the geothermal energy recovery device 352 by the pump 50, and the high-pressure air 910H produced by the compressor 31 and the exhaust 95 from the discharge port 240A are guided to the ground. The high-pressure air 910H is stored in the high-pressure air tank 551.
When heat remains in the high-pressure air 910H and the exhaust 95, the heat energy recovery devices 351 shown in FIG.

  The geothermal energy recovery unit 353 is installed in the vicinity of the underground geothermal source 79 instead of taking out the high-temperature geothermal heat to the ground. can do. Environmental impact is low because volcanic gas is difficult to get out on the ground. It is necessary to send air as low as possible.

FIG. 17 is an explanatory diagram (a) of a high-pressure air utilization system (Example 14), a longitudinal sectional view (b) of a heat exchange expander 325 (Example 15), and a compressible fluid pressure regulator 351 (Example 16). It is explanatory drawing (c).
The high-temperature and high-pressure air adiabatically compressed by the compressor 31 of the city gas engine 336 in FIG. 17A is stored in the high-pressure air tank 551 by lowering the temperature via the high-temperature heat accumulator 545 or the thermal energy recovery device 351. .
When there is a demand for hot water, it is appropriate to install and store the hot water storage tank 541 and use it directly without changing the heat to high-pressure air. Hot water in the hot water storage tank 541 is used for hot water supply from a hot water supply pipe 811 to a bath or the like. When hot water in the hot water storage tank 541 is used, water is supplied from the water pipe 81. Heat is transferred from the high temperature regenerator 545 to the hot water storage tank 541 by natural circulation of high temperature air and the heat exchanger 325.

As this other high-pressure air source, the high-pressure or high-temperature high-pressure air by the energy recovery device of Examples 10 to 13 such as wind or sunlight can be used.
The high-pressure air in the high-pressure air tank 551 is increased in temperature through the high-temperature heat accumulator 545 to be high-temperature high-pressure air 910H, which can be used as a heat source for floor heating 524, nozzle blower 525, warm storage, various dryers, and the like. Unlike the hot water type, since the heat source fluid 91 is the high temperature air 910, it is not necessary to circulate and can be discharged into the room after use, so that it can be used easily.

The city gas engine 336 of FIG. 17A is configured by the compressor 31 and the expander 32 that share the rotation axis by making the eccentric radius e constant and reducing the diameter Dr at the center.
In starting, an appropriate amount of gas is fed into the closed cavity of the dilator 32, ignited and burned, and the rotor is rotated. The compressed air is branched from the middle of the compressor 31. When compressed air is sent into the dilator 32, a predetermined compression ratio is ensured, and an efficient steady operation is performed. Since the city gas engine 336 stops in a state where the combustion gas is discharged, a starter such as a starter motor can be omitted.

FIG. 17B shows a longitudinal sectional view of a heat exchanger 325 using a variable volume uniaxial eccentric screw pump. It consists of a dilator 32 and a spiral channel 243 with an actual volume ratio increasing upwards of 1.02, and counter-flow heat to the heat source fluid 92 (hot air 910 or 910H) and the water in the cavity The rotor 1 is rotated by the volume increase accompanying the temperature change of water.
The heat source fluid 91 is assumed to greatly exceed 100 ° C. However, when the heat source fluid 91 is a heat source whose temperature and flow rate vary depending on the state of the heat supply source, in a general heat exchanger, the water in the hot water storage tank 541 is not boiled. It is difficult to heat to 95-98 ° C. The heat exchanger 325 using a variable volume single-shaft eccentric screw pump changes its rotation speed in proportion to the temperature of the water. When bubbles are generated inside, the rotation becomes faster and the water 991 is pumped up in an appropriate amount. There is no stable water heater. (The volume ratio needs to be adjusted.)

  The high-temperature and high-pressure air pipe 802, the high-pressure air outlet 805, the equipment using high-temperature and high-pressure air, and the hose connected to these have a double structure, and air at normal temperature is allowed to flow outside, It is structured to prevent the temperature from becoming high. A compressible fluid pressure regulator 350 shown in FIG. 17 (c) is incorporated in a device that uses high-temperature and high-pressure air, and the pressure is adjusted by a frustoconical matching valve 281. Air is sucked and cooled from the air flow path, and the fluctuating pressure is adjusted to be constant.

The high-pressure air in the low-temperature high-pressure air pipe 801 in FIG. 17A can be used as a power source for a compressed-air vehicle, a compressed-air tool, a nozzle-type blower 525, and the like. The generator 165 connected to the dilator 32 using a universal joint can be converted into electric power. The air whose temperature has been reduced by reducing the pressure can be used as a cooling heat source for cooling and refrigerators.
By operating the switching gear 159, disconnecting the generator 165 and driving the compressor 31, high-temperature and high-pressure air is created, heat is exchanged with room air using the counter-flow heat exchanger 571, and the high-temperature air 910 is Can be used for heating etc. The cooling air 930 can be recovered as high-pressure air by exhausting the outside of the room or using the cold energy recovery device of Example 11. The high-pressure air is effectively used for driving the dilator 32 again.

The electric power of the generator 165 is fed to the distribution line 831 as a direct current having a maximum voltage of 160 V, and has a characteristic that the voltage decreases with the upper limit of the supplied power as the current increases. The commercial power 83 is changed by the rectifier 53 from a direct current having an average voltage of 100V to 110V, and the distribution line 831 is also fed. The LED luminaire 521 with a built-in inverter operates with a DC voltage in the range from 80V to over 160V. The electric power of the generator 165 is preferentially used, and the insufficient electric power is automatically supplied from the rectifier 53.
The rectifier 53 is composed of only a rectifier and has almost no standby power. Although not described in FIG. 17A, when a large amount of power supply is required, an inverter type power supply device can be activated to supply a large amount of power.

Further, the power of the solar cell panel can be supplied to the distribution line 831. Also in this case, the voltage decreases with the upper limit of the supplied power as the current increases. When the voltage of the distribution line 831 exceeds 150V, it is determined that there is surplus power, so the DC / AC power converter 51 is activated and sold to the commercial power 83.
Many electronic devices that incorporate an inverter power supply device that operates at an AC voltage of 100 V can be easily changed in design to operate at both an AC voltage of 100 V and a DC voltage of 80 to 160V. A power plug that is upwardly compatible with the AC outlet is used to connect to the DC outlet 835 for use.

  High pressure air can be separated into air with different temperatures up to plus 50 degrees and minus 50 degrees using vortex tube 56. The refrigeration / warm storage 523 using the vortex tube 56 can use hot and cold simultaneously. There is also a usage method in which one of the heat source and the cold heat source is used and the other is exhausted outdoors. The vortex tube can create high-temperature and low-temperature air by a simple method, and the principle is described in Non-Patent Document 7.

FIG. 18 is a longitudinal sectional view (a) of a temperature difference drive integrated generator 361 (Example 17) using the generator integrated expander 36, and a longitudinal section of the compressed air drive integrated generator 362 (Example 18). It is the cross-sectional view (c) and longitudinal cross-sectional view (d) of a surface view (b) and a heat recovery panel type generator (Example 19).
A temperature difference drive generator 361 in FIG. 18A is an expander 36 with a volume ratio increasing upwards of 1.01, and an electromagnetic coil 249 is wound around the stator 2 made of an insulator. The rotor 1 is equipped with a magnet 149.
The air in the cavity is heated by the heat of sunlight or the like to increase the volume, thereby rotating the rotor 1 in which the magnet 149 is embedded, generating electric power by the electromagnetic coil 249 by electromagnetic induction action, and outputting it to the electrode 583. (The power generation function can also be used as a monitor for the rotation state of the rotor. If only the rotational force is used, the power generation function is not necessary.)
It is necessary to suck in as cool air as possible from the opening 241.

FIG. 18B shows a portable compressed air generator using the expander 32 having a large volume ratio utilizing the expansion force of compressed air.
An insulator material is used for the stator 2, an electromagnetic coil 249 is wound around the stator 2, a part of the rotor 1 is used as a magnet 149, and a compressed air cylinder 552 is integrated to form an air-driven generator 362.
For portable use, it can be used anywhere like a battery, can be filled with compressed air in a short time from an air filling port 582 with a check valve, and has a shape in which a plurality of cylindrical cylinders are arranged. The connection to the device is performed by an electrode 583 in the opening 24, and a rotation inhibiting mechanism of the rotor 1 is released by pushing a pipe that also serves as ventilation and pushing a lock fitting 584.
Since the air discharged from the discharge port 240 has a reduced temperature, it can be used for cooling the electronic circuit. The output can be increased by circulating the air inside the apparatus to circulate the air whose temperature has risen and heating the compressed air cylinder 552. Since the pressure inside the device casing increases, it contributes to the waterproof property of simple waterproofing. In the case of a completely sealed waterproof device, it is necessary to be able to release air from a check valve or similar structure.
It is conceivable to embed the magnet 149 in the rotor 1 to obtain electric power for driving the electronic circuit, or to directly use the rotational force of the rotor.
Compressed air cannot supply a large amount of power because of its low energy density, but it can be used with peace of mind in environments where air can be filled at any time, without having to worry about battery degradation.

18C and 18D are a cross-sectional view and a vertical cross-sectional view of one unit of the heat recovery panel generator 363, respectively. A large number of panels are arranged and attached to a heat source or used like a solar panel.
A trochoid expander 32c is constituted by a spiral trochoid rotor 1c (r5, r6) having 5 and 6 teeth, a magnet 149 is arranged on the outer rotor 1c (r6), and an electromagnetic coil 248 is arranged on the housing 29. It constitutes a generator.
The closed cavity generated between the two trochoidal rotors 1c increases in volume toward the right in FIG. 18 (d). There are gaps between the rotor 1c, the casing 29, and the central shaft 150 so that the rotor 1c can freely rotate. Radiant heat is applied from the heat receiving panel 291 side to heat and expand the internal air. Heat exchange with the rotor 1c is performed while passing through the spiral flow paths 143 and 243. As the compressive fluid in the cavity expands, the rotor 1c rotates in a direction in which the volume increases, and power generation starts. Although the circulation of the compressive fluid and the heat is quick, heat exchange is performed in the rotor 1c, so that the heat is confined.
The heat that has not been heat exchanged is dissipated from the panel 290. A method in which the panel 290 is omitted and opened is also conceivable.
Since the expansion ratio of the trochoidal rotor 31c in FIG. 18D is large, a large temperature difference is necessary for driving. Although it is possible to design a small expansion ratio, in order to operate with a small temperature difference, it is necessary to use a magnetic fluid bearing to eliminate the effects of rotational friction and to increase the sealing of the cavity There is. In addition to a method that uses a liquid such as oil to make the surface easy to be familiar with the liquid, the opposing surfaces of the two rotors 1c are magnetized and processed so as to be an N pole and an S pole, respectively, thereby increasing the degree of adhesion. At the same time, a method of obtaining a sealing property at the fitting portion using a magnetic fluid is conceivable.
The surface of the rotor 1c, in which the panel 291 is made transparent, a counter flow path is provided inside the housing 29, a condensing reflector 514 is provided, in order to guide sunlight, radiant heat, and a compressive fluid whose temperature has risen to the center as much as possible. Is colored black.

  In addition to being used as a compressor for air conditioners, refrigerators, and freezers, by increasing the number of cavities, it is possible to handle large pressure differences that cannot be handled by conventional pumps. Since it is a positive displacement pump, it is possible to operate with high efficiency at an extremely low speed and to perform compression and expansion of thermodynamically ideal gas, so that it can be used as an efficient engine. In addition to bringing about thermodynamic reforms, it can be applied to the collection of natural energy and resources in a completely new way that is different from conventional methods.

1 Rotor (inner rotor)
1a Oval rotor 1b Wankel rotor
1c Trochoidal rotor 1d Elliptic arc rotor
DESCRIPTION OF SYMBOLS 10 Rotor cross section 11 Rotor vertical cross section 1s Rotor side surface and external appearance 143 Spiral flow path in rotor 148 Electromagnetic coil 149 Magnet 151 Universal joint 152 Drive shaft 153 Anti-vibration crank 154 Gear 159 Switching gear 161 Electric motor 162 Propeller 165 Generator 166 Fin 171 Partition plate

2 Stator (outer rotor)
2a Tricam-type stator 2b Wankel-type stator
2c Trochoid type stator 2d Cardioid type stator
20 Stator cross section 21 Stator vertical section 2 s Stator side face / appearance 24 Opening 240 Discharge port 241 Suction port 242 Drive water supply port
243 Spiral channel 244 Return pipe 248 Electromagnetic coil
249 Magnet 250 Support roller 253 Anti-vibration support 254 Internal gear 255 Air chamber 261 Fuel supply tube 263 Ignition device
265 Pressure relief chamber
28 Alignment valve 280 Frustum-shaped cylindrical alignment valve
281 Frustum-shaped cylindrical alignment valve (suction side) 28s Appearance of frustum-shaped alignment valve
283 Check valve 284 Check valve (open) 285 Incompressible fluid trap
287 Control valve 288 Start valve
29 Housing (outer shell) 290 Heat radiation panel 291 Heat receiving panel 299 Heat insulation material

3 Volume-variable uniaxial eccentric screw pump or volume-variable uniaxial screw pump
3a Tricam type 3b Wankel type
3c Trochoid type / Multiple trochoid type 3d Cardioid type
31 Compressor 311 Adiabatic Compressor 312 Vacuum Pump
315 Heat Exchange Compressor 31c Multiple Trochoid Compressor 32 Expander 321 Insulation Expander 322 Steam Expander
323 Compressed air engine 324 Air engine generator 325 Heat exchange expander 326 Gas engine 32c Trochoid expander
33 Physical / Chemical Reactor 331 Air Conditioner 332 Air Liquefaction Device 335 Internal Combustion Engine 336 Gas Engine
34 Remote drive pump 341 Remote pumping pump 342 Seabed resource extraction pump 345 Cold energy recovery unit
35 Compressible fluid pressure transducer 350 Compressible fluid pressure regulator
351 Thermal energy recovery device 352 Solar energy recovery device
353 Geothermal energy recovery device 361 Temperature difference drive generator
362 Compressed air drive generator 365 Electric blower
372 Compressed air driven hot / cold heat source
38 Physical / Chemical reactor (Part 2)

50 Pump 501 Uniaxial eccentric screw pump (constant volume)
50c Internal gear pump (constant volume, trochoid type, etc.) 51 DC / AC power converter 511 Rectifier 513 Resource drilling vessel 514 Solar condensing reflector
521 LED lighting fixtures 523 Refrigerated / hot storage 524 Floor heating
525 Nozzle blower 53 Vacuum container 531 Vacuum chamber
532 Vacuum Freeze Drying Chamber 541 Hot Water Storage Tank 545 High Temperature Regenerator
55 Air storage container 550 Low pressure air tank 551 High pressure air tank
552 Compressed air cylinder 56 Vortex tube
571 Counterflow heat exchanger 58 Valve 582 Air filling port with check valve
583 Electrode 584 Unlocking metal fittings 59 Heat insulation and heat insulation

60 Central axis 61 Eccentric shaft (rotor rotational axis) 610 Eccentric shaft locus
62 Position of transverse section 63 Circle (spherical section) centering on the intersection of the central axis and the eccentric axis
64 Intersection of central axis and eccentric shaft 65 Gear (gear) pitch circle

71 Sunlight 72 Wind 73 Ground 74 Geothermal Source 75 Water Surface
76 Submarine resource mud

80 Air piping 801 Low pressure air piping 802 High temperature high pressure air piping
803 Normal pressure air flow path 805 High pressure air outlet 806 High pressure air plug 81 Water pipe 811 Hot water supply pipe 82 City gas pipe 83 Commercial power 831 DC power distribution 835 DC outlet
840 Tube up 841 Tube down

90 Compressible working fluid 900 Air 900H High pressure air
901 Low temperature steam 904 Nitrogen gas
91 Heat source fluid 910 High temperature air 910H High temperature high pressure air
911 high temperature steam 911H high temperature high pressure steam 930 cooling air
95 Exhaust 99 Incompressible fluid 991 Water 992 Liquid carbon dioxide 993 Liquid oxygen 994 Liquid nitrogen

JP 2013-53601 “Uniaxial Eccentric Screw Pump and Fluid Motor” Dainippon Screen Mfg. Co., Ltd. JP 2007-170374 "Axial volume worm gas generator" General Electric Company

Japanese Patent Application Laid-Open No. 2013-53601 “Uniaxial Eccentric Screw Pump and Fluid Motor” in Patent Document 1 proposes a constant volume uniaxial eccentric screw pump having a Wankel type cross section.
The uniaxial eccentric screw pump having a Wankel-type cross section is a variable volume uniaxial eccentric screw pump that can rotate while changing the volume as shown in the longitudinal sectional view of FIG. 6 (f) by changing the eccentric radius in the axial direction. Become. Each circle 63 centering on the intersection of the center axis 60 of the stator 2b and the rotation axis of the rotor 1b, that is, the eccentric shaft 61, shows the state of the cross section on the spherical surface at each position in the longitudinal sectional view (f) from (g1) ( g5). Although it is a spherical surface, it cannot be represented correctly on a plane, but the rotor 1b projected onto the spherical surface rotates eccentrically along each spherical surface 63 and is a stator defined by a peritrochoidal curve expanded on the spherical surface. It shows that the reciprocating motion is reciprocating in the bowl-shaped hole 2b. The volume can be varied by changing the wavelength λs (pitch) in addition to the eccentric radius e.
Non-Patent Literatures 5 and 6 introduce a cardioid type (h1), a Wankel type (h2), a higher order (h3), and a shape closer to a circle than the cardioid type (h4).
In Japanese Patent Application Laid-Open No. 2007-170374 “Axial Flow Displacement Warm Gas Generator” in Patent Document 2, as shown in FIG. 6 (h5), an epicycloid-shaped stator and a hypocycloid-shaped rotor are both substantially basic shapes. Things are used.

The graphics categorized in Tables 1 and 2 can be extended to constant-volume axial flow pumps (uniaxial eccentric screw pumps and uniaxial screw pumps with variable volume) by twisting them in the axial direction in a spiral manner. The area S obtained by subtracting the cross-sectional area of the rotor from the opening area of
S = T · e ²
Can be described.
Here, e is an eccentric radius, T is a shape constant determined by the shape, number of stripes, and combinations of the stator and rotor, and a number of elements such as the presence / absence and shape of the elliptical arc and the diameter Dc of the circle that generates the envelope It changes with.
When used as a uniaxial eccentric screw pump, the volume Q discharged per one rotation of the rotor of wavelength λr is expressed by the following equation.
Q = S · Ns · λr
= T ・ e ²・ Nr ・ λs
Here, Nr: number of rotor stripes, Ns: number of stator stripes, λs: length of one wavelength of the stator.
The MONO type shape constant T _M is such that the direction in which the rotor moves eccentrically and the direction in which the diameter Dr contributes are orthogonal,
T _M = 4 · Dr / e
If so, the MONO-type discharge volume Q _M has Nr of 1, so
Q _M = 4 · e · Dr · λs
Which is consistent with the equation for volume Q _M listed in paragraph 0006.
In addition, since it correct | amends with the envelope formed by rolling the circle | round | yen of diameter Dc, in the MONO type,
Dr = 2 · Dc
It is.
The length of the closed cavity is one wavelength for a hypocycloid stator and two wavelengths for an epicycloid stator (in the basic figure of two or more epicycloids, it is longer than two wavelengths, and the corrected one is The length of the stator is required depending on the correction method.
The discharge volume Q of the uniaxial screw pump that rotates the stator together with the rotor corresponds to the case where the difference between the rotation speeds of the stator and the rotor is 1.
The graphics classified in Table 1 and Table 2 and the graphics not arranged in the table are extended while spirally twisting in the axial direction, and the eccentric radius e, the shape constant T, and the wavelength λs ( By changing the (pitch), it can be expanded to a uniaxial eccentric screw pump and a uniaxial screw pump with variable volume.
Here, the eccentric radius e and the shape constant T in the axial direction (meaning that the diameter Dc of the circle used for correction is continuously varied. It is difficult to vary continuously by changing the basic shape). In addition, an axial flow screw pump (a variable volume uniaxial eccentric pump and a variable volume uniaxial screw pump) that can vary the volume of the cavity by changing the wavelength λs is proposed.

1 Rotor (inner rotor)
1a Oval rotor 1b Wankel rotor
1c Trochoidal rotor 1d Elliptic arc rotor
DESCRIPTION OF SYMBOLS 10 Rotor cross section 11 Rotor vertical cross section 1s Rotor side surface and external appearance 143 Spiral flow path in rotor 148 Electromagnetic coil 149 Magnet 151 Universal joint 152 Drive shaft 153 Anti-vibration crank 154 Gear 159 Switching gear 161 Electric motor 162 Propeller 165 Generator 166 Fin 171 Partition plate

2 Stator (outer rotor)
2a Tricam-type stator 2b Wankel-type stator
2c Trochoid type stator 2d Cardioid type stator
20 Stator cross section 21 Stator vertical section 2 s Stator side face / appearance 24 Opening 240 Discharge port 241 Suction port 242 Drive water supply port
243 Spiral channel 244 Return pipe 248 Electromagnetic coil
249 Magnet 250 Support roller 253 Anti-vibration support 254 Internal gear 255 Air chamber 261 Fuel supply tube 263 Ignition device
265 Pressure relief chamber
28 Alignment valve 280 frustoconical (cylindrical) alignment valve (discharge side)
281 Conical trapezoidal (cylindrical) matching valve (suction side) 28s Appearance of frustoconical (cylindrical) matching valve 283 Check valve 284 Check valve (open) 285 Incompressible fluid trap
287 Control valve 288 Start valve
29 Housing (outer shell) 290 Heat radiation panel 291 Heat receiving panel 299 Heat insulation material

3 Volume-variable uniaxial eccentric screw pump or volume-variable uniaxial screw pump
3a Tricam type 3b Wankel type
3c Trochoid type / Multiple trochoid type 3d Cardioid type
31 Compressor 311 Adiabatic Compressor 312 Vacuum Pump
315 Heat Exchange Compressor 31c Multiple Trochoid Compressor 32 Expander 321 Insulation Expander 322 Steam Expander
323 Compressed air engine 324 Air engine generator 325 Heat exchange expander 326 Gas engine 32c Trochoid expander
33 Physical / Chemical Reactor 331 Air Conditioner 332 Air Liquefaction Device 335 Internal Combustion Engine 336 Gas Engine
34 Remote drive pump 341 Remote pumping pump 342 Seabed resource extraction pump 345 Cold energy recovery unit
35 Compressible fluid pressure transducer 350 Compressible fluid pressure regulator
351 Thermal energy recovery device 352 Solar energy recovery device
353 Geothermal energy recovery device 361 Temperature difference drive generator
362 Compressed air drive generator 363 Heat recovery panel type generator 372 Compressed air drive hot and cold source
38 Physical / Chemical reactor (Part 2)

A throttle valve is generally used to adjust the air pressure. However, since the pressure loss when passing through the throttle valve is large, the energy of the compressed air cannot be fully utilized.
In the embodiment of FIG. 9A, a frustoconical (cylindrical) matching valve 281 is used, and the opening 24 is opened in order from the smallest of the cavities for each rotation angle, and high pressure air is filled. It has become.
In order to obtain the required torque, the cylindrical valve 281 is operated and adjusted so that the cavity corresponding to the load is filled with high-pressure air.

The frustoconical (cylindrical) matching valve 281 is required to have a structure that can be adjusted from the outside without being affected by the pressure of the high-pressure air chamber 255.
When the pressure in the high-pressure air chamber 255 decreases, the frustoconical (cylindrical) matching valve 281 is rotated and opened several stages to compensate for the decrease in rotational force.
A frustoconical (cylindrical) matching valve 280 is also provided on the discharge side, and can be adjusted to appropriately expand the compressed air.

A plurality of holes 24 are spirally formed along the projecting portion of the double thread of the stator 2 and are opened and closed by an opening 24 provided in a frustoconical (cylindrical) matching valve 28.
FIG. 9C is a sectional view including the opening 24 of the frustoconical (cylindrical) matching valve 28. The frustoconical (cylindrical) alignment valve 28 is rotated, and the cavity is opened when the opening 24 overlaps the opening 24 of the stator 2. The shapes of the spirally aligned openings 24 and the frustoconical (cylindrical) matching valve 28 of the stator 2 are similar to those of FIG. 9C (opening angle of the frustoconical (cylindrical) matching valve opening 24. Is different).

Since the temperature of the discharged air decreases during the expansion process, it can be used for indoor cooling.
By closing all of the frustoconical (cylindrical) matching valves 281, the inside of the cavity gradually becomes negative pressure and rotation is suppressed, so that a braking operation can be performed. A regenerative operation can be performed by rotating the rotor 1 of the compressed air engine 323 in the reverse direction by sucking and compressing the air and filling the high pressure air chamber 255 by turning the transmission gear in the reverse rotation state during traveling. it can. The braking amount is adjusted by the frustoconical (cylindrical) matching valves 280 and 281.

FIG. 12 is a longitudinal sectional view (a) and an in-vehicle image (b) of the internal combustion engine 335 (Example 6).
Two volume-variable single-shaft eccentric screw pumps are arranged as rotation targets as a compressor 31 and an expander 32, and are coupled on the short diameter side to form a high-pressure air chamber 255 at the center. The rotating shaft of the rotor 1 and the center line of the stator 2 are arranged in a straight line and are directly connected. Power is transmitted from the long diameter side of the dilator 32 to the drive shaft 152 via the universal joint 151.
A plurality of matching valve openings 24 are provided in the spiral projecting portion of the stator 2, and frustoconical (cylindrical) matching valves 280 and 281 are arranged. The frustoconical (cylindrical) alignment valves 280 and 281 are structured to open the opening 24 in order from the larger cavity by rotation thereof. FIG. 12A shows a state where approximately half is open.

By rotating a frustoconical (cylindrical) matching valve 281 attached to the compressor 31, the air compression stroke is adjusted. By rotating a frustoconical (cylindrical) matching valve 280 attached to the dilator 32, the expansion stroke can be adjusted. Since the amount of compressed air, the amount of fuel input, and the expansion stroke can be changed in a wide range, the rotational speed and the generated torque can be adjusted in a wide range. During operation, the control valve 287 is opened, and the high-pressure air chamber 155 is filled with compressed air. By stopping the fuel supply and opening the control valve 287, braking and regenerative operations can be performed. In the stop state, the control valve 287 is opened, high-pressure air is sent to the compressor 31 and operated as an expander, so that it can be rotated in reverse and the vehicle can be moved backward.

Inhalation of source fluid 91H from the intake port 241 A, the spiral flow path 243 around the stator 2 of the dilator 32 speculating, heat transferred to the stator 2, a heat source fluid from the discharge port 240A at a temperature close to ambient temperature The exhaust is 95. When the stator 2 is heated and the air in the cavity expands, the rotor 1 starts to rotate. The air 900 taken from the suction port 241B in the center is divided into left and right, and the air that has advanced to the right is heated and expanded to become high-temperature air 910, and then folds around the spiral flow path of the dilator 32, and the stator Heat is returned to 2, and the low-temperature air is exhausted 95 from the discharge port 240B. On the other hand, the air that has advanced to the left is compressed by the compressor 31 to produce high-temperature high-pressure air 910H, and is discharged from the discharge port 240C through the check valve 283.
The heat source fluid 91H and the hot air 910 both travel around the spiral flow path 243, but the paths are different and do not mix. In consideration of the temperature distribution of the dilator 32, the position where the hot air 910 is folded is determined.
The inner surface of the stator 2 of the dilator 32 and the surface of the rotor 1 are not smooth, but have a stepped shape that rotates every 30 degrees. Its shape does not hinder the rotation of the rotor, increases the surface area of the heat exchange, and stirs the air inside the cavity to make the heat exchange efficient. The heat exchange expander 325 is an external combustion engine such as a Stirling engine, but is an open type heat engine that does not require a heat exchanger on the cold heat source side.

FIG. 14B is an explanatory diagram for effectively using the thermal energy recovery device 351 in the wind energy utilization system. The compressor 31 is driven by a wind turbine propeller 262 to generate high-pressure air. At this time, a large amount of heat is generated due to adiabatic compression. Although high-pressure air can be stored in the compressed air tank 551, it is one of the factors that hinder the efficient use of natural energy because it is difficult to store heat.
The high-temperature and high-pressure air produced by the wind turbine compressor 31 is sent to the suction port 241A of the thermal energy recovery device 351 as the heat source fluid 91H , and discharged to the discharge port 240A through the spiral flow path 243. Heat exchange is performed with the air 900 taken from the suction port 241B, and the expansion force of the air is changed to a rotational force. High-pressure air 910H is produced by the compressor 31 from this rotational force. Since this high-pressure air 910H also includes heat, it is mixed with the heat source fluid 91H and recovered again, and then the high-pressure air 900H is sent from the discharge port 240A to the high- pressure air tank 551 for storage. In order to store high-pressure air, a high-pressure air tank is sufficient, and it is not necessary to use scarce and expensive resources like a secondary battery, so an economically large-scale system can be constructed.

The high-temperature and high-pressure air pipe 802, the high-pressure air outlet 805, the equipment using high-temperature and high-pressure air, and the hose connected to these have a double structure, and air at normal temperature is allowed to flow outside, It is structured to prevent the temperature from becoming high. A compressible fluid pressure regulator 350 shown in FIG. 17 (c) is built in a device using high-temperature and high-pressure air, and the pressure is adjusted by a frustoconical (cylindrical) matching valve 281. Air is sucked and cooled from the outside atmospheric pressure air flow path, and the fluctuating pressure is adjusted to be constant.

18C and 18D are a cross-sectional view and a vertical cross-sectional view of one unit of the heat recovery panel generator 363, respectively. A large number of panels are arranged and attached to a heat source or used like a solar panel.
A trochoid expander 32c is constituted by a spiral trochoid rotor 1c (r5, r6) having 5 and 6 teeth, a magnet 149 is arranged on the outer rotor 1c (r6), and an electromagnetic coil 248 is arranged on the housing 29. It constitutes a generator.
The closed cavity generated between the two trochoidal rotors 1c increases in volume toward the right in FIG. 18 (d). There are gaps between the rotor 1c, the casing 29, and the central shaft 150 so that the rotor 1c can freely rotate. Radiant heat is applied from the heat receiving panel 291 side to heat and expand the internal air. Heat exchange with the rotor 1c is performed while passing through the spiral flow paths 143 and 243. As the compressive fluid in the cavity expands, the rotor 1c rotates in a direction in which the volume increases, and power generation starts. Circulation of compressible fluid and heat may turn faster, but because heat is exchanged rotor 1c, operates to confine heat.
The heat that has not been heat exchanged is dissipated from the panel 290. A method in which the panel 290 is omitted and opened is also conceivable.
Since the expansion ratio of the trochoidal rotor 31c in FIG. 18D is large, a large temperature difference is necessary for driving. Although it is possible to design a small expansion ratio, in order to operate with a small temperature difference, it is necessary to use a magnetic fluid bearing to eliminate the effects of rotational friction and to increase the sealing of the cavity There is. In addition to a method that uses a surface treatment that is easy to adjust to the liquid and uses a liquid such as oil, a method is conceivable in which the opposing surfaces of the two rotors 1c are made magnetized, and a sealing property is obtained by using a magnetic fluid at the fitting portion. .
The surface of the rotor 1c, in which the panel 291 is made transparent, a counter flow path is provided inside the housing 29, a condensing reflector 514 is provided, in order to guide sunlight, radiant heat, and a compressive fluid whose temperature has risen to the center as much as possible. Is colored black.

1 Rotor (inner rotor)
1a Oval rotor 1b Wankel rotor
1c Trochoidal rotor 1d Elliptic arc rotor
DESCRIPTION OF SYMBOLS 10 Rotor cross section 11 Rotor vertical cross section 1s Rotor side surface and external appearance 143 Spiral flow path in rotor 148 Electromagnetic coil 149 Magnet 151 Universal joint 152 Drive shaft 153 Anti-vibration crank 154 Gear 159 Switching gear 161 Electric motor 162 Propeller 165 Generator 166 Fin 171 Partition plate

2 Stator (outer rotor)
2a Tricam-type stator 2b Wankel-type stator
2c Trochoid type stator 2d Cardioid type stator
20 Stator cross section 21 Stator vertical section 2 s Stator side face / appearance 24 Opening 240 Discharge port 241 Suction port 242 Drive water supply port
243 Spiral channel 244 Return pipe 248 Electromagnetic coil
249 Magnet 250 Support roller 253 Anti-vibration support 254 Internal gear 255 Air chamber 261 Fuel supply tube 263 Ignition device
H.264 pressure relief chamber
28 Alignment valve 280 frustoconical (cylindrical) alignment valve (discharge side)
281 Conical trapezoidal ( cylindrical ) alignment valve (suction side) 28s Appearance of frustoconical ( cylindrical ) alignment valve 283 Check valve 284 Check valve (open) 285 Incompressible fluid trap
287 Control valve 288 Start valve
29 Housing (outer shell) 290 Heat radiation panel 291 Heat receiving panel 299 Heat insulation material

3 Volume-variable uniaxial eccentric screw pump or volume-variable uniaxial screw pump
3a Tricam type 3b Wankel type
3c Trochoid type / Multiple trochoid type 3d Cardioid type
31 Compressor 311 Adiabatic Compressor 312 Vacuum Pump
315 Heat Exchange Compressor 31c Multiple Trochoid Compressor 32 Expander 321 Insulation Expander 322 Steam Expander
323 Compressed air engine 324 Air engine generator 325 Heat exchange expander 326 Gas engine 32c Trochoid expander
33 Physical / Chemical Reactor 331 Air Conditioner 332 Air Liquefaction Device 335 Internal Combustion Engine 336 Gas Engine
34 Remote drive pump 341 Remote pumping pump 342 Seabed resource extraction pump 345 Cold energy recovery unit
35 Compressible fluid pressure transducer 350 Compressible fluid pressure regulator
351 Thermal energy recovery device 352 Solar energy recovery device
353 Geothermal energy recovery device 361 Temperature difference drive generator
362 Compressed air drive generator 363 Heat recovery panel type generator 372 Compressed air drive hot and cold source
38 Physical / Chemical reactor (Part 2)

50 Pump 501 Uniaxial eccentric screw pump (constant volume)
50c Internal gear pump (constant volume, trochoid type, etc.) 51 DC / AC power converter 511 Rectifier 513 Resource drilling vessel 514 Solar condensing reflector
521 LED lighting fixtures 523 Refrigerated / hot storage 524 Floor heating
525 Nozzle blower 53 Vacuum container 531 Vacuum chamber
532 Vacuum Freeze Drying Chamber 541 Hot Water Storage Tank 545 High Temperature Regenerator
55 Air storage container 550 Low pressure air tank 551 High pressure air tank
552 Compressed air cylinder 56 Vortex tube
571 Counterflow type heat exchanger 573 Radiator 58 Valve 582 Air filling port with check valve
583 Electrode 584 Unlocking metal fittings 59 Heat insulation and heat insulation

60 Central axis 61 Eccentric shaft (rotor rotational axis) 610 Eccentric shaft locus
62 Position of transverse section 63 Circle (spherical section) centering on the intersection of the central axis and the eccentric axis
64 Intersection of central axis and eccentric shaft 65 Gear (gear) pitch circle

71 Sunlight 72 Wind 73 Ground 74 Geothermal Source 75 Water Surface
76 Submarine resource mud

80 Air piping 801 Low pressure air piping 802 High temperature high pressure air piping
803 Normal pressure air flow path 805 High pressure air outlet 806 High pressure air plug 81 Water pipe 811 Hot water supply pipe 82 City gas pipe 83 Commercial power 831 DC power distribution 835 DC outlet
840 Tube up 841 Tube down

90 Compressible working fluid 900 Air 900H High pressure air
901 Low temperature steam 904 Nitrogen gas
91 Heat source fluid 91H High pressure heat source fluid 910 High temperature air 910H High temperature high pressure air 911 High temperature steam 911H High temperature high pressure steam 930 Cooling air
95 Exhaust 99 Incompressible fluid 991 Water 992 Liquid carbon dioxide 993 Liquid oxygen 994 Liquid nitrogen

Claims (9)

  Equipped with a male-screw-shaped spiral rotor and a female-screw-shaped spiral stator, and the rotor and stator are fitted together to form one or more closed cavities. As a result, the cavity is transported in the axial direction, and any one or two of the eccentricity radius, the shape factor determined by the cross-sectional shape of the rotor and the stator, and the wavelength (pitch), which are the factors that determine the volume of the cavity, Alternatively, the uniaxial eccentric screw pump is characterized in that all elements are changed in the axial direction. In a cross section perpendicular to the central axis of the rotor or stator, or when changing the eccentric radius, in a spherical cross section centering on the intersection of the central axis and the eccentric axis,
Based on the shape of the stator defined by two or more hypocycloids, it is an open shape that takes into account the modifications made to the rotor, and the shape of the cross section of the rotor is defined by the hypocycloid that is one fewer than the stator. Based on a cross-sectional shape modified to an envelope made by rolling a circle,
The shape of the stator is based on the shape of a regular polygon with three or more rounded corners, and is an open shape that takes into account modifications made to the rotor. The cross-sectional shape of the rotor is defined by a hypocycloid that is one fewer than the stator. The shape is an envelope that is formed by rolling a circle based on the shape of the center part that is replaced by elliptic arcs (arcs, including a part of a cycloid curve; the same shall apply hereinafter) equal to the number of streaks. A modified cross-sectional shape,
In addition, based on the shape of the stator defined by one or more epicycloids, it is an open shape that takes into account modifications made to the rotor, and the shape of the rotor is defined by a hypocycloid that is one more than the stator. Roll the circle based on the shape of the cross-section modified to an envelope created by rolling the circle, or by expanding the central part by replacing it with the number of elliptical arcs equal to the number of strips of the rotor. The uniaxial eccentric screw pump according to claim 1, wherein the uniaxial eccentric screw pump has a cross-sectional shape corrected to an envelope that can be formed.   A uniaxial screw pump in which the rotor and the stator rotate together, wherein the stator according to claim 1 is configured as a rotatable outer rotor and is fixed so that the rotation shaft of the rotor does not rotate eccentrically.   A structure in which the axial flow screw pumps (uniaxial eccentric screw pump and uniaxial screw pump) according to claims 1 to 3 are combined by sharing a rotating shaft of a rotor, a structure in which a plurality of rotors are overlapped, and a structure in which these are combined. Axial-flow screw pump (uniaxial eccentric screw pump and uniaxial screw pump.)   Pressure relief chamber, air chamber, check valve, alignment valve, regulating valve, control valve, start valve, incompressible fluid trap, and a stator (including outer rotor) provided with a plurality of openings and a truncated cone shape A pressure adjusting function in the cavity having one or more valves among the truncated conical cylinder valves capable of sequentially opening and closing a plurality of openings by fitting and rotating with the cylinder. Item 1 to 4 axial flow screw pumps (uniaxial eccentric screw pump and single screw pump).   6. An axial screw pump (uniaxial eccentric screw pump and uniaxial screw pump) according to claim 1, wherein a spiral flow path for fluid for heat exchange is provided around the stator (including the outer rotor) or inside the rotor.   A rotor, a stator (including an outer rotor), or an outer shell (housing) are provided with permanent magnets and electromagnetic coils facing each other, and can generate power, be electrically driven, or monitor the rotational state. Axial-flow screw pump (uniaxial eccentric screw pump and uniaxial screw pump.)   Claims using magnetic fluid on the rotor, the stator (including the outer rotor) or the surface that contacts the outer shell (housing) while rotating (the contact surface and the bearing that forms the cavity). Item 8. An axial screw pump according to items 1 to 7 (uniaxial eccentric screw pump and uniaxial screw pump).   Claims for compressible fluid pumps, compressible fluid compressors, compressible fluid expanders, physicochemical reactors (internal combustion engines), remote-driven pumps, compressible fluid pressure transducers, thermal energy recoverers (external combustion engines), etc. Products using 1 to 8 axial flow screw pumps.