CN103953443A - Centrifugal fluid-channel impeller engine - Google Patents
Centrifugal fluid-channel impeller engine Download PDFInfo
- Publication number
- CN103953443A CN103953443A CN201410101688.2A CN201410101688A CN103953443A CN 103953443 A CN103953443 A CN 103953443A CN 201410101688 A CN201410101688 A CN 201410101688A CN 103953443 A CN103953443 A CN 103953443A
- Authority
- CN
- China
- Prior art keywords
- fluid passage
- centrifugal fluid
- turbine
- running shaft
- injection channel
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a centrifugal fluid-channel impeller engine. The centrifugal fluid-channel impeller engine comprises a rotation shaft, a compressor impeller and a centrifugal fluid channel. The rotation shaft is fixedly and coaxially connected to the compressor impeller. The centrifugal fluid channel is arranged in the compressor impeller. The centrifugal fluid channel is communicated with a working medium inlet of an injection channel. The injection channel and the rotation shaft are ranged at an interval. The centrifugal fluid-channel impeller engine has the advantages of high power density, less pollutant discharge, good fuel diversity and low production cost.
Description
Technical field
The present invention relates to heat energy and power field, especially a kind of centrifugal fluid passage vane motor.
Background technique
The energy and environmental problem become more and more important, and conventional engines specific power is low, disposal of pollutants serious, fuel diversity is poor, cost of production is high, therefore needs to invent a kind of new work engine.
Summary of the invention
In order to address the above problem, the technological scheme that the present invention proposes is as follows:
Scheme 1: a kind of centrifugal fluid passage vane motor, comprise running shaft, compression impellor and centrifugal fluid passage, the setting that is connected of described running shaft and described compression impellor coaxial line, described centrifugal fluid passage is arranged in described compression impellor, described centrifugal fluid passage is communicated with the working medium entrance of injection channel, and described injection channel and described running shaft have square setting.
Scheme 2: a kind of centrifugal fluid passage vane motor, comprise running shaft, compression impellor and centrifugal fluid passage, the setting that is connected of described running shaft and described compression impellor coaxial line, described centrifugal fluid passage is arranged in described compression impellor, described centrifugal fluid passage is communicated with fluid supply, described centrifugal fluid passage is communicated with the working medium entrance of injection channel, and described injection channel and described running shaft have square setting.
Scheme 3: a kind of centrifugal fluid passage vane motor, comprise running shaft, turbine and centrifugal fluid passage, the setting that is connected of described running shaft and described turbine coaxial line, described centrifugal fluid passage is arranged in described turbine, described centrifugal fluid passage is communicated with the working medium entrance of injection channel, and described injection channel and described running shaft have square setting.
Scheme 4: a kind of centrifugal fluid passage vane motor, comprise running shaft, turbine and centrifugal fluid passage, the setting that is connected of described running shaft and described turbine coaxial line, described centrifugal fluid passage is arranged in described turbine, described centrifugal fluid passage is communicated with fluid supply, described centrifugal fluid passage is communicated with the working medium entrance of injection channel, and described injection channel and described running shaft have square setting.
Scheme 5: a kind of centrifugal fluid passage vane motor, comprise running shaft, compression impellor, turbine and centrifugal fluid passage, the setting that is connected of described running shaft and described compression impellor coaxial line, the setting that is connected of described running shaft and described turbine coaxial line, described centrifugal fluid passage is arranged in described compression impellor, turbine fluid passage is set in described turbine, described centrifugal fluid passage and described turbine fluid passage are communicated with, described turbine fluid passage is communicated with the working medium entrance of injection channel, described injection channel and described running shaft have square setting, the pressurized gas outlet heater via of described compression impellor is communicated with the working medium entrance of described turbine.
Scheme 6: a kind of centrifugal fluid passage vane motor, comprise running shaft, compression impellor, turbine and centrifugal fluid passage, the setting that is connected of described running shaft and described compression impellor coaxial line, the setting that is connected of described running shaft and described turbine coaxial line, described centrifugal fluid passage is arranged in described compression impellor, turbine fluid passage is set in described turbine, described centrifugal fluid passage is communicated with fluid supply, described centrifugal fluid passage and described turbine fluid passage are communicated with, described turbine fluid passage is communicated with the working medium entrance of injection channel, described injection channel and described running shaft have square setting, the pressurized gas outlet heater via of described compression impellor is communicated with the working medium entrance of described turbine.
Scheme 7: on the basis of scheme 5 or scheme 6, further selectively described heater is made as external combustion heater, internal combustion heater or is made as heat exchanger type heater.
Scheme 8: on the basis of arbitrary scheme, further selectively described compression impellor is made as axial flow compression impellor or is made as radial-flow type compression impellor in above-mentioned all schemes that are provided with described compression impellor.
Scheme 9: on the basis of arbitrary scheme, further selectively described turbine is made as axial turbine or is made as radial turbine in above-mentioned all schemes that are provided with described turbine.
Scheme 10: in above-mentioned all schemes that are provided with described fluid supply on the basis of arbitrary scheme, further selectively described centrifugal fluid passage is communicated with described fluid supply through swivel joint, or described centrifugal fluid passage is communicated with described fluid supply for form with distant, or described centrifugal fluid passage is communicated with described fluid supply through centrifugal pump.
Scheme 11: on the basis of arbitrary scheme, further selectively the bearing capacity of the working medium ingress of described injection channel is greater than 2MPa in above-mentioned all schemes.
Scheme 12: on the basis of arbitrary scheme, when further selectively described centrifugal fluid passage is to described centrifugal fluid passage vane motor feed liquid, this liquid advances into described centrifugal fluid passage in vaporization in above-mentioned all schemes.
In the present invention, described compression impellor can be made as single-stage or be made as multistage.
In the present invention, described turbine can be made as single-stage or be made as multistage.
In the present invention, described compression impellor comprises the blade of calming the anger, compression impellor.
In the present invention, described turbine comprises leaf formula turbine, turbo type turbine.
In the present invention, described injection channel refers to that all can spray fluid and obtain the passage of reaction force, for example, and subsonic effuser, supersonic nozzle (being Laval nozzle), turbine, turbine or water conservancy diversion injection channel etc.
In the present invention, the object of described injection channel setting is to produce reaction force by Fluid injection.
In the present invention, " described injection channel and described running shaft have square setting " refers to that reaction force suffered when described injection channel sprays produces the set-up mode of moment of torsion to the spin axis of described running shaft.
In the present invention, the fuel that enters described internal combustion heater can enter described internal combustion heater by the mode of individual injection, also after can being mixed together with air, enter described internal combustion heater, can also be input to described internal combustion heater through swivel joint or with distant for mode by described running shaft.
In the present invention, so-called " distant for form " refers to non-contact liquid transmission means, for example, A with distant for form and B connection refer to A with B under the prerequisite that does not exist solid to contact, fluid in A enters the connection form in B, comprise the form of splashing into, inject form, spray into form, suction form and spiral pump into form etc., do not comprise the centrifugal form that pumps into.
In the present invention, described spiral pumps into form and refers in the vias inner walls at the fluid intake place of described centrifugal fluid passage and establish helix structure, or in the fluid intake inside of described centrifugal fluid passage, static element is set, on described static element, establish helix structure, described static element does not contact with described centrifugal fluid passage.
In the present invention, so-called " the centrifugal form that pumps into " refer to that described running shaft is connected with the rotary blade of centrifugal pump, drive the rotary blade of described centrifugal pump to rotate the mode of communicating that liquid is pumped into by described running shaft.
In the present invention, the bearing capacity of the working medium ingress of described injection channel is greater than 2MPa, 2.5MPa, 3MPa, 3.5MPa, 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa, 17.5MPa, 18MPa, 18.5MPa, 19MPa, 19.5MPa, 20MPa, 20.5MPa, 21MPa, 21.5MPa, 22MPa, 22.5MPa, 23MPa, 23.5MPa, 24MPa, 24.5MPa, 25MPa, 25.5MPa, 26MPa, 26.5MPa, 27Pa, 27.5MPa, 28MPa, 28.5MPa, 29MPa, 29.5MPa or be greater than 30MPa.
In the present invention, the power pressure of the working medium ingress of described injection channel should match with its bearing capacity, and the highest power pressure of the working medium ingress of described injection channel reaches its bearing capacity.
In the present invention, so-called " centrifugal fluid passage " refers in radial direction has the fluid passage of distribution and by the fluid passage having in the radial direction the fluid passage of distribution and forming in the fluid passage not distributing in the radial direction, for example completely according to the fluid passage of radial direction setting, by gradually opening or the spiral fluid passage of convergent form setting, having in the radial direction fluid passage repeatedly etc.
In the present invention, so-called " turbine fluid passage " refers to the fluid passage being arranged on turbine.
In the present invention, optionally according to known technology, condensate cooler, regenerator and/or liquor pump and wet tank are set, in the structure that is provided with described condensate cooler, the working medium of being sprayed by described injection channel enters described condensate cooler.
In the present invention, described fluid supply refers to liquid working substance source, device, unit, system or the storage tank of water or other liquid working substance (for example organic Rankine cycle fluid) for example can be provided, for example, the system being formed by wet tank and liquor pump, again for example, wet tank or by the wet tank of gravity force liquid-supply body etc.
In the present invention, the liquid working substance in described fluid supply can optionally be selected water, alkane, freon or alcohols etc.
In the present invention, described fluid supply is optionally made as described mixed-burned gas liquefaction source, mixed-burned gas liquefaction in described mixed-burned gas liquefaction source refers to the gas for gaseous state under the standard state being liquefied, the gas here refers to that under standard state, its steam divides air pressure to be more than or equal to an atmospheric material, for example, liquefaction nitrogen, liquefied oxygen, liquefied carbon dioxide or liquefied air etc.
In the present invention, so-called A and B are communicated with and refer to that between A and B, working medium occurs to flow, and comprise that working medium flows to B or flows to A from B from A, or working medium first flows to B from A and flows to A from B again.So-called " connection " comprises direct connection, indirect communication and is communicated with through operating unit, and described operating unit comprises valve, control mechanism, feed mechanism (pump) and heat exchanger etc.
In the present invention, above and certain the numerical value A of certain numerical value A includes given figure A below.
The inventor thinks according to thermodynamic (al) basic principle and on the observation of universe phenomenon: do not having under the prerequisite of external factor impact, heat can not absolutely convert other any type of energy or material to.In the tradition second law of thermodynamics, only set forth and do not had under the prerequisite of external factor impact, heat can not absolutely be changed successfully, and this law is correct, but is unilateral.Can heat be defined as with popular language to the minimum form of energy, or be the rubbish in universe referred to as this.By analysis, the inventor also thinks: the growing process of any biology (animal, plant, microorganism, virus and bacterium) is all heat release.By analysis, the inventor also thinks: any one process or any one circulation (are not limited to thermodynamic process, for example chemical reaction process, biochemical reaction process, photochemical reaction process, biological growth process, growing process are all included) its maximum acting ability conservation, the inventor thinks does not have photosynthetic growing process can not improve its acting ability, that is to say, the acting ability of bean sprouts is the acting ability sum that impossible add the nutrient of its absorption higher than the acting ability of bean or pea; Why the acting ability of one tree wood is greater than the acting ability of sapling, is because sunlight has participated in the growing process to trees by sapling with photosynthetic form.
The inventor thinks: the basic logic of heat engine work be restrain-be heated-disperse.So-called convergence is the increase process of the density of working medium, and for example condensation, compression all belong to convergence process, and under same pressure, the working medium degree of convergence that temperature is low is large; It is exactly the endothermic process of working medium that what is called is heated; What is called is dispersed the process of the density reduction that refers to working medium, for example, expand or spray.Any one disperses process and all can form the reduction of acting ability, and for example, the acting ability of the air of gaseous state will be well below the acting ability of liquid air; The heat that methanol plus water adds moderate temperature generates carbon monoxide and hydrogen, although the carbon monoxide generating and the ignition heat of hydrogen are greater than ignition heat 20% left and right of methyl alcohol, but it is very little that its acting ability is greater than the ratio of acting ability of methyl alcohol, although its reason is this process and inhaled the heat of 20% left and right, the degree of divergence of resultant carbon monoxide and hydrogen is far longer than methyl alcohol.Therefore, utilizing physochlaina infudibularis that temperature is not high to add chemical reaction is the acting ability of having no idea effectively to improve resultant.
The inventor thinks: it is the process that entropy increases that distance increases, and the distance between cold & heat source also affects efficiency, and the little efficiency of distance is high, and the large efficiency of distance is low.
In the present invention, should, according to the known technology in heat energy and power field, in necessary place, necessary parts, unit or system etc. be set.
beneficial effect of the present invention is as follows:
Described centrifugal fluid passage of the present invention vane motor specific power is high, disposal of pollutants is few, fuel diversity is good, cost of production is low.
Brief description of the drawings
Shown in Fig. 1 is the structural representation of the embodiment of the present invention 1;
Shown in Fig. 2 is the structural representation of the embodiment of the present invention 2;
Shown in Fig. 3 is the structural representation of the embodiment of the present invention 3;
Shown in Fig. 4 is the structural representation of the embodiment of the present invention 4;
Shown in Fig. 5 is the structural representation of the embodiment of the present invention 5;
Shown in Fig. 6 is the structural representation of the embodiment of the present invention 6;
Shown in Fig. 7 is the structural representation of the embodiment of the present invention 7;
Shown in Fig. 8 is the structural representation of the embodiment of the present invention 8;
Shown in Fig. 9 is the structural representation of the embodiment of the present invention 9;
Shown in Figure 10 is the structural representation of the embodiment of the present invention 10;
Shown in Figure 11 is the structural representation of the embodiment of the present invention 11;
Shown in Figure 12 is the structural representation of the embodiment of the present invention 12;
Shown in Figure 13 is the structural representation of the embodiment of the present invention 13;
Shown in Figure 14 is the structural representation of the embodiment of the present invention 14;
In figure:
1 running shaft, 2 compression impellors, 3 centrifugal fluid passages, 4 injection channels, 41 spray nozzle plates, 5 turbines, 51 turbine fluid passages, 6 heaters, 61 internal combustion heaters, 7 fluid supplies.
Embodiment
Embodiment 1
Centrifugal fluid passage vane motor as shown in Figure 1, comprise running shaft 1, compression impellor 2 and centrifugal fluid passage 3, the setting that is connected of described running shaft 1 and described compression impellor 2 coaxial lines, described centrifugal fluid passage 3 is arranged in described compression impellor 2, described centrifugal fluid passage 3 is communicated with fluid supply 7, described centrifugal fluid passage 3 is communicated with the working medium entrance of injection channel 4, and described injection channel 4 has square setting with described running shaft 1.
In the present embodiment, described injection channel 4 has been located on described compression impellor 2, and the sender property outlet of described injection channel 4 is arranged on the outside of the housing of described compression impellor 2; What described compression impellor 2 was concrete has been made as radial-flow type compression impellor; The pressurized gas outlet of described compression impellor 2 is arranged on the position near described running shaft 1.
Embodiment 2
Centrifugal fluid passage vane motor as shown in Figure 2, itself and embodiment's 1 difference is: described injection channel 4 changes and is located at independently on spray nozzle plate 41.
Embodiment 3
Centrifugal fluid passage vane motor as shown in Figure 3, itself and embodiment's 1 difference is:
Described compression impellor 2 changes and is made as axial flow compression impellor.
Embodiment 4
Centrifugal fluid passage vane motor as shown in Figure 4, itself and embodiment's 1 difference is:
The pressurized gas outlet of described compression impellor 2 changes on the position at top of the blade that is arranged on close described compression impellor 2.
Embodiment 5
Centrifugal fluid passage vane motor as shown in Figure 5, comprise running shaft 1, turbine 5 and centrifugal fluid passage 3, the setting that is connected of described running shaft 1 and described turbine 5 coaxial lines, described centrifugal fluid passage 3 is arranged in described turbine 5, described centrifugal fluid passage 3 is communicated with fluid supply 7, described centrifugal fluid passage 3 is communicated with the working medium entrance of injection channel 4, and described injection channel 4 has square setting with described running shaft 1.
In the present embodiment, described injection channel 4 has been located on described turbine 5, and the sender property outlet of described injection channel 4 is arranged on the outside of the housing of described turbine 5; What described turbine 5 was concrete be made as radial-flow type calms the anger turbine; The sender property outlet of described turbine 5 is arranged on the described position near described running shaft 1.
As the mode of execution that can convert, the sender property outlet of described injection channel 4 can change the inside of the housing that is arranged on described turbine 5 into.
Embodiment 6
Centrifugal fluid passage vane motor as shown in Figure 6, itself and embodiment's 5 difference is: described injection channel 4 changes and is located at independently on spray nozzle plate 41.
Embodiment 7
Centrifugal fluid passage vane motor as shown in Figure 7, itself and embodiment's 5 difference is:
Described turbine 5 changes and is made as axial turbine.
As the mode of execution that can convert, the sender property outlet of described injection channel 4 can change the inside of the housing that is arranged on described turbine 5 into.
Embodiment 8
Centrifugal fluid passage vane motor as shown in Figure 8, itself and embodiment's 5 difference is:
The sender property outlet of described turbine 5 changes on the position at top of the blade that is arranged on close described turbine 5.
As the mode of execution that can convert, the sender property outlet of described injection channel 4 can change the inside of the housing that is arranged on described turbine 5 into.
Embodiment 9
Centrifugal fluid passage vane motor as shown in Figure 9, comprise running shaft 1, compression impellor 2, turbine 5 and centrifugal fluid passage 3, the setting that is connected of described running shaft 1 and described compression impellor 2 coaxial lines, the setting that is connected of described running shaft 1 and described turbine 5 coaxial lines, described centrifugal fluid passage 3 is arranged in described compression impellor 2, in the interior turbine fluid passage 51 that arranges of described turbine 5, described centrifugal fluid passage 3 is communicated with fluid supply 7, described centrifugal fluid passage 3 and described turbine fluid passage 51 are communicated with, described turbine fluid passage 51 is communicated with the working medium entrance of injection channel 4, described injection channel 4 has square setting with described running shaft 1, the pressurized gas outlet heater via 6 of described compression impellor 2 is communicated with the working medium entrance of described turbine 5.
In the present embodiment, described compression impellor 2 has specifically been made as radial-flow type compression impellor; Described turbine 5 has specifically been made as radial turbine; Described injection channel 4 has been located at independently on jet pipe dish 41.
Embodiment 10
Centrifugal fluid passage vane motor as shown in figure 10, itself and embodiment's 9 difference is:
Described injection channel 4 changes and has been located on described turbine 5, and the sender property outlet of described injection channel 4 is arranged on the inside of the housing of described turbine 5.
As the mode of execution that can convert, can also reference example 5 sender property outlet of described injection channel 4 be changed into the outside of the housing that is arranged on described turbine 5.
When embodiment 9 and embodiment 10 and disposable mode of execution specific embodiment thereof, described heater 6 can be made as to external combustion heater, internal combustion heater 61, heat exchanger type heater or be made as other any type of heaters.
Embodiment 11
Centrifugal fluid passage vane motor as shown in figure 11, itself and embodiment's 9 difference is:
Set up compression impellor 2 described in one-level, make described centrifugal fluid passage vane motor comprise compression impellor 2 described in two-stage, and compression impellor described in two-stage 2 is made as to axial flow compression impellor; Described turbine 5 is changed and is made as axial turbine; By concrete described heater 6 internal combustion heater 61 that has been made as.
In the present embodiment, what described injection channel 4 was concrete has been located on described turbine 5, and the sender property outlet of described injection channel 4 is arranged on the inside of the housing of described turbine 5.
Embodiment 12
Centrifugal fluid passage vane motor as shown in figure 12, itself and embodiment's 11 difference is:
The sender property outlet of described injection channel 4 changes the outside of the housing that is arranged on described turbine 5 into.
Embodiment 13
Centrifugal fluid passage vane motor as shown in figure 13, itself and embodiment's 11 difference is:
Reduce the described compression impellor 2 of level described in one-level, make described centrifugal fluid passage vane motor only comprise compression impellor 2 described in one-level, and described injection channel 4 is changed and has been located at independently on spray nozzle plate 41.
Embodiment 14
Centrifugal fluid passage vane motor as shown in figure 14, itself and embodiment's 13 difference is:
The sender property outlet of described injection channel 4 changes the outside of the housing that is arranged on described turbine 5 into.
As the mode of execution that can convert, embodiment 11 is made as other any type of heaters to described heater 6 being changed to be made as external combustion heater, heat exchanger type heater or to change in embodiment 14.
In the present invention, be arranged in the structure of inside of the housing of described turbine 5 at the sender property outlet of described injection channel 4, the working medium of the working medium after described turbine 5 actings after the acting spraying through described injection channel 4 is discharged after mixing; Be arranged in the outside structure of housing of described turbine 5 at the sender property outlet of described injection channel 4, the working medium of working medium after described turbine 5 actings after the acting spraying through described injection channel 4 is not mixed, when each mode of execution of the application is specifically implemented, the position that can select as required the sender property outlet that described injection channel 4 is set, is not subject to the restriction of above-mentioned mode of execution.
As the mode of execution that can convert, in all mode of executions that described compression impellor 2 is set of the present invention, can described compression impellor 2 be made as multistage.
As the mode of execution that can convert, in all mode of executions that described turbine 5 is set of the present invention, can described turbine 5 be made as multistage, now described injection channel 4 can be arranged on described in afterbody on turbine 5, or with reference to embodiment 14, independently spray nozzle plate 41 is in the end set after turbine 5 described in one-level, and described injection channel 4 is arranged on to this independently on spray nozzle plate 41.
As the mode of execution that can convert, in all of the embodiments of the present invention, described fluid supply 7 can not established, and now, can use in use independently fluid supply.
When all of the embodiments of the present invention is specifically implemented, described injection channel 4 optionally can be made as to subsonic effuser, supersonic nozzle (being Laval nozzle), turbine, turbine or water conservancy diversion injection channel etc.
In order better to adopt described centrifugal fluid passage 3, working medium is carried out to supercharging, all of the embodiments of the present invention in the specific implementation, can make described centrifugal fluid passage 3 to described centrifugal fluid passage vane motor feed liquid time, this liquid advances into described centrifugal fluid passage 3 in vaporization.
All of the embodiments of the present invention in the specific implementation, can optionally make described centrifugal fluid passage 3 be communicated with described fluid supply 7 through swivel joint, or described centrifugal fluid passage 3 is communicated with described fluid supply 7 for form with distant, or described centrifugal fluid passage 3 is communicated with described fluid supply 7 through centrifugal pump.
As the mode of execution that can convert, when all of the embodiments of the present invention is specifically implemented, can optionally the bearing capacity of the working medium ingress of described injection channel 4 be made as and be greater than 2MPa, 2.5MPa, 3MPa, 3.5MPa, 4MPa, 4.5MPa, 5MPa, 5.5MPa, 6MPa, 6.5MPa, 7MPa, 7.5MPa, 8MPa, 8.5MPa, 9MPa, 9.5MPa, 10MPa, 10.5MPa, 11MPa, 11.5MPa, 12MPa, 12.5MPa, 13MPa, 13.5MPa, 14MPa, 14.5MPa, 15MPa, 15.5MPa, 16MPa, 16.5MPa, 17MPa, 17.5MPa, 18MPa, 18.5MPa, 19MPa, 19.5MPa, 20MPa, 20.5MPa, 21MPa, 21.5MPa, 22MPa, 22.5MPa, 23MPa, 23.5MPa, 24MPa, 24.5MPa, 25MPa, 25.5MPa, 26MPa, 26.5MPa, 27Pa, 27.5MPa, 28MPa, 28.5MPa, 29MPa, 29.5MPa or be made as and be greater than 30MPa, thereby improve the efficiency of described motor.
In all mode of executions of the application, described injection channel 4 or be arranged on independently on spray nozzle plate 41, be arranged on corresponding compression impellor 2 or turbine 5, as disposable mode of execution, when each mode of execution of the application is specifically implemented, can select as required the set-up mode of described injection channel 4, not be subject to the restriction of above-mentioned mode of execution, and described injection channel 4 can also adopt other any suitable set-up mode, as long as ensure that itself and described running shaft 1 have square setting.
Obviously, the invention is not restricted to above embodiment, according to the known technology of related domain and technological scheme disclosed in this invention, can derive or association goes out many flexible programs, all these flexible programs, also should think protection scope of the present invention.
Claims (10)
1. a centrifugal fluid passage vane motor, comprise running shaft (1), compression impellor (2) and centrifugal fluid passage (3), it is characterized in that: the setting that is connected of described running shaft (1) and described compression impellor (2) coaxial line, described centrifugal fluid passage (3) is arranged in described compression impellor (2), described centrifugal fluid passage (3) is communicated with the working medium entrance of injection channel (4), and described injection channel (4) has square setting with described running shaft (1).
2. a centrifugal fluid passage vane motor, comprise running shaft (1), compression impellor (2) and centrifugal fluid passage (3), it is characterized in that: the setting that is connected of described running shaft (1) and described compression impellor (2) coaxial line, described centrifugal fluid passage (3) is arranged in described compression impellor (2), described centrifugal fluid passage (3) is communicated with fluid supply (7), described centrifugal fluid passage (3) is communicated with the working medium entrance of injection channel (4), and described injection channel (4) has square setting with described running shaft (1).
3. a centrifugal fluid passage vane motor, comprise running shaft (1), turbine (5) and centrifugal fluid passage (3), it is characterized in that: the setting that is connected of described running shaft (1) and described turbine (5) coaxial line, described centrifugal fluid passage (3) is arranged in described turbine (5), described centrifugal fluid passage (3) is communicated with the working medium entrance of injection channel (4), and described injection channel (4) has square setting with described running shaft (1).
4. a centrifugal fluid passage vane motor, comprise running shaft (1), turbine (5) and centrifugal fluid passage (3), it is characterized in that: the setting that is connected of described running shaft (1) and described turbine (5) coaxial line, described centrifugal fluid passage (3) is arranged in described turbine (5), described centrifugal fluid passage (3) is communicated with fluid supply (7), described centrifugal fluid passage (3) is communicated with the working medium entrance of injection channel (4), and described injection channel (4) has square setting with described running shaft (1).
5. a centrifugal fluid passage vane motor, comprise running shaft (1), compression impellor (2), turbine (5) and centrifugal fluid passage (3), it is characterized in that: the setting that is connected of described running shaft (1) and described compression impellor (2) coaxial line, the setting that is connected of described running shaft (1) and described turbine (5) coaxial line, described centrifugal fluid passage (3) is arranged in described compression impellor (2), turbine fluid passage (51) is set in described turbine (5), described centrifugal fluid passage (3) and described turbine fluid passage (51) are communicated with, described turbine fluid passage (51) is communicated with the working medium entrance of injection channel (4), described injection channel (4) has square setting with described running shaft (1), the pressurized gas outlet heater via (6) of described compression impellor (2) is communicated with the working medium entrance of described turbine (5).
6. centrifugal fluid passage vane motor as claimed in claim 5, is characterized in that: described heater (6) is made as external combustion heater, internal combustion heater (61) or is made as heat exchanger type heater.
7. a centrifugal fluid passage vane motor, comprise running shaft (1), compression impellor (2), turbine (5) and centrifugal fluid passage (3), it is characterized in that: the setting that is connected of described running shaft (1) and described compression impellor (2) coaxial line, the setting that is connected of described running shaft (1) and described turbine (5) coaxial line, described centrifugal fluid passage (3) is arranged in described compression impellor (2), turbine fluid passage (51) is set in described turbine (5), described centrifugal fluid passage (3) is communicated with fluid supply (7), described centrifugal fluid passage (3) and described turbine fluid passage (51) are communicated with, described turbine fluid passage (51) is communicated with the working medium entrance of injection channel (4), described injection channel (4) has square setting with described running shaft (1), the pressurized gas outlet heater via (6) of described compression impellor (2) is communicated with the working medium entrance of described turbine (5).
8. centrifugal fluid passage vane motor as claimed in claim 7, is characterized in that: described heater (6) is made as external combustion heater, internal combustion heater (61) or is made as heat exchanger type heater.
9. centrifugal fluid passage vane motor as described in claim 1,2,5,6,7 or 8, is characterized in that: described compression impellor (2) is made as axial flow compression impellor or is made as radial-flow type compression impellor.
10. centrifugal fluid passage vane motor as described in any one in claim 3 to 8, is characterized in that: described turbine (5) is made as axial turbine or is made as radial turbine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410101688.2A CN103953443B (en) | 2013-03-18 | 2014-03-18 | Centrifugal fluid channel vane motor |
Applications Claiming Priority (13)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310086468.2 | 2013-03-18 | ||
| CN201310086468 | 2013-03-18 | ||
| CN2013100864682 | 2013-03-18 | ||
| CN201310088399 | 2013-03-19 | ||
| CN2013100883999 | 2013-03-19 | ||
| CN201310088399.9 | 2013-03-19 | ||
| CN201310100251.2 | 2013-03-26 | ||
| CN2013101002512 | 2013-03-26 | ||
| CN201310100251 | 2013-03-26 | ||
| CN201310108764 | 2013-03-29 | ||
| CN201310108764.8 | 2013-03-29 | ||
| CN2013101087648 | 2013-03-29 | ||
| CN201410101688.2A CN103953443B (en) | 2013-03-18 | 2014-03-18 | Centrifugal fluid channel vane motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103953443A true CN103953443A (en) | 2014-07-30 |
| CN103953443B CN103953443B (en) | 2018-08-21 |
Family
ID=51330768
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410101688.2A Active CN103953443B (en) | 2013-03-18 | 2014-03-18 | Centrifugal fluid channel vane motor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103953443B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109339867A (en) * | 2018-11-15 | 2019-02-15 | 翁志远 | Reaction nozzle-type impeller, rotor, steam turbine, steamer equipment and prime mover |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3899874A (en) * | 1974-09-11 | 1975-08-19 | Henry E Bailey | Turbine engine |
| CN1115004A (en) * | 1995-04-20 | 1996-01-17 | 郭颖 | Reaction type jet engine |
| CN2387274Y (en) * | 1999-09-22 | 2000-07-12 | 蔡盛龙 | Rotary jet shaft engine |
| CN1356454A (en) * | 2000-12-05 | 2002-07-03 | 祝长宇 | Centrifugal engine |
| US20080173592A1 (en) * | 2007-01-24 | 2008-07-24 | Honeywell International Inc. | Oil centrifuge |
-
2014
- 2014-03-18 CN CN201410101688.2A patent/CN103953443B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3899874A (en) * | 1974-09-11 | 1975-08-19 | Henry E Bailey | Turbine engine |
| CN1115004A (en) * | 1995-04-20 | 1996-01-17 | 郭颖 | Reaction type jet engine |
| CN2387274Y (en) * | 1999-09-22 | 2000-07-12 | 蔡盛龙 | Rotary jet shaft engine |
| CN1356454A (en) * | 2000-12-05 | 2002-07-03 | 祝长宇 | Centrifugal engine |
| US20080173592A1 (en) * | 2007-01-24 | 2008-07-24 | Honeywell International Inc. | Oil centrifuge |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109339867A (en) * | 2018-11-15 | 2019-02-15 | 翁志远 | Reaction nozzle-type impeller, rotor, steam turbine, steamer equipment and prime mover |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103953443B (en) | 2018-08-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103953441B (en) | Runner is to forwarding motivation | |
| CN102278233B (en) | Supersonic rotor engine | |
| CN202745952U (en) | Low-entropy mixed-combustion gas liquid injection air-powered engine | |
| CN105545369A (en) | Condensation type kinetic energy power converting device and heat power system thereof | |
| CN103982298A (en) | Internal-combustion gas liquefied substance high-temperature engine | |
| CN104912691A (en) | Internal combustion closed-loop hydrocarbon fuel thermo-motive system | |
| CN103867298B (en) | Distant for external combustion rotary engine | |
| CN103953444B (en) | Centrifugal fluid channel shell disc rotor engine | |
| CN103953443A (en) | Centrifugal fluid-channel impeller engine | |
| CN103939236A (en) | External combustion propelling engine | |
| CN104454169A (en) | External internal combustion engine | |
| CN103994014B (en) | Hydraulic system and use its vehicle | |
| CN103953440B (en) | Centrifugal fluid passage rotating disk motor | |
| CN103821614A (en) | Thermodynamic gas turbine adopting liquid-air working medium environment and working method of thermodynamic gas turbine | |
| CN104061066A (en) | Rotor motor for gas liquefied materials | |
| CN202690226U (en) | Efficient composite power impeller mechanism | |
| CN103867491A (en) | Rotating body liquid remote supply device for engine | |
| CN103953442B (en) | Runner rotary engine | |
| CN103982330A (en) | Rotor engine with extreme pressure ratio | |
| CN103850795B (en) | Many rotating disks motor | |
| CN103899418A (en) | Remotely-transferred rotor engine | |
| CN104131914A (en) | Air-compressing nozzle propulsion engine | |
| CN103982616A (en) | Hydraulic rotor speed change mechanism | |
| CN203702344U (en) | Liquid air working mediumenvironment thermodynamic gas turbine | |
| CN103993979A (en) | Phase-change engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20200921 Address after: Songling town (bacha) Economic Development Zone, Wujiang City, Suzhou City, 215200 Jiangsu Province Patentee after: SUZHOU SHENGXIN OPTOELECTRONICS TECHNOLOGY Co.,Ltd. Address before: 100101, Beijing, Chaoyang District Beiyuan Road, No. 168, Sheng Sheng building, 24 floor Patentee before: MOLECULE POWER BEIJING TECH Co. |