CN100460675C - Combined compressing apparatus - Google Patents

Combined compressing apparatus Download PDF

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Publication number
CN100460675C
CN100460675C CNB2006101567842A CN200610156784A CN100460675C CN 100460675 C CN100460675 C CN 100460675C CN B2006101567842 A CNB2006101567842 A CN B2006101567842A CN 200610156784 A CN200610156784 A CN 200610156784A CN 100460675 C CN100460675 C CN 100460675C
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CN
China
Prior art keywords
compressor
compressing apparatus
pressurized gas
crankcase
end plate
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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.)
Expired - Fee Related
Application number
CNB2006101567842A
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Chinese (zh)
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CN101000049A (en
Inventor
井上弘
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Anest Iwata Corp
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Anest Iwata Corp
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Publication of CN101000049A publication Critical patent/CN101000049A/en
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Expired - Fee Related legal-status Critical Current
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

In a scroll compressor, a fixed wrap of a fixed end plate engages with an orbiting wrap of an orbiting plate to form a compressing chamber. A gas is introduced into the compressing chamber from the outer circumference and compressed towards the center as the orbiting end plate revolves with a driving shaft with respect to the fixed end plate. The gas is sent to a reciprocating compressor in which a piston moves up and down in a cylinder and further compressed therein.

Description

Combined compressing apparatus
Technical field
The present invention relates to a kind of in downstream compressor, the compression from the combined compressing apparatus of the pressurized gas of upstream compressor discharge.
Background technique
JP2703319B2 has disclosed a kind of combined compressing apparatus, wherein turbocompressor (turbo-type compressor) is used as the upstream compressor, and positive displacement compressor (volume-typecompressor) (for example reciprocal compressor or scroll compressor) is as downstream compressor.A pressurized gas in the turbocompressor advances to positive displacement compressor, and wherein pressurized gas is further compressed in described positive displacement compressor and discharges as the secondary high-pressure pressurized gas.
Yet, in known combined compressing apparatus, a large amount of low pressure pressurized gass is discharged from the turbocompressor as the upstream compressor, make that big positive displacement compressor is used to draw a large amount of pressurized gass from turbocompressor, thereby make the size of described combined compressing apparatus big and increase dynamic load.
Summary of the invention
Consider shortcoming of the prior art, an object of the present invention is to provide a kind of combined compressing apparatus, described combined compressing apparatus makes size less and reduce dynamic load, thereby produces high pressure compressed gas effectively.
An object of the present invention is to provide a kind of combined compressing apparatus, comprise: scroll compressor, described scroll compressor comprises live axle, fixed charge method end plate and be installed to the moving end plate of described live axle in rotatable mode, the fixed scroll of described fixed charge method end plate engages with the moving scroll of described moving end plate to form pressing chamber, by the gas that the rotation of described live axle is introduced towards central authorities via the vortex inlet of the excircle that is arranged in described fixed charge method end plate with respect to the rotating described moving end plate compression of described fixed charge method end plate, discharge a pressurized gas to export via the vortex that is positioned at central authorities; And reciprocal compressor, described reciprocal compressor comprises cylinder and the piston that moves up and down in described cylinder, described cylinder has cylinder inlet and cylinder outlet, described cylinder inlet is connected to described vortex outlet, is compressed so that a described pressurized gas can be introduced in the described cylinder and by the to-and-fro motion in described cylinder of described piston.
Description of drawings
The features and advantages of the present invention will become clearer from the following explanation about as shown in the drawing embodiment, wherein:
Fig. 1 is the schematic representation according to combined compressing apparatus of the present invention;
Fig. 2 is the vertical cross-section diagram according to first embodiment of combined compressing apparatus of the present invention; And
Fig. 3 is the vertical cross-section diagram according to second embodiment of combined compressing apparatus of the present invention.
Embodiment
As shown in fig. 1, in combined type compressor according to the present invention (combined compressor), fabulous and the scroll compressor 1 of saving energy of noiseless is as the upstream compressor, and simple in structure and reciprocal compressor 2 that high pressure can be provided is as downstream compressor.A pressurized gas A by scroll compressor 1 compression is sent to reciprocal compressor 2, and wherein pressurized gas A further is compressed into the secondary compression gas B of the high pressure that will be sent to container 3 by described reciprocal compressor.
First embodiment of combined compressing apparatus shown in Figure 2, wherein the rear portion of the cylindrical housings 11 of scroll compressor 1 is fixed to the front portion of the crankcase 22 of reciprocal compressor 2.Monomotor 4 is installed to the rear portion of crankcase 22.The effect of motor 4 is as being used to drive the power source of scroll compressor 1 and reciprocal compressor 2.
Scroll compressor 1 comprises the involute fixed scroll (involutefixed wrap) 13 that is positioned at seal casinghousing 11 and engages to form the moving scroll (orbiting wrap) 15 of pressing chamber 16 with fixed scroll 13.
Fixed scroll 13 is set on the back side of fixed charge method end plate 12, and moving scroll 15 is set in rotatable mode and is installed on the moving end plate 14 in the housing 11.
Moving end plate 14 is installed to the eccentric axial portion 42 of live axle 41 in rotatable mode, and wherein said live axle is by the central authorities of the hood 24 at the back side of enclosing housing 11 and by motor 4 rotations.Hood 24 still is the part of crankcase 22 of reciprocal compressor 2.Moving end plate 14 turns round with eccentric manner by the rotation of live axle 41, and is connected to hood 24 with the anti-locking apparatus 17 of three crankpin formulas spinning that is positioned on the circumference.
The excircle of the fixed charge method end plate 12 of housing 11 and centre have the vortex that is used for that extraneous gas sucked the vortexs inlet 111 in the pressing chamber 16 and is used to discharge a pressurized gas A of compression pressing chamber 16 in respectively and export 112.
When moving end plate 14 turned round with eccentric manner by motor 4, the volume of the pressing chamber 16 that is limited by fixed scroll 13 and moving scroll 15 reduced gradually from excircle to central authorities.Therefore, the extraneous gas that sucks from vortex inlet 111 is gradually reduced towards the center, and a pressurized gas A discharges from vortex outlet 112.A pressurized gas A from vortex outlet 112 advances to reciprocal compressor 2, and part is introduced in the crankcase 22 of reciprocal compressor 2.
In reciprocal compressor 2, piston 23 in cylinder 21 to-and-fro motion to suck and to discharge gas repeatedly.Be useful on a pressurized gas A who to discharge from vortex outlet 112 on the cylinder 23 and introduce cylinder inlet 25 in the cylinder 21 and the cylinder outlet 26 that is used to discharge the secondary compression gas B of compression in cylinder 21.
The crankshaft 43 of piston 23 by the live axle 41 that driven by motor 4 is through piston rod 27 to-and-fro motion in cylinder 21.
Be useful on the crankcase that will partly suck in the crankcase 22 in the top of crankcase 22 and enter the mouth 221 from the pressurized gas A that vortex outlet 112 is discharged.
Piston 23 to-and-fro motion in cylinder 21 makes that a pressurized gas A is introduced and further is compressed from cylinder inlet 25 by the suction valve on the piston in the cylinder 21 23 28.Then, the secondary compression gas B of high pressure discharges and is sent to container 3 by expulsion valve 26 from cylinder outlet 26.
During the to-and-fro motion of piston 23, a pressurized gas A who discharges from the vortex outlet 112 of scroll compressor 1 is partly introduced in the crankcase 22, so that the internal pressurization of crankcase 22 is to being higher than barometric pressure.Thereby pressurized gas in the pressing chamber on the piston 23 and the pressure difference between the pressurized gas in the crankcase 22 are less than the barometric pressure degree in the crankcase 22.Therefore, if the upper surface of piston 23 and the pressure difference between the lower surface are very big, the then quick and powerful downward application of force acts on the piston 23, makes the too much and unequal application of force be applied to the external peripheral surface of piston 23, thereby causes piston ring, bearing and sealed department to break down too early.In an embodiment of the present invention, pressure difference becomes less and breaks down to avoid causing too early, thereby discharges the pressurized gas of less high pressure effectively.
In first embodiment, fabulous and the pressurized gas A that save energy of the noiseless of compression is compressed in reciprocal compressor 2 once more in scroll compressor 1, wherein said reciprocal compressor is simple in structure, and has the high pressure usability so that secondary high-pressure pressurized gas B discharges.Scroll compressor 1 and reciprocal compressor 2 are driven by monomotor 4 together, thereby reduce size and save cost.In addition, as mentioned above, a pressurized gas A who discharges from the vortex outlet 112 of scroll compressor 1 partly is introduced in the crankcase 22, thereby reduces the size of reciprocal compressor 2 and improve noiseless.
Among second embodiment of the combined compressing apparatus in Fig. 3, scroll compressor 1 and reciprocal compressor 3 comprise separately the motor 4,5 as power source.Selector valve 6 is set on the fluid path, and wherein a pressurized gas A of compression enters the mouth 25 via the cylinder that described fluid path advances to reciprocal compressor 2 in scroll compressor 1.In addition similar to first embodiment.Identical symbol branch is tasked the member identical with member among first embodiment and is omitted explanation to it.
The motor 5 that is used to drive scroll compressor 1 is installed in the front of the cylindrical housings 11 of sealing.Moving end plate 14 with moving scroll 15 is installed to by motor 5 in rotatable mode and drives and the eccentric axial portion 52 of the live axle 51 at hood 18 centers by housing 11, and described moving end plate is connected to hood 18 to turn round with eccentric manner by the rotation of live axle 51 by the anti-locking apparatus 17 of crankpin formula spinning.
Be useful on the top of housing 11 extraneous gas is sucked vortexs inlet 111A in the pressing chamber 16, be used to discharge a pressurized gas that pressing chamber 16 compressed passes fixed charge method end plate 12 with the vortexs outlet 112A in the crankcase 22 of described gas being introduced reciprocal compressor 2 center.
A pressurized gas A who discharges from vortex outlet 112A is introduced in the crankcase 22 via the axially extended through hole 44 in end towards the live axle 41 of motor 4.
Be formed with on the top of crankcase 22 to be used to discharge introduce a pressurized gas A in the crankcase 22 and make described gas advance to cylinder inlet 25 interior crankcases and export 222.
Selector valve 6 is set on the fluid path between crankcase outlet 222 and the cylinder inlet 25, is used to make pressurized gas A that discharge from crankcase outlet 222 to advance to enter the mouth second fluid path 10 in the downstream side that 25 first fluid path 9 or be transformed into is used to make described gas advance to cylinder outlet 26 around reciprocal compressor 2 of cylinder so that selector valve 6 can be transformed into.
Selector valve 6 is changed by the control gear 7 with circuit, and motor 4,5 is driven, stops and being controlled by control gear 7.The pressure transducer 8 that is used for the pressure of measuring vessel 3 is set at the downstream side of cylinder outlet 26.Information such as the measured value of pressure transducer 8 is transferred to control gear 7, when the pressurized gas that advances to container 3 is increased motor 4,5 is stopped.
For obtaining secondary high-pressure pressurized gas B, the switch (not shown) that is used for control gear 7 is switched to the high pressure side.Therefore, open in the first fluid path 9 of selector valve 6 and second fluid path 10 is closed, thereby motor 4,5 is driven together.
As a result, scroll compressor 1 and reciprocal compressor 2 all activated, and make a pressurized gas A who compresses in scroll compressor 1 be introduced in the crankcase 22 and from crankcase outlet 222 via vortex outlet 112A and through hole 44 and discharge.
Advance to cylinder inlet 25 by selector valve 6 and first fluid path 9 and be introduced in the cylinder 21 from a pressurized gas A of crankcase outlet 222.Therefore, secondary high-pressure pressurized gas B discharges from cylinder outlet 26.
For obtaining low pressure pressurized gas A one time, the switch of control gear 7 is switched to low voltage side.Therefore, the solenoid 61 of selector valve 6 magnetizes, with the first fluid path 9 of closing selector valve 6 and open second fluid path 10 and drive motor 5 only.As a result, only there is scroll compressor 1 to operate, makes a pressurized gas A who in scroll compressor 1, compresses be introduced in the crankcase 22 and and discharge from crankcase outlet 222 via vortex outlet 112A and through hole 44.And can not advance to cylinder inlet 25 from the pressurized gas A that crankcase outlet 222 is discharged, but advance to the downstream side of cylinder outlet 26 by the selector valve 6 and second fluid path 10.
In a second embodiment, similarly to first embodiment can obtain the secondary high-pressure pressurized gas effectively.A pressurized gas A of compression is introduced in the crankcase 22 in scroll compressor 1, thereby makes reciprocal compressor 2 become littler and improve noiseless.In addition, if desired, can optionally obtain low pressure pressurized gas A and secondary compression gas B by conversion selector valve 6.Especially, when a low pressure pressurized gas of needs A, reciprocal compressor 2 stops so that only there being scroll compressor 1 to be driven, thereby improves noiseless and save energy.
Embodiments of the invention have been described, and under the prerequisite of the scope that does not depart from following claim, can have made following change and modification.
(i) in first embodiment in scroll compressor 1 compression and a pressurized gas A discharging described in second embodiment, be introduced directly in the crankcase 22 of reciprocal compressor 2.And a pressurized gas A who introduces in the crankcase 22 discharges and advances to cylinder inlet 25 from crankcase 22.
(ii) in a second embodiment in scroll compressor 1 compression and implement as first from the pressurized gas A that scroll compressor 1 is discharged described in partly introduced in the crankcase 22 of reciprocal compressor.
(iii) in a second embodiment, be higher than particular value according to the pressure transducer 8 measured numerical value of measuring the pressure of storage from the container 6 of the secondary compression gas B of cylinder outlet 26 discharges of reciprocal compressor 2, selector valve 6 cuts out first fluid path 9 and second fluid path 10 is opened, and being lower than particular value according to pressure transducer 8 measured numerical value, selector valve 6 is opened first fluid path 9 and second fluid path 10 is closed.

Claims (13)

1. combined compressing apparatus comprises:
Scroll compressor, described scroll compressor comprises live axle, fixed charge method end plate and is installed to the moving end plate of described live axle in rotatable mode, the fixed scroll of described fixed charge method end plate engages with the moving scroll of described moving end plate to form pressing chamber, by the gas that the rotation of described live axle is introduced towards central authorities via the vortex inlet of the excircle that is arranged in described fixed charge method end plate with respect to the rotating described moving end plate compression of described fixed charge method end plate, discharge a pressurized gas to export via the vortex that is positioned at central authorities; And
Reciprocal compressor, described reciprocal compressor comprises cylinder and the piston that moves up and down in described cylinder, described cylinder has cylinder inlet and cylinder outlet, described cylinder inlet is connected to described vortex outlet, is compressed so that a described pressurized gas can be introduced in the described cylinder and by the to-and-fro motion in described cylinder of described piston.
2. combined compressing apparatus according to claim 1, wherein said reciprocal compressor further comprise crankcase, be installed to piston rod on the lower surface of described piston and the crankshaft that is connected to the bottom of described piston rod in described crankcase in described crankcase.
3. combined compressing apparatus according to claim 2, wherein said scroll compressor and described reciprocal compressor are driven by single power source.
4. combined compressing apparatus according to claim 3, wherein said power source comprises motor.
5. combined compressing apparatus according to claim 2, wherein said vortex outlet is also connected to the crankcase inlet of described crankcase, so that a described pressurized gas is introduced in the described crankcase to increase the internal pressure in the described crankcase.
6. combined compressing apparatus according to claim 3, the described live axle that wherein drives described moving end plate is connected to the described crankshaft of described reciprocal compressor, so that described scroll compressor and described reciprocal compressor are driven together.
7. combined compressing apparatus according to claim 1, wherein said scroll compressor and described reciprocal compressor are respectively by first and second drive power source.
8. combined compressing apparatus according to claim 7, wherein said power source comprises motor.
9. combined compressing apparatus according to claim 7, comprise further being positioned at a described pressurized gas that described selector valve is used for making a described pressurized gas advance to described reciprocal compressor or directly discharging and can not advance between the described reciprocal compressor and change from the selector valve of described scroll compressor to the flow path of described reciprocal compressor.
10. whether combined compressing apparatus according to claim 9 further comprises the control gear that is connected to described control valve, be used for should being sent between the described reciprocal compressor at a described pressurized gas changing.
11. combined compressing apparatus according to claim 10, further comprise the container of final reception pressurized gas and the pressure transducer of measuring the pressure in the described container, whether described pressure transducer is connected to described control gear with pressure information in the container that transmits described control gear, should further be compressed in described reciprocal compressor to determine a described pressurized gas.
12. combined compressing apparatus according to claim 8, wherein said scroll compressor is communicated with described crankcase via the through hole along the central axis of described scroll compressor.
13. combined compressing apparatus according to claim 10, wherein when need be when making in described first and second power sources that are connected to described scroll compressor and described reciprocal compressor one stop to make in described scroll compressor and the described reciprocal compressor one to stop, described control gear be connected to described first power source and described second power source.
CNB2006101567842A 2006-01-12 2006-12-27 Combined compressing apparatus Expired - Fee Related CN100460675C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006004677A JP4709016B2 (en) 2006-01-12 2006-01-12 Complex compressor
JP2006004677 2006-01-12

Publications (2)

Publication Number Publication Date
CN101000049A CN101000049A (en) 2007-07-18
CN100460675C true CN100460675C (en) 2009-02-11

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US (1) US20070160482A1 (en)
JP (1) JP4709016B2 (en)
KR (1) KR100816358B1 (en)
CN (1) CN100460675C (en)

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JP4709016B2 (en) 2011-06-22
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US20070160482A1 (en) 2007-07-12
KR20070075350A (en) 2007-07-18

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