CN102834618B - The lubrication of screw machine - Google Patents

The lubrication of screw machine Download PDF

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Publication number
CN102834618B
CN102834618B CN201180018654.1A CN201180018654A CN102834618B CN 102834618 B CN102834618 B CN 102834618B CN 201180018654 A CN201180018654 A CN 201180018654A CN 102834618 B CN102834618 B CN 102834618B
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China
Prior art keywords
rotor
dilator
working fluid
bearing
faceted pebble
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CN102834618A (en
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I·K·史密斯
N·R·斯托希克
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City University of London
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City University of London
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N15/00—Lubrication with substances other than oil or grease; Lubrication characterised by the use of particular lubricants in particular apparatus or conditions
    • F16N15/04—Lubrication with substances other than oil or grease; Lubrication characterised by the use of particular lubricants in particular apparatus or conditions with water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/04—Lubrication
    • F01C21/045—Control systems for the circulation of the lubricant
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • 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
    • F04C2210/00—Fluid
    • F04C2210/24—Fluid mixed, e.g. two-phase fluid
    • F04C2210/242—Steam
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/91—Coating
    • 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
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/14—Self lubricating materials; Solid lubricants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/14—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load specially adapted for operating in water

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

A kind of screw machine utilizing the working fluid containing liquid phase includes the rotor of helical structure that have engagement, that lubricated.Rotor has " N " the shape profile as disclosed in patent WO 97/43550.In use, the lubrication of the lubrication of the helical structure of rotor and optional rotor bearing substantially liquid phase only by working fluid realizes.

Description

The lubrication of screw machine
Technical field
The present invention relates to the one such as lubrication of the screw machines (screw machines) such as screw rod dilator, it can Such as steam is used to generate electricity as working fluid.
Background technology
Positive displacement dilator is applied the most more and more widely in generating.One of most successful Stirling engine Being multiscrew machine, its most frequently used embodiment is dual-screw-stem machine.This machine is at Svenska Rotor Maskiner(SRM) public in patent GB1197432 of company, GB1503488 and GB2092676 Open.
Screw machine can use as compressor or dilator.The topmost theory of the present invention relate to this two The screw machine of type, but the present invention is particularly useful in dilator field.Therefore this specification is main Relate to as the screw machine of dilator and be incorporated as the screw machine of dilator to describe the present invention.At this In description, the screw machine as dilator will be simply referred to as screw rod dilator.
Screw rod dilator be better than turbine expander it is critical that be operable to wet working fluid (i.e., Comprise the fluid of gas phase and liquid phase) and almost without the risk damaged.This is because the fluid in screw machine The order of magnitude of the fluid velocity that the order of magnitude of speed runs into the most in the turbine.Therefore, spiral shell Bar dilator can allow the fluid of any composition from neat liquid to dry steam, simultaneously these phase places it Between keep thermodynamical equilibrium.On the contrary, if being entrained with substantial portion of liquid phase, then whirlpool in working fluid Wheel dilator is susceptible to blade erosion.
Screw rod dilator includes housing, and it has at least two overlap but disjoint hole.These holes accommodate The rotor of respective meshing spiral shape band leaf, they reversely rotate in the housing fixed.Housing is with pole Rotor is surrounded in its close cooperation completely.The central longitudinal axis of this some holes is the most coplanar and usual Parallel.Convex rotor (or " main rotor ") and female rotor (or " gate rotor ") are installed on bearing Housing, for rotating around its respective axis, multiple with housing of each of which in these axis A respective axis in axially bored line overlaps.
Rotor is generally made up of metals such as such as mild steel, but they can be made up of high-speed steel.Rotor is also Can be made of ceramic materials.Generally, if be made of metal, then they are by machining, but replace For property ground, they can be ground or cast.
Each rotor is respectively provided with spiral faceted pebble (helical land), the faceted pebble of other rotor of itself and at least one Between spiral slot engagement.The rotor of engagement is effectively formed one or more pairs of helical gears, simultaneously Its salient angle (lobe) plays the effect of tooth.Along cross-sectional view, this convex rotor or each convex rotor all have Have corresponding to faceted pebble and from the outwardly one group of salient angle of its pitch circle.Similarly along cross-sectional view, This female rotor or each female rotor are respectively provided with the pitch circle from it and extend internally and corresponding to female rotor One group of recess of groove.The faceted pebble of convex rotor and the quantity of groove are different from the faceted pebble of female rotor and the quantity of groove.
The example of the prior art of rotor profile is at Fig. 1 (a) to 1(d of accompanying drawing) and Fig. 2 (a) Shown in Fig. 2 (d), and will be described in further detail after a while.
The operation principle of screw rod dilator is based on three-dimensional stereomutation.Any two of each rotor is even The continuous space between salient angle and surrounding housing form single operating room.The volume of this room turns along with two The rotation that causes of transfer of the contact line between son and change.Whole length between salient angle because of rotor it Between engagement contact and accessible time, the volume of this room is maximum.On the contrary, at end surfaces rotor Between time there is engagement contact completely, the volume of this room is minimum, almost close to 0 value.
Fluid to be expanded is by entry port (being predominantly located at the frontal plane of housing) or forms opening of high pressure Mouth enters screw rod dilator.Therefore, it is allowed in the room that fluid filled limits between salient angle.Work as rotation Rotating into the contact line between row and rotor when returning, the volume obtained in each room increases.At upstream end When mouth is cut off, fill or access process terminates, and further rotation will cause fluid passing through spiral shell Expand during bar dilator downstream.
Further downstream, when convex rotor salient angle and female rotor salient angle start again to engage, expose housing In low-pressure port or discharge port.The fluid retained between further rotary compression salient angle and housing Volume, this port is opened further.This makes fluid to be arranged close to constant pressure by discharge port Put.This process lasts till that the volume retained is reduced to almost 0 and substantially retains between salient angle All fluid all has been drained off.
Then, this process is all repeated in each room.Therefore, according to the number of the salient angle in convex rotor and female rotor Amount, and then according to the quantity of the room between these salient angles, realize in rotating every time continuous print fill, swollen Swollen and discharge process.
When the rotor rotates, the engagement action of salient angle is substantially identical with the engagement action of spiral gear. But, it addition, the shape of salient angle must make at any contact position, seal line is formed between rotor And between rotor and housing, in order to prevent from occurring between a sequence of room internal leak.Further want Room between Seeking Truth salient angle should be big as far as possible, so that the displacement of fluid rotated maximizes every time.Additionally, Contact force between rotor should be relatively low, so that internal friction loss minimizes and make abrasion to minimize.
When manufacture requirements specifies to have less gap between rotor and between rotor and housing Time, rotor profile determines that the most important feature of the efficiency of flow velocity and screw rod dilator.Multiple rotor wheel Exterior feature has been tested a lot of year, and changes Degree of Success.
As shown in Figure 1 (a), screw rod dilator the earliest uses very simple symmetry rotor Profile.Along cross-sectional view, convex rotor 10 includes around some circles that pitch circle is equiangularly spaced (part-circular) salient angle 12, the center of its radius is all positioned on pitch circle 14.Female rotor 16 Profile is mirrored into the most therewith by one group of part circle recess 18 of equity.The most such right Title property rotor profile has the biggest hole area, and this can produce the biggest internal leak.This is by symmetry Property rotor profile get rid of outside comprising the application of high-pressure ratio or even middle pressure ratio.
In order to solve this problem, SRM introduces its " A " shape profile, its shown in Fig. 1 (b) also And in aforesaid British patent GB1197432, GB1503488 and GB2092676 in a variety of forms Open.This " A " shape profile greatly reduce internal leak and therefore make helical-lobe compressor obtain with The efficiency of reciprocator same order.Cyclon profile shown in Fig. 1 (c) further reduces Seepage, but this is with the salient angle weakening female rotor 16 as cost.This is in recessed turn of high pressure differential There is the risk of distortion in son 16, and makes them be difficult to manufacture.Hyper wheel shown in Fig. 1 (d) Exterior feature attempts to overcome this defect by reinforcement female rotor 16.
In all rotor profile of above prior art, the relative movement between the rotor of engagement is to rotate With the combination slided.
With reference to this background, applicant has developed the international patent application of Publication No. WO97/43550 " N " shape rotor profile disclosed in PCT/GB97/01333.The content of WO97/43550 is with the side of quoting Formula is expressly incorporated herein.In this specification " N " shape rotor profile is quoted and refer to WO97/43550 Described in and the profile of invention that limits.
" N " shape rotor profile is characterised by, when along cross-sectional view, at least salient angle to convex turn The profile of outside those parts protruded of the pitch circle of son and at least to the inside of the pitch circle of female rotor The profile of the recess extended is produced by identical rack configurations.The latter edge is around one of male rotor axis Direction and edge, around the rightabout bending of female rotor axis, produce the tooth-strip part of the high pressure flank of rotor Divide and produced by the rotor conjugation action between rotor.
Valuably, a part for tooth bar, the part of high pressure flank that preferably forms rotor lobes are rotation The shape of wheel line (cycloid).Alternatively, this part is formed as the parabola of broad sense, such as ax+byqThe form of=1.
Generally, the bottom of the groove of convex rotor is within being positioned at pitch circle as " tooth root " portion, and The tip of the faceted pebble of female rotor extends beyond its pitch circle as " tooth top " portion.Preferably, these teeth Root and tooth crest produce also by rack configurations.
Main rotor (or convex rotor) 1 shown in the diagrammatic cross-sectional view of the dual-screw-stem machine of Fig. 2 (a) and lock Rotor (or female rotor) 2 is at their pitch circle P1、P2On around their center O1And O2Rotate By corresponding angle ψ and τ=Z1/Z2ψ=ψ/i。
The radius of pitch circle P is proportional with the quantity of the faceted pebble on corresponding rotor and groove.
If segmental arc is defined as the arbitrary function of angular dimensions φ and by subscript on main rotor or gate rotor D represents:
xd=xd(φ) (1)
yd=yd(φ) (2)
Then the corresponding segmental arc on another rotor is the function of φ and ψ:
X=x (φ, ψ)=-acos (ψ/i)+xd coskψ+ydsinkψ (3)
Y=y (φ, ψ)=asin (ψ/i)-xd sinkψ+ydcoskψ (4)
ψ is the anglec of rotation of main rotor, and the first segmental arc and the second segmental arc have the contact point of this anglec of rotation.This angle Degree meets Sakun in nineteen sixty described in Vintovie kompressori, the Mashgiz Leningrad Conjugate condition:
(δxd/δφ)(δyd/δψ)-(δxd/δψ)(δyd/δφ)=0 (5)
This is the differential equation of all " d " envelope of curves line (envelope).Its expansion is:
(δyd/δxd)((a/i)sinψ-kyd)-(-(a/i)cosψ+kxd)=0 (6)
This can be expressed as the quadratic equation of sin ψ.Although it can use analytic process to untie, but Due to its mixing root, so being proposed with number solution.Once determine, then ψ is inserted into (3) and (4) In to obtain the conjugate curves on relative rotor.This step requires the segmental arc that definition only one is given. Another segmental arc obtains always by general step.
Even if the coordinate system of these equations defines independent of rotor, they are also effective.Therefore, All of " d " curve can be specified in the case of without reference to rotor.This set enables some curves Express with simpler mathematical form, and additionally be able to simplify curve generation step.
Such special coordinates system is that tooth bar (rotor of unlimited radius) coordinate system is (at Fig. 2 B () represents with R), it illustrates tooth bar for producing the rotor profile shown in Fig. 2 (a) One unit.Then, the segmental arc on tooth bar is defined as the arbitrary function of parameter:
xd=xd(φ) (7)
yd=yd(φ) (8)
The second segmental arc on rotor thus derives as the function of φ and ψ
x=x(φ,ψ)=xd cosψ-(yd-rwψ)sinψ(9)
y=y(φ,ψ)+xd sinψ+(yd-rwψ)cosψ(10)
ψ represents the anglec of rotation of the rotor at given segmental arc protrusion, and it defines contact point.This angle meets bar Part (5), it is:
(dyd/dxd)(rwψ-yd)-(rw-xd)=0 (11)
Then, explicit solution ψ is inserted into (9) and (10) with the conjugation segmental arc obtaining on rotor.
Fig. 2 (c) shows the rack configurations of Fig. 2 (b) and the relation of the rotor shown in Fig. 2 (a), And show the rotor that tooth bar and this tooth bar produce.Fig. 2 (d) shows existing in the way of comparison The rotor of technology is to upper stacking chart 2(c) shown in the profile of rotor.
The most where providing curve, it facilitates form may is that
ax d p + by d q = 1 - - - ( 12 )
It is " conventional circle " curve.For as p=q=2 and a=b=1/r, it is round. In the case of a and b is unequal, ellipse will be obtained；A and b of opposite sign will obtain hyperbola；At p=1 In the case of q=2, parabola will be obtained.
In addition to defined the facility of all curves provided by a coordinate system, with rotor coordinate System is compared, and tooth bar is formed provides two advantages: a) compared with other rotor, and tooth bar profile represents the shortest Contact path, it means that will protrude into from the point of tooth bar do not have on rotor any overlap or other Shortcoming；B) straight line on tooth bar will protrude on rotor as involute.
In order to minimize the stomatal size on the high-pressure side of rotor profile, this profile is generally by two rotors Conjugation action produces, the two rotor undercutting (undercut) their high-pressure side.This practice obtains extensively Ground application: in patent GB 1197432, uses the odd number point on main rotor and gate rotor；In patent GB 2092676 and GB 2112460 uses circle；Ellipse is used in patent GB 2106186；And And in patent EP 0166531, use parabola.Suitably undercutting can not directly obtain from tooth bar in advance ?.It is found that only exist an analysis on the tooth bar of conjugation action that can accurately substitute rotor Curve.Preferably cycloid, it is as the epicycloid on main rotor and as the hypocycloid on gate rotor And undercut.This is contrary with producing undercutting produced by epicycloidal odd number point on two rotors.This The defect of sample is generally able to minimum by making the gate rotor external diameter in the pitch circle of gate rotor be substantially reduced Change.This reduces stomatal size, but also reduces production capacity.
Conjugation action is when point (or the multiple points on the curve) cutting rotated on one rotor of period is another The process in its (or the they) path on one rotor.If the same time exists two or more During many mutual tangent point, undercutting occurs, and this produces " depression (pocket) " in profile.When significantly Slip when occurring, if less curved portion (or point) produces longer curved portion, then lead to Often can undercut.
" N " shape rotor profile overcomes this defect, because the high-voltage section of tooth bar is by undercuting this tooth bar On the rotor conjugation action of suitable profile and produce.This tooth bar is later used to be produced by common tooth bar Step forms the profile of main rotor and gate rotor.
Described in detail below be designed for by the step combined obtain to air, conventional cold-producing medium and The simple rotor lobes shape of the profile race that the tooth bar that various procedures gas is effectively compressed produces.This profile Almost comprise all elements of the modern screw rotor profile provided in disclosed documents and materials, but it is special Levy and provide safe basis for additional trickle improvement and optimization.
Coordinate herein relative to all main segmental arc on tooth bar coordinate system summary tooth bar.
The salient angle of this profile is divided into multiple segmental arc.
Boundary between profile segmental arc is represented by capitalization and each segmental arc is defined respectively, such as figure Shown in 2(c).
Section A-B is on p=0.43 and q=1 hour rack The conventional segmental arc of type.
B-C section is the straight line on tooth bar, p=q=1.
C-D section is the arc section on tooth bar, p=q=2, a=b.
D-E section is the straight line on tooth bar.
E-F section is the arc section on tooth bar, p=q=2, a=b.
F-G section is straight line.
G-H section is segmental arc G2-H2Undercutting, when it is p=1 and q=0.75 on main rotor The conventional segmental arc of type.
H-A section on tooth bar is segmental arc A1-H1Undercutting, it is p=1 on gate rotor, during q=0.25The general segmental arc of type.
At each abutment A ... at H, adjacent section has common tangent line.
Tooth bar coordinate is obtained by the program reverse with equation (7) to (11).
Result, it is thus achieved that tooth bar curve E-H-A, it is shown in Fig. 2 (c).
Fig. 2 (d) shows the main rotor 3 and the profile of gate rotor 4 produced by this tooth bar program, and this is taken turns Wide with the known profile 5,6 of the respective rotor produced according to patent GB 2092676 5/7 textural Overlapping.
By the same distance between center and identical root diameter, the profile that tooth bar produces increases by 2.7% Displacement, the salient angle of female rotor is thicker and the firmest simultaneously.
In the modification of the tooth bar shown in Fig. 2 (c), GH section and HA section are by y=Rocosτ-Rp, y=Rosinτ-RpThe continuous segment GHA of the cycloid of τ form is formed, wherein ROBe main rotor (and therefore It is its hole) outer radius, RPIt it is the pitch circle radius of this main rotor.
AB, BC, CD, DE, EF and FG section is all to be produced by above equation (12).For For AB section, a=b, p=0.43, q=1.For other section, a=b=1/r, and p=q=2.p ± 10% can be changed with the value of q.For BC, DE and FG section, r is more than the pitch circle of main rotor Radius, and preferably infinity so that each this section is straight line.As p=q=2, CD It is the arc section of a=b curve with EF section.
" N " described above shape rotor profile is mathematical theory based on gear.Therefore, with join before Examining the rotor profile difference that Fig. 1 (a) to Fig. 1 (d) describes, the relative movement between rotor is almost to connect Nearly pure rolling: the contact band between rotor is in the position very close to its pitch circle.
" N " shape rotor profile has the most extra advantage compared with other rotor profile, including: low The actuating device of moment of torsion, therefore the contact force between rotor is less；Female rotor is firm；Displacement is big and causes The seal line of low seepage is short.Generally speaking, its use improves the heat-proof quality of screw rod dilator, especially It is the heat-proof quality at relatively low end speed, its than record currently used in other rotor profile Situation can improve 10%.
Common knowledge of the prior art is, if the helical structure of rotor is not lubricated, then outside is nibbled " regularly " gear closed must be arranged to the relative motion of domination synchronous rotor.Same between rotor The transmission of step moment of torsion comes into force via timing gear, therefore which obviates between the meshing spiral structure of rotor Directly contact.So, timing gear allows the helical structure of rotor not lubricated.
Alternatively, outside timing gear can omit so that synchronizing by their meshing relation of rotor Individually determine.This imply inevitably the transmission from a rotor to the synchronous torque of another rotor be via Their meshing spiral structure.It that case, the helical structure of rotor must be lubricated, to avoid Hard contact between rotor, result causes abrasion and may kill.
For the consideration of these the substituting approach to the synchronization of rotor and their different lubricating requirement, spiral shell Bar dilator has two main Types: " oil-filled " type and " oil-free " type.
Oil charging machine relies on the oil carried in working fluid to come helical structure and the bearing thereof of lubricated rotor, and Gap between canned rotor and between rotor and housing around.Oil charging machine need outside sealing but It is to need not inner sealing, and it is simple in terms of Machine Design.Therefore, its low cost of manufacture, and And it is compact and efficient.
On the contrary, oil will not be made to mix with working fluid without oil machine.Therefore, timing gear is arranged to avoid Contact between the helical structure of rotor.Each timing gear is rotated by a corresponding rotor, and Those gears are in the external engagement of housing, and wherein they are lubricated by oil in outside.Therefore, " oil-free " Refer to the inside of housing, rather than whole machine.In order to prevent oil from entering housing and bringing working fluid into In, need on each axle between housing and gear, to carry out inner sealing and outside sealing.Result It is, obvious huger than oil charging machine without oil machine and more much higher than the manufacturing cost of oil charging machine.But, nothing The rotor of oil machine can rotate with higher speed, and does not has too much viscous drag.Therefore, without oil machine The flow of each unit volume higher than oil charging machine.
Oil charging machine and without oil machine be required for before being again loaded into machine for lubricating oil external heat exchange Device.In the application of dilator, the purposes of heat exchanger oil charging machine and without oil machine in be different.
Heat exchanger is used to cool down oil without oil machine.In order to complete circulation, fuel tank, oil filter and circulation Pump is required for making oil return to bearing and timing gear.On the contrary, oil charging machine needs dividing of dilator downstream From device to go oil removing from the working fluid of discharge.Then, the oil of separation must be re-pressurized in pump, And heat exchanger must add deep fat before oil returns to the high-pressure side of housing.This avoids and makes entrance shell The working fluid of body turns cold, and otherwise this will reduce the efficiency of dilator.
These lubricating systems increase two kinds of dilator totle drilling cost, but the cost being to increase than for Oil-free dilator much bigger.It is true that the totle drilling cost of oil-free dilator is generally more than on the order of magnitude The cost of the oil-filled dilator of capacity.
In addition to the cost, oil-free and oil-filled lubricating system all have other defect.
The difficulty that the trial of production oil-free dilator has caused is that inner shaft seals and can not be kept completely separate Working fluid and the oil of lubrication timing gear.It it is the nytron being highly soluble in lubricating oil at working fluid In the case of thing or cold-producing medium, this problem is particularly pertinent.
In the case of oil-filled dilator, it becomes virtually impossible to after inflation by oil from working fluid complete Entirely separate and remove.This causes oil to build up in the other parts of system, thus creates operation Problem.Certainly, there is also identical problem in oil-free dilator, its sealing device can not make oil and work It is kept completely separate as fluid.But, oil-free dilator is more better than oil-filled dilator in this respect. Therefore, especially sensitive application scenario is contaminated for greasy dirt, it may be necessary to use oil-free dilator, although its Bulky, complicated and relatively costly.
As it has been described above, the rotor of screw rod dilator is installed to the housing on bearing, in order to corresponding around it Axis rotate.Various types of bearing can be used.Certainly lubrication is also a problem at this.
Most screw machines use rolling body bearing to support rotor.This allows bearing fit tolerance the least, enters And make the gap that must retain between rotor and between rotor and housing minimize.Therefore this make inside ooze Leakage minimizes and thus makes efficiency maximize.
Rolling body bearing includes ball bearing and roller bearing.Their function is by separately two surfaces One group of spherical ball or cylindrical or frusto-conical shape roller keep rotating contact.If arranging suitable When, rolling body bearing can support radial load and axial load.No matter rolling element operates above with at them Track between main rolling movement how, the boundary film of oil preferably must be held between those parts so that Wear and tear and frictionally heat and minimize.
International Patent Application PCT/the GB2006/02148 of Publication No. WO 2006/131759 of applicant Even if showing when the liquid component of working fluid only comprises the dissolved oil of low concentration, it is also possible to lubrication spiral shell Rolling body bearing in bar dilator.If this liquid component is fed to bearing, working fluid will be because of friction Heat and evaporate, and required by staying enough oil to make bearing effectively operate with supply in bearing housing Boundary film.But, when use is used for expanding fluid (this fluid e.g. steam, or oil can not dissolve Other fluid any in its liquid phase) screw rod dilator time, it is impossible to use patent WO The lubrication principle of 2006/131759, or even not in working fluid exists the lubricating oil of trace.
Patent US 6217304 of Shaw discloses the helical-lobe compressor for refrigerating plant, in theory should Helical-lobe compressor can use the drop of the liquid refrigerant brought in vapor phase refrigerant to seal, cool down and Lubricated rotor.If it is desired, it is possible to by the droplet injection of liquid refrigerant to cold-producing medium stream, its The problem with negative consequence.But, how patent US 6217304 does not provide this compressor Can be without the feasible program run under oil condition in working fluid.It merely relate to so that rotor it Between the thermoplastic of the less convex rotor in gap or the use of other suitable composite.
Although not mentioned in patent US 6217304, but according to the knowledge of applicant, do not have in the refrigerant Being dissolved with or carry under a lot of oil condition, refrigeration compressor can not smooth operation.If with Open type (open-circuit) dilator that closed type compressor is contrary uses steam as working fluid, So this does not select.Additionally, use liquid refrigerant to lubricate compressor mean that cold-producing medium is incomplete Evaporation, therefore intended that the coefficient of performance (i.e. refrigerating efficiency) is excessively poor.Therefore, in patent US 6217304 The design alternative of middle proposition is difficult to be proven in actual machine.
Summary of the invention
In order to overcome the problem in this background technology, it is proposed that the present invention.
For one side, the present invention relates to the use of the screw machine of the working fluid comprising liquid phase, described spiral shell Bar machine include two or more there is engagement, the rotor of helical structure that lubricated, Qi Zhongsuo State rotor and there is " N " as defined herein shape profile, and in use, the spiral type of described rotor The lubrication of structure realizes (or the most such) only by the liquid phase of working fluid.
The present invention also can be expressed as the method for lubrication screw machine during the working fluid that a kind of use comprises liquid phase, Described screw machine include two or more there is engagement, the rotor of helical structure that lubricated, Described rotor has " N " as defined herein shape profile, wherein the method include substantially just with The liquid phase of working fluid lubricates the helical structure of described rotor.
" the most only " mentioned in this specification is attempt to represent and can carry relatively in working fluid A small amount of or other fluids various of trace, even if adding wherein indeliberately, and other stream described Body can have the lubricant effect that some are the slightest.But, effective lubrication is still complete or main Depend on the existence of the liquid phase of specific working fluid so that it is invalid that the shortage of this liquid phase can cause lubricating.
Substantially, therefore all of lubrication responsibility is performed by the liquid phase of specific working fluid.Additionally, The lubricating fluid carried in working fluid preferably obtains, the most not from the working fluid entering dilator More liquid can be added in advance to working fluid.This is useful simple mechanism.However, if it is desired to If, more liquid can be added in advance, and this being added on broadly is not precluded from the present invention.
The liquid phase using working fluid eliminates for by oil lubrication as the lubricant for helical structure Agent is transported to the expensive lubricating system of those structures.The greasy dirt that present invention also avoids working fluid contaminates also And avoid working fluid separate from working fluid after machine oil needs.
Rotor can be made up of any suitable material.In order to make contingent abrasion minimize, they Helical structure can be coated with low-friction coating, the Balinit C2 such as provided by Oerlikon Balzers (trade mark).Balinit C2 is " WC/C " coating, and it is sunk by physical vaporous deposition (PVD) Amass and include Carbide Phases and carbon phase.Low friction is preferably used to be coated with at least helical structure of rotor Layer, the wear characteristic at this makes this coating be worth.But, for cost reasons, if can If energy, the preferably helical structure of rotor keeps being not coated with.The potential advantage of the present invention just exists In by using " N " shape profile rotor to allow this situation.
In order to determine that rotor is lubricated satisfactorily, the rotor of " N " shape profile of use coating is Safest.But, the test of applicant displays that, if being coated with (such as Balinit C2 etc.) Low-friction coating, the rotor with other profile can convincingly be used in some application.Therefore, On the other hand, the invention still further relates to utilize the screw machine of the working fluid comprising liquid phase, conveying screw rod Machine include two or more be coated with low-friction coating, engagement, the helical structure that lubricated Rotor, the most in use, the lubrication of the helical structure of rotor is substantially only by working fluid Liquid phase realize.The program of the present invention can also be expressed as the working fluid that a kind of use comprises liquid phase Time lubrication screw machine method, conveying screw rod machine includes that having of two or more is coated with low friction Coating, engagement, the rotor of helical structure that lubricated, wherein the method the most only includes The helical structure of lubricated rotor is carried out by the liquid phase of working fluid.
In all schemes of the present invention, rotor is preferably by bearings, and described bearing is the most also The most only lubricated by the liquid phase of working fluid.Use liquid phase to lubricate bearing to eliminate for by oil Lubricant is transported to the expensive lubricating system of those bearings.It also avoid the pollution of working fluid, and And also avoid working fluid separate from working fluid after machine oil needs.
For simplicity, the liquid phase of working fluid the bearing lubricated is preferably Hydrodynamic, but They can be static pressure.Meanwhile, larger gap needed for hydrodynamic bearing and therewith in bearing The rotation of axle can make the efficiency of machine more slightly lower than the efficiency of the same machines using rolling body bearing, spiral shell Bar steam dilator can be manufactured into and use the water of liquid phase as bearing lubricant.
Hydrodynamic bearing is by maintaining lubricant between rotating part or sliding part and their composite seal Thin film and run so that do not come in contact between them in addition to starting and shutting down.That runs is the most former Reason be this thin film be not uniform thickness.In the case of journal bearing, this moves apart at the center of rotation of axle Occur during the center of radius of around housing.This can cause the thin film of the lubricant around this axle uneven, from And the pressure caused in lubricant in the region that thin film is the thinnest dramatically increases.Pressure differential foot around thin film To force this axle to return into the housing alignment with surrounding, therefore prevent axle and housing from coming in contact.
The pressure produced in lubricant film depends on viscosity and the thickness of the lubricant of realization in lubricant film The minimizing of degree.Normally, this bearing is oil lubrication.But, such as Wisconsin, USA Some specialized companies such as Waukesha Bearings company have been developed over using the liquid of low-down viscosity The hydrodynamic bearing of the fluid (such as water and Hydrocarbon) of body.These bearings are successfully it is crucial that energy Enough run by the most small minimum film thickness, and the bearing material used is starting and shutting down Period is not easy to block or wear and tear.
In broad idea of the present invention, hydrostatic bearing is also possible, but owing to they need outside Pump and blood circulation implement them, so they are not most preferred.Especially, this bearing prevents Armature spindle is by allowing that one group of liner in the housing that gases at high pressure or liquid pass connects with the housing of surrounding Touch.The balance of the pressure between armature spindle and liner prevents from coming in contact between them and armature spindle is at it By fluid support during rotation.
Such as the rolling body bearing of those ball-types or roller bearing type also is able to when being suitably designed for supporting Rotor.
It is possible that the liquid of lubrication bearing individually derives from working fluid.But, such as the spiral of rotor Shape structure is such, and lubricating bearing by the liquid phase obtained from working fluid is to be cleverly and therefore Preferably.
In dilator is applied, working fluid is water or moist steam the most valuably so that for lubricating screw The liquid phase of shape structure and the liquid phase being selectively also used for lubricating bearing are aqueous waters, the most permissible It is carried at the aqueous water in steam stream.But, screw machine can also be similarly designed as any Working fluid, such as Hydrocarbon or cold-producing medium, as long as the liquid phase of same fluid is readily used for lubricated rotor Helical structure and the most also be readily used for lubricate bearing.
Another advantage is that of low-viscosity (mobile) liquid (the such as water) of the helical structure of use lubricated rotor The viscous drag that lubricant causes is more less than oil.Therefore, rotor can be with more higher than the oil charging machine of equivalent Speed rotates, and this is conducive to flow.
For simple, the compact and purpose of low cost, especially for avoiding unwanted oil lubrication, non- The most preferably, rotor connects not over single timing gear.Therefore, as oil charging machine, turn The cooperation of the helical structure that the synchronization of son is only dependent upon engagement is useful.This means synchronising torque base In basis, only meshing spiral shape structure via them is delivered to another from a rotor.
In some moment in past, steam screw rod dilator has been manufactured and has been tested, but not to it Any one in carries out the record of process fluid lubrication, and any of which is the most successfully grasped The record made.
By the present invention, if working fluid also is able to for lubricating bearing, then whole oil lubrication system And can be removed without the optional feature required for oil machine or oil charging machine.
Test 1
In test has the screw machine of " N " shape rotor profile, applicant utilizes the air pressure of oil-filled type Contracting machine is tested, so not having timing gear.Therefore, this compressor relies on the helical structure of rotor Between lubricating contact synchronize these rotors.
Being contrary to general knowledge, applicant is by only by replacing oil to be injected in working fluid in water lubricating turning Son helical structure and test.It that case, the bearing mounting the rotor to housing is rolling Ejector half and be filled with lubricant.Rotor is coated with the steel of Balinit C2 coating.
Then, compressor runs 150 hours by the contact between the helical structure of rotor, the most logical Cross the water replacing oil to be injected in working fluid to lubricate.At the end of this stage, these rotors are examined, And it is displayed without abrasion or the sign damaged, simply on contact band, has slight polishing.
Test 2
The rotor of " N " shape profile of steel that the coating rotor of example 1 is not applied by a pair substitute and Run other five hours.At the end of this period, checking uncoated rotor, they the most do not demonstrate bright Aobvious signs of wear.
Test 3
Subsequently, in the case of being injected in working fluid entirely without water, there is " N " not being applied The compressor of shape profile rotor runs two hours mistakenly.Rotor still maintains and the most significantly damages, when So, if machine runs more than considerably long in the case of not helical structure to rotor is lubricated Period, it is contemplated that can produce some damage.
Applicant has inferred, for there is the screw machine of the rotor of " N " shape profile, and lube system The major function of system is lubrication bearing.As long as there are some liquid on the helical structure of rotor (even if should Liquid is low viscous, such as water), it is no need for timing gear to avoid direct rotor contact.The present invention Apply this discovery and implement this principle.
Accompanying drawing explanation
Fig. 1 (a) to Fig. 1 (d) and Fig. 2 (a) by reference to accompanying drawing describe to Fig. 2 (d) The rotor profile of prior art.In order to the present invention can be more easily understood, now will be by example reference Accompanying drawing, wherein:
Fig. 3 is the schematic cross sectional views through the steam dilator according to the first embodiment of the present invention；With And
Fig. 4 is the schematic cross sectional views through steam dilator according to the second embodiment of the present invention.
Detailed description of the invention
With reference first to the Fig. 3 in accompanying drawing, screw rod dilator 20 includes fixing housing 22, and it comprises two The spiral band leaf rotor 10,16 of engagement, the two rotor is reverse around parallel axis in housing Rotate.Rotor 10,16 is made up of any suitable material (such as steel), is optionally coated with low rubbing Erasing layer (Balinit C2 as the aforementioned).It is public in patent WO 97/43550 that they have applicant " N " the shape rotor profile opened.
Each rotor 10,16 is installed to corresponding axle 24,26, axle 24,26 and then each by supporting The hydrodynamic bearing of each end of individual axle is installed to housing 22.One in axle 26 extends to housing 22 Outside with drive for generating electromotor (not shown).
Working fluid (in this example for moist steam) to be expanded passes through entry port with high pressure conditions 30 enter housing 22.Steam is flowed by the inside of housing 22 and is expanded, thus causes rotor 10,16 with high-speed rotation, and steam leaves housing 22 by discharge port 32 with low-pressure state.
Without timing gear so that rotor 10,16 synchronous rotary.As an alternative, rotor 10,16 is because of it The engagement of helical structure is connected and synchronizes.This needs to be lubricated helical structure, and this is by wet steaming The liquid phase water carried in vapour supply guarantees.
In the illustrated embodiment, bearing 28 is also lubricated by the water supplied from moist steam.Water storage Portion 34 is connected with entry port 30 and is fed to often by the water being under pressure by feeding pipe 36 Individual bearing 28.
In selectable improvement project shown in Fig. 4 of accompanying drawing, the end of each armature spindle 24,26 Dummy piston (balance piston) 38 at portion utilizes the pressure of working fluid to resist the most negative of axle Carry, thus the load that the bearing 28 decreasing support shaft is born.So, pressure piping 40 will balance Piston 38 is connected to entry port 30.
Working fluid for expanding can obtain from multiple source (steam as from geothermal source).? This respect, can recall, and screw rod dilator is to process wet work to the key advantages of turbine expander Make fluid (i.e., simultaneously comprising the fluid of gas phase and liquid phase) and almost without the risk damaged.Processing That pollute or dirt working fluid (such as comprises the sand from geothermal source or the rust from corrosion pipeline Moist steam Deng molecule) aspect, screw rod dilator is also much better than turbine expander.Another is excellent Gesture is that screw rod dilator has more cost benefit than the turbine for relatively small power output potentially.
Foregoing teachings illustrates, the steam dilator of present invention design and manufacture is without as without required by oil machine Timing gear, inner shaft sealing member, lubricant storage portion, lubricant pump, lubricant filter or heat Exchanger or without the lubricant pump as required by oil charging machine, heat exchanger and oil eliminator.This Outward, asking for, lubricant pollution working fluid the most common without oil machine and oil charging machine of the prior art Topic is fully overcome by the present invention.
Industrial steam system code is according to the main potential application of the screw rod dilator of the present invention.A lot Industrial process is required for supplying steam, such as, prepare food, papermaking and chemical process.Generally, central authorities Boiler produces and is in the steam of moderately high pressure, and this steam via conduit system be distributed in factory, Near workshop or other industrial plants.Steam is discharged in the position of each needs by lateral.
Owing to the various process in industrial plants may need different steam pressures, so each branch Pipeline is generally of control valve, described control valve by steam throttling to discuss in process required for relatively low Pressure.Screw rod dilator can be used to substitute choke valve to reduce steam pressure.This allows to from swollen Reclaim power during swollen, keep with required lower pressure supply steam simultaneously.Brought by the present invention About cost, robustness, compactedness, reliability, efficiency and avoid the benefits such as greasy dirt dye for accept Steam dilator is used for this application, especially in industrial plants, replaces being intended that of multiple throte valve Vital.

Claims (15)

1. moist steam is used as a screw rod dilator for working fluid, and described dilator includes:
Housing, it has the disjoint hole of at least two, and the axis in the hole that described at least two intersects is The most coplanar, and convex rotor and female rotor be mounted for around described convex rotor with described recessed turn The axis of the respective dead in line with the hole in each described housing of son rotates, in described rotor Individual have spiral faceted pebble, the spiral slot between the faceted pebble of described spiral faceted pebble and at least another rotor Engagement, described convex rotor has corresponding to described faceted pebble and outside from its pitch circle along cross-sectional view Protrude one group of salient angle, described female rotor have along cross-sectional view extend internally from its pitch circle and Corresponding to one group of recess of the groove of described female rotor, the faceted pebble of described convex rotor and the quantity of groove are different from The faceted pebble of described female rotor and the quantity of groove；
Wherein along cross-sectional view, described salient angle at least outwardly from the pitch circle of described convex rotor Those parts profile and at least to the inside of the pitch circle of described female rotor extend described recess Profile be to be produced by identical rack configurations, the latter is along one of the axis around described convex rotor Individual direction and the rightabout bending along the axis around described female rotor, produce the height of described rotor The section of rack of knob side be by described rotor between rotor conjugation action and produce；
Synchronising torque is turned from one by wherein said rotor by the helical structure of the engagement via them Son is delivered to another rotor and is synchronized, and does not has timing gear to act between described rotor；And
In use, the lubrication of the helical structure of described rotor is the most only by moist steam working fluid In the water that carries be responsible for.
Dilator the most according to claim 1, wherein said helical structure is coated with low friction Coating.
Dilator the most according to claim 2, wherein said coating includes Carbide Phases and carbon Phase.
4. according to the dilator described in aforementioned any one claim, wherein said convex rotor and described Female rotor by least one bearings, at least one bearing described the most only by Water lubricates.
Dilator the most according to claim 4, wherein said bearing is hydrodynamic bearing.
Dilator the most according to claim 4, wherein said bearing is rolling body bearing.
Dilator the most according to claim 4, wherein said bearing is by from moist steam working fluid The water of middle acquisition lubricates.
8., according to the dilator described in any one in Claim 1-3, also include resisting on rotor The thrust piston of axial load.
Dilator the most according to claim 8, wherein said thrust piston is worked by moist steam The pressure of fluid and play a role.
10. according to the dilator described in any one in Claim 1-3, wherein moist steam workflow Body carries lubrication water from enter described dilator moist steam obtain, substantially without in advance to Moist steam adds more water.
11. 1 kinds of method of lubrication screw rod dilator, described expansions when moist steam being used as working fluid Prop includes:
Housing, it has the disjoint hole of at least two, and the axis in the hole that described at least two intersects is The most coplanar, and convex rotor and female rotor be mounted for around described convex rotor with described recessed turn The axis of the respective dead in line with the hole in each described housing of son rotates, in described rotor Individual have spiral faceted pebble, the spiral slot between the faceted pebble of described spiral faceted pebble and at least another rotor Engagement, described convex rotor has corresponding to described faceted pebble and outside from its pitch circle along cross-sectional view Protrude one group of salient angle, described female rotor have along cross-sectional view extend internally from its pitch circle and Corresponding to one group of recess of the groove of described female rotor, the faceted pebble of described convex rotor and the quantity of groove are different from The faceted pebble of described female rotor and the quantity of groove；
Wherein along cross-sectional view, described salient angle at least outwardly from the pitch circle of described convex rotor Those parts profile and at least to the inside of the pitch circle of described female rotor extend described recess Profile be to be produced by identical rack configurations, the latter is along one of the axis around described convex rotor Individual direction and the rightabout bending along the axis around described female rotor, produce the height of described rotor The section of rack of knob side be by described rotor between rotor conjugation action and produce；
Synchronising torque is turned from one by wherein said rotor by the helical structure of the engagement via them Son is delivered to another rotor and is synchronized, and does not has timing gear to act between described rotor；And
The helical structure of described rotor substantially comes just with the water carried in moist steam working fluid Lubrication.
12. methods according to claim 11, lubricate the described convex rotor of support and institute including using water State the bearing of female rotor.
13. methods according to claim 12, described including obtaining lubrication from moist steam working fluid The water of bearing.
14. according to the method for any one in claim 11 to 13, wherein in moist steam working fluid The lubrication water carried obtains, substantially without in advance to wet steaming from the moist steam entering described dilator Vapour adds more water.
15. 1 kinds of dynamic force generating units, including according to the spiral shell described in any one in claim 1 to 10 Bar dilator, or have and operate according to the method described in any one in claim 11 to 14 Screw rod dilator.
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WO2011098835A2 (en) 2011-08-18
CN102834618A (en) 2012-12-19
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EP2534339A2 (en) 2012-12-19
GB2477777A (en) 2011-08-17

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