CN103306977A - Compressor unit of grade two and compressor system using the same - Google Patents
Compressor unit of grade two and compressor system using the same Download PDFInfo
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- CN103306977A CN103306977A CN2012104193644A CN201210419364A CN103306977A CN 103306977 A CN103306977 A CN 103306977A CN 2012104193644 A CN2012104193644 A CN 2012104193644A CN 201210419364 A CN201210419364 A CN 201210419364A CN 103306977 A CN103306977 A CN 103306977A
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- rotor
- gear
- exhaust port
- compressor
- mouth
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/10—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
Abstract
A compressor unit of grade two, and a compressor system using the same are provided. The compressor system includes a compressor unit having a triple trochoidal rotor, which includes a first rotor, a second rotor, a third rotor, a casing, second and first suction ports, and second and first discharge ports; and a driving unit that rotates the three rotors such that external working fluid is sucked into the suction port and the working fluid sucked into the suction port is discharged to the discharge port in a state of being compressed. The compressor unit may be constructed as a triple trochoidal rotor such that working fluid can be compressed in a two-stage compression manner to enable the working fluid to be supplied at high pressure and provide a high-speed, high-pressure compression capability.
Description
Technical field
The present invention relates to a kind of 2 stage compressor unit and have the technology of the compressor assembly of described compressor unit, by consisting of compressor unit by 3 heavy co-cycloidal rotors, can carry out 2 grades of compressions to working fluid, thereby can send working fluid with high pressure, and intake and the discharge capacity of increase working fluid, and then can provide the high speed and high pressure compression performance.
Background technique
Usually, what is called has the compressor unit of co-cycloidal rotor (trochoidal rotor), comprise, and 2 gear rotors, to be rotated under the intermeshing state, working fluid passes through 2 gear rotors to each other, thus compression working fluid; Shell holds described gear rotor.Co-cycloidal rotor is the rotor of the trochoidal curve of outer circumferential face formation within it generating gear.
Described existing compressor unit comprises: the 1st rotor forms the trochoidal curve shape gear teeth (teeth) at its outer circumferential face; The 2nd rotor is contained in position for the rotating center eccentric shaft of itself with described the 1st rotor, and side face forms and is engaged in the gear teeth of described the 1st rotor within it, and the trochoidal curve shape gear teeth that contact with the 1st rotor line; Shell, described the 1st rotor and the 2nd rotor are held in sealing.
The existing compressor unit that consists of as mentioned above by changing the volume between the 1st rotor and the 2nd rotor, has the fundamental mechanism of the compression of sucking and exhaust fluid with this.Because structure is relatively simple and Miniaturizable, so many decades is used in fluid pump more.
But described existing compressor unit only uses 2 rotors, and is therefore, restricted to its compression ratio.That is, even increase to greatest extent the running torque of the 1st rotor, whenever revolve when turning around at the 1st rotor and all to discharge working fluid, therefore, the pressure of the working fluid that is discharged can be too not high.Therefore, when using in the place of the higher lift of needs, its use is limited, and mass rate of emission is also limited, and the high speed pump performance can not be provided.
Therefore, be badly in need of the following compressor assembly that has the compressor unit of triple co-cycloidal rotors and have described compressor unit of exploitation, this system can carry out 2 grades of compressions and can send working fluid with high pressure working fluid, and traffic attraction and the discharge capacity of increase working fluid, thereby can provide the high speed and high pressure compression performance.
Summary of the invention
The present invention proposes in order to solve described existing issue point, its purpose is, provide by consisting of compressor unit and can carry out 2 grades of compressions to working fluid by 3 heavy co-cycloidal rotors, thereby can send the compressor unit with 3 heavy co-cycloidal rotors of working fluid and have the compressor assembly of described compressor unit with high pressure.
The object of the invention is to, provide by consisting of traffic attraction and the discharge capacity that compressor unit increases working fluid by 3 heavy co-cycloidal rotors, thereby 2 stage compressor unit of high speed and high pressure compression performance can be provided and have the compressor assembly of described compressor unit.
For reaching the 2 stage compressor unit according to a preferred embodiment of the invention of described purpose, it is characterized in that, comprising: the 1st rotor, form a plurality of trochoidal curve gears at outer circumferential face, be fixed with stationary axle at its rotating center; The 2nd rotor, hold prejudicially described the 1st rotor in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 1st rotor, many one of the gear teeth of described the 1st rotor of the gear ratio of described trochoidal curve gear also are formed with the trochoidal curve gear teeth with the identical number of inner peripheral surface at outer circumferential face; The 3rd rotor holds described the 2nd rotor prejudicially in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 2nd rotor outer circumferential face, many one of the gear teeth of described the 2nd rotor of the gear ratio of described trochoidal curve gear; Shell, described the 1st rotor, the 2nd rotor and the 3rd rotor are held in sealing, and play a supportive role so that connect the live axle of the stationary axle of the 1st rotor and the 3rd rotor and be rotated to prolong outstanding state towards the outside; The 2nd attracts mouth and the 1st to attract mouth, be arranged at described live axle sidepiece and be used for the inside and outside of connected with outer casing, when the 2nd attraction mouth is located at the 1st rotor, the 2nd rotor and the 3rd rotor, the inboard gear of the gear of the 1st rotor and the 2nd rotor leaves mutually maximum position, and the 1st attracts the gear of mouthful outboard gears that is positioned at the 2nd rotor and the 3rd rotor to leave mutually maximum position; The 2nd exhaust port and the 1st exhaust port, the 2nd exhaust port is arranged at when the 1st rotor, the 2nd rotor and the 3rd rotor, the position that the inboard gear of the gear of described the 1st rotor and the 2nd rotor is adjacent to each other, the 1st exhaust port are positioned at the outboard gears of described the 2nd rotor and the gear position adjacent to each other of the 3rd rotor.
For reaching the compressor assembly of described purpose, it is characterized in that, comprising: compressor unit and drive portion with 3 heavy co-cycloidal rotors, wherein, compressor unit comprises: the 1st rotor, form a plurality of trochoidal curve gears at outer circumferential face, be fixed with stationary axle at its rotating center; The 2nd rotor, hold prejudicially described the 1st rotor in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 1st rotor, many one of the gear teeth of described the 1st rotor of the gear ratio of described trochoidal curve gear also form the trochoidal curve gear teeth with the inner peripheral surface equal number at outer circumferential face; The 3rd rotor holds described the 2nd rotor prejudicially in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 2nd rotor outer circumferential face, many one of the gear teeth of described the 2nd rotor of the gear ratio of described trochoidal curve gear; Shell, described the 1st rotor, the 2nd rotor and the 3rd rotor are held in sealing, and play a supportive role so that connect the live axle of the stationary axle of the 1st rotor and the 3rd rotor and be rotated to prolong outstanding state towards the outside; The 2nd attracts mouth and the 1st to attract mouth, be arranged at described live axle sidepiece and be used for the inside and outside of connected with outer casing, when the 2nd attraction mouth is located at the 1st rotor, the 2nd rotor and the 3rd rotor, the inboard gear of the gear of the 1st rotor and the 2nd rotor leaves mutually maximum position, and the 1st attracts the gear of mouthful outboard gears that is located at the 2nd rotor and the 3rd rotor to leave mutually maximum position; The 2nd exhaust port and the 1st exhaust port, the 2nd exhaust port is arranged at the 1st rotor, when the 2nd rotor and the 3rd rotor, the position that the inboard gear of the gear of described the 1st rotor and the 2nd rotor is adjacent to each other, the 1st exhaust port is positioned at the outboard gears of described the 2nd rotor and the gear position adjacent to each other of the 3rd rotor, drive portion, be connected in described live axle, apply running torque to live axle and rotate the 1st rotor, the 2nd rotor and the 3rd rotor, thereby can be by described attraction mouthful attraction operate outside fluid, simultaneously, by state discharging the working fluid by attract mouth attract of exhaust port with compression.
Described the present invention, it is characterized in that, connect the 1st exhaust port and the 2nd by connecting pipings and attract mouth, in order to the working fluid that attracted to described the 1st attraction mouth and discharge by the 1st exhaust port after 1 compression between the 2nd rotor and the 3rd rotor can be guided to the 2nd attraction mouth, and between the 1st rotor and the 2nd rotor, carry out 2 times and compress, the fluid of 1 discharging by the 2nd attraction mouthful attraction, therefore can reduce the temperature by the fluid of the 2nd exhaust port discharging after cool off the centre.
Described the present invention, it is characterized in that, further comprise: suction resistance prevents groove, when described the 1st rotor, the 2nd rotor and the 3rd rotor, be fixed in the inboard of the compressor shroud of outer cover at the centre rotational axis with the 1st rotor, attract the hole of mouth and the 2nd attraction mouth to prolong and form groove from the 1st; Compression residual gas rotational resistance prevents groove, prolongs from the hole of the 1st exhaust port and the 2nd exhaust port and forms groove; The compression ratio adjustment groove prolongs from the hole of the 1st exhaust port and the 2nd exhaust port and forms.
Described the present invention, it is characterized in that, has the compressor of 3 heavy co-cycloidal rotors except industrial compressor, also applicable to 2 grades of expansion turbine, 2 grades of fluid pumps, vacuum pump compressing expansion machine (compressor and decompressor) and expansion pumps (the inboard pump of outside decompressor).
The compressor assembly that has 2 stage compressor unit of 3 heavy co-cycloidal rotors and have a described compressor unit according to the present invention has following effect.
The first, therefore the present invention, can carry out 2 grades of compressions to working fluid, and can send working fluid by high pressure by consisting of compressor unit by 3 heavy co-cycloidal rotors.
The second, the present invention is by consisting of compressor unit by 3 heavy co-cycloidal rotors, therefore, increases the traffic attraction of working fluid and discharge capacity and the high speed and high pressure compression performance can be provided.
Description of drawings
Fig. 1 is in order to illustrate according to the drawing shown in the 2 stage compressor unit with 3 heavy co-cycloidal rotors of one embodiment of the invention.
Fig. 2 is the drawing of formation that the front shroud of the compressor unit among described Fig. 1 is shown.
Fig. 3 is the drawing of formation that the rotor of the compressor unit among described Fig. 1 is shown.
Fig. 4 is the drawing that the side of the compressor unit among described Fig. 1 is shown.
Fig. 5 is the drawing that illustrates according to the formation of the 2 stage compressor systems with 3 heavy co-cycloidal rotors of one embodiment of the invention.
Fig. 6 is the drawing that illustrates for the compression mechanism that the compressor assembly among described Fig. 5 is described.
Fig. 7 is the drawing that illustrates for other embodiments' that the compressor assembly among described Fig. 5 is described compression mechanism.
Fig. 8 is the drawing that the oil supply gallery of the 3rd rotor among described Fig. 1 is shown.
Fig. 9 is the drawing that the oil supply gallery of the 2nd rotor among described Fig. 1 is shown.
Figure 10 is the drawing that the oil supply gallery of the 1st rotor among described Fig. 1 is shown.
Among the figure:
1: the 1 attraction mouth, 2: the 1 attraction mouthful grooves, 3: the 2 attraction mouths, attracted a mouthful groove, 5: the 1 exhaust ports, 6: the 1 exhaust port compression ratio adjustment grooves in 4: the 2,1 exhaust port resistance prevented from using groove in 7: the, 8: the 2 exhaust ports, 9: the 2 exhaust port compression ratio adjustment grooves, 2 exhaust port resistances prevented from using groove, 11 in 10: the: pouring orifice, 12: compressor unit, 13: the 3 rotors, 14: the 2 rotors, 15: the 1 rotors, 16: axle center, 17: shell, 18: the co-cycloidal rotor assembly body, 19: compressor front shroud, 20: live axle, 21: drive portion, 22: oil separator dual-purpose fuel tank, 23: compressed air reservoir, 24: connecting pipings, 24-1: pouring orifice, 25: accumulator, the oil supply gallery of 26: the 3 rotors, the oil supply gallery of 27: the 3 rotors, 28: oily supply port, 29: lubrication channel, 30: oily passage, 31: oily passage, 32: lubrication channel, 33: oil supply gallery, 34: bearing, 35: oily passage, 36: oily passage
Embodiment
Below, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings then is as follows, but when explanation is of the present invention, be judged as in the time of to make main idea of the present invention indefinite for specifying of related known technology or formation, omit detailed description thereof, term described later is to consider function of the present invention and the term that defines, can be according to the user, fortune user's intention or convention etc. and different, therefore, its definition should be to illustrate that the whole content of this specification of compressor assembly that has the compressor unit of 3 heavy co-cycloidal rotors and have a described compressor unit of the present invention is as benchmark.
Below, describe in detail according to a preferred embodiment of the invention with reference to accompanying drawing.
Fig. 1 is in order to illustrate according to the drawing shown in the 2 stage compressor unit with 3 heavy co-cycloidal rotors of one embodiment of the invention, Fig. 2 is the drawing of formation that the front shroud of the compressor unit among described Fig. 1 is shown, Fig. 3 is the drawing of formation that the rotor of the compressor unit among described Fig. 1 is shown, Fig. 4 is the drawing that the side of the compressor unit among described Fig. 1 is shown, and Fig. 5 is the drawing that illustrates according to the formation of the 2 stage compressor systems with 3 heavy co-cycloidal rotors of one embodiment of the invention.
Among Fig. 2 in described figure, drawing symbol 11 is the pouring orifice towards the supply of wheel flank, symbol 24-1 is that symbol 25 is accumulator towards the pouring orifice of the accumulator side supply of compressor shroud inboard, is the oily cassette for supplying towards the 1st rotor, the 2nd rotor and the 3rd rotor and stationary axle centre bearing supply oil.Symbol 26 is the 3rd rotor oil supply gallery towards the 3rd rotor-side supply oil.
In Fig. 4, drawing symbol 34 is bearing, and symbol 35 is for to be formed on towards the oily passage of the inside of live axle 20, and symbol 36 is the oily passage that forms towards bearing 34 sides in live axle 20 inside.
Referring to figs. 1 through Fig. 5, the compressor unit 12 according to one embodiment of the invention comprises, 18,3 co-cycloidal rotors 14 of co-cycloidal rotor assembly body, 13,15 consist of with intermeshing state; Shell 17 is contained in its inside with described assembly body 18 sealings.Described shell 17 is made to have the cylindrical of predetermined diameter.
Described co-cycloidal rotor assembly body 18 comprises: the 1st rotor 15; Described the 1st rotor 15 is contained in the 2nd rotor 14 of the position of its inner off-centre; Described the 2nd rotor 14 is contained in the 3rd rotor 13 of the position of its inner off-centre.
Identical with common trochoid gear pump, described the 1st rotor 15 contacts with the 2nd rotor 14 intermeshing isochrones, contacts with the engagement line for the 2nd rotor 14, the 3 rotors.At the rotary middle spindle of described the 1st rotor 15, stationary axle is fixed in outer cover 19 by axle center 16.
And live axle 20 prolongs along its length and becomes as shown in Figure 5 with the state with 13 combinations of the 3rd rotor, runs through shell 17 and gives prominence to predetermined length towards the outside.Described live axle 20 obtains running torque and carries out the axle rotation from the drive portion 21 of outside.Described live axle 20 rotates as mentioned above, and with this, the 1st rotor 15, the 2nd rotor 14 and the 3rd rotor 13 also are rotated, and with reference to Fig. 5 described later as can be known, the live axle 20 of compressor unit 12 is connected in drive portion 21.Described drive portion 21 is motor or motors that moment can be provided.
The 1st attracts mouthful the 1 and the 2nd an attraction mouth 3 all opening, the 2nd exhaust port 8 is connected in oil separator dual-purpose fuel tank 22, the fluid of discharging promoted the pressure of the inside of oil separator dual-purpose fuel tanks 22 when the 1st rotor 15, the 2nd rotor 14 and the 3rd rotor 13 rotated by the 2nd exhaust port 8, thereby the lubricant oil of inside is fed to the 3rd rotor 13 and the 2nd rotor 14 by lubricated oiling 11.The pressure of described oil separator dual-purpose fuel tank 22 is connected in compressed air reservoir 23.Described compressed air reservoir 23 plays interim storage from the effect of the pressurized gas of compressor unit 12 dischargings, can not arrange according to embodiment.
When described compressed air reservoir 23 not being set, oil separator dual-purpose fuel tank 22 is directly connected in by the air venting connecting pipings needs the compressed-air actuated place that needs.When not needing high-pressure air, cut off the 2nd attraction mouth 3 that is connected with the 1st exhaust port 5, connect the 1st and attract mouth the 1 and the 2nd to attract mouth 3, connect the 2nd exhaust port 8 and the 1st exhaust port 5, compress the pressurized air that uses low pressure by 1 section.
As mentioned above, because the 1st attraction mouthful the 3 and the 2nd an attraction mouth 1 is connected to each other, attracts the amount of air also to become many with this, so once can discharge the low-pressure compressed air of volume.The compressor that consists of as mentioned above needing to be suitable for the high pressure of volume and the compressed-air actuated place of low pressure within the limited time.As mentioned above, attract mouthful the 3 and the 2nd attraction mouthful the 1 and the 1st exhaust port 5 and the 2nd to discharge by the 1st
But 8 connecting means simple production high pressure, low-pressure air illustrate the detailed driving mechanism of the 1st rotor, the 2nd rotor and the 3rd rotor of compressor unit 12 inside by Fig. 6.
With reference to Fig. 5 as can be known the 1st exhaust port 5 be connected in the 2nd by connecting pipings 24 and attract mouthfuls 3.And the 2nd exhaust port 8 is connected in oil separator dual-purpose fuel tank 22, and is connected in compressed air reservoir 23 by connecting pipings.
When consisting of as mentioned above, during by drive portion 21 axle rotating driveshaft 20, outside air attracts to attract mouth 1 to the 1st.Attract to the described the 1st to attract mouthful 1 air such as Fig. 2 to shown in Figure 4, the 1st attract mouthful groove 2 to the attraction air of under unresisted state, supplying volume between the 3rd rotor 13 and the 2nd rotor 14 along what the front shroud 19 at compressor was recessed to form.What be recessed to form in front shroud 19 inboards of compressor the 1st attracts mouthful groove 2 to use as the purpose of the resistance of the air that prevents from attracting, between the 2nd rotor 14 and the 3rd rotor 13, rotational shell 17 and by after 1 compression by the 1st exhaust port 5 exhausting air.At this moment, pressurized gas arrived compression ratio adjustment groove 6 before arriving the 1st exhaust port 5.The purpose of described compression ratio adjustment groove 6 is, adjusts the amount of compressed-air actuated compression ratio, 1 discharged air and the amount that attracts air 2 times, and the length of compression ratio adjustment groove 6 according to adjusting compressed-air actuated amount difference.The air of compression by the discharging of the 1st exhaust port 5 after, in order to prevent the residual air compression, and shown in Fig. 2 to 7, form the pressurized air resistance that depression forms in the inboard of the front shroud 19 of compressor and prevent with groove 7.Described resistance prevents from being with the purpose of groove 7, and pressurized air discharges 5 the 1st not have all dischargings and compressed and provide resistance to the rotation of rotor, thus the lubricant oil that successfully discharging is supplied.
Pressurized air by 5 dischargings of described the 1st exhaust port attracts mouth 3 to move by connecting pipings 24 towards the 2nd, such as Fig. 2 and shown in Figure 4, described pressurized air attracts between the 2nd rotor 14 and the 1st rotor 15 without suction resistance ground along the 2nd attraction mouthful groove 4 of front shroud 19 inboards of compressor, the described the 2nd attracts the purpose of mouthful groove 4 to be, prevent the compressed-air actuated suction resistance that attracts, and again compressed and arrive compression ratio adjustment groove 9 between the 1st rotor 15 and the 2nd rotor 14.The purpose of described compression ratio adjustment groove 9 is to regulate compression ratio.
Through described compression ratio adjustment groove 9 and by 8 dischargings of the 2nd exhaust port, and the residual air that is not discharged and the oil pressurized air resistance by the 2nd exhaust port prevents with groove (Fig. 2 10) discharging.Described the 2nd exhaust port resistance prevents from being with the purpose of groove 10, removes the rotational resistance of rotor and is rotated smoothly by the compression of compression residual air and oil.Be discharged into when being fed to oil separator dual-purpose fuel tank 22 behind shell 17 outsides by described the 2nd exhaust port 8, because the rising of internal pressure, with pouring orifice 11 grooves of interior oil by compressor front shroud 19, to supplying lubricating oil between the 3rd rotor 13 and the 2nd rotor 14.At this moment, the 3rd rotor 13 and the 2nd rotor are opened first, and therefore, its inside becomes vacuum, thereby pass through the smooth supplying lubricating oil of interior pressure of oil separator dual-purpose fuel tank 22.
As mentioned above, the pressurized air that is gathered in oil separator dual-purpose fuel tank 22 moves to compressed air reservoir 23 by connecting pipings and is stored temporarily, and when need not to store pressurized air, can need not to arrange described compressed air reservoir 23.
Fig. 6 is the drawing that illustrates for the compression mechanism that the compressor assembly among described Fig. 5 is described.
The motion mechanism of compressor as shown in Figure 5 is for attracting simultaneously working fluid by 2 attraction mouths and discharging simultaneously by 2 exhaust ports.
As shown in Figure 6, when described live axle 20 rotation, with this, whole co-cycloidal rotor assembly body 18 is rotated, at this moment, being formed with the 1st attracts mouthful the 1st rotor 15 of the 1 and the 2nd attraction mouth 3 and the space between the space between the 2nd rotor 14 and the 2nd rotor 14 and the 3rd rotor 13 to be expanded.Therefore, the pressure step-down between the 1st rotor 15, the 2nd rotor 14 and the 3rd rotor 13, thus shown in Fig. 6 a, outside working fluid attracts mouthful the 1 and the 2nd attraction mouth 3 to flow into the inside of shell 17 by the 1st.
Under described state, when continuing rotating driveshaft 20, shown in Fig. 6 a, working fluid is to be closed in state between the 1st rotor 15, the 2nd rotor 14 and the 3rd rotor 13 and to be rotated and compressed, and near towards the 1st exhaust port 5 and the 2nd exhaust port 8 side joints.
Shown in Fig. 6 c, when the working fluid that moves with the state that is closed between the 1st rotor 15, the 2nd rotor 14 and the 3rd rotor 13 just in time arrives the 1st exhaust port 5 and the 2nd exhaust port 8, working fluid is discharged simultaneously by the 1st exhaust port 5 and the 2nd exhaust port 8, and then being supplied to needs to locate or be stored in the compressed air reservoir 23 temporarily.
Fig. 7 is the drawing that illustrates for other embodiments' that the compressor assembly among described Fig. 5 is described compression mechanism.
Generally, the motion mechanism of compressor unit as shown in Figure 5 at first is attracted to working fluid the 1st and attracts mouthful 1 and after carrying out 1 compression, attracts mouthfuls 3 to carry out 2 compressions in shell 17 via the 1st exhaust port 5 and the 2nd, finally by 8 dischargings of the 2nd exhaust port.
Shown in Fig. 7 a, during by drive portion 21 (Fig. 5) rotating driveshaft 20, outside working fluid attracts mouth 1 to move to shell 17 inside by the 1st.Attract mouthful 1 working fluid that moves to shell 17 inside being closed in the state between the 2nd rotor 14 and the 3rd rotor 13 by the described the 1st, in the time of towards the 1st exhaust port 5 side shifting compressed (with reference to Fig. 7 b, 7c).
Shown in Fig. 7 c, the working fluid that arrives the 1st exhaust port 5 flows out to the outside of shell 17 by the 1st exhaust port 5, and moves to the 1st attraction mouth 3 by connecting pipings 24 (Fig. 5).
As implied above, move to the working fluid of the 2nd attraction mouth 3, shown in Fig. 7 d, after between attraction to the 1 rotor 15 and the 2nd rotor 14, shown in Fig. 7 c, with compressed state again between the 1st rotor 15 and the 2nd rotor 14, move to the 2nd exhaust port 8 and be discharged into outside (with reference to Fig. 7 f).
In addition, Fig. 8 is the drawing that the oil supply gallery of the 3rd rotor among described Fig. 1 is shown, and Fig. 9 is the drawing that the oil supply gallery of the 2nd rotor among described Fig. 1 is shown, and Figure 10 is the drawing that the oil supply gallery of the 1st rotor among described Fig. 1 is shown.
With reference to the lubrication system of described drawing explanation according to the compressor unit of one embodiment of the invention.
Oil separator dual-purpose fuel tank 22 (Fig. 5) externally, supply oil to the oiling 11 (Fig. 2) and the oil supply inlet 24 (Fig. 2) that are positioned at the front outer cover 19 (Fig. 4) of compressor, and the oil that flow into oil supply inlet 24 (Fig. 2) is filled in accumulator 25 (Fig. 2) and the oil supply gallery 26 (Fig. 2) of the inboard that is positioned at front shroud, and as shown in Figure 9, supply oil to the oil supply gallery 27 that is formed at the 3rd rotor 13 with circle, make to become lubricated between the outer cover 19 of the 3rd rotor 13 and front side.
With reference to Figure 10 that the oil supply gallery of the 2nd rotor 14 is shown, accumulator 25 (Fig. 2) and the oil supply gallery 26 (Fig. 2) of the inboard by being positioned at front shroud, to the 2nd rotor 14, the 1st rotor 15 and stationary axle bearing supply oil, and the oily passage 30 (Figure 10) by the 2nd rotor 14 makes it lubricated to wheel toothed portion supply oil, and by the oily hole of supplying 28 (Figure 10), the 2nd rotor 14 supply oil that contact to the live axle with the gear opposition side make it lubricated.
In Fig. 9, symbol 29 is illustrated in the lubrication channel of the rotor wheel toothed portion in the 2nd rotor 14.
With reference to Figure 10 of the oil supply gallery of the 1st rotor 15 is shown, the accumulator 25 (Fig. 2) of the inboard by being positioned at front shroud makes the gear side become lubricated to oil supply gallery 33 supply oil, and makes to wheel toothed portion supply oil and to become lubricated between front shroud and the gear.At this moment, the hole by oily passage 31 makes live axle and Gear Contact Surface become lubricated to the oily passage 31, lubrication channel 32, the oil supply gallery 33 supply oil that are positioned at the part of opposite direction live axle and gear contacts side surfaces.
In Figure 10, drawing symbol 32 is lubrication channels of the toothed portion of the 1st rotor 15.
On the one hand, the oil of sending from oil separator dual-purpose fuel tank 22 passes through the oily passage 35 of Fig. 4, and by oily passage 36 supplies, finally runs through the center of the 1st rotor 15 in the rotor assembling body 18, to the stationary axle bearing 34 supply oil of the outer cover 19 that is arranged at the front side.
As mentioned above, according to the 2 stage compressor unit of one embodiment of the invention, accelerate the mass rate of emission of working fluid or carry out the compression in 2 stages, thereby embody the compressive force of high pressure.
The aforesaid compressor assembly that has 2 stage compressor unit of 3 heavy co-cycloidal rotors and have described compressor unit is applicable to the industrial compressor of the compressive force that can embody high pressure, 2 grades of expansion turbine, 2 grades of fluid pumps, vacuum pump compressing expansion machine (compressor decompressor), expansion pump (the inboard pump of outside decompressor).
Having disclosed best embodiment in drawing and specification, but term purpose of the present invention and using as an illustration just as used herein, is not in order to limit definition or to be limited in the scope of the present invention of putting down in writing in the claim scope and to use.Therefore, those skilled in the art can carry out various deformation and other impartial embodiments thus, and therefore, real technical protection scope of the present invention should be determined by the technological thought of claim scope.
Claims (8)
1. a stage compressor unit is characterized in that, comprising:
The 1st rotor forms a plurality of trochoidal curve gears at outer circumferential face, is fixed with stationary axle at its rotating center;
The 2nd rotor, hold prejudicially described the 1st rotor in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 1st rotor, many one of the gear teeth of described the 1st rotor of the gear ratio of described trochoidal curve gear also are formed with the trochoidal curve gear teeth with the identical number of inner peripheral surface at outer circumferential face;
The 3rd rotor holds described the 2nd rotor prejudicially in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 2nd rotor outer circumferential face, many one of the gear teeth of described the 2nd rotor of the gear ratio of described trochoidal curve gear;
Shell, described the 1st rotor, the 2nd rotor and the 3rd rotor are held in sealing, and play a supportive role so that connect the live axle of the stationary axle of the 1st rotor and the 3rd rotor and be rotated to prolong outstanding state towards the outside;
The 2nd attracts mouth and the 1st to attract mouth, be arranged at described live axle sidepiece and be used for the inside and outside of connected with outer casing, when the 2nd attraction mouth is located at the 1st rotor, the 2nd rotor and the 3rd rotor, the inboard gear of the gear of the 1st rotor and the 2nd rotor leaves mutually maximum position, and the 1st attracts the gear of mouthful outboard gears that is positioned at the 2nd rotor and the 3rd rotor to leave mutually maximum position;
The 2nd exhaust port and the 1st exhaust port, the 2nd exhaust port is arranged at when the 1st rotor, the 2nd rotor and the 3rd rotor, the position that the inboard gear of the gear of described the 1st rotor and the 2nd rotor is adjacent to each other, the 1st exhaust port are positioned at the outboard gears of described the 2nd rotor and the gear position adjacent to each other of the 3rd rotor.
2. 2 stage compressor unit according to claim 1, it is characterized in that, further comprise: suction resistance prevents groove, when described the 1st rotor, the 2nd rotor and the 3rd rotor, be fixed in the inboard of the compressor shroud of outer cover at the centre rotational axis with the 1st rotor, attract the hole of mouth and the 2nd attraction mouth to prolong and form groove from the 1st; Compression residual gas rotational resistance prevents groove, prolongs from the hole of the 1st exhaust port and the 2nd exhaust port and forms groove; The compression ratio adjustment groove prolongs from the hole of the 1st exhaust port and the 2nd exhaust port and forms.
3. a compressor assembly is characterized in that, comprising:
Have 2 stage compressor unit of 3 heavy co-cycloidal rotors, comprising:
The 1st rotor forms a plurality of trochoidal curve gears at outer circumferential face, is fixed with stationary axle at its rotating center;
The 2nd rotor, hold prejudicially described the 1st rotor in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 1st rotor, many one of the gear teeth of described the 1st rotor of the gear ratio of described trochoidal curve gear also form the trochoidal curve gear teeth with the inner peripheral surface equal number at outer circumferential face;
The 3rd rotor holds described the 2nd rotor prejudicially in inside, and side face formation within it is engaged in the trochoidal curve gear of the gear doubling contact of the 2nd rotor outer circumferential face, many one of the gear teeth of described the 2nd rotor of the gear ratio of described trochoidal curve gear;
Shell, described the 1st rotor, the 2nd rotor and the 3rd rotor are held in sealing, and play a supportive role so that connect the live axle of the stationary axle of the 1st rotor and the 3rd rotor and be rotated to prolong outstanding state towards the outside;
The 2nd attracts mouth and the 1st to attract mouth, be arranged at described live axle sidepiece and be used for the inside and outside of connected with outer casing, when the 1st attraction mouth is located at the 1st rotor, the 2nd rotor and the 3rd rotor, the inboard gear of the gear of the 1st rotor and the 2nd rotor leaves mutually maximum position, and the 1st attraction mouth is located at the outboard gears of the 2nd rotor and the gear of the 3rd rotor leaves mutually maximum position;
The 2nd exhaust port and the 1st exhaust port, the 2nd exhaust port is arranged at when the 1st rotor, the 2nd rotor and the 3rd rotor, the position that the inboard gear of the gear of described the 1st rotor and the 2nd rotor is close, the 1st exhaust port are positioned at the outboard gears of described the 2nd rotor and the close position of gear of the 3rd rotor
Drive portion, be connected in described live axle, and apply running torque and rotate the 1st rotor, the 2nd rotor and the 3rd rotor to live axle, thus can be by described attraction mouthful attraction operate outside fluid, simultaneously, the working fluid that is attracted with the state discharging of compressing by exhaust port.
4. compressor assembly according to claim 3, it is characterized in that, for the working fluid that will attracted to described the 1st attraction mouth and discharge by the 1st exhaust port after 1 compression between the 2nd rotor and the 3rd rotor guides to the 2nd attraction mouth, and between the 1st rotor and the 2nd rotor, carry out 2 times and compress, and the 1st exhaust port and the 2nd is attracted mouthful to be connected to the inside of outside connecting pipings or front shroud, attract mouthful and attract thereby connect the 1st exhaust port and the 2nd.
5. compressor assembly according to claim 3, it is characterized in that, further comprise: suction resistance prevents groove, when described the 1st rotor, the 2nd rotor and the 3rd rotor, be fixed in the inboard of the compressor shroud of outer cover at the centre rotational axis with the 1st rotor, attract the hole of mouth and the 2nd attraction mouth to prolong and form groove from the 1st; Compression residual gas rotational resistance prevents groove, prolongs from the hole of the 1st exhaust port and the 2nd exhaust port and forms groove; The compression ratio adjustment groove prolongs from the hole of the 1st exhaust port and the 2nd exhaust port and forms.
6. according to claim 1 or 3 described compressor assemblies, it is characterized in that, have 2 stage compressor unit of 3 heavy co-cycloidal rotors except industrial compressor, also applicable to one in 2 grades of expansion turbine, 2 grades of fluid pumps, vacuum pump, compressing expansion machine (compressor and decompressor) and the turboexpander pumps (outside expansion turbine and inboard pump).
7. compressor assembly according to claim 3 is characterized in that, comprises lubrication system,
In the inboard of compressor front shroud accumulator and oil supply gallery are set, to the oil supply gallery supply oil of the 3rd rotor,
Part in the 1st rotor, the 2nd rotor, the contact of the 3rd rotor arranges accumulator, to the 1st rotor, the 2nd rotor, the 3rd rotor and central fixed shaft bearing supply oil,
Form oily circle groove at described each rotor, make the surface of contact of compressor front shroud and described each rotor become lubricated.
8. compressor assembly according to claim 3 is characterized in that, further comprises lubrication system,
Oily by the oily passage supply that is formed on live axle inside, and oily to the bearing supply that is disposed at live axle by the oily passage that forms towards the bearing side in live axle inside,
Oily by the oily passage supply that is formed on live axle inside, and the 1st rotor center that runs through in live axle and the rotor assembling body is oily to the bearing supply that is disposed at the stationary axle that is arranged on the compressor front shroud.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/KR2013/001842 WO2013133641A1 (en) | 2012-03-07 | 2013-03-07 | Two-stage compressor unit and compressor system having same |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US13/414,253 US20130236345A1 (en) | 2012-03-07 | 2012-03-07 | Compressor unit including gear rotor and compressor system using the same |
| US13/414,253 | 2012-03-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103306977A true CN103306977A (en) | 2013-09-18 |
Family
ID=49114287
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012104193644A Pending CN103306977A (en) | 2012-03-07 | 2012-10-29 | Compressor unit of grade two and compressor system using the same |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US20130236345A1 (en) |
| CN (1) | CN103306977A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109252945A (en) * | 2018-05-17 | 2019-01-22 | 左方 | Cycloid rotor engine |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106321422A (en) * | 2016-09-29 | 2017-01-11 | 武汉大学 | Two-stage internal gear pump |
| WO2019054637A1 (en) * | 2017-09-13 | 2019-03-21 | 엘지이노텍 주식회사 | Electric pump and motor |
| CN109827059A (en) * | 2019-01-23 | 2019-05-31 | 浙江零跑科技有限公司 | A kind of cycloid gear pump of two-way fuel feeding |
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|---|---|---|---|---|
| US2737341A (en) * | 1950-02-25 | 1956-03-06 | Trico Products Corp | Rotary pump |
| US4658583A (en) * | 1984-06-11 | 1987-04-21 | Trw Inc. | Double staged, internal rotary pump with flow control |
| US5310326A (en) * | 1992-09-14 | 1994-05-10 | Mainstream Engineering Corporation | Rotary compressor with improved bore configuration and lubrication system |
| US20030140717A1 (en) * | 2002-01-29 | 2003-07-31 | Bennett John L. | Planetary drive assembly with idlers for low floor vehicle |
| CN1474059A (en) * | 1997-09-17 | 2004-02-11 | ������������ʽ���� | Vortes compressor |
| JP2004060545A (en) * | 2002-07-29 | 2004-02-26 | Yamada Seisakusho Co Ltd | Trochoid pump |
| KR100530447B1 (en) * | 2003-10-06 | 2005-11-25 | 김우균 | Compressor unit having triple trochoidal rotor and Compressor having the compressor unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6195990B1 (en) * | 1999-01-13 | 2001-03-06 | Valeo Electrical Systems, Inc. | Hydraulic machine comprising dual gerotors |
| JP3626166B2 (en) * | 2003-01-17 | 2005-03-02 | 日産自動車株式会社 | Hybrid transmission |
-
2012
- 2012-03-07 US US13/414,253 patent/US20130236345A1/en not_active Abandoned
- 2012-10-29 CN CN2012104193644A patent/CN103306977A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2737341A (en) * | 1950-02-25 | 1956-03-06 | Trico Products Corp | Rotary pump |
| US4658583A (en) * | 1984-06-11 | 1987-04-21 | Trw Inc. | Double staged, internal rotary pump with flow control |
| US5310326A (en) * | 1992-09-14 | 1994-05-10 | Mainstream Engineering Corporation | Rotary compressor with improved bore configuration and lubrication system |
| CN1474059A (en) * | 1997-09-17 | 2004-02-11 | ������������ʽ���� | Vortes compressor |
| US20030140717A1 (en) * | 2002-01-29 | 2003-07-31 | Bennett John L. | Planetary drive assembly with idlers for low floor vehicle |
| JP2004060545A (en) * | 2002-07-29 | 2004-02-26 | Yamada Seisakusho Co Ltd | Trochoid pump |
| KR100530447B1 (en) * | 2003-10-06 | 2005-11-25 | 김우균 | Compressor unit having triple trochoidal rotor and Compressor having the compressor unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109252945A (en) * | 2018-05-17 | 2019-01-22 | 左方 | Cycloid rotor engine |
Also Published As
| Publication number | Publication date |
|---|---|
| US20130236345A1 (en) | 2013-09-12 |
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Application publication date: 20130918 |