CN1807889A - Helical-lobe compressor for refrigerating plant - Google Patents
Helical-lobe compressor for refrigerating plant Download PDFInfo
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- CN1807889A CN1807889A CNA2005101185468A CN200510118546A CN1807889A CN 1807889 A CN1807889 A CN 1807889A CN A2005101185468 A CNA2005101185468 A CN A2005101185468A CN 200510118546 A CN200510118546 A CN 200510118546A CN 1807889 A CN1807889 A CN 1807889A
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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
- 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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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02H—EMERGENCY PROTECTIVE CIRCUIT ARRANGEMENTS
- H02H7/00—Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions
- H02H7/08—Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions for dynamo-electric motors
- H02H7/085—Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions for dynamo-electric motors against excessive load
- H02H7/0852—Emergency protective circuit arrangements specially adapted for specific types of electric machines or apparatus or for sectionalised protection of cable or line systems, and effecting automatic switching in the event of an undesired change from normal working conditions for dynamo-electric motors against excessive load directly responsive to abnormal temperature by using a temperature sensor
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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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
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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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Abstract
The screw compressor 1 for a refrigeration device is driven by a motor 21 whose revolution is controlled via an inverter 22 which receives the control signal from a controller 23, and is set in a circulation-flow path I together with a condenser 11, expansion valve 12 and evaporator 13. The revolution of the motor 21 is maintained, increased or reduced correspondingly to a cooling thermal load, and when the revolution becomes lower than the lowest one which is defined as the lower limit of revolution at which there is no further lowering of power consumption, the motor 21 is stopped.
Description
Technical field
The present invention relates to the helical-lobe compressor for refrigerating plant by motor driven, described motor is by convertor controls.
Background technique
Be that the helical-lobe compressor for refrigerating plant that the rotating speed of motor is implemented control is well-known with transducer to drive portion in the past.
For example, the spy of the open special permission communique of Japan opens in the 2002-81391 communique, discloses following helical-lobe compressor for refrigerating plant, and it is in the increase and decrease of the suction pressure in the man-to-man relation according to loading with the heat of cooling, the increase and decrease drive portion is the rotating speed of motor, to avoid its overload.This helical-lobe compressor for refrigerating plant has the durability that improves motor, the effect of reducing power consumption in the zone of heat of cooling load to the proportional relation of power consumption.
Spy at day disclosure special permission communique opens under the situation of the helical-lobe compressor for refrigerating plant of putting down in writing in the 2002-81391 communique, with respect to the heat of cooling load peaked ratio be heat of cooling duty ratio and with respect to the peaked ratio of power consumption be power consumption than between relation (transverse axis: heat of cooling duty ratio (%), the longitudinal axis: power consumption is than (%)) as shown in Figure 7.That is, along with heat of cooling duty ratio diminishes from maximum value, the rotating speed of motor descends, and power consumption is than also descending pro rata with heat of cooling duty ratio.Yet, when heat of cooling duty ratio excessive descent, drop to about about 20%, when the rotating speed of the screw rotor in the helical-lobe compressor that is driven by said motor descends gradually, the increase of air leakage causes the compression efficiency of coolant gas to descend between the screw rotor teeth groove, thereby power consumption descends with heat of cooling duty ratio pro rata than no longer, but increases.Promptly, have a following problems, when among Fig. 7 shown in the P point, when heat of cooling duty ratio for example dropped to 20% left and right sides, the decline of power consumption ratio shown in dotted line was significantly slack-off, even heat of cooling duty ratio further descends, power consumption is than also no longer how descending.
Summary of the invention
The present invention proposes in order to solve above-mentioned prior art problems, a kind of helical-lobe compressor for refrigerating plant is provided, it can be that the useless power consumption of motor is restricted to minimum degree with drive portion under the situation that particularly heat of cooling duty ratio is little, can improve cooling effectiveness.
In order to solve above-mentioned problem, a kind of helical-lobe compressor for refrigerating plant of the present invention is assembled in the circulation stream of circulate coolant of the above-mentioned refrigerating plant that has condenser, expansion valve and vaporizer, it is characterized in that, comprising: control device; Transducer receives the control signal from this control device; And motor, via the controlled rotating speed of this transducer; Wherein,
Above-mentioned control device, receive suction pressure and detected temperatures, generate and rotating speed that output makes said motor signal to be between predefined maximum speed and the minimum speed and to control with the difference of eliminating between above-mentioned detected temperatures and the control temperature, and when controlling rotating speed less than above-mentioned minimum speed, generate and control signal that output stops said motor, wherein, above-mentioned suction pressure is the pressure that the above-mentioned compressor of pressure transducer detection sucks, above-mentioned detected temperatures is the temperature that is arranged on above-mentioned vaporizer or near the detection of the temperature transducer it, and above-mentioned control temperature is the temperature based on predefined target temperature.
In addition, above-mentioned control device comprises: thermostat unit, more above-mentioned detected temperatures and above-mentioned target temperature and output bias signal; And controller, generate and the signal of the rotating speed of output control said motor.
In addition, above-mentioned minimum speed is that in the little zone of heat of cooling load, the slippage of the consumption electric power of said motor does not reach the rotating speed of set amount.
In addition, the above-mentioned control temperature based on predefined target temperature is identical with above-mentioned target temperature.
In addition, be in than the high upper limit target temperature of above-mentioned target temperature with than between the low lower limit target temperature of above-mentioned target temperature based on the above-mentioned control temperature of predefined target temperature,
Based on the temperature difference between above-mentioned detected temperatures and the above-mentioned upper limit target temperature, and above-mentioned detected temperatures and above-mentioned lower limit target temperature between temperature difference, generate above-mentioned control signal.
In addition, above-mentioned minimum speed can be in the heat of cooling be loaded little zone, determines as the lower limit of the significantly slack-off above-mentioned rotating speed of the decline of said motor power consumption.
In addition, above-mentioned temperature based on predefined target temperature can be identical with target temperature.
In addition, above-mentioned temperature based on predefined target temperature can comprise than big upper limit target temperature of target temperature and the lower limit target temperature littler than target temperature,
Based on the temperature difference between above-mentioned detected temperatures and the above-mentioned upper limit target temperature, and above-mentioned detected temperatures and above-mentioned lower limit target temperature between temperature difference, try to achieve above-mentioned control signal.
If constitute helical-lobe compressor for refrigerating plant of the present invention by said structure, then especially under the little situation of heat of cooling load, can be drive portion that the useless power consumption of motor is restricted to inferior limit, can play the effect of improving cooling effectiveness.
Description of drawings
Fig. 1 is that the figure that the integral body of the refrigerating plant of helical-lobe compressor of the present invention constitutes has been used in expression.
Fig. 2 is the figure of the relation between the control range of rotating speed of the suction pressure of helical-lobe compressor in the expression refrigerating plant shown in Figure 1 and its motor.
Fig. 3 is the flow chart of the control content in the expression refrigerating plant shown in Figure 1 helical-lobe compressor controlled.
Fig. 4 is the figure of the relation between heat of cooling duty ratio and the power consumption in the expression refrigerating plant shown in Figure 1.
Fig. 5 is the flow chart of other control content of in the expression refrigerating plant shown in Figure 1 helical-lobe compressor being controlled.
Fig. 6 is that the figure that the integral body of other refrigerating plants of helical-lobe compressor of the present invention constitutes has been used in expression.
Fig. 7 is the figure of the relation between heat of cooling duty ratio and the power consumption in the refrigerating plant of representing in the past.
Embodiment
With reference to the accompanying drawings an embodiment of the invention are described.
Fig. 1 has represented to use the refrigerating plant A of helical-lobe compressor for refrigerating plant 1 of the present invention.Refrigerating plant A has with helical-lobe compressor 1 and links to each other, and is equipped with the circulate coolant stream I of condenser 11, expansion valve 12 and vaporizer 13.
Helical-lobe compressor 1 has the motor 21 and the control device of a pair of screw rotor rotation of the intermeshing negative and positive that make its inside.This motor 21 carries out work by the electric power of supplying with via transducer 22.In addition, control device has as the attemperator 25 of thermostat unit and controller 23, and transducer 22 is connected on the controller 23, based on the control signal of coming self-controller 23, the rotating speed of motor 21 is controlled.
In addition, helical-lobe compressor 1 sucks the coolant gas of from evaporator drier 13, it is compressed, and pass out in the condenser 11.This coolant gas is condensed that device 11 seizes heat and condensation, arrives expansion valve 12 after becoming coolant fluid, by in the process of expansion valve 12, pressure and temperature decline becomes the gas-liquid mixed state because the throttling expansion effect makes.And then this freezing mixture flows to vaporizer 13, here evaporates from absorbing heat on every side and turns back to compressor 11 once more, then with said process circulation repeatedly in the same manner.
In vaporizer 13, be provided with the temperature transducer 24 that detects its inside temperature, expression by this sensor 24 detected detected temperatures t (℃) temperature signal be output in the attemperator 25.In this attemperator 25, to the target temperature T that is made as the temperature that should keep in advance in the inside of vaporizer 13 (℃) and detected temperatures t (℃) compare, as hereinafter described, will export controller 23 based on the deviation signal that this comparative result obtains.And in the circulate coolant stream I that is between vaporizer 13 and the helical-lobe compressor for refrigerating plant 1, being provided with and detecting coolant pressure is the pressure transducer 26 of the suction pressure of helical-lobe compressor 1, and expression is by the suction pressure P of its detection
s(ata) pressure signal is to controller 23 outputs, then based on from the deviation signal of attemperator 25 and from the pressure signal of pressure transducer 26, as hereinafter described, slave controller 23 is controlled the rotating speed of motor 21 to transducer 22 output control signals.In addition, in controller 23, expression is preestablished corresponding to the maximum speed of the motor 21 of suction pressure Ps and the data of minimum speed.This maximum speed is made as the function f (Ps) of suction pressure Ps, minimum speed is made as the function g (Ps) of suction pressure Ps, Fig. 2 (transverse axis: suction pressure, the longitudinal axis: motor rotary speed) represent an example of the relation between they and the suction pressure Ps.Hatched area among Fig. 2 is for carrying out the scope of rotating speed control according to 22 pairs of motors of transducer 21.In Fig. 2, (2) of longitudinal axis value is corresponding with the P point among above-mentioned Fig. 7, is about 20% of (1) value, and this P is corresponding to the point on the line of the minimum speed g (Ps) under each suction pressure Ps of expression.As described later, the P point is the remarkable slack-off starting point of decline of the power consumption ratio of motor 21 with respect to the decline of the heat of cooling duty ratio of vaporizer 13, promptly, the slippage of the consumption electric power of motor 21 do not reach the point of set amount.Thereby with respect to maximum speed f (Ps), minimum speed g (Ps) is its value of 20% in Fig. 2, but the present application not only is confined to this, for example also can be made as definite value to minimum speed g (Ps).Also have, the fall Δ r under the situation about descending for the rotating speed R of motor 21 also sets in controller 23 in advance.
Below, the controlling method that just is used for the helical-lobe compressor 1 of the refrigerating plant A that is made of said structure with reference to Fig. 3 describes.
Helical-lobe compressor 1 is started, after the control flow in the controller 23 shown in Figure 3 begins, at first in step 1 (S1), about detected temperatures t, whether judgement demonstrates Th 〉=t 〉=T1 from the deviation signal of attemperator 25, under the situation of YES, carries out the judgement of this step 1 repeatedly; Enter step 2 (S2) under the situation of NO.At this, Th and T1 are in order to make near upper limit target temperature, the lower limit target temperature that has the uniform temperature amplitude and set target temperature T, this be because, as detected temperatures t during near target temperature T, can be from duct thermostat 25 at short notice continually to the deviation signal of controller 23 outputs change rotation status of motor 21, this should be avoided from the viewpoint that prevents motor 21 scaling loss.This upper limit target temperature, lower limit target temperature and target temperature T have the relation of Th＞T＞T1.
In step 2, judge whether represent Th＜t from the deviation signal of attemperator 25, under the situation that enters step 3 (S3), NO under the situation of YES, enter step 4 (S4).
In step 3, the ability of vaporizer 13, i.e. the cooling capacity deficiency of refrigerating plant A is necessary to strengthen its ability, thus to transducer 22 outputs to be used to make the rotating speed R of motor 21 be the control signal of maximum speed f (Ps), return step 1 afterwards.
In step 4, need make the ability drop of vaporizer 13, so output is used to make the rotating speed R of motor 21 to reduce the control signal of fall Δ r to transducer 22, enter step 5 (S5) afterwards.
In step 5, about the rotating speed R of motor 21, judge whether it is R≤g (Ps), under the situation of YES, enter step 6 (S6), return step 1 under the situation of NO.
In step 6, even make rotating speed R continue to descend, power consumption also not too descends, and efficient reduces, thus the signal that 22 outputs stop motor 21 to transducer, and enter step 7.
In step 7, be Th＜t with the same judging whether in the step 2, enter step 8 (S8) under the situation of YES, return step 6 under the situation of NO, keep the outage state of motor 21.
In step 8, the scarce capacity of vaporizer 13 is necessary to make its to increase, thereby starter motor 21 once more, returns step 1.
After, this control flow is carried out repeatedly so that refrigerating plant A running.So, shown in Fig. 4 corresponding (transverse axis: heat of cooling duty ratio (%), the longitudinal axis: power consumption is than (%)) with above-mentioned Fig. 7, the rotating speed with motor 21 of having to be reduced to descend than the heat of cooling duty ratio in vaporizer 13 under the also low situation of the significantly slack-off starting point P point of the decline of power consumption ratio of motor 21, motor 21 is stopped, useless power consumption is limited in inferior limit, improved cooling effectiveness, can avoid the rotating speed of motor 21 to change continually at short notice again, can avoid its scaling loss.
Then, with reference to Fig. 5 other controlling methods that are applied to helical-lobe compressor 1 are described.
After helical-lobe compressor 1 is begun by the control flow in starting, the controller 23 shown in Figure 5, at first in step 1 (S1), about detected temperatures t, whether judgement represents target temperature T=t from the deviation signal of attemperator 25, under the situation of YES, carry out the judgement of this step 1 repeatedly, under the situation of NO, carry out step 2 (S2).
In step 2, judge whether represent T＜t from the deviation signal of attemperator 25, under the situation of YES, enter step 3 (S3), under the situation of NO, enter step 5 (S5).
In step 3, the ability of vaporizer 13 is the refrigerating capacity deficiency of refrigerating plant A, is necessary to make its to increase, so 22 outputs are used to make the rotating speed R of motor 21 to become the control signal of maximum speed f (Ps) to transducer, enters step 4 (S4) afterwards.
In step 4, utilize timer, treat that process is for fear of causing motor 21 scaling loss and after the predefined standby time, return step 1 owing to motor 21 rotating speeds frequently changing repeatedly.
In step 5, need to reduce the ability of vaporizer 13, be used to make the rotating speed R of motor 21 to reduce the control signal that reduces amplitude, ao r to transducer 22 outputs, enter step 6 (S6) afterwards.
In step 6, utilize timer, treat to enter step 7 (S7) through after the above-mentioned standby time.
In step 7, about the rotating speed R of motor 21, judge whether it is R≤g (Ps), under the situation of YES, enter step 8 (S8), under the situation of NO, return step 1.
In step 8, even rotating speed R is further reduced, power consumption also not too descends, and efficient is lower, so export the signal that motor 21 is stopped to transducer 22, enters step 9 (S9).In step 9, utilize timer, treat to enter step 10 (S10) through after the above-mentioned standby time.
In step 10, judge whether the same with step 2 is T＜t, under the situation of YES, enters step 11 (S11), under the situation of NO, returns step 8 (S8), keeps the outage state of motor 21.
In step 11, the scarce capacity of vaporizer 13 is necessary to make its increase, so starter motor 21 once more enters step 12 (S12).
In step 12, utilize timer, treat to return step 1 through after the above-mentioned standby time.
After, this control flow carries out repeatedly so that refrigerating plant A running.And, with identical under the situation of above-mentioned control flow, the rotating speed with motor 21 of having to be reduced to descend than the heat of cooling duty ratio in vaporizer 13 under the also low situation of the significantly slack-off starting point P point of the decline of power consumption ratio of motor 21, motor 21 is stopped, useless power consumption is limited in inferior limit, improved cooling effectiveness, and avoided motor 21 to carry out frequent driving repeatedly stopping.
Moreover, in control flow shown in Figure 5, be to turn back to step 1, but also can turn back to step 2 from step 12 as shown in phantom in Figure 5 from step 12.The rotating speed of motor 21 is not to maintain the statusquo as the situation of having passed through step 1 in this case, but constantly changes and maintain on the suitable value.
In addition, also can replace the step 4,6,9 and 12 of utilizing timer to keep standby, but shown in double dot dash line among Fig. 5, same step is located at before the step 1, and conduct is from step 1,3,7 and 12 steps of returning.Under this situation, because it is limited to change the necessity of above-mentioned rotating speed at short notice constantly, so in reality, do not have problem.
Further, also the judgement of the step 1 among this Fig. 5 can be made as and judge whether Th 〉=t 〉=T1, and the judgement in step 2 and the step 10 is made as judges whether Th＜t.
Above, for vaporizer 13, show the situation that is provided with the temperature transducer 24 that detects its inside temperature.At vaporizer 13 is to take in cooled object and it is cooled off under the situation of freezing form, and this state is suitable.But temperature transducer 24 is not limited to be arranged on the form of vaporizer 13 inside.
For example, Figure 6 shows that the refrigerating plant B that has used helical-lobe compressor for refrigerating plant 1 of the present invention.Refrigerating plant B and above-mentioned refrigerating plant A are general on the structure of majority.But, in refrigerating plant B, for make by vaporizer 13 inside freezing mixture and can carry out heat exchange as the fluid (water etc.) of cooled object, be provided with and be used to the stream 27 that is cooled that cooled object is flow through.And temperature transducer 24 is arranged near the outlet that starts from vaporizer 13 of the stream 27 that is cooled.That is, temperature transducer 24 is not arranged on vaporizer 13 inside, and is arranged near it.In addition, the detected temperatures t of temperature transducer 24 (℃) not the temperature of the atmosphere of vaporizer 13 inside, and roughly be exactly the temperature of cooled object itself.This scheme does not add the unnecessary component parts that hinders the heat exchange between freezing mixture and the cooled object in the inside of vaporizer 13, so help the efficient of heat exchange.Maintenance for temperature transducer 24 is also more favourable.Thereby, be under the situation of liquid especially at cooled object, this scheme is preferred.Certainly, if the heat exchange between freezing mixture and the cooled object is fully carried out, then also temperature transducer 24 can be arranged on the inside of vaporizer 13.
In addition, in the above-described embodiment, the detected temperatures of temperature transducer and the deviation signal between the target temperature are exported to controller, but also the detected temperatures of temperature transducer can be exported to controller, try to achieve deviation signal from target temperature in controller inside.
In addition, in the above-described embodiment, the detected temperatures of temperature transducer than the high situation of target temperature (perhaps upper limit target temperature) under, directly output makes the rotating speed of motor become the control signal of maximum speed, but motor rotary speed is increased to maximum speed cascade ground.
In addition, in the above-described embodiment, making the reduction amplitude, ao r under the situation that motor rotary speed reduces is fixed value, but Δ r also can be according to the value decision of this motor rotary speed R constantly.
Claims (5)
1. helical-lobe compressor for refrigerating plant,
Be assembled in the circulation stream of circulate coolant of the above-mentioned refrigerating plant that has condenser, expansion valve and vaporizer, it is characterized in that, comprising:
Control device;
Transducer receives the control signal from this control device; And
Motor is via the controlled rotating speed of this transducer; Wherein,
Above-mentioned control device, receive suction pressure and detected temperatures, generate and rotating speed that output makes said motor signal to be between predefined maximum speed and the minimum speed and to control with the difference of eliminating between above-mentioned detected temperatures and the control temperature, and when controlling rotating speed less than above-mentioned minimum speed, generate and control signal that output stops said motor, wherein
Above-mentioned suction pressure is the pressure that the above-mentioned compressor of pressure transducer detection sucks,
Above-mentioned detected temperatures is the temperature that is arranged on above-mentioned vaporizer or near the detection of the temperature transducer it,
Above-mentioned control temperature is the temperature based on predefined target temperature.
2. helical-lobe compressor for refrigerating plant as claimed in claim 1 is characterized in that, above-mentioned control device comprises:
Thermostat unit, more above-mentioned detected temperatures and above-mentioned target temperature and output bias signal; With
Controller generates and the signal of the rotating speed of output control said motor.
3. helical-lobe compressor for refrigerating plant as claimed in claim 1 is characterized in that,
Above-mentioned minimum speed is that in the little zone of heat of cooling load, the slippage of the consumption electric power of said motor does not reach the rotating speed of set amount.
4. helical-lobe compressor for refrigerating plant as claimed in claim 1 is characterized in that,
Above-mentioned control temperature based on predefined target temperature is identical with above-mentioned target temperature.
5. helical-lobe compressor for refrigerating plant as claimed in claim 1 is characterized in that,
Be in than the high upper limit target temperature of above-mentioned target temperature with than between the low lower limit target temperature of above-mentioned target temperature based on the above-mentioned control temperature of predefined target temperature,
Based on the temperature difference between above-mentioned detected temperatures and the above-mentioned upper limit target temperature, and above-mentioned detected temperatures and above-mentioned lower limit target temperature between temperature difference, generate above-mentioned control signal.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005014158A JP4559241B2 (en) | 2005-01-21 | 2005-01-21 | Refrigeration equipment |
| JP014158/05 | 2005-01-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1807889A true CN1807889A (en) | 2006-07-26 |
| CN100445561C CN100445561C (en) | 2008-12-24 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005101185468A Expired - Fee Related CN100445561C (en) | 2005-01-21 | 2005-10-31 | Helical-lobe compressor for refrigerating plant |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP4559241B2 (en) |
| KR (1) | KR100724654B1 (en) |
| CN (1) | CN100445561C (en) |
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| CN108351132A (en) * | 2015-11-06 | 2018-07-31 | Bsh家用电器有限公司 | Domestic refrigerator with refrigerant circuit and the method for running the Domestic refrigerator with refrigerant circuit |
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| JP4608537B2 (en) | 2007-12-05 | 2011-01-12 | 株式会社神戸製鋼所 | Refrigeration equipment |
| BRPI1100026A2 (en) * | 2011-01-26 | 2013-04-24 | Whirlpool Sa | reciprocal compressor system and control method |
| JP5772811B2 (en) * | 2012-12-28 | 2015-09-02 | ダイキン工業株式会社 | Refrigeration equipment |
| KR101983697B1 (en) * | 2013-09-23 | 2019-06-04 | 한온시스템 주식회사 | Method for controlling electric compressor of heat pump system for a automotive vehicle |
| KR102004354B1 (en) * | 2014-03-07 | 2019-07-29 | 한온시스템 주식회사 | Control method for driving electric compressor |
| CN108644116A (en) * | 2018-07-13 | 2018-10-12 | 麦克维尔空调制冷(苏州)有限公司 | Screw compressor system and heat-exchange system comprising the screw compressor system |
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| GB1564897A (en) * | 1975-09-29 | 1980-04-16 | Sevenska Rotor Maskiner Ab | Gas compression system and method with oil cooling |
| JPS5718484A (en) * | 1980-07-09 | 1982-01-30 | Mayekawa Mfg Co Ltd | Revolution speed control unit of screw type compressor |
| US4335582A (en) * | 1981-02-20 | 1982-06-22 | Dunham-Bush, Inc. | Unloading control system for helical screw compressor refrigeration system |
| JPS60204291A (en) * | 1984-03-28 | 1985-10-15 | Hokuetsu Kogyo Co Ltd | Control system for motor-driven compressor |
| JPH01130077A (en) * | 1987-11-13 | 1989-05-23 | Toshiba Corp | Capacity controller of compressor |
| JPH0610876A (en) * | 1992-06-23 | 1994-01-21 | Hitachi Ltd | Capacity control method for lubricating screw compressor |
| JP2001255032A (en) * | 2000-03-13 | 2001-09-21 | Mitsubishi Electric Corp | Screw type refrigerating machine |
| JP3950304B2 (en) * | 2000-06-23 | 2007-08-01 | 株式会社神戸製鋼所 | Screw compressor for refrigeration equipment |
| JP3916426B2 (en) * | 2001-08-02 | 2007-05-16 | 株式会社神戸製鋼所 | Screw refrigerator |
| JP2003278683A (en) * | 2002-03-22 | 2003-10-02 | Kobe Steel Ltd | Compressor and freezer |
| JP4330369B2 (en) * | 2002-09-17 | 2009-09-16 | 株式会社神戸製鋼所 | Screw refrigeration equipment |
| JP4313083B2 (en) * | 2003-05-13 | 2009-08-12 | 株式会社神戸製鋼所 | Screw refrigeration equipment |
-
2005
- 2005-01-21 JP JP2005014158A patent/JP4559241B2/en active Active
- 2005-10-06 KR KR1020050093652A patent/KR100724654B1/en not_active IP Right Cessation
- 2005-10-31 CN CNB2005101185468A patent/CN100445561C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108351132A (en) * | 2015-11-06 | 2018-07-31 | Bsh家用电器有限公司 | Domestic refrigerator with refrigerant circuit and the method for running the Domestic refrigerator with refrigerant circuit |
| CN108351132B (en) * | 2015-11-06 | 2020-06-12 | Bsh家用电器有限公司 | Domestic refrigeration device having a refrigerant circuit and method for operating a domestic refrigeration device having a refrigerant circuit |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2006200465A (en) | 2006-08-03 |
| CN100445561C (en) | 2008-12-24 |
| JP4559241B2 (en) | 2010-10-06 |
| KR100724654B1 (en) | 2007-06-04 |
| KR20060085162A (en) | 2006-07-26 |
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