CN1703584A - Screw pump - Google Patents
Screw pump Download PDFInfo
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- CN1703584A CN1703584A CNA2003801011997A CN200380101199A CN1703584A CN 1703584 A CN1703584 A CN 1703584A CN A2003801011997 A CNA2003801011997 A CN A2003801011997A CN 200380101199 A CN200380101199 A CN 200380101199A CN 1703584 A CN1703584 A CN 1703584A
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- Prior art keywords
- pump
- rotor
- fluid
- temperature
- control
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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
- F04C28/28—Safety arrangements; Monitoring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
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- 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
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
A pump comprises a stator and at lest one rotor mounted within a housing. The housing comprises a first fluid channel extending about the rotor, the rotor comprising at least one second fluid channel. A first sensor is configured to output a signal indicative of the temperature of the stator, and a second sensor is configured to output a signal indicative of the temperature of the rotor. The temperature of fluid in the channel is controlled depending on the magnitude of signals output from the sensors.
Description
Technical field
The present invention relates to field of vacuum.It specifically is heat control with vacuum pump of screw-type structure.
Technical background
General screw pump includes two parallel rotating shafts spaced apart from each other, and every rotating shaft all has and has externally threaded rotor, and the screw thread of rotor is meshing with each other in the pump housing thereby described rotating shaft is installed in.Close tolerance between the rotor screw thread at contact points place is with the internal surface of the pump housing of being used as stator, make at the gas flow that aspirates between the entrance and exit to be limited between the screw thread and described internal surface of rotor, thereby force this gas to pass through pump along with rotor rotation.
The screw pump of prior art uses the heat of water-cooled overcoat to leave and to produce because of compression around the part of machine (pump).But, because in low temperature, the heat that does not produce because of compression in the ingress need leave, so the inlet of described machine does not have cooling system.When pressure raises, by the increase of flowing through inlet gas unnecessary heat is left from this inlet.When pump is arranged under the colder environment, the surface temperature in the inlet of pump can reduce and form cold spots significantly, thereby is fluid accumulation thing at these than the cool region cohesion from the gaseous state reject product that aspirating chamber comes.These accumulations may be made up of height corrosion acid content or akaline liquid, can cause the damage of pump parts, thereby shorten the life-span of equipment.
Oneself knows two outlets of an inlet supply in the both-end screw pump, and rotor is installed with the form of conllinear.Temperature contrast in this pump between its intake section and the exit portion is more remarkable, thereby the concentricity of housing parts mesopore becomes important.If housing parts has departed from directrix, because very little tolerance reduces forr a short time or do not had, rotor bumps with stator possibly.
Screw pump just more and more uses in using widely.For example same pump may need the purposes that realizes that many kinds are different in the pharmacy procedure field.Simultaneously pump structure may design at concrete an application, when this application has changed, and the just no longer existence of the environment of imagination, pump just can not operate under the highest/optimizing efficiency.
Summary of the invention
The objective of the invention is to overcome the above-mentioned problem relevant that mention of part with the screw pump technology.
According to a feature of the present invention, a kind of pump is provided, comprising:
Stator;
Be installed at least one rotor in the housing, described housing is included in the first fluid passage that peritrochanteric extends, and described rotor comprises at least one the second fluid passages;
First sensor is configured to export the signal of indicating described stator temperature;
Second sensor is configured to export the signal of indicating described temperature of rotor; With
Heat control device, the signal magnitude that is used for exporting according to sensor when there is fluid in described passage is controlled the temperature of this fluid.
First temperature transducer can be arranged on the stator, and second temperature transducer can be arranged on the rotor in exhaust pressure district or the housing discharge portion with handle gas generation fluid communication place, perhaps be arranged in the gear-box of pump.
Described heat control mechanism can comprise first and second control mechanisms, is used for being controlled at respectively the temperature of any fluid of first and second passages.Any heat control mechanism comprises at least one speed change flow pump, a thermostatic control valve and a heat exchanger.They can be arranged to the temperature that output size according to one or more sensors removes to control fluid in the respective channel.Heat control mechanism can comprise microprocessor or be controlled by microprocessor.
One of them thermostatic control valve can comprise mechanical temperature differential valve.This valve can comprise the three-fluid passage with the second fluid passage thermal communication.Flow restrictor can be arranged on the fluid ratio of crossing this passage in the described three-fluid passage with control flows.The position of described Flow restrictor can be by the SC sigmal control that receives from described first and second sensors by signal receiver, and described signal receiver can be the part of described valve.Each signal receiver can comprise a sealed member, and the volume of sealing parts can expand in the time of use.The degree that expands depends on the size of the signal that receives, and has determined the relevant position of described limiter in the three-fluid passage.The sealed member of signal receiver can comprise expandable bellows.Flow restrictor can comprise axle and valve seat, thereby axle and valve seat cooperatively interact to open and close the fluid flow that an aperture control flows is crossed.
Pump can be a known structure arbitrarily, for example but be not strictly limited to screw pump, pawl formula pump (claw pump) and Roots pump (Root's blower).
Another characteristics of the present invention have provided the double-ended pump that comprises at least one rotor, comprising:
An intake section and two discharge portions;
Stator; With
Housing, second cavity that it comprises inner casing and shell, constitute between the described inner casing of first cavity that is made of inner casing, described housing and the shell, rotor is installed in described first cavity, fluid circulates by described second cavity, when using, described second cavity extends and around described rotor.
Another characteristics of the present invention have provided a kind of valve, and it comprises;
The fluid passage;
In described fluid passage the transportable Flow restrictor that is used for the fluid flow that control flows crosses and
Two signal receivers are used to receive corresponding signal and according to the position of big or small control flow rate limiter in described passage of the signal that receives.
Another characteristics of the present invention provide a kind of method of unclamping the pump rotor that blocks, and described rotor is to block owing to the lip-deep deposited material of internal work that pump the time has appearred being set in cooling, and described method comprises:
Introduce hot fluid in the cavity that is arranged in pump case, described cavity loop is around described rotor part;
The hot fluid that will be arranged in described cavity is heated to a predetermined temperature, and this temperature is enough high with softening described sediments; With apply torque and give the rotor of pump to overcome all remaining resistances that cause by the sediments on the internal work surface that is positioned at pump.
Another characteristics of the present invention provide a kind of method of controlling the gap between pump rotor of the present invention and the stator, comprising:
(a) temperature by each stator of sensor record and rotor;
(b) temperature difference between described stator of calculating and the described rotor;
(c) described temperature difference is compared with predetermined value;
(d) value of the suitable flow of the fluid of decision in described first and second fluid passages and temperature is to reach predetermined temperature difference; With
(e) the described heat control of control mechanism is with the value in the performing step (d).
Described method step can repeat at interval automatically at preset time, to control the disturbance in the pump structure in time.Described predetermined temperature difference can be revised so that the gap between parts changes at interval at preset time, thereby the sediments of accumulation can be removed from the surface of the parts of pump.
Described heat controller can comprise microprocessor, described microprocessor can be included in the computer, thereby can when this software is installed on the described computer, make computer carry out the method step of above-mentioned (a) to (e) optionally by computer software programming control.
The present invention makes pump have the heat control level of improvement.This makes in the process of described equipment running and obtains benefit in the following areas: provide tolerance that the running clearance of optimization improved pump with get rid of back-pressure as far as possible, reduce pump the ingress cold spots appearance, in the minimizing equipment heat stagnation (thermal lag) and when exist because of cooling form sedimental the time improve the possibility that restarts.
Description of drawings
Now with reference to accompanying drawing an example of the present invention is described, wherein:
Fig. 1 is the schematic cross sectional view of screw pump of the present invention;
Fig. 2 is the sectional drawing of both-end screw pump of the present invention;
Fig. 3 is the schematic representation of temperature control circuitry of the present invention;
Fig. 4 shows the pump rotor among Fig. 2 and the further details of the interface between the stator;
Fig. 5 shows more perfect scheme of the present invention;
Fig. 6 shows the present invention and is used for another example under the stricter environment;
Fig. 7 shows the details of the temperature differential valve in the pump that is used in Fig. 6;
Fig. 8 shows the Roots blower of execution heat control of the present invention.
Embodiment
In Fig. 1 and Fig. 2, screw pump has been shown.Two rotors 1 are arranged in the frame 2.The central shaft that the rotor 1 of the engagement of described two mutual counter-rotation is arranged to them is parallel to each other.Rotor 1 is installed on the housing 2 by bearing 3.Single ended pump among Fig. 1 comprises inlet stator 4 and exhaust stator 5, and the double-ended pump of example comprises inlet stator 4 between two exhaust stator 5 among Fig. 2.
The conventional pump that has hot jacket generally uses convection current to make hot liquid stream pass through stator.Can cause the temperature distributing disproportionation on the pump like this, particularly, colder part is positioned at the bottom of pump and is positioned at top than hot part.The cold spots of this localization can make to be handled gas and condenses and become and have corrosivity further.By in hot fluid, using recycle pump can reach consistent heat control, minimum thereby the localized variation of temperature can become.
In some cases, the reject product by pump includes material cured property or the height stickiness, and forms sediments in operation process on the surface of pump.When pump is shut down, these deposits cool and may solidifying.When such sediments is gap area between parts, pump is blocked.Motor just may not provide enough torques to go to overcome this extra frictional force and pump is rotated.Can provide extra torque by the lever rod member being inserted in the socket in the rotating shaft, thereby pump can rotate artificially.Yet this technology has applied bigger active force and may cause damage on rotor.But, also may not apply enough active forces and discharge this device and make rotating shaft rotate, in this case, this equipment just may need because of replacing or maintenance is stopped using and served.Under the situation that pump blocks owing to cooling, can select to use water overcoat of the present invention.Fluid in the cavity 6 of housing 2 can heat to improve the temperature of stator 4,5 and rotor 1.The ductility of residue can be improved like this and described device can be helped to unclamp.
It is how to be used for hot state in the control pump that Fig. 3 shows fluid line 11,12,12a and 15.Provide cooling fluid by recycle pump 17 in first closed circuit 11, the typical case is the mixture of water and freezing thing.Second fluid line 12 includes flow route and the thermostatic control valve 13 with pressure.Typically, main current 25 offer this circuit and discharge from exporting 26 from entering the mouth.Between these two fluid lines 11 and 12, be provided with heat-exchanging part 14.Valve 13 is from being arranged on thermosensor 21 receiving inputted signals on the stator, and utilizes this signal keeping suitable flow in second circuit 12, thus the temperature gradient on the control heat-exchanging part 14.And this temperature gradient has kept the temperature of first circuit 11.
As shown in Figure 2, rotor 1 comprises threaded section 9 and the rotating axis component 8 that separates.Helical thread portion 9 provides inner cooling cavity 7, and the main body of the rotating shaft 8 that separates is inserted in this cavity.The main body of rotating shaft 8 is slightly smaller than the diameter of the cooling cavity 7 that is positioned at rotor subject on diameter.Thereby cooling channel, coolant material typical case are provided is that oil can pass through this passage.It is little so that described flow of coolant speed is high as far as possible that this passage keeps, thereby so that by keeping the temperature difference between described rotor and the described freezing mixture and passing heat back the freezing mixture reservoir and improve refrigerating function.The entrance and exit of described cooling system is provided by described rotating axis component 8.
Turn back to Fig. 3, as can be seen, described oil remains in another closed circuit 15.This circuit 15 comprises recycle pump 19, filter 20 and heat-exchanging part 14a.This heat-exchanging part is connected with the second cooling circuit 12a, and comprises other thermostatic control valve 16.Thermostatic control valve 16 is from second thermosensor, 22 receiving inputted signals, and this sensor is being indicated the temperature of rotor by the processing gas in the end part of oil in the circuit 15 or rotor.Can monitor the temperature of lining, exhaust pressure district (promptly the end of rotor and the cavity between the stator wall), but temperature can be lower than the temperature of rotor very soon here.
By introducing two radiator valves of having described, with respect to the temperature of stator and the temperature of control pump rotor becomes possibility.Gap d (as shown in Figure 4) between control screw pump rotor and stator is a function of the described temperature difference between rotor and the stator.By the temperature control to described parts, the size of controlling this gap d becomes possibility.In addition, this gap d has determined the leakiness of the processing gas between rotor and stator, thereby shown in the 231st page of " modern vacuum practice " (Modern Vacuum Practice) (Nigel Harris work, McGraw Hill publishes), for flowing of middle transitional, leakage rate and d
3Be directly proportional.Because the leakage contribution pump performance, so pump performance can be optimized by the temperature of controlling these parts.In addition, it is useful keeping gap d, and any fraction of particle of handling gas like this can not form obstacle and limit freely rotating of rotor in these gaps.Because the restriction of the processing gas that flows through, also have the extra torque that applies by motor for the rotational velocity that keeps suitable rotor, these obstacles can have a strong impact on pump performance.
By temperature-control circuit is provided in rotor, becomes possibility with respect to the thermostatically control of the temperature of rotor of stator temperature, thereby optimize the gap d of rotor/stator.In the simplest enforcement of the present invention, the present invention is used to avoid simply cold spots, therefore eliminated above-mentioned discussion because the corrosion that formation is condensed and produced.In more complicated enforcement, can obtain input signal from the sensor that is installed on each stator 4,5 and the rotor 1, these signals can for example be less than 135 ° by closed loop control system analysis/processing to keep a temperature series.Allow to use pump of the present invention to handle safely like this and have the material that oneself knows spontaneous ignition temperature.
But as discussed above, the present invention can be used under the higher situation of complexity selecting concrete temperature, thereby reaches and keep concrete gap d.Fig. 5 shows processor or central processing unit (CPU) the 27th, how can be combined in the described system with received signal, and described signal comes from sensor 22a and 21a and indicating the temperature of rotor and stator respectively.These signals provide input so that processor 27 can determine the temperature that each parts is required.The valve 13a of processor 27 control electric starts and 16a provide suitable cooling fluid level to give heat-exchanging part 14,14a then, thus the gap d that reaches desired thermal equilibrium and obtain therefrom.
Under normal stable working order, the gap between rotor and the stator has determined the speed of specifically pumping of dry pump.If the inlet pressure to pump increases, more gas will enter in the pump.This extra gas can make rotor cool down with respect to stator, thereby the gap d between these two parts will increase.Then, can big leakage rate appear at peritrochanteric under higher pressure.When pumping gaseous species for example helium the time, this will bother especially, when near atmospheric gas pressure the time, typically causes low speed of pumping and gas pumpability.By control characteristic of the present invention, the gap d that artificially reduces between rotor and the stator is possible.Therefore the leakage of peritrochanteric can reduce, and the efficient of pump can brightly improve effectively.In the above example, when pumping helium, in order to prevent to leak, the slit that keeps little wishes to obtain.Yet on Another application, same pump may be used for pumping argon gas and the bigger slit of needs.By a kind of pump is provided, it can be optimized basically so that work efficiently under the condition of various variations in operation process, thereby obtains a kind of multipurpose pump.This multifunctionality can reach good effect on various fields, for example make up a prescription or chemical process industry (CPI) on, a pump need use same tool and be used for different application.
Temperature controlling is variable in concrete process.Since the thermal mass of associated components than big difference, the temperature of rotor increases with the speed faster than stator, therefore generally when starting has a bigger temperature difference.Yet this temperature difference will reduce when pump reaches steady state.By dynamic control temperature, can minimize this early stage difference, thereby gap d can remain on approximate stationary value.Thereby the more maintenance level that causes pump efficiency.
When pump operated under normal operation, the dynamic control in described gap can be implemented in the circuit mode.At preset time at interval, heat condition can be revised to reduce the gap between rotor and stator in one period short time.This has the effect that the process sediments that sticks on the parts is removed/removed.If this process repeats at certain time intervals, can significantly reduce the accumulation of solid matter on the internal surface of pump and form, thereby prevent blocking of pump.
By the pressure in the extra sensor pump or the energy consumption of pump are provided, can further avoid blocking of pump.If one in these values increases significantly, this may indicate described gap just becoming obstruction and will block.By detecting these values, make the maximum cool condition of initialization rotor part become possibility, thereby prevent blocking of pump with the gap between maximization rotor 1 and the stator 4,5.
In addition, heat control mechanism can be provided by pure mechanical mechanism as shown in Figure 6 and Figure 7, and wherein the actual temp that can keep automatically between stator and the rotor is poor.In this case, be provided with comparatively simple in pump but firmer device, described pump is exposed to especially under the harsh conditions.Machinery heat control device 24 is directly connected on sensor 22 and 23, described sensor 22 is placed into as above-mentioned description the temperature with oil in temperature of indicating rotor by the processing gas in swept volume or the gear-box, and described sensor 23 is placed in the stator of pump.This aftermentioned sensor 23 can be arranged on to Fig. 3 in provide on the similar position of the sensor 21 of input for heat control valve (HCV) 13.Each end of temperature differential valve obtains different temperature and seal sensor/bellows arrangement is heated from each sensor, thereby makes bellows expansion.These two bellows arrangement work in combination are to locate inner valve.The positioning control of this valve the cool stream scale of construction that can be by heat circuit, thereby change the heat dissipating capacity of heat exchange unit 14a.So just can be by the temperature that changes the pump parts gap in the control pump.This comparatively simple example only kept temperature difference between rotor 1 and the stator 4,5, rather than each parts of control separately initiatively.But by keeping these relevant temperature, consistent gap just can keep.Valve 24 can physically change, and for example, limits the expansion of one of them bellows components in order to adjust temperature extent between rotor 1 and the stator 4,5, thereby adapts to different processes.
The present invention is not limited in and is applied on the screw pump, and the pump that can also easily be applied to other types is pawl formula pump or Roots pump for example.In fact in some Roots blowers, can run into quite high exhaust pressure (reaching 2 to 3 crust sometimes).These increased pressure cause the remarkable rising of part temperatures in the pump, thereby have problems when keeping appropriate gap.By using according to dynamic heat control of the present invention, thereby these gaps can remain on consistent level improves pump under the different operating condition tolerance.
Fig. 8 shows the rotor 35 of Roots blower, in order to introduce heat control of the present invention, need introduce similar cooling channel 34 in Fig. 2 helical rotor 1 in rotor 35.In order to pass the freezing mixture reservoir back by the temperature difference between maintenance rotor 35 and the freezing mixture and with heat, the typical case is the gear-box (not shown), thereby improves refrigerating function, and described passage is same to keep little so that described flow of coolant speed is high as far as possible.The inlet 32 and the outlet 33 of cooling channel are provided by rotor shaft parts 31.The cooling channel is passed in each convex portion 30 on the rotor 35 of Roots blower, is positioned at epitrochanterian convex portion and can is as shown in the figure 2, also can be 3,4 or more a plurality of.
Be noted that aforesaid description only is several embodiments of the present invention, undoubtedly, under the prerequisite that does not break away from true scope of the present invention, the reader who is skilled in technique can expect other embodiments, and scope of the present invention is defined by the appended claims.
Claims (31)
1. pump comprises:
Stator;
Be installed at least one rotor in the housing, described housing comprises the first fluid passage that extends along described peritrochanteric, and described rotor comprises at least one the second fluid passages;
First sensor is configured to export the signal of indicating described stator temperature;
Second sensor is configured to export the signal of indicating described temperature of rotor;
Heat control device, the signal magnitude that is used for exporting according to sensor when there is fluid in described passage is controlled the temperature of this fluid.
2. pump according to claim 1 is characterized in that: described first temperature transducer is positioned on the described stator.
3. according to claim 1 or the described pump of claim 2, it is characterized in that: described second sensor is arranged in gear-box.
4. according to claim 1 or the described pump of claim 2, it is characterized in that: described second temperature transducer is arranged in described housing, contacts with processing gaseous fluid in the discharge portion of described rotor in the time of use.
5. according to the described pump of each aforementioned claim, it is characterized in that: described heat control device comprises:
First control device, it is used for controlling the fluid temperature (F.T.) of first fluid passage;
Second control device, it is used for controlling the fluid temperature (F.T.) of described at least one the second fluid passages.
6. pump according to claim 5 is characterized in that: described first control device comprises:
At least one flow pump;
At least one control valve; With
At least one heat exchanger.
7. according to claim 5 or the described pump of claim 6, it is characterized in that: described first control device is arranged to according to the signal magnitude of first sensor output and goes to control fluid temperature (F.T.) in the first fluid passage.
8. according to each described pump in the claim 5 to 7, it is characterized in that: described second control device comprises:
At least one flow pump;
At least one control valve; With
At least one heat exchanger.
9. according to each described pump in the claim 5 to 8, it is characterized in that: described second control device is arranged to according to the described at least second signal of sensor size and goes to control fluid temperature (F.T.) in described at least one the second fluid passages.
10. according to each described pump in the claim 5 to 9, it is characterized in that: described second sensor arrangement becomes according to the signal magnitude of described second sensor and additional sensors output to go to control fluid temperature (F.T.) in described at least one the second fluid passages, and described additional sensors is configured to export the signal of indicating described stator temperature.
11. according to each described pump in the claim 5 to 9, it is characterized in that: described second control device is arranged to according to the signal magnitude of described first and second sensors output and goes to control fluid temperature (F.T.) in described at least one the second fluid passages.
12. according to each described pump in the claim 5 to 11, it is characterized in that: comprise microprocessor, it is used for controlling described first and second control gear at least one.
13. according to each described pump in the claim 5 to 12, it is characterized in that: comprise microprocessor, it is used to control described first and second control gear.
14. according to the pump described in claim 12 or the claim 13, it is characterized in that: comprise the 3rd sensor, be configured to output signal to described microprocessor, described signal is being indicated in the pressure of described pump and the energy consumption, and wherein microprocessor is arranged to the described at least second control device of size control according to described signal.
15. according to each described pump in the claim 9 to 12 that is subordinated to claim 8, it is characterized in that: described at least one control valve of second control device comprises mechanical type temperature differentiator.
16. pump according to claim 15 is characterized in that: described mechanical valve comprises:
The three-fluid passage, itself and the described at least one the second fluid passage thermal communications;
Flow restrictor, it can move in described three-fluid passage, the fluid flow of crossing with control flows; With
Two signal receivers are used for respectively from the described first and second sensor received signals, and control the position of described flow dontroller described third channel according to the signal magnitude that receives from described first and second sensors.
17. pump according to claim 16 is characterized in that: each signal receiver comprises sealed member, and in the time of work, described each parts collapse with the signal magnitude that receives, thereby controls the relevant position of described limiter in the three-fluid passage.
18. pump according to claim 17 is characterized in that: each signal receiver comprises expandable bellows.
19. according to each described pump in the claim 16 to 18, it is characterized in that: described Flow restrictor comprises:
Axle; With
Valve seat, in the time of work, described axle and described valve seat match work with the opening and closing aperture, thus control flows is crossed fluid flow wherein.
20. according to the described pump of aforementioned each claim, it is characterized in that: described pump is a screw pump, a kind of in pawl formula pump and the Roots pump.
21. according to the described pump of aforementioned each claim, it is characterized in that: described housing comprises inner casing and shell, described inner casing has formed first cavity, described rotor is installed in wherein, formed described first fluid passage between the inner casing of described housing and the shell, described passage is along the length direction extension of described rotor and around described rotor.
22. pump according to claim 21 is characterized in that: in the time of use, the inner casing of described housing provides described stator.
23. a double-ended pump comprises:
At least one rotor, it has an intake section and two discharge portions;
Stator; With
Housing, it comprises inner casing and shell, described inner casing has formed first cavity, described rotor is installed on wherein, and second cavity that forms between the inner casing of described housing and the shell, when using, fluid flows by this cavity, and wherein said second cavity is along the length direction extension of described rotor and around described rotor.
24. a valve comprises:
The fluid passage;
Flow restrictor, it can move in described fluid passage, the fluid flow of crossing with control flows; With
Two signal receivers are used for respectively received signal and control the position of described Flow restrictor at described passage according to the signal magnitude that receives.
25. a method of unclamping the pump rotor that blocks owing to the appearance of species precipitate thing, this sludge are that to be formed on the internal work of pump in cooling lip-deep, said method comprising the steps of:
Hot fluid is incorporated in the cavity in the shell of described pump, and described cavity loop is around rotor part;
To be heated to a predetermined temperature at the hot fluid in the described cavity, this temperature is enough to make described sludge softening; With
Rotor to pump applies torque to overcome any resistance that exists that is caused by the lip-deep sediments of the internal work of pump.
26. a method of controlling the rotor in each described pump and the gap between the stator in the claim 1 to 22 said method comprising the steps of:
(a) utilize signal of sensor to write down the temperature of each rotor and stator;
(b) temperature difference between calculating stator and the rotor;
(c) this temperature difference is compared with a predetermined value;
(d) determine the suitable flow of the fluid in first and second fluid passages and the value of temperature, with the temperature difference that obtains to be scheduled to; With
(e) the control heat control device is with the value in the performing step (d)
27. method according to claim 26 is characterized in that: described method step repeats at interval automatically at preset time, to control the disturbance in the pump structure in time.
28. according to claim 26 or 27 described methods, it is characterized in that: described predetermined temperature difference is revised with the gap between the change parts at interval at preset time, thereby the sediments that gathers is removed from the surface of the parts of pump.
29. a computer program when installing on computers, carries out as claim 26,27 or 28 described methods computer.
30. a computer readable carrier medium, it is loaded with computer program as claimed in claim 29.
31. computer readable carrier medium according to claim 30 is characterized in that: described medium is from floppy disk, and CD is selected in mini-disk or the digital tape.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GBGB0223769.1A GB0223769D0 (en) | 2002-10-14 | 2002-10-14 | A pump |
| GB0223769.1 | 2002-10-14 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1703584A true CN1703584A (en) | 2005-11-30 |
Family
ID=9945809
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2003801011997A Pending CN1703584A (en) | 2002-10-14 | 2003-10-10 | Screw pump |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US20060153696A1 (en) |
| EP (1) | EP1552153A1 (en) |
| JP (1) | JP2006503220A (en) |
| KR (1) | KR101120887B1 (en) |
| CN (1) | CN1703584A (en) |
| AU (1) | AU2003271940A1 (en) |
| GB (1) | GB0223769D0 (en) |
| TW (1) | TW200422522A (en) |
| WO (1) | WO2004036049A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101341336B (en) * | 2005-12-15 | 2013-09-25 | 爱德华兹有限公司 | Apparatus for detecting a flammable atmosphere within a compressor, in particular vacuum pump |
| CN105041648A (en) * | 2015-09-15 | 2015-11-11 | 珠海格力电器股份有限公司 | Screw compressor and machine body thereof |
| CN107709787A (en) * | 2015-09-24 | 2018-02-16 | 李仁喆 | Vavuum pump with cooling device |
| CN108884833A (en) * | 2017-02-10 | 2018-11-23 | 恩泰克尼亚咨询有限公司 | The method and vacuum pump of manufacture and group armored pump |
| CN111749896A (en) * | 2020-07-07 | 2020-10-09 | 杭州派祺空气净化科技有限公司 | Energy-saving air compressor capable of eliminating friction force by utilizing magnetic suspension |
| US20220164013A1 (en) * | 2003-11-07 | 2022-05-26 | Asetek Danmark A/S | Cooling system for a computer system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7963744B2 (en) | 2004-09-02 | 2011-06-21 | Edwards Limited | Cooling of pump rotors |
| GB0502149D0 (en) | 2005-02-02 | 2005-03-09 | Boc Group Inc | Method of operating a pumping system |
| GB0508872D0 (en) * | 2005-04-29 | 2005-06-08 | Boc Group Plc | Method of operating a pumping system |
| GB0510892D0 (en) * | 2005-05-27 | 2005-07-06 | Boc Group Plc | Vacuum pump |
| GB0525378D0 (en) | 2005-12-13 | 2006-01-18 | Boc Group Plc | Screw Pump |
| JP4821308B2 (en) * | 2005-12-21 | 2011-11-24 | 株式会社島津製作所 | Vacuum pump |
| JP6418838B2 (en) * | 2014-07-31 | 2018-11-07 | エドワーズ株式会社 | Dry pump and exhaust gas treatment method |
| CN108302040B (en) * | 2018-03-14 | 2023-05-09 | 深圳市志橙半导体材料有限公司 | Anti-seizing device and anti-seizing method for dry vacuum pump |
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| FR2637655B1 (en) * | 1988-10-07 | 1994-01-28 | Alcatel Cit | SCREW PUMP TYPE ROTARY MACHINE |
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- 2002-10-14 GB GBGB0223769.1A patent/GB0223769D0/en not_active Ceased
-
2003
- 2003-10-10 CN CNA2003801011997A patent/CN1703584A/en active Pending
- 2003-10-10 EP EP03753778A patent/EP1552153A1/en not_active Withdrawn
- 2003-10-10 US US10/531,558 patent/US20060153696A1/en not_active Abandoned
- 2003-10-10 JP JP2004544445A patent/JP2006503220A/en active Pending
- 2003-10-10 WO PCT/GB2003/004415 patent/WO2004036049A1/en not_active Application Discontinuation
- 2003-10-10 AU AU2003271940A patent/AU2003271940A1/en not_active Abandoned
- 2003-10-10 KR KR1020057006340A patent/KR101120887B1/en not_active IP Right Cessation
- 2003-10-14 TW TW092128450A patent/TW200422522A/en unknown
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20220164013A1 (en) * | 2003-11-07 | 2022-05-26 | Asetek Danmark A/S | Cooling system for a computer system |
| CN101341336B (en) * | 2005-12-15 | 2013-09-25 | 爱德华兹有限公司 | Apparatus for detecting a flammable atmosphere within a compressor, in particular vacuum pump |
| CN105041648A (en) * | 2015-09-15 | 2015-11-11 | 珠海格力电器股份有限公司 | Screw compressor and machine body thereof |
| US10487834B2 (en) | 2015-09-15 | 2019-11-26 | Gree Electric Appliances, Inc. Of Zhuhai | Screw compressor and a compressor body thereof |
| CN107709787A (en) * | 2015-09-24 | 2018-02-16 | 李仁喆 | Vavuum pump with cooling device |
| CN107709787B (en) * | 2015-09-24 | 2020-07-07 | 李仁喆 | Vacuum pump with cooling device |
| CN108884833A (en) * | 2017-02-10 | 2018-11-23 | 恩泰克尼亚咨询有限公司 | The method and vacuum pump of manufacture and group armored pump |
| CN111749896A (en) * | 2020-07-07 | 2020-10-09 | 杭州派祺空气净化科技有限公司 | Energy-saving air compressor capable of eliminating friction force by utilizing magnetic suspension |
| CN111749896B (en) * | 2020-07-07 | 2022-11-08 | 山东顺和新材料科技有限公司 | Energy-saving air compressor capable of eliminating friction force by utilizing magnetic suspension |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2006503220A (en) | 2006-01-26 |
| AU2003271940A1 (en) | 2004-05-04 |
| KR101120887B1 (en) | 2012-02-27 |
| US20060153696A1 (en) | 2006-07-13 |
| TW200422522A (en) | 2004-11-01 |
| WO2004036049A1 (en) | 2004-04-29 |
| GB0223769D0 (en) | 2002-11-20 |
| KR20050050133A (en) | 2005-05-27 |
| EP1552153A1 (en) | 2005-07-13 |
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