CN1079912C - Turbine type compressor - Google Patents
Turbine type compressor Download PDFInfo
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- CN1079912C CN1079912C CN97112412A CN97112412A CN1079912C CN 1079912 C CN1079912 C CN 1079912C CN 97112412 A CN97112412 A CN 97112412A CN 97112412 A CN97112412 A CN 97112412A CN 1079912 C CN1079912 C CN 1079912C
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- turbine
- compression
- cylinder barrel
- moving 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
- F04C28/265—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
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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
- F04C18/02—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
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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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
To provide a proper pressing force under all operational conditions without requiring any large torque at the time of start by providing a stopper part for blocking the movement of a moving member when the elastic force of an elastic member reaches a specified value in such a way that an elastic member makes pressing energization on a fixed scroll by means of a specified elastic force. High pressure gas ejected from an ejection port 9 is filled in a spatial part between inner and outer cylinder part 18, 21 simultaneously with start of compressive operation so as to apply back pressure to a moving cylinder 16. The moving cylinder 16 is moved downward against the elastic force of a coil spring 15 and when it descends by a preset distance, it is hocked on a stopper part 17 and its descending movement is regulated so as to force the preset elastic force of the coil spring 15 to act on a fixed scroll 7. The fixed scroll 17 is pressed on a turning scroll 6 by this elastic force and the seal of the compressive space S wider compressive operation is made in its perfect state. Thereby, without requiring any large torque at start and under all operational conditions, a proper pressing force can be obtained.
Description
The present invention relates to as turbocompressor such as the compressor use that constitutes cooling recirculation system in the air conditioner.
Such as in the compressor of the cooling recirculation system that forms air conditioner, with common rotor-type compressor relatively, tend at present to use that the motion noise is extremely low, compression performance good and because the turbocompressor that does not need parts such as air-breathing, outlet valve that component number is reduced.
This kind compressor operating principle is: make the swirl shape impeller of fixed turbine and the swirl shape impeller of rotary turbine be meshed, form compression volume between above-mentioned each impeller and each turbine end plate, rotary turbine is rotated, cooling medium is sucked compression volume, discharge again after the compression.
But the sealing of above-mentioned turbocompressor compression volume is that impeller end and relative with it respectively end plate are slidingly matched and form separately by fixing, rotary turbine.
Like this, if rotary turbine is firmly pressed to fixed turbine,, hindered the flexible rotation of rotary turbine though can keep sealing.
In addition, compression volume might not be in the normal pressure state usually.For example, fluid power container operation conditions occurs when sucking liquid coolant and compressing, at this moment, compression volume is in the abnormal pressure state.This state continues for a long time, will produce big stress on each turbine impeller, and the danger of breaking is arranged thereupon.
So, proposed here the said fixing turbine is pressed to rotary turbine to form the mode of compression volume sealing with suitable pressure, attempt to solve above-mentioned all problems.
For example, USP3 in 874,827 (the ADL patents), is to make the pressurized gas head pressure of spring pressure after compression that fixed turbine is pressed to rotary turbine one side.
In addition, the spy opens clear 58-22901 communique (Toyota's automatic loom) and the spy opens in the flat 7-72541 communique (Ke Pulande コ-プ ヲ ソ De), proposed the pressure that merges mutually by the head pressure of the pressurized gas that will compress and intermediate pressure in the compression process, made fixed turbine press to the scheme of rotary turbine one side.
Yet in the invention of previous USP, following problems is arranged: after out of service, spring still with when operation essential spring force fixed turbine is pressed to rotary turbine one side.Like this, very big moment is just arranged during starting, and must be equipped with the large-size machine of Driven Compressor, the result also just makes structure large-scaleization, component expense and operating cost increase inevitably.
If use the little spring of elastic force then can reduce starting torque, but because the variation of operating conditions makes exhaust pressure also produce change, then when exhaust pressure was very high, pushing force also can be excessive.
For fear of the problems referred to above, also the exhaust aperture can be reduced, when moving under the very high condition of exhaust pressure, can obtain more suitable pushing force, but when moving under the very low condition of exhaust pressure, the pushing force deficiency will appear, fixed turbine is easy to separate with rotary turbine and has destroyed sealing, the result causes problems such as gas leakage, compression performance reduction.
In addition, open clear 58-222901 communique or the special technological scheme that proposes in the flat 7-72541 communique of opening if resemble the spy, utilize exhaust pressure and intermediate pressure to make fixed turbine press to rotary turbine one side, then can rotate the axial force that acts on the turbine and the excessive problem of contact force between fixed turbine and the rotary turbine owing to the difference of compressor operation conditions.
The present invention is the starting point to solve above-mentioned all problems, and its objective is provides a kind of turbocompressor, and its starting the time does not need big moment, can obtain also can improving compression performance on suitable pushing force, the basis in high reliability under all operating conditionss.
For achieving the above object, the present invention takes following technological scheme:
A kind of turbocompressor, wherein, make the swirl shape impeller 7b of fixed turbine 7 be meshed with the swirl shape impeller 6b of rotary turbine 6, between each impeller 7,6b and each end plate 7a, 6a, be formed with compression volume S, rotary turbine 6 is rotatablely moved, pressurized gas is inhaled into above-mentioned compression volume S, with this gas compression and discharge, it is characterized in that having:
With elastic force fixed turbine 7 is pressed to rotary turbine 6 and formed the elastic member 15 that seals between two turbines;
Promote to axially move and make elastic member 15 produce the moving member 16 of elastic force by the pressurized gas of compression synchronous generation in service; With
Described elastic member 15 stops the stop component 17 that moving member 16 moves with certain elastic force pushing fixed turbine 7 when the elastic force of described elastic member 15 reaches institute's definite value.
Described turbocompressor is characterized in that:
Moving the pushing force that produces synchronously and above-mentioned moving member is moved with compression is the exhaust pressure of compressed pressurized gas.
Described turbocompressor is characterized in that:
Moving the pushing force that takes place synchronously and above-mentioned moving member is moved with compression is to be produced by the intermediate-pressure gas of taking out gas in the compression process.
Described turbocompressor is characterized in that:
When above-mentioned elastic member stops in the compression operation, fixed turbine is pushed to rotary turbine.
Described turbocompressor is characterized in that:
Have a plurality of above-mentioned elastic members, its relative central shaft is provided with at regular intervals.
A kind of turbocompressor, it has compressor arrangement portion 4, wherein, the swirl shape impeller 7b of fixed turbine 7 is meshed at each impeller 7b with the swirl shape impeller 6b of rotary turbine 6,6b and each end plate 7a, be formed with compression volume S between the 6a, rotary turbine 6 rotatablely moved, will be compressed gas suck above-mentioned compression volume S, with the compression of this pressurized gas and discharge, it is characterized in that having:
In load onto the housing 1 of stating compressor arrangement portion 4;
This housing 1 is divided into above-mentioned compressor structural portion one side and the detached body 19 of exhaust chamber 23 1 sides of part in addition;
Be located at exhaust chamber 23 1 sides that are separated out by above-mentioned detached body 19, and be formed with the inboard cylinder barrel 18 of the exhaust pressure chamber 18a that can temporarily receive the pressurized gas of discharging by 4 compressions of above-mentioned compressor structural portion;
Be located at inboard cylinder barrel 18 peripheral parts, the outside cylinder barrel 21 that has certain intervals to be provided with inboard cylinder barrel 18;
Be erected at above-mentioned inboard cylinder barrel 18 between the outside cylinder barrel 21 and by moving the axially movable moving member 16 of pushing masterpiece that produces synchronously with compression;
Be arranged on the above-mentioned outside cylinder barrel 21 and can limit the stop component 17 of above-mentioned moving member 16 amount of movements;
Be arranged between above-mentioned detached body 19 and the above-mentioned moving member 16, be subjected to the locomotivity of moving member 16, said fixing turbine 7 elasticity are pressed to the elastic member 15 of rotary turbine 6 one sides.
Described turbocompressor is characterized in that:
Above-mentioned detached body can be that the said fixing turbine reaches either party in the back pressure plate that is provided with at regular intervals with this fixed turbine.
Described turbocompressor is characterized in that:
Above-mentioned back pressure plate has can make the above-mentioned outside cylinder barrel of above-mentioned moving member from the opposing side insertion of an opposite side with fixed turbine, and is provided with exhaust pressure safety check portion.
Described turbocompressor is characterized in that:
Above-mentioned moving member is by several tabular ring elements and be clipped between this plate plate ring element that side face with inboard cylinder barrel and outside cylinder barrel slips and the Sealing that maintains pressure difference in both sides is formed.
The turbocompressor of described invention has following feature: be meshed with the swirl shape impeller of rotary turbine at this swirl shape impeller of fixed turbine that makes, between each impeller and each end plate, be formed with compression volume, rotary turbine is rotatablely moved, pressurized gas is inhaled into above-mentioned compression volume, and in the turbocompressor that gas compression is discharged again, have fixed turbine elasticity is pressed to rotary turbine and formed the elastic member that seals between two turbines, promote to move axially and stop that moving member continues mobile stop component after its elastic force reaches institute's definite value when making elastic member produce the elastic force pushing fixed turbine of the moving member of elastic force and elastic member by the pressurized gas of compression synchronous generation in service.
Described invention has under the following spy: with above-mentioned compression operation pushing force that above-mentioned moving member the moves pressurized gas exhaust pressure after by compression takes place synchronously and makes and produce.
Described invention has following feature: the pushing force to moving member that takes place synchronously with above-mentioned compression operation is produced by the gas that has intermediate pressure in the compression process.
Described invention has following feature: above-mentioned elastic member also has pushing force to make it to press to rotary turbine to fixed turbine in the compression operation when stopping.
Described invention has following feature: above-mentioned elastic member is arranged at intervals with several surely by institute on respect to the circumference at center.
Described turbo type compression of the present invention has following feature: be meshed with the swirl shape impeller of rotary turbine at this swirl shape impeller of fixed turbine that makes, have between each impeller and each end plate after forming compression volume and will sucking pressurized gas compression in it again in the turbocompressor of the compressor arrangement portion of discharge, load onto the housing of stating compressor arrangement portion in having, this housing is divided into above-mentioned compressor structural portion one side and the detached body of exhaust chamber one side formed of each several part in addition, be formed with the inboard cylinder barrel that is located at exhaust chamber one side that above-mentioned separation is separated out and can temporarily receives the exhaust pressure chamber of the pressurized gas of discharging in it by above-mentioned compressor structure compression back, inner surface and this inboard cylinder barrel peripheral part are by the decide outside cylinder barrel of setting at interval, be erected at above-mentioned inboard cylinder barrel between the cylinder barrel of the outside and by moving the axially movable moving member of pushing masterpiece that produces synchronously with compression, be arranged between above-mentioned detached body and the above-mentioned moving member and since the mobile generation elastic force pushing said fixing turbine elastic compression of moving member to the elastic member of rotary turbine.
Described invention has following feature: above-mentioned detached body can be either party in said fixing turbine or the back pressure plate that is provided with at regular intervals with this fixed turbine.
Described invention has following feature: not only have the above-mentioned outside cylinder barrel that moving member is inserted from an opposite side of fixed turbine on the above-mentioned back pressure plate, be provided with the exhaust pressure non-return simultaneously and push away valve arrangement.
Described invention has following feature: above-mentioned moving member is made up of several tabular ring elements and Sealing, and the sealing part is clipped between these tabular ring elements, slips with the side face of inboard cylinder barrel and outside cylinder barrel and maintains pressure difference in both sides.
According to the method for above-mentioned solution problem, do not need big moment during starting, and under all operating conditionss, can make fixed turbine press to rotary turbine with suitable pushing force.
The good effect of invention:
According to above-mentioned invention, with elastic force fixed turbine is pressed to rotary turbine and form the elastic member that seals between two turbines owing to having, promote to axially move and make elastic member produce the elastic force pushing fixed turbine of the moving member of elastic force and elastic member by the compression pressure of compression synchronous generation in service, when its elastic force reaches institute's definite value simultaneously, stop the stop component that moving member moves, so do not need big moment during starting, no matter can both obtain suitable pushing force under what operating conditions, so not only can improve reliability, and improve compression performance.
According to described invention, produce owing to pushing force that moving member the moves pressurized gas exhaust pressure after by compression takes place and makes synchronously with compression operation, so structure is simplified, and the sealing position can reach minimum.
According to described invention, because the pushing force to moving member that takes place synchronously with the compression operation is produced by the gas that has intermediate pressure in the compression process, so the pushing force to fixed turbine during starting can rise rapidly, fixed turbine can reach steady operational status rapidly.
According to described invention,,, also reduced noise so can suppress the loosening bump between fixed turbine and the rotary turbine because elastic member also has pushing force to make it to press to rotary turbine to fixed turbine in the compression operation when stopping.
According to above-mentioned invention,,, improved performance so can suppress the loosening bump of fixed turbine in the running owing to above-mentioned elastic member is arranged at intervals with several surely by institute on respect to the circumference at center.
According to described invention, owing to have the separated detached body of exhaust chamber in the housing with compressor arrangement portion and the formation of other parts, be located at exhaust chamber one side and form the inboard cylinder barrel of exhaust pressure chamber, the moving member that is arranged on the outside cylinder barrel that becomes certain intervals with inboard cylinder barrel and the position, space between this inboard cylinder barrel and moves by the axial push power that produces synchronously with the compression operation, be arranged on cylinder barrel place, the outside and can limit the moving element of moving member amount of movement and move pushing and the elastic force that produces is pressed to fixed turbine elasticity the elastic member of rotary turbine one side by moving member, so hermetic unit is minimized and is made designs simplification, do not need big starting torque during starting, and can under any operating conditions, form suitable pushing force, so not only improve reliability, and be improved compression performance.
According to described invention, detached body can be either party in said fixing turbine or the back pressure plate that is provided with at regular intervals with this fixed turbine, so simplify the structure.
According to described invention, not only have above-mentioned outside cylinder barrel that moving member is inserted from the opposite side of fixed turbine on the back pressure plate, be provided with the exhaust pressure check valve structure simultaneously, so the wrong problem of Sealing dress of elastomer and moving body can not take place, like this, can not only be correctly, assembling simply, also improved assembly process process simultaneously.
According to described invention, because moving member by several tabular ring elements and be clipped between this tabular ring element and with inboard cylinder barrel and outside cylinder barrel outer, inner peripheral surface is slidingly matched and the Sealing that maintains pressure difference in both sides is formed, so can be reliable, keep sealing simply.
Following with reference to accompanying drawing, describe embodiments of the invention in detail:
Fig. 1 is the local longitudinal section of the turbocompressor schematic representation of the invention process form.
Fig. 2 is the local longitudinal section of the turbocompressor schematic representation of another embodiment of the present invention.
Fig. 3 is the local longitudinal section of the turbocompressor schematic representation of the present invention's the 3rd form of implementation.
Fig. 4 is the moving member longitudinal section schematic representation that uses in the turbocompressor shown in Figure 3.
Fig. 5 is local longitudinal section of the turbocompressor of the present invention's the 4th form of implementation and cooling circuit schematic representation.
Fig. 6 is the present invention and conventional construction axial pushing force and contact force variation characteristic comparison schematic representation under different operating conditionss.
Fig. 1 has represented the local mechanism such as the turbocompressor that uses in the refrigerating plant.
1 is airtight housing among the figure, is provided with support 2 in this closed shell 1, and its upper support can free rotating turning axle 3.
The top of above-mentioned turning axle 3 will be connected by described compressor arrangement parts 4 with the back, and the bottom is provided with motor component not shown in the figures.The underpart of turning axle 3 is bearing in by motor component outstanding and be installed in (not shown) the auxiliary bearing on the above-mentioned closed shell 1 from the below, and is free to rotate.
Above-mentioned compressor structure member 4 is made up of following parts, promptly comprise by spring bearing 5 be bearing in the above-mentioned support 2 and rotary turbine 6 free to rotate, with the fixed turbine 7 of these rotary turbine 6 engagements with this fixed turbine 7 is pressed to all the time the push part 8 of rotary turbine 6.
Above-mentioned rotary turbine 6 by end plate 6a with the hub 6c that matches with above-mentioned turning axle 3 upper end eccentric part 3a with outstanding by this end plate 6a top and becomes the swirl shape impeller 6b of integral body to form with end plate.
Said fixing turbine 7 is by end plate 7a, outstanding and becomes the swirl shape impeller 7b of integral body to form with end plate 7a by this end plate bottom, and this impeller 7b and above-mentioned impeller 6b are meshing with each other.
Above-mentioned rotary turbine 6 forms compression volume S between end plate 6a, the 7a of fixed turbine 7 and impeller 6b, the 7b, by distolateral entering in the process that central part moves of week, its volume diminishes gradually, plays the effect of being compressed as the refrigerant gas of pressurized gas.
On the end plate 6a of said fixing turbine, be provided with the exhaust cavity 9 that is communicated with above-mentioned compression volume S central part.
Said fixing turbine 7 is supported for and can moves in very little certain distance vertically.Form flange-like at the end plate 7a of this fixed turbine 7 peripheral part place, its top and bottom connect and are provided with a plurality of pin-and-holes 10.On above-mentioned support, be provided with screw 11, to be communicated with pin-and-hole 10 separately.
Respectively from the slow sleeve pipe 12 that inserts, its lower end is bearing in support 2 tops in the pin-and-hole 10 of the end plate 7a of fixed turbine, slightly outstanding segment length above the end plate 7 of its medial end portions by fixed turbine.
The inside of this sleeve pipe 12 is inserted with location bolt 13, and the lower end of this bolt 13 screws in the screw of above-mentioned support 2.This location is with between the head of bolt 3 and sleeve pipe 12 upper end portions pad 14 being housed.
Because in said structure, sleeve pipe 12 is fixed on the location with between bolt 13 and the support 2 by pad 14, and the pin-and-hole 10 slow sleeve pipes 12 that insert of fixed turbine 7, so this fixed turbine 7 can axially moving freely along sleeve pipe 12.
But above-mentioned mobile scope has only very little distance range between the end plate 7a top of fixed turbine and the above-mentioned pad 14, and this scope is positioned and determines with bolt 13.That is, fixed turbine end plate 7a top has become definite fixed turbine 7 amount of movements with distance between pad 14 bottoms and the gap of establishing.
The push part 8 of said fixing turbine has the elastic member helical spring 15 of fixed turbine 7 elasticity being pressed to rotary turbine 6 and making it sealing mutually, is moved and made the shift(ing) ring 16 and the moving element 17 of above-mentioned helical spring 15 generation elastic forces by the power that takes place synchronously in the compression running.This moving element 17 is used for after the elastic force of helical spring 15 reaches certain value stoping moving of shift(ing) ring 16, make helical spring 15 with fixed elastic force pushing fixed turbine.
Above-mentioned exhaust cavity 9 end plate top one side on every side that is provided with at fixed turbine end plate 7a central position place is formed with the inboard cylinder barrel 18 that projects upwards.The top of this inboard cylinder barrel 18 is opening-like cylinders, and this cylinder is communicated with above-mentioned exhaust cavity 9, is formed with the temporary transient exhaust pressure chamber 18a that stops of pressurized gas in it.
On the outer circumferential face of above-mentioned inboard cylinder barrel 18, be formed with and the airtight structure of above-mentioned shift(ing) ring 16 maintenances, and be slidingly matched mutually.Top one side of this shift(ing) ring 16 is compared outwards outstanding with the bottom, be circular with the cooperation place section of inboard cylinder barrel 18, and all the other major parts are the very big flange-like structure of diameter.
Dispose above-mentioned helical spring 15 between this shift(ing) ring 16 and the fixed turbine end plate 7a.The internal diameter of this helical spring 15 is more bigger than the external diameter that cooperates with inboard cylinder barrel 18 on the above-mentioned shift(ing) ring 16, side contacts and it is played the elastic support effect under the flange-like structure of one end and shift(ing) ring 16.
The upper space of closed shell 1 inner compressor structure 4 is by being divided into two-part up and down as the back pressure plate 19 of detached body, the reverse stop valve 20 of exhaust pressure that is contained on this back pressure plate 19.
This back pressure plate 19 is formed with flange-like structure periphery with above-mentioned shift(ing) ring 16 and is slidingly matched and maintains bubble-tight flange connecting part 21 mutually along central shaft upside position.
These flange connecting part 21 downsides are connected with above-mentioned retainer 17, and these retainer 17 inboards are inwardly stretched out but do not touched above-mentioned helical spring 15.When shift(ing) ring 16 move down and exceed when deciding scope, above-mentioned retainer 17 can block the flange part of shift(ing) ring 16, has so just limited its falling head.
Above-mentioned exhaust pressure check valve components 20 has at interval with the upper end edge of above-mentioned interior side ring 18, and the flange connecting part 21 upper end open portions sealing that is arranged on the back pressure plate 19 is integral.
The position is provided with the valve seat 22 with safety check in the central, and is communicated with above-mentioned exhaust cavity 9.That is to say that the valve seat 22 of above-mentioned exhaust cavity 9 by having safety check is with the spatial communication of back pressure plate 19 upsides.
Like this, by above-mentioned exhaust pressure check valve components 20 and back pressure plate 19 airtight housing 1 inside is divided into two-part up and down, its upside space has become the temporary transient exhaust chamber 23 that stops of the pressurized gas of discharging.
1 upper side place is connected with outlet pipe 24 at airtight housing, and this outlet pipe 24 couples together the condenser (not shown) of exhaust cavity 23 and refrigerating plant.1 lower side place is connected with sucking pipe not shown in the figures at airtight housing, and this sucking pipe will be coupled together (not shown) by the vaporizer of the lower space of back pressure plate 19 and exhaust pressure check valve components 20 separated closed shells 1 and refrigerating plant.
In the turbocompressor of said structure, when electrical power and Driven Compressor structure member 4, low pressure refrigerant gas enters in the airtight housing 1 by sucking pipe and is full of the space of back pressure plate 19 downsides.
Refrigerant gas enters between rotary turbine 6 and the fixed turbine 7 compression volume S outer Monday of the rear flank that forms, and along with the rotation of rotary turbine 6 is transferred to the center portion of side Monday in the compression volume S gradually, and is compressed owing to volume diminishes.
When rising institute level pressure power, compressed pressurized gas discharge by exhaust cavity 9 and temporal aggregate in the 18a of exhaust pressure chamber, the valve seat 22 through the reverse thrust valve 20 of exhaust pressure enters exhaust chamber 23 then.After being filled, this exhaust chamber 23 just is discharged in the outside condenser by outlet pipe 24.
As mentioned above, after compression process begins, after the pressurized gas of being discharged by exhaust cavity 9 are full of exhaust pressure chamber 18a, the space in a part of pressurized gas will be full of between side ring 18 and the outside cylinder barrel 21, at this moment, pressurized gas add back pressure just for the shift(ing) ring 16 that can move freely.
The elastic force that the above-mentioned shift(ing) ring 16 that is coupled with back pressure has overcome helical spring 16 moves down, behind the decline institute set a distance by stop component 17 stop, thereby stop to descend.
On the other hand, because the decline of shift(ing) ring 16, helical spring 15 is compressed distortion, after shift(ing) ring 16 and is in the state of qualification stop component 17 stop, helical spring 15 also with fixed spring force act on the fixed turbine 7.
Because the elastic force of helical spring 15 is pressed on the rotary turbine 6 fixed turbine 7, guarantees that compression volume S is in good sealing state in the compression process, thereby improved the efficient of compression operation.
In said structure, shift(ing) ring 16 is moved by the exhaust pressure pushing that when operation compression produces, thereby makes helical spring 15 produce elastic force, so required moment is very little during starting.
In service in compression, when if generation rises the compression volume pressure anomaly because of certain reason, since the influence of this abnormal pressure make fixed turbine with scope that holding down bolt 14 contact in on unsteady, removed the sealing state of compression volume S like this, formed certain clearance.
Can so just can not make to constitute impeller 7b, 6b generation ABNORMAL STRESS fixing, rotary turbine 7,6 to compression volume S outer drain from the gas of above-mentioned gap location abnormal pressure, this has promptly given play to so-called flexibility function.
On the other hand, as long as compression operation one stops, the pushing force that exhaust pressure is eliminated 16 pairs of helical springs 15 of back shift(ing) ring also just disappears.This shift(ing) ring 16 upwards floats under the effect of the elastic restoring force of helical spring 15.
After shift(ing) ring 16 and 20 times side contacts of exhaust pressure check valve components, promptly stop upwards to float.Under this state, helical spring 15 upwards has elastic force that these two parts are close to respectively on direction separately to shift(ing) ring 16, downward fixed turbine 7 is acted on respectively.
This that is to say, even under the compressor halted state, the spring force of a certain size that fixed turbine not only produces with deadweight but also by helical spring 15 acts on the surface of contact of rotary turbine, so still can guarantee the sealing of compression volume S.
In above-mentioned form of implementation, be to be wound on the periphery of shift(ing) ring 16 to form as the helical spring 15 of elastic member, in fact be not limited to this form, also can be structure as shown in Figure 2.
In Fig. 2, the same parts that Fig. 1 has illustrated is got identical symbol, its explanation is also omitted, and is illustrated parts in addition below.
The elastic member 15A that constitutes fixed turbine push part 8A is formed by the very little helical spring of diameter, and disposes several (only having represented one among the figure).Above the fixed turbine end plate 7a and the relative position place below the flange part of shift(ing) ring 16 is formed with the fitting seat 25 of spill respectively, is used to embed the upper and lower end parts of above-mentioned helical spring 15A.
In this structure, except several helical springs 15A this point difference was arranged, the compressor that operational effect and front illustrated was just the same.
In addition, also can use as shown in Figure 3 fixed turbine push part 8B.
On fixed turbine end plate 7a, have on the periphery of certain intervals with inboard cylinder barrel 18, the outstanding outside cylinder barrel 21a that is provided with of one, its upper end portion is installed with the side-prominent stop component 17a of cylinder barrel to the inside 18 1.
Between inboard cylinder barrel 18 and outside cylinder barrel 21a, set up by the moving member 16A (back will described) of elastic member 15B work, but this moving member 16A easy on and off moves in order to elastic pushing pressure.
Above-mentioned elastic member 16b is formed by some helical springs respectively, and be arranged on and exhaust pressure check valve components 20 all-in-one-piece back pressure plate 19a and above-mentioned moving member 16A between.
Fig. 4 is the enlarged diagram of above-mentioned moving member 16A.Wherein have section and be the plane annular seal 30 of reverse U shape, the upper and lower surface of sealing part 30 is pressed with the ring-type plate 31,32 that sheet metal forms respectively, and this ring-type plate 31,32 by rivet 32 and sealing plate 30 riveted fixing together.
As shown in Figure 3, above-mentioned moving member 16A is arranged between inboard cylinder barrel 18 and the outside cylinder barrel 21a.The inner peripheral surface of the outer circumferential face of the outer circumferential face of the inner peripheral surface of above-mentioned Sealing 30 and inboard cylinder barrel 18, Sealing 30 and outside cylinder barrel 21a is slidingly matched.
On the other hand, between the compression volume S and medial and lateral cylinder barrel 18,21a and the formed annulus of moving member 16A that fixed turbine 7 and rotary turbine 6 form, be communicated with by the intermediate pressure guide hole 33 that is located on the fixed turbine end plate 7a.
That is to say that the part pressurized gas in the compression volume S is just entered by inside and outside cylinder barrel 18,21a and the formed annulus of moving member 16A, so this annulus is called intermediate pressure chamber 34 again by intermediate pressure guide hole 33 before rising to institute's level pressure power.
When out of service, because the elastic force of helical spring 15B pushing moving member 16A makes it to contact and produce the trend of compressing with fixed turbine end plate 7a.Fixed turbine 7 is contacted with rotary turbine 6, protected the sealing of compression volume S.
After compression operation beginning, gas with intermediate pressure enters in the intermediate pressure chamber 34 through intermediate pressure guide hole 33 from compression volume S, the back pressure that promptly part surface and the moving member 16A of fixed turbine end plate 7a, interior outside cylinder barrel 18,21a is produced intermediate pressure after being full of.
At this moment, because moving member 16A moves to the top of figure, make helical spring 15B produce the elastic compression distortion.At last, this moving member 16A is made it to continue to move by stop component 7a stop.
In the compression running, owing to be full of gas in the intermediate pressure chamber 34 with intermediate pressure, so moving member 16A is in by the state of stop component 17a stop always.At this moment, be equivalent to fixed turbine 7 and be in integrated state with moving member 16A.
Like this, the elastic force of helical spring 15B by moving member 16A, pass to fixed turbine 7, fixed turbine 7 is pressed towards rotary turbine 6 one sides, makes compression volume S keep sealing.
In this structure, because the volume of the intermediate pressure chamber that intermediate pressure forms is littler than the exhaust pressure chamber volume that exhaust pressure forms, so that when starting helical spring 15B compression stroke and time shorten, thereby also shortened from starting to the required time of stable operation process.
Fig. 5 is illustrated in the above-mentioned compressor basic structure with fixed turbine push part 8A shown in Figure 2, the situation that cooling circuit R and said releasing mechanism use simultaneously.
50 is condensed devices, the 51st among this figure, throttling arrangement, the 52nd, vaporizer.These devices have constituted cooling circuit R with above-mentioned turbocompressor.Above-mentioned releasing mechanism 40 is communicated with compression volume S.Gas in the compression process is directly imported cooling circuit R.
For example, when the cooling chamber running state that is in daytime during to the night transition, supercooled state will appear.At this moment, the open and close valve 41 of open releasing mechanism 40 makes the gas in the compression process return cooling circuit R, just can reduce cooling capacity consciously.
Above-mentioned releasing mechanism 40 is by the release aperture 42 that is provided with on the identical structure of basic and said fixing turbine 7, be connected these release aperture 42 ends and pass closed shell 1 and with the vaporizer 52 that is communicated with above-mentioned cooling circuit R and turbocompressor between the releasing tube 43 that links to each other of refrigerator pipe P and above-mentioned open and close valve 41 compositions that are arranged on these releasing tube 43 middle parts.
Be provided with flexible pipe 44 on releasing tube 43 positions in closed shell 1.This flexible pipe 44 also can form spiral helicine scalable pipeline by common pipe arrangement and make.
When rotary turbine 6 rotates, the micro breadth oscillation that self produces is passed to fixed turbine, and can further pass to the releasing tube 43 that is connected with fixed turbine, but, can absorb above-mentioned vibration fully, stoped transmission to exterior line owing to be provided with flexible pipe 44.
That is to say,, can prevent the breakage of releasing tube 43 undoubtedly owing to have flexible pipe 44.
In air conditioner with heat pump type cooling circuit, in order to increase the intensification ability of the operation that heats up, import compression volume again after the part cooling medium bypass with the compressor discharge, this promptly has the air conditioner of injecting the loop.
In this case, constitute inject the loop inject pipe be connected form on the fixed turbine and be communicated with compression volume S inject bore ends.That is to say in closed shell 1 to have the identical structure of compressor that has illustrated with Fig. 5 with the front, but, also can obtain effect same as described above owing to being provided with flexible pipe on the position of injecting pipe in it.
Among Fig. 6, transverse axis is represented representational air conditioner service condition A～F, and the longitudinal axis is represented axial force and contact force, and wherein contact force is meant the minimum contact force of fixed turbine and rotary turbine impeller end among the present invention.
The minimum value of getting fixed turbine of the present invention and rotary turbine contact force is 1, and the mutual pushing force (axial force) of turbine and contact force rod figureization promptly reaches Fig. 5 in structure of the present invention that respectively theoretical calculation is obtained then and the conventional construction.
Among Fig. 6, a represents the pushing force of structure of the present invention, and b represents the pushing force of conventional construction, and c represents the contact force of structure of the present invention, and d represents the contact force of conventional construction.
The contact force C of structure of the present invention is minimum in operating conditions D, and the contact force d of conventional construction is minimum in operating conditions C, and its minimum value is respectively 1 to equate basically.
Compare with minimum value, the contact force of structure of the present invention is maximum in operating conditions B, is about 3.2 times, and the contact force of conventional construction is maximum in operating conditions F, is about 4.9 times.
From the pushing force analysis, the pushing force a of structure of the present invention is maximum in operating conditions F, is about 9.7 times, and the pushing force d of conventional construction is maximum in operating conditions E, is about 1 2.2 times.
Can know that from above-mentioned relevant peaked analysis the compressor in the structure of the present invention is compared with the compressor of conventional construction, load is diminished, thereby improve reliability and other performance of compressor.
Claims (9)
1, a kind of turbocompressor, wherein, the swirl shape impeller (7b) of fixed turbine (7) is meshed with the swirl shape impeller (6b) of rotary turbine (6), between each impeller (7b, 6b) and each end plate (7a, 6a), is formed with compression volume (S), rotary turbine (6) is rotatablely moved, pressurized gas is inhaled into above-mentioned compression volume (S), with this gas compression and discharge, it is characterized in that having:
With elastic force fixed turbine (7) is pressed to rotary turbine (6) and formed the elastic member (15) that seals between two turbines;
Promote to axially move and make elastic member (15) produce the moving member (16) of elastic force by the pressurized gas of compression synchronous generation in service; With
Described elastic member (15) stops the stop component (17) that moving member (16) moves with certain elastic force pushing fixed turbine (7) when the elastic force of described elastic member (15) reaches institute's definite value.
2, according to right 1 described turbocompressor, it is characterized in that:
Moving the pushing force that produces synchronously and above-mentioned moving member is moved with compression is the exhaust pressure of compressed pressurized gas.
3, turbocompressor according to claim 1 is characterized in that:
Moving the pushing force that takes place synchronously and above-mentioned moving member is moved with compression is to be produced by the intermediate-pressure gas of taking out gas in the compression process.
4, turbocompressor according to claim 1 is characterized in that:
When above-mentioned elastic member stops in the compression operation, fixed turbine is pushed to rotary turbine.
5, turbocompressor according to claim 1 is characterized in that:
Have a plurality of above-mentioned elastic members, its relative central shaft is provided with at regular intervals.
6, a kind of turbocompressor, it has compressor arrangement portion (4), wherein, the swirl shape impeller (7b) of fixed turbine (7) is meshed at each impeller (7b with the swirl shape impeller (6b) of rotary turbine (6), 6b) with each end plate (7a, be formed with compression volume (S) 6a), rotary turbine (6) rotatablely moved, will be compressed gas suck above-mentioned compression volume (S), with the compression of this pressurized gas and discharge, it is characterized in that having:
In load onto the housing (1) of stating compressor arrangement portion (4);
This housing (1) is divided into above-mentioned compressor structural portion one side and the detached body (19) of exhaust chamber (23) one sides of part in addition;
Be located at exhaust chamber (23) one sides that are separated out by above-mentioned detached body (19), and be formed with the inboard cylinder barrel (18) of the exhaust pressure chamber (18a) that can temporarily receive the pressurized gas of discharging by above-mentioned compressor structural portion (4) compression;
Be located at inboard cylinder barrel (18) peripheral part, the outside cylinder barrel (21) that has certain intervals to be provided with inboard cylinder barrel (18);
Be erected at above-mentioned inboard cylinder barrel (18) between the outside cylinder barrel (21) and by moving the axially movable moving member of pushing masterpiece (16) that produces synchronously with compression;
Be arranged on above-mentioned outside cylinder barrel (21) and go up and can limit the stop component (17) of above-mentioned moving member (16) amount of movement;
Be arranged between above-mentioned detached body (19) and the above-mentioned moving member (16), be subjected to the locomotivity of moving member (16), said fixing turbine (7) elasticity is pressed to the elastic member (15) of rotary turbine (6) one sides.
7, turbocompressor according to claim 6 is characterized in that:
Above-mentioned detached body can be that the said fixing turbine reaches either party in the back pressure plate that is provided with at regular intervals with this fixed turbine.
8, turbocompressor according to claim 7 is characterized in that:
Above-mentioned back pressure plate has can make the above-mentioned outside cylinder barrel of above-mentioned moving member from the opposing side insertion of an opposite side with fixed turbine, and is provided with exhaust pressure safety check portion.
9, turbocompressor according to claim 1 is characterized in that:
Above-mentioned moving member is made up of several tabular ring elements and Sealing, and the sealing part is clipped between these tabular ring elements, slips with the side face of inboard cylinder barrel and outside cylinder barrel and maintains pressure difference in both sides.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15133796A JPH09329090A (en) | 1996-06-12 | 1996-06-12 | Scroll type compressor |
| JP151337/96 | 1996-06-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1177062A CN1177062A (en) | 1998-03-25 |
| CN1079912C true CN1079912C (en) | 2002-02-27 |
Family
ID=15516376
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97112412A Expired - Fee Related CN1079912C (en) | 1996-06-12 | 1997-05-16 | Turbine type compressor |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPH09329090A (en) |
| KR (1) | KR100196122B1 (en) |
| CN (1) | CN1079912C (en) |
| TW (1) | TW437854U (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20000050619A (en) * | 1999-01-12 | 2000-08-05 | 구자홍 | Device protecting gas leak through axial clearance for scroll compressor |
| KR100439651B1 (en) * | 2000-11-06 | 2004-07-12 | 미츠비시 쥬고교 가부시키가이샤 | Scroll compressor |
| KR100390430B1 (en) * | 2000-12-26 | 2003-07-07 | 엘지전자 주식회사 | Axial compliance mechanism of scroll machine |
| US7717687B2 (en) * | 2007-03-23 | 2010-05-18 | Emerson Climate Technologies, Inc. | Scroll compressor with compliant retainer |
| KR101151206B1 (en) * | 2008-08-05 | 2012-05-29 | 주식회사 두원전자 | A scroll compressor improved in function of back pressure control |
| CN103790831B (en) * | 2012-10-30 | 2016-09-07 | 艾默生环境优化技术(苏州)有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
| KR102166427B1 (en) * | 2014-05-02 | 2020-10-15 | 엘지전자 주식회사 | Scroll compressor |
| KR102166421B1 (en) * | 2014-05-02 | 2020-10-15 | 엘지전자 주식회사 | Scroll compressor |
| CN106574618B (en) * | 2014-10-07 | 2019-09-20 | 松下知识产权经营株式会社 | Scroll compressor |
| WO2016056174A1 (en) * | 2014-10-09 | 2016-04-14 | パナソニックＩｐマネジメント株式会社 | Scroll compressor |
| CN106368947A (en) * | 2016-11-28 | 2017-02-01 | 天津商业大学 | Totally-closed scroll compressor in elastic contact seal |
| JP6709971B2 (en) * | 2017-01-27 | 2020-06-17 | パナソニックＩｐマネジメント株式会社 | Scroll compressor |
| KR102408562B1 (en) * | 2017-09-01 | 2022-06-14 | 삼성전자주식회사 | Scroll compressor |
| CN108952867B (en) * | 2018-07-17 | 2020-12-01 | 日照亿铭科技服务有限公司 | Biomass combustion power generation device adopting supercritical carbon dioxide circulation |
| US11692548B2 (en) | 2020-05-01 | 2023-07-04 | Emerson Climate Technologies, Inc. | Compressor having floating seal assembly |
| GB2600716B (en) * | 2020-11-05 | 2023-05-03 | Edwards Ltd | Scroll pump |
| WO2022127768A1 (en) * | 2020-12-15 | 2022-06-23 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| US11767846B2 (en) * | 2021-01-21 | 2023-09-26 | Copeland Lp | Compressor having seal assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4435137A (en) * | 1980-04-05 | 1984-03-06 | Sanden Corporation | Scroll-type fluid compressor with scroll stabilizing mechanism |
| US4545747A (en) * | 1982-12-17 | 1985-10-08 | Hitachi, Ltd. | Scroll-type compressor |
| US5403172A (en) * | 1993-11-03 | 1995-04-04 | Copeland Corporation | Scroll machine sound attenuation |
| CN1113549A (en) * | 1994-04-21 | 1995-12-20 | 科普兰公司 | Scroll machine sound attenuation |
| CN1113548A (en) * | 1994-05-31 | 1995-12-20 | 三菱重工业株式会社 | Vortex hydraulic mechanism |
| JPH0861258A (en) * | 1995-08-28 | 1996-03-08 | Matsushita Electric Ind Co Ltd | Scroll compressor |
-
1996
- 1996-06-12 JP JP15133796A patent/JPH09329090A/en active Pending
-
1997
- 1997-01-31 TW TW89219423U patent/TW437854U/en not_active IP Right Cessation
- 1997-02-19 KR KR1019970004919A patent/KR100196122B1/en not_active IP Right Cessation
- 1997-05-16 CN CN97112412A patent/CN1079912C/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4435137A (en) * | 1980-04-05 | 1984-03-06 | Sanden Corporation | Scroll-type fluid compressor with scroll stabilizing mechanism |
| US4545747A (en) * | 1982-12-17 | 1985-10-08 | Hitachi, Ltd. | Scroll-type compressor |
| US5403172A (en) * | 1993-11-03 | 1995-04-04 | Copeland Corporation | Scroll machine sound attenuation |
| CN1113549A (en) * | 1994-04-21 | 1995-12-20 | 科普兰公司 | Scroll machine sound attenuation |
| CN1113548A (en) * | 1994-05-31 | 1995-12-20 | 三菱重工业株式会社 | Vortex hydraulic mechanism |
| JPH0861258A (en) * | 1995-08-28 | 1996-03-08 | Matsushita Electric Ind Co Ltd | Scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| TW437854U (en) | 2001-05-28 |
| JPH09329090A (en) | 1997-12-22 |
| KR100196122B1 (en) | 1999-06-15 |
| CN1177062A (en) | 1998-03-25 |
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