CN1705826A - Variable inner volume ratio-type inverter screw compressor - Google Patents
Variable inner volume ratio-type inverter screw compressor Download PDFInfo
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- CN1705826A CN1705826A CNA200380101612XA CN200380101612A CN1705826A CN 1705826 A CN1705826 A CN 1705826A CN A200380101612X A CNA200380101612X A CN A200380101612XA CN 200380101612 A CN200380101612 A CN 200380101612A CN 1705826 A CN1705826 A CN 1705826A
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- 230000006835 compression Effects 0.000 claims abstract description 35
- 238000007906 compression Methods 0.000 claims abstract description 35
- 238000006243 chemical reaction Methods 0.000 claims description 16
- 230000008859 change Effects 0.000 claims description 13
- 239000007921 spray Substances 0.000 claims description 5
- 230000033228 biological regulation Effects 0.000 abstract description 3
- 230000007246 mechanism Effects 0.000 abstract description 3
- 230000001105 regulatory effect Effects 0.000 abstract 2
- 230000001934 delay Effects 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 14
- 238000000034 method Methods 0.000 description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 7
- 230000009471 action Effects 0.000 description 6
- 239000002826 coolant Substances 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 239000003507 refrigerant Substances 0.000 description 4
- 239000006200 vaporizer Substances 0.000 description 4
- 238000003860 storage Methods 0.000 description 3
- 239000003795 chemical substances by application Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012467 final product Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
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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
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
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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
- F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
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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
- F04C2240/00—Components
- F04C2240/40—Electric motor
- F04C2240/403—Electric motor with inverter for speed control
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Regulating compression capability to a load is performed by an inverter (15) that regulates revolution number of an electric motor (11). This makes unload control in capability regulation unnecessary, preventing operational efficiency from lowering. Further, a capacity control valve for capacity control is eliminated for a simplified valve control mechanism. Regulating a variable inner volume ratio achieves the highest compressor efficiency corresponding to operating condition (capability). When a low inner volume ratio command is issued, a slide valve (19) is moved by a compression section controller (27) in an axial direction toward the electric motor (11). This advances completion time of a compression step to advance discharge of a compressed gas. When a high inner volume ratio command is issued, the slide valve (19) is moved in an axial direction toward a piston (25), which delays time of completion of compression step to delay discharge of a compressed gas.
Description
Technical field
The present invention relates to a kind of ratio that can change the suction volume of helical-lobe compressor and spray volume, i.e. the variable inner volume ratio formula frequency conversion screw compressor of internal capacity ratio.
Background technique
In the past, as the variable inner volume ratio formula screw type compressor that can change above-mentioned internal capacity ratio, compressor shown in Figure 7 (for example, with reference to No. 3159762 communique of patent) was arranged.
In this variable inner volume ratio formula screw type compressor, needs change above-mentioned internal capacity than the time, utilize stepper motor 1 to make connecting rod (rod) 2 rotation, variable VI (internal capacity than) valve 3 is for example retreated.At this moment, capacity control drive 4 retreats with variable VI valve 3, when variable VI valve 3 is fixed in new desired location, fixed once more with the state that contacts variable VI valve 3, like this, the front end of above-mentioned capacity control drive 4 retreat into change after internal capacity than corresponding position, stipulate the opening degree of ejiction opening 5 again.
During this situation, detected pressures P
D1, and provide to stepper motor 1 and to make this detected pressures P
D1With the ejection pressure P
D2Difference Δ P be minimum signal, specify above-mentioned internal capacity ratio thus, described pressure P
D1Be the space and ejection spatial communication pressure before that rotor and housing 7 inwalls by when running form.Perhaps, the parameter trend of the suction pressure when utilizing control gear 10 to analyze running, ejection pressure etc. is predicted best internal capacity ratio, and provides the signal of the value of this best internal capacity ratio of expression to stepper motor 1, specifies above-mentioned internal capacity ratio thus.
In said structure, the fluid that sucks from inlet hole 6 after being compressed by yin, yang rotor (not shown) housing 7 in, passes through ejiction opening 5 and sprays to spraying hole 8.
Under this state, impose on the load change of variable inner volume ratio formula screw type compressor, needing under the situation of volume controlled, according to this control command, hydraulic piston 9 carries out forward motion, make the amount that 4 of capacity control drives advance to be needed, so between variable VI valve 3 and capacity control drive 4, produce the gap.And, the fluid in the compression from the gap of variable VI valve 3 and capacity control drive 4 at suction side bypass (by-pass).
Promptly, in No. 3159762 communique of above-mentioned patent, make from the internal capacity ratio of the pressurized gas of capacity control drive 4 ejection and can change,, and reach the highest compressor efficiency so that corresponding to full load ability (100% load) the height pressure condition during running down.
But, in No. 3159762 communique of above-mentioned patent in the past, in the disclosed variable inner volume ratio formula screw type compressor, have following problem.
Promptly, the variable inner volume ratio technology of above-mentioned variable inner volume ratio formula screw type compressor in the past, make from the internal capacity ratio of the pressurized gas of ejiction opening 5 ejection and can change, so that reach the highest compressor efficiency corresponding to the height pressure condition in when running, but the setting when forming corresponding to full load ability (100% load).And, when the sub load ability (during partial load) and since make compression fluid midway from the gap of variable VI valve 3 and capacity control drive 4 in the suction side bypass, need carry out ability adjustment (Unloading Control), so there is the relatively poor problem of efficient.
In addition, owing to be provided with the variable VI valve 3 and the capacity control drive 4 that carries out volume controlled of change internal capacity ratio, so need be provided with respectively the change internal capacity than the time variable VI valve 3 control mechanisms and capacity control drive 4 control mechanisms of control during capacity, have the valve control device complicated problems.
Summary of the invention
The objective of the invention is to, provide a kind of can be according to load (operating condition) often with the variable inner volume ratio formula helical-lobe compressor of maximal efficiency running.
In order to achieve the above object, variable inner volume ratio formula frequency conversion screw compressor of the present invention is characterised in that to have: variable inner volume ratio valve, can change the internal capacity ratio at the concluding time of the compression step by change screw compression portion; The motor of the above-mentioned screw compression of rotation driving portion; Control the frequency variator of the speed of above-mentioned motor according to load.
According to said structure, when adjusting compressed capability, utilize the speed of inverter control motor according to load.Like this, do not carry out Unloading Control and can carry out the ability adjustment.And, in order to reach the highest compressor efficiency corresponding, the aperture of control variable inner volume ratio valve, the concluding time of the compression step of setting screw compression portion with the speed of the above-mentioned motor of being adjusted.As a result, can often turn round according to load with maximal efficiency.
And, variable inner volume ratio formula frequency conversion screw compressor of the present invention is characterised in that, have control device,, control the aperture of above-mentioned variable inner volume ratio valve according to the speed of suction side pressure and the ejection side pressure and the above-mentioned motor of above-mentioned screw compression portion.
According to said structure, when above-mentioned variable inner volume ratio, utilize control device, according to the suction side pressure of above-mentioned screw compression portion and the speed of ejection side pressure and above-mentioned motor, control the aperture of above-mentioned variable inner volume ratio valve.Therefore, can utilize the speed of predefined compression ratio and motor and the relation of best internal capacity ratio, accurately and easily control above-mentioned internal capacity ratio, to reach the speed the highest pairing compressor efficiency of the above-mentioned motor of adjusting by above-mentioned frequency variator.
Description of drawings
Figure 1A, 1B are the major component structural drawing of variable inner volume ratio formula frequency conversion screw compressor of the present invention.
Fig. 2 is the figure of the ability internal capacity ratio control system of expression variable inner volume ratio formula frequency conversion screw compressor shown in Figure 1.
Fig. 3 is the figure of the expression ability internal capacity ratio control system different with Fig. 2.
Fig. 4 is the figure of relation of each speed of expression compression ratio and best internal capacity ratio.
Fig. 5 is the figure of relation of each compression ratio of expression refrigerating capacity and compressor efficiency.
Fig. 6 A, 6B are the figure of the relation of the internal volume of expression screw type compressor and pressure.
Fig. 7 is the sectional drawing of variable inner volume ratio formula screw type compressor in the past.
Embodiment
Below, describe the present invention in detail according to illustrated embodiment.Fig. 1 is the summary construction diagram of the variable inner volume ratio formula frequency conversion screw compressor of present embodiment.Figure 1A represent low internal capacity than the time, when Figure 1B represents that high internal capacity compares.
In Fig. 1,11 represent motor, have to be fixed on stator 12 that is fixed in housing (not shown) and a distolateral and rotor rotated 13 that is fixed in main shaft 14.Motor 11 carries out frequency conversion drive by frequency variator (inverter) 15.The two ends of above-mentioned main shaft 14 are supported by bearing 16,17, at another distolateral screw rotor (screw rotor) 18 that is installed with of main shaft 14.When main shaft 14 rotated by motor 11, screw rotor 18 rotations utilized thread groove (not shown) compression of outer circumferential face to suck gas.Be provided with the guiding valve cylindraceous 19 in the face of the outer circumferential face of screw rotor 18, it has the ejiction opening 20 of specific length in the axial direction, and the gas that is compressed by screw rotor 18 sprays from ejiction opening 20.
At the opposition side end face of the motor 11 of above-mentioned guiding valve 19 end of a plurality of connecting rods (rod) 22 is installed, it is being supported by dunnage 21 and is being free to slide.The other end of each connecting rod 22 is installed on the connecting plate 23.Opposite side surfaces central authorities at the screw rotor 18 of dunnage 21 are provided with cylinder 24, and piston 25 is accommodated in this cylinder 24, at the opposition side of the screw rotor 18 of piston 25 piston rod 26 are installed, and at the front end of piston rod 26 connecting plate 23 are installed.Like this, along with piston 25 moves to axial, guiding valve 19 by piston rod 26, connecting plate 23 and connecting rod 22 to moving axially.
Advance to be discharged to the working fluid in the working room of piston 25 both sides in the above-mentioned cylinder 24, according to control signal, by fluid control device 28 controls from press part controller 27.In addition, the concrete structure of above-mentioned fluid control device 28 is, when the reduction internal capacity compares, according to making piston 25 shown in Figure 1A to screw rotor 18 side shiftings, and when the raising internal capacity compares, move according to the opposition side that makes piston 25 to screw rotor 18 shown in Figure 1B,, just be not particularly limited as long as have this structure.
In the variable inner volume ratio formula frequency conversion screw compressor of said structure, utilize the rotating speed control of 15 pairs of motor 11 of frequency variator, carry out the ability adjustment of relative load.Like this, when ability is adjusted, do not need to carry out Unloading Control, can suppress the reduction of running efficiency.In addition, do not need to carry out the capacity control drive of volume controlled, can simplify valve control device.
To this, utilize the position of press part controller 27 control guiding valves 19, make above-mentioned variable inner volume ratio reach the peak efficiency corresponding with operating condition.And, when low internal capacity ratio instructs, make guiding valve 19 (that is, the initial position of ejiction opening 20) to axial motors 11 side shiftings, accelerate the concluding time of the compression step of press part thus, spray pressurized gas as early as possible.On the other hand, when high internal capacity ratio instructs, make guiding valve 19 (that is, the initial position of ejiction opening 20), postpone the concluding time of the compression step of press part, postpone the ejection pressurized gas to axial piston 25 side shiftings.That is, in the present embodiment, utilize guiding valve 19 to constitute above-mentioned variable inner volume ratio valve.
And, as mentioned above, utilize above-mentioned frequency variator 15 to set the rotating speed of motor, utilize press part controller 27 to set the position of guiding valves 19 after, the suction gas that sucks from suction port is imported into screw rotor 18 by motor 11 inside.And, by the above-mentioned thread groove compression that is formed at screw rotor 18 outer circumferential faces, from ejiction opening 20 ejections of guiding valve 19.
Below, the rotating speed control of motor 11 of present embodiment and the positioning control of guiding valve 19 are described.
Fig. 2 is the figure of the ability internal capacity ratio control system of this variable inner of expression volume ratio formula frequency conversion screw compressor.In Fig. 2, be that example describes with the helical-lobe compressor 31 that is installed in compression heating and cooling agent on the refrigerating machine.
Above-mentioned refrigerating machine constitutes helical-lobe compressor 31, condenser 32, expansion valve 33 and vaporizer 34 is linked in sequence circlewise.Carry out heat exchange with cooling water or air from the high-temperature high-pressure refrigerant of helical-lobe compressor 31 ejection condenser 32 and be condensed, the liquid refrigerant that becomes cryogenic high pressure is supplied with expansion valve 33.The low temperature low pressure liquid refrigerants that is reduced pressure by expansion valve 33 is carried out heat exchange with water and is evaporated in vaporizer 34, become low-pressure gas and return helical-lobe compressor 31.The cold water that is cooled at vaporizer 34 is used for air-cooling system.
Refrigerant pipe at above-mentioned vaporizer 34 is installed with temperature transducer 35, and expression is transfused to the rotating speed carry-out part 37 of control gear 36 from the testing signal of the coolant water temperature Tw of this temperature transducer 35.Like this, rotating speed carry-out part 37 is based on the coolant water temperature Tw of the testing signal of the being imported information as load side, according to for example poor with setting temperature, calculate the speed Hz of the motor 11 that is used to obtain needed refrigerating capacity, export to the best internal capacity specific output portion 38 and the frequency variator 15 of control gear 36.Frequency variator 15 is controlled the rotating speed of motor 11 according to the speed Hz of above-mentioned reception.Thus, carry out the ability adjustment of relative load.
On the other hand, low-pressure lateral pressure sensor 40 is installed, high side pressure sensor 41 is installed in the ejection side in the suction side of the screw compression portion 39 that comprises above-mentioned screw rotor 18 and guiding valve 19.And expression is from the testing signal of the low-pressure LP of low-pressure lateral pressure sensor 40 and the expression testing signal from the high pressure HP of high side pressure sensor 41, is transfused to best internal capacity specific output portion 38.Like this, best internal capacity specific output portion 38 is according to suction side low-pressure LP and ejection side high pressure HP based on the testing signal of being imported, detects the operational situation behind the rotating speed of setting motor 11.And, according to low-pressure LP and high pressure HP and from the speed Hz of rotating speed carry-out part 37, carry out calculation process, calculate the best internal capacity ratio of current speed Hz, export to press part controller 27.Like this, press part controller 27 is according to the action than control flows member control apparatus 28 of the internal capacity of above-mentioned reception.And, carry out the internal capacity corresponding than control with operational situation.
But, the structure of above-mentioned fluid control device 28 has when carrying out with guiding valve 19 to the parts (external drive motors of operated pilot valve (pilot valve) etc.) of axial mobile proportional action, can detect the position of guiding valve 19 according to the operating position of above-mentioned parts.During this situation, testing signal, via press part controller 27 or directly import best internal capacity specific output portion 38 from the position SV of the expression guiding valve 19 of fluid control device 28.In best internal capacity specific output portion 38, obtain current internal capacity ratio according to the position SV of the guiding valve 19 of above-mentioned reception, best internal capacity ratio is carried out feedback control.Like this, can carry out the control of variable inner volume ratio accurately.
In addition, the structure of above-mentioned fluid control device 28 for can not detect guiding valve 19 the position structure (for example, constitute by pipe arrangement and solenoid valve) time, the best internal capacity specific output portion 38 takes advantage of the output internal capacity ratio that rises when calculating self-starting, and, take advantage of this calculation internal capacity ratio as current internal capacity ratio, calculate controlled quentity controlled variable Δ VI, can carry out feedback control thus best internal capacity ratio.
Fig. 3 is the figure of the expression ability internal capacity ratio control system different with Fig. 2.In Fig. 3, helical-lobe compressor 31 also is installed on the refrigerating machine.And control gear 51 has the structure different with Fig. 2 with frequency variator 54.Below, give identical label to the parts identical with Fig. 2, the action of control gear 51 and frequency variator 54 mainly is described.
Identical with situation shown in Figure 2, expression is transfused to rotating speed carry-out part 52 to control gear 51 from the testing signal of the coolant water temperature Tw of temperature transducer 35.And expression is from the testing signal of the low-pressure LP of low-pressure lateral pressure sensor 40 and the expression testing signal from the high pressure HP of high side pressure sensor 41, is transfused to the best internal capacity specific output portion 53 to control gear 51.Utilize rotating speed carry-out part 52, calculate the speed Hz of the motor 11 of the refrigerating capacity that is used to obtain needs, utilize the rotating speed of frequency variator 54 control motor 11 according to coolant water temperature Tw.Thus, carry out the ability adjustment of relative load.
Driving voltage V and driving current A (or driving electric power W) that the frequency variator 54 of present embodiment can detect above-mentioned motor 11 send back to rotating speed carry-out part 52 to driving voltage V that is detected and driving current A (or driving electric power W).By rotating speed carry-out part 52, the driving voltage V of above-mentioned speed Hz that calculates and above-mentioned reception and driving current A (or driving electric power W) are sent to best internal capacity specific output portion 53.
Like this, above-mentioned best internal capacity specific output portion 53 is identical with situation shown in Figure 2, according to from the low-pressure LP of pressure transducer 40,41 and high pressure HP and from the speed Hz of rotating speed carry-out part 52 with from the position SV of the guiding valve 19 of fluid control device 28, carry out calculation process, calculate controlled quentity controlled variable Δ VI, export to press part controller 27 best internal capacity ratio.
In addition, in the present embodiment, utilize 53 storages of above-mentioned best internal capacity specific output portion to pass from the driving voltage V of rotating speed carry-out part 52 and the variation of driving current A (or driving electric power W).And one side is carried out above-mentioned internal capacity repeatedly than action, and one side is carried out internal capacity than control, so that driving voltage V and driving current A (or driving electric power W) are minimum.
After, identical with situation shown in Figure 2, utilize above-mentioned press part controller 27, according to the controlled quentity controlled variable Δ VI of above-mentioned reception, the action of control flows member control apparatus 28, feedback control is corresponding to the internal capacity ratio of operational situation.
In addition, situation with Fig. 2 during this situation is identical, the structure of above-mentioned fluid control device 28 is for can not detect the structure of position of guiding valve 19 time, after the best internal capacity specific output portion 53 takes advantage of the output internal capacity ratio that rises when calculating self-starting, calculate internal capacity ratio as current internal capacity ratio taking advantage of, calculate the controlled quentity controlled variable Δ VI of best internal capacity ratio.
In the best internal capacity specific output portion 38,53 of Fig. 2 and control gear 36,51 shown in Figure 3, carry out calculation process and calculate controlled quentity controlled variable Δ VI best internal capacity ratio.But, from the low-pressure LP of low-pressure lateral pressure sensor 40 and from the high pressure HP of high side pressure sensor 41 and from the speed Hz sequential storage of rotating speed carry-out part 37,52 in storage, and, low-pressure LP, high pressure HP and speed Hz when last time carrying out internal capacity than action low-pressure LP and high pressure HP and speed Hz relatively, variation according to them is passed, and also can obtain the controlled quentity controlled variable Δ VI to best internal capacity ratio.
Fig. 4 represents to be used to from the high pressure HP of above-mentioned high side pressure sensor 41 with from the relation of each operating frequency Hz (=30Hz, 60Hz, 90Hz) of the compression ratio of ratio (HP/LP) expression of the low-pressure LP of low-pressure lateral pressure sensor 40 and best internal capacity ratio.Straight line among Fig. 4 is to utilize VI=(HP/LP)
1/k(k: Biao Shi the theoretical value refrigeration agent ratio of specific heat).Obtain this compression ratio and the best internal capacity relation of operating frequency Hz when at every kind of refrigeration agent, above-mentioned relation is added in the operational formula when utilizing Fig. 2 and shown in Figure 3 best internal capacity specific output portion 38,53 to carry out calculation process.
Like this, by the calculation process of above-mentioned best internal capacity specific output portion 38,53, can accurately calculate under the current speed Hz controlled quentity controlled variable Δ VI to best internal capacity ratio.
As mentioned above, in the present embodiment, utilize the motor 11 of frequency variator 15 frequency conversion drive helical-lobe compressors.And, according to control signal, utilize fluid control device 28 control to advance to be discharged to working fluid in the working room in the cylinder 24 from press part controller 27, control the axial position of guiding valve 19 thus, the initial position of these guiding valve 19 regulation ejections.
And, utilize the rotating speed carry-out part 37,52 that constitutes control gear 36,51, the information of coolant water temperature Tw as load side, calculate the speed Hz that is used to obtain needed refrigerating capacity, utilize frequency variator 15,54 that the rotating speed of motor 11 is controlled to be this speed Hz, carry out the ability adjustment of relative load thus.Therefore, when ability is adjusted, do not need to carry out Unloading Control, can suppress the reduction of running efficiency.In addition, do not need to carry out the capacity control drive of volume controlled, simplify valve control device.
In addition, utilize the best internal capacity specific output portion 38,53 of above-mentioned control gear 36,51, according to the low-pressure LP of suction side and the high pressure HP and the speed Hz of ejection side, carry out calculation process, the best internal capacity of calculating current speed Hz is than (or Δ VI), utilize press part controller 27 and fluid control device 28 to set the axial position of guiding valve 19, the initial position of regulation ejection is realized above-mentioned variable inner volume ratio thus.Therefore, can set the internal capacity ratio, to reach the highest compressor efficiency corresponding with the speed Hz of motor 11.
Therefore, according to present embodiment, in order to carry out the ability adjustment of relative load, the reduction of the compressor efficiency in the time of can be the speed Hz of control helical-lobe compressor 31 is suppressed to inferior limit.
Fig. 5 represents the relation of refrigerating capacity and compressor efficiency.Transverse axis is represented refrigerating capacity Q, and the refrigerating capacity when utilizing the 60Hz of the variable inner volume ratio formula helical-lobe compressor of in the past variable inner volume ratio and Unloading Control and usefulness is made as 100% percentaeg and represents.On the other hand, the longitudinal axis is represented compressor efficiency.In addition, make above-mentioned compression ratio be changed to 2.1,3.9,5.5,7.9.
According to this figure, the variable inner volume ratio formula frequency conversion screw compressor of the variable inner volume ratio of present embodiment and VFC and usefulness, compare with the variable inner volume ratio formula helical-lobe compressor in the past of variable inner volume ratio and Unloading Control and usefulness, under the refrigerating capacity Q below 100%, no matter which kind of compression ratio can improve compressor efficiency.And refrigerating capacity is low more, can improve compressor efficiency greatly more, can obtain bigger effect.And this variable inner volume ratio formula frequency conversion screw compressor utilizes VFC to carry out the ability adjustment of relative load.Therefore, can carry out ability adjustment more than 100%.In addition, the helical-lobe compressor in the past that the ability of utilizing Unloading Control to carry out relative load is adjusted can not carry out the ability adjustment more than 100% certainly.
, though helical-lobe compressor under identical pressure condition therefore the living difference because speed is cut down output in making exist the value of the best internal capacity ratio of corresponding each frequency.The internal volume of (Fig. 6 B) and the relation of pressure when (Fig. 6 A) and frequency 90Hz when Fig. 6 represents frequency 30Hz.Dotted line is the curve of the relation of the expression internal volume during than the fixing internal volume ratio of the best internal capacity ratio that is fixed on frequency 60Hz and pressure internal capacity among the figure.The curve of the internal volume when in addition, the single-point line is the representation theory adiabatic compression and the relation of pressure.In said fixing internal capacity ratio, when the 30Hz frequency, produce insufficient compression in the moment (A), pressure sharply reduces.And, when the 90Hz frequency, produce excess compression in the moment (B), compare theoretical value pressure and increase greatly.Thus, can not merely be applicable to frequency variator the volume controlled of helical-lobe compressor.
, as present embodiment,, shown in solid line, can eliminate when the fixing internal volume ratio by forming the variable inner volume ratio, the insufficient compression that under 30Hz frequency situation, is produced, and reduce the amplitude of pressure oscillation; And, can eliminate when the fixing internal volume ratio, the excess compression that is produced under 90Hz frequency situation reduces the amplitude of pressure oscillation.
In addition, in the above-described embodiment,, still the invention is not restricted to this so that the ability internal capacity ratio control system of this variable inner volume ratio formula frequency conversion screw compressor is applicable to that refrigerating machine is that example is illustrated.In a word, in Fig. 2 and Fig. 3, input to control gear 36,51 rotating speed carry-out part 37,52 testing signal so long as the expression load condition signal get final product.
Claims (2)
1. variable inner volume ratio formula frequency conversion screw compressor is characterized in that having:
Variable inner volume ratio valve (19), can change the internal capacity ratio at the concluding time of compression step by change screw compression portion (39);
Rotation drives the motor (11) of above-mentioned screw compression portion (39);
Control the frequency variator (15) of the speed of above-mentioned motor (11) according to load.
2. variable inner volume ratio formula frequency conversion screw compressor according to claim 1, it is characterized in that, has control device (36,51,27,28), according to the suction side pressure and the speed that sprays side pressure and above-mentioned motor (11) of above-mentioned screw compression portion (39), control the aperture of above-mentioned variable inner volume ratio valve (19).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP301870/2002 | 2002-10-16 | ||
| JP2002301870A JP4147891B2 (en) | 2002-10-16 | 2002-10-16 | Variable VI inverter screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1705826A true CN1705826A (en) | 2005-12-07 |
| CN100406738C CN100406738C (en) | 2008-07-30 |
Family
ID=32105031
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200380101612XA Expired - Lifetime CN100406738C (en) | 2002-10-16 | 2003-10-14 | Variable inner volume ratio-type inverter screw compressor |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US20060039805A1 (en) |
| EP (1) | EP1553300B1 (en) |
| JP (1) | JP4147891B2 (en) |
| CN (1) | CN100406738C (en) |
| AU (1) | AU2003271184A1 (en) |
| ES (1) | ES2503716T3 (en) |
| TW (1) | TWI230761B (en) |
| WO (1) | WO2004036045A1 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
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- 2002-10-16 JP JP2002301870A patent/JP4147891B2/en not_active Expired - Fee Related
-
2003
- 2003-10-14 ES ES03751474.2T patent/ES2503716T3/en not_active Expired - Lifetime
- 2003-10-14 US US10/531,294 patent/US20060039805A1/en not_active Abandoned
- 2003-10-14 CN CNB200380101612XA patent/CN100406738C/en not_active Expired - Lifetime
- 2003-10-14 WO PCT/JP2003/013117 patent/WO2004036045A1/en active Application Filing
- 2003-10-14 EP EP03751474.2A patent/EP1553300B1/en not_active Expired - Lifetime
- 2003-10-14 AU AU2003271184A patent/AU2003271184A1/en not_active Abandoned
- 2003-10-16 TW TW092128699A patent/TWI230761B/en not_active IP Right Cessation
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101375062B (en) * | 2005-12-12 | 2010-12-08 | 江森控制丹麦有限公司 | Screw compressor |
| CN101726135B (en) * | 2009-11-15 | 2013-05-08 | 广东工业大学 | Air-conditioning system with two working modes and control method thereof |
| CN103097734B (en) * | 2010-09-14 | 2016-03-23 | 江森自控科技公司 | Compressor and the method for controlling the volume ratio of compressor |
| CN103097734A (en) * | 2010-09-14 | 2013-05-08 | 江森自控科技公司 | Volume ratio control system and method |
| CN102052316B (en) * | 2011-01-20 | 2013-01-02 | 上海康可尔压缩机有限公司 | Outer rotor vortex permanent magnet frequency conversion screw compressor system |
| CN102052316A (en) * | 2011-01-20 | 2011-05-11 | 上海康可尔压缩机有限公司 | Outer rotor vortex permanent magnet frequency conversion screw compressor system |
| CN104912805A (en) * | 2015-06-30 | 2015-09-16 | 特灵空调系统(中国)有限公司 | Controlling method of helical-lobe compressor |
| CN107269530A (en) * | 2017-06-08 | 2017-10-20 | 浙江德拉戈机械有限公司 | A kind of permanent-magnetic variable frequency screw two-stage compression air compressor machine |
| CN108332464A (en) * | 2018-02-09 | 2018-07-27 | 珠海格力电器股份有限公司 | Compressor control method, control device and air-conditioner set |
| CN110617639A (en) * | 2019-10-25 | 2019-12-27 | 浙江国祥股份有限公司 | Variable-frequency screw water chilling unit with variable internal volume ratio device and control method |
| CN112325502A (en) * | 2020-09-23 | 2021-02-05 | 浙江国祥股份有限公司 | Evaporative cold air source heat pump adopting variable-frequency variable-internal-volume-ratio compressor and control method |
| CN114109823A (en) * | 2021-09-28 | 2022-03-01 | 上海履正能源科技有限公司 | Control method for combining frequency conversion and capacity regulating slide valve of screw compressor |
| CN114109823B (en) * | 2021-09-28 | 2022-11-22 | 上海履正能源科技有限公司 | Control method for combining frequency conversion and capacity-regulation slide valve of screw compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| AU2003271184A1 (en) | 2004-05-04 |
| JP2004137934A (en) | 2004-05-13 |
| US20060039805A1 (en) | 2006-02-23 |
| TWI230761B (en) | 2005-04-11 |
| JP4147891B2 (en) | 2008-09-10 |
| EP1553300A1 (en) | 2005-07-13 |
| EP1553300A4 (en) | 2009-09-02 |
| TW200412397A (en) | 2004-07-16 |
| WO2004036045A1 (en) | 2004-04-29 |
| ES2503716T3 (en) | 2014-10-07 |
| CN100406738C (en) | 2008-07-30 |
| EP1553300B1 (en) | 2014-09-10 |
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