CN100540904C - Be used to control the system and the controlling method thereof of the compressor of cooling system - Google Patents

Be used to control the system and the controlling method thereof of the compressor of cooling system Download PDF

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Publication number
CN100540904C
CN100540904C CNB2004800201791A CN200480020179A CN100540904C CN 100540904 C CN100540904 C CN 100540904C CN B2004800201791 A CNB2004800201791 A CN B2004800201791A CN 200480020179 A CN200480020179 A CN 200480020179A CN 100540904 C CN100540904 C CN 100540904C
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CN
China
Prior art keywords
compressor
suction inlet
cylinder
valve
motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CNB2004800201791A
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Chinese (zh)
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CN1823228A (en
Inventor
裵智荣
朴坰俊
张昌龙
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LG Electronics Inc
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LG Electronics Inc
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Filing date
Publication date
Priority to KR1020030030348 priority Critical
Priority to KR10-2003-0030348A priority patent/KR100525412B1/en
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Publication of CN1823228A publication Critical patent/CN1823228A/en
Application granted granted Critical
Publication of CN100540904C publication Critical patent/CN100540904C/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B49/00Arrangement or mounting of control or safety devices
    • F25B49/02Arrangement or mounting of control or safety devices for compression type machines, plant or systems
    • F25B49/025Motor control arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B49/00Arrangement or mounting of control or safety devices
    • F25B49/02Arrangement or mounting of control or safety devices for compression type machines, plant or systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06Control using electricity
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/04Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for reversible pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10Control 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
    • F04C28/14Control 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 rotating valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B1/00Compression machines, plant, or systems with non-reversible cycle
    • F25B1/04Compression machines, plant, or systems with non-reversible cycle with compressor of rotary type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00Control; Monitoring or safety arrangements
    • F04C2270/03Torque
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/02Compressor control
    • F25B2600/025Compressor control by controlling speed
    • F25B2600/0251Compressor control by controlling speed with on-off operation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/23Time delays
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21Temperatures
    • F25B2700/2104Temperatures of an indoor room or compartment
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2500/00Problems to be solved
    • F25D2500/04Calculation of parameters

Abstract

The invention discloses a kind of system that is used to control the compressor of cooling system.This control system comprises: compressor, and it has the live axle of can be clockwise and being rotated counterclockwise, and utilizes the power of exporting the motor of different torque characteristicses according to the sense of rotation of live axle to make this compressor operating; Selector, it is used to select the output torque characteristic of motor; Switch sections, it is used to connect or disconnect motor; And control unit, it is used to control selector, thereby with the torque characteristics Driven Compressor of the object that is fit to cool off.According to aspects of the present invention, provide a kind of method of operating that is used for controlling the cooling system compressor.The method comprising the steps of: (a) initial start step, start the compressor of having equipped motor with first torque characteristics, and motor is exported different torque characteristicses according to the sense of rotation of live axle; (b) determine the Operating torque characteristic of motor; (c) when determining that by execution in step (b) motor is worked with first torque characteristics, if during compressor operating, satisfy first condition then make compressor shutdown; (d) under the situation of compressor shutdown, determine whether to be fit to continue to make motor with the first torque characteristics work; if determine to be fit to then to keep the Operating torque characteristic of motor; if determine to be not suitable for then the Operating torque characteristic of motor be transformed to second torque characteristics from first torque characteristics, and if satisfy second condition then make compressor operating.

Description

Be used to control the system and the controlling method thereof of the compressor of cooling system
Technical field
The method that the present invention relates to a kind of cooling system and be used to control its compressor, the present invention relates more particularly to a kind of use, and wherein motor can be with the cooling system of forwards/reverse rotation compressor and the method that is used to control this compressor.
Background technique
Usually, compressor is power to be provided and the working fluid such as air or refrigerant is applied compression work by the power generator such as motor, turbine etc., with the machine of the pressure of rising working fluid.This compressor is widely used in the various application, from such as the household electric appliance of air conditioner, refrigerator etc. to industry equipment.
According to its compression method, compressor is divided into two types: positive displacement compressor and power compressor (turbocompressor).Positive displacement compressor is widely used in industrial field, and the configuration positive displacement compressor is to improve pressure by reducing its volume.Positive displacement compressor can further be divided into reciprocal compressor and rotary compressor.
The configuration reciprocal compressor is in order to the Piston Compression working fluid that is used in straight reciprocating motion in the cylinder.The configuration reciprocal compressor is in order to the Piston Compression working fluid that is used in straight reciprocating motion in the cylinder.The advantage of reciprocal compressor is that compression efficiency is high and simple in structure.The configuration rotary compressor is with the cylinder compression working fluid of utilization along the inner periphery eccentric rotary of cylinder, and its advantage is, compares with reciprocal compressor and can obtain high compression efficiency with low speed, therefore, has reduced noise and vibration.
Simultaneously, according to the difference of various environmental conditionss, reciprocal compressor that cooling system adopts or rotary compressor require different moments of torsion.
In other words, because the temperature of and the object that will cool off very high in the temperature of refrigerant is also very high (for example, buttery for refrigerator, perhaps for the interior space of air conditioner) the initial start operation time, the internal pressure of cooling tube is very high, so Driven Compressor needs high pulling torque.
In addition, after cooling system quit work for a long time, the temperature of the object that cool off raise, and when therefore making cooling system work again, the internal pressure height in the cooling tube, therefore, driving this cooling system needs high pulling torque.
Simultaneously,, near having absorbed, form frost on the surface of the heat exchanger of heat, cause and reduced heat exchange efficiency if cooling system works long hours.Therefore, should periodically carry out defrost operation.In this case, the temperature of heat exchanger and the temperature of refrigerant raise, and make Driven Compressor need high pulling torque.
The situation that needs little moment of torsion when on the contrary, also existing in Driven Compressor.In other words, if when Driven Compressor, the internal pressure of cooling tube is in low state, for example, if, then need little moment of torsion by making object remain on the temperature that low temperature keeps freezing mixture.In addition, when driving cooling system, with short period during discontinuous operation, need little moment of torsion at compressor.
As mentioned above, when Driven Compressor, according to different conditions, cooling system needs different driving torques.Yet although the moment of torsion different according to different condition needs, the moment of torsion of the compressor of cooling system is unalterable.Therefore, compressor must have the Maximum Torque that satisfies above-mentioned condition.In this case,, then produced the problem of unnecessary power consumpiton, and increased the size of compressor if use big capacity compressor.Simultaneously, the driving torque in order to obtain according to condition to require can use two or more a plurality of compressor.Yet in this case, the structure of cooling system is poor efficiency very, and has additionally increased installation cost.
Summary of the invention
Therefore, the present invention relates to a kind of system that has overcome the cooling system of one or more problem that produces because of the restriction of prior art and defective basically and be used to control compressor.
The purpose of this invention is to provide compressor of a kind of employing and produced the cooling system of two kinds of different moments of torsion and the system that is used to control this compressor with operating conditions according to cooling system.
Another object of the present invention provides a kind of method that can efficiently produce the compressor of two kinds of different moments of torsion according to the operating conditions of cooling system with suitable driving torque that is used to control.
Other advantage of the present invention, purpose and feature will partly be described in explanation subsequently, and through following check or study from the practice of the present invention, above-mentioned advantage, purpose and feature are conspicuous for the person of ordinary skill of the art.Objects and advantages of the present invention can realize and obtain as specifically noted in appended specification and claims and the accompanying drawing.
In order to realize these purposes and other advantages, and according to purposes of the present invention, as this institute concrete and broadly described, the system that is used to control the compressor of cooling system comprises: compressor, it has can be with clockwise and the live axle that is rotated counterclockwise, and make this compressor operating by the power of exporting the motor of different torque characteristicses according to the sense of rotation of live axle; Selector, it is used to select the output torque characteristic of motor; Switch sections, it is used to connect or disconnect motor; And control unit, thereby it is used to control the torque characteristics Driven Compressor of selector with the suitable object that will cool off.
In order to realize another purpose of the present invention's electricity, the method of operating that is used to control the cooling system compressor comprises step: (a) initial start step, start the compressor of having equipped motor with first torque characteristics, the sense of rotation of the live axle of motor basis is exported different torque characteristicses; (b) determine the Operating torque characteristic of motor; (c) by execution in step (b), when determining that motor is worked with first torque characteristics,, then make compressor shutdown if during compressor operating, satisfy first condition; (d) under the situation of compressor shutdown; determine whether to be fit to continue to make motor with the first torque characteristics work; be fit to if determine; the Operating torque characteristic that then keeps motor; if and determine to be not suitable for; then the Operating torque characteristic with motor is transformed to second torque characteristics from first torque characteristics, and if satisfy second condition, then make compressor operating.
Should be appreciated that aforementioned general description of the present invention and following specific descriptions all are exemplary and explanat, and be intended to provide the present invention's further explanation as claimed in claim.
Description of drawings
Accompanying drawing comprises in order further to understand the present invention, and be included into a part that constitutes this specification in this specification, these accompanying drawings show one or more embodiment of the present invention, and are used for this specification principle of the present invention being described.In the accompanying drawings:
Fig. 1 is the schematic representation that the structure of cooling system is shown;
Fig. 2 is the schematic representation that is used to control the system of compressor according to the embodiment of the invention;
Fig. 3 is the schematic representation that is used to control the system of compressor according to another embodiment of the present invention;
Fig. 4 is the schematic representation that Fig. 2 and compressor embodiment shown in Figure 3 are shown;
Fig. 5 is the perspective exploded view that the compression unit of compressor shown in Figure 4 is shown;
Fig. 6 A to 6C is the sectional view of the cylinder that the is illustrated in compressor shown in Figure 4 cylinder internal when rotating counterclockwise;
Fig. 7 A to 7B is the sectional view of the cylinder that is illustrated in compressor shown in Figure 4 cylinder internal when clockwise rotating;
Fig. 8 is the schematic representation that another embodiment of compressor shown in Fig. 2 and 3 is shown;
Fig. 9 is the perspective exploded view that the compression unit of compressor shown in Figure 8 is shown;
Figure 10 is the sectional view of compression unit shown in Figure 9;
Figure 11 is the sectional view that the inside of compressor shown in Figure 8 is shown;
Figure 12 A and 12B are the planimetric maps that the control gear embodiment of the valve assembly in the compression unit shown in Figure 9 is shown;
Figure 13 A to 13C is the sectional view of the cylinder that the is illustrated in compressor shown in Figure 8 cylinder internal when rotating counterclockwise;
Figure 14 A to 14C is the sectional view of the cylinder that the is illustrated in compressor shown in Figure 8 cylinder internal when clockwise rotating;
Figure 15 is the flow chart of method that is used to control the cooling system compressor that illustrates according to the embodiment of the invention; And
Figure 16 is the flow chart that the method that is used to control the cooling system compressor according to another embodiment of the present invention is shown.
Embodiment
Below will be in detail with reference to the preferred embodiments of the present invention, the example shown in the drawings.In any possible place, in whole accompanying drawing, use identical reference number to represent same or analogous part.
Fig. 1 is the schematic representation that illustrates according to the structure of cooling system of the present invention.With reference to figure 1, cooling system of the present invention comprises: compressor 510, first heat exchanger 520, second heat exchanger 530 and expansion cell 540.Certainly, also compressor 510 is provided with the compressor control unit (not shown).
Compressor 510 has can be in a clockwise direction and the counter clockwise direction drive shaft rotating.Compressor 510 is provided by the power that can produce according to the motor of the variable output torque characteristic of the sense of rotation of live axle, and this will be explained below.Compressor control unit comprises: selector, and it is used to select the output torque characteristic of motor; Switch element, it is used for the on/off motor; And microcomputer (micom), it is used to control selector, with the torque characteristics Driven Compressor according to the Obj State that is fit to cool off.The following describes compressor control unit with above-mentioned structure.
Compressor 510 then, is discharged it with the freezing mixture that high pressure compressed sucks.Therefore, freezing mixture is applied mobilization force, pass through each element with pipeline 550 by cooling system.The freezing mixture of compression is sent to first heat exchanger 520.First heat exchanger 520 is heat-shift between object that will cool off and adiabatic air, thereby makes the freezing mixture condensation of compression.At this moment, first fan 525 is blown into first heat exchanger 520 with outdoor air.Freezing mixture in 520 compressions of first heat exchanger moves to expansion cell 540 by pipeline 550.Expansion cell 540 expands the high pressure of cooling and cryogenic coolant, to produce low pressure and cryogenic coolant.The freezing mixture that expands enters second heat exchanger 530.By carrying out heat exchange with indoor heat converter, second heat exchanger 530 absorbs and evaporates the heat of object.At this moment, second fan 535 will be because of carrying out the object that the air directive of heat exchange cooling will cool off with second heat exchanger 530, so that cool off this object.Low temperature and low pressure gaseous coolant in 530 evaporations of second heat exchanger enter compressor 510.By repeating top process, this object is continued cooling.
Simultaneously, although not shown, cooling system according to the present invention may further include several bypasses, so that the object heating.Below it is done brief description.Although not shown, the freezing mixture that compressor 510 is discharged in bypass directly is directed to second heat exchanger 530.At this moment, by not being connected to the side of expansion cell 540, the freezing mixture of bypass guiding directly enters second heat exchanger 530.By carrying out heat exchange with the object that will cool off, the freezing mixture that is bypassed to second heat exchanger 530 is condensed.At this moment, the object radiations heat energy of high temperature and high pressure freezing mixture to cooling off then, becomes low temperature and low pressure coolant.This object of heat directive that sends by second fan, 535, the second heat exchangers 530, thus make this object heating.The refrigerant that has carried out heat exchange at second heat exchanger 530 enters expansion cell 540, and to change into low temperature and low-pressure refrigeration agent, then, they enter first heat exchanger 520.At first heat exchanger 520, the heat in the refrigerant absorption chamber outer air then, is vaporized.Then, refrigerant enters compressor 510.By repeating top process, cooling system of the present invention can make the object heating.
Cooling system of the present invention can be applied to be used to cool off or heat the interior space air-conditioning system, be used to cool off predetermined storeroom so that the refrigerator of food fresh keeping etc.Simultaneously, under various environmental conditionss, this cooling system requires different performance characteristic, more particularly, requires motor to have different torque characteristicses.For the various environmental conditionss that require different torque characteristicses, compressor of the present invention provides a kind of optimization torque characteristics.In addition, the invention provides a kind of system and method that is used to control this compressor.
To describe the system and method that is used to control this compressor in detail referring to accompanying drawing below.
Fig. 2 is the schematic representation of system that is used to control compressor according to the embodiment of the invention, and Fig. 3 is the schematic representation that is used to control the system of compressor in accordance with another embodiment of the present invention.Will be with reference to figure 2 and 3 explanations each embodiment of the present invention.
With reference to figure 2, the system that is used to control compressor according to the embodiment of the invention comprises: compressor, selector 620, switch element 650 and control unit 610.This compressor provides: power generator is used to produce power; And compression unit, be provided power to compress refrigerant and to discharge compressed refrigerant.Describe the structure of compression unit in detail below with reference to Fig. 4 to 14C, and motor is done brief description at this.
The motor that compressor of the present invention uses has live axle 13, and it can counterclockwise or turn clockwise, and according to the difference of the sense of rotation of live axle 13, it can export different torque characteristicses.In order to realize this torque characteristics, motor comprises: first winding 634, and it connects first end 632 and common port 631, and live axle 13 is rotated with first torque characteristics; And second winding 635, it connects second end 632 and common port 631, and live axle 13 is rotated with second torque characteristics.At this, problem is supposed first moment of torsion greater than second moment of torsion for convenience of explanation, and when obtaining first moment of torsion, that is, when the first winding side was applied power, live axle 13 was rotated counterclockwise.According to compressor of the present invention, in order to obtain high pulling torque when live axle 13 is rotated counterclockwise, first winding 634 should have the thick coil that its diameter is big and the number of turn is many.On the contrary, when live axle 13 turned clockwise, working efficiency should be high, but moment of torsion is little.Therefore, the diameter of second winding 635 should be less than the diameter of first winding 634, and the number of turn also should be lacked.By doing like this, in the initial start operation period that requires high pulling torque, perhaps when the pipeloop that makes refrigerant because object that will cool off or refrigerant are in high temperature was in high pressure conditions, first winding 634 was used to make live axle 13 to be rotated counterclockwise.When the less moment of torsion of needs, in other words, when making the refrigerant pipeloop be in low-pressure state because object that will cool off or refrigerant are in low temperature, second winding 635 is used to make live axle 13 to turn clockwise.With utilizing first winding 634 situation of live axle 13 rotations is compared, utilized second winding 635 to make the situation of live axle 13 rotations have little output torque, therefore, reduced power consumpiton, make this cooling system to work very economically.
Under the control of control unit 610, selector 620 is selected the output torque characteristic of motor.For this reason, selector comprises: first contact 623, and it links to each other with first end 633; Second contact 622, it links to each other with second end 632; And common 621, it links to each other with first contact 623 or second contact 622.If as above construct selector 620, then control unit 610 can be controlled selector 620, to export near the torque characteristics of the environment that is fit to motor.In other words, if near environmental requirement compressor output high pulling torque, then control unit 610 sends to selector 620 with control signal, thereby common 621 is linked to each other with second contact 622.
The motor of switch element 650 on/off compressors.In the system of the compressor that is used for controlling cooling system according to the present invention, control unit 610 control switch unit 650.In other words, according to external information, control unit 610 determines whether cooling system works.If control unit 610 trends towards making cooling system work, then control unit 610 sends to switch element 650 with control signal, thereby makes switch element 650 conductings.Then, the circuit that is used for power is delivered to motor is switched on, and therefore, power is supplied with motor by the winding side of selecting from selector 620.Therefore, with first moment of torsion or the second torque drive live axle 13.On the other hand, if control unit 620 trends towards making cooling system to shut down, then control unit 620 sends to switch element 650 with control signal, thus cut-off switch unit 650.Then, the circuit that is used for power is delivered to motor is disconnected, and then, power is offered motor.Therefore, motor quits work.
In the system that is used for controlling compressor according to the present invention, according to the information of the object that will cool off, control unit 610 control selector 620 and switch elements 650.At this, utilize detection device, for example, be used to measure the temperature transducer of the temperature of the object that will cool off, can obtain the information of the object that will cool off.In Fig. 2, temperature transducer detects the temperature of the buttery or the interior space, then, temperature information is sent to control unit 610.Then, according to detection device, for example, the temperature information that temperature transducer sends, control unit 610 control selector 620 and switch elements 650.
Simultaneously, overload protective device is connected in series between switch element 650 and the motor, is damaged because of the overload phenomenon to prevent motor.A plurality of capacitors 645 are connected in parallel between motor and the selector 620.The Ref. No. of Miao Shuing " 646 " is not positive temperature coefficient (P.T.C), and it is used for by the excess current of restriction starting stage effectively protective circuit, perhaps effectively supports starting compressor by improving the initial start moment of torsion when the circuit of starting compressor.
Below brief description is used to control the running of the system of compressor according to the present invention.
When control unit 610 was carried out the work of starting compressor according to the temperature of temperature transducer 60 measurements, control unit 610 sent to switch element 650 with control signal, thereby makes switch element 650 conductings.Then, the circuit that is used for power is delivered to motor is switched on, and therefore, power is sent to motor.Therefore, live axle 13 rotations are to drive cooling system.At this, before switch element 650 was switched on, the common 621 of selector 620 was connected to first contact 623 or second contact 622.For realizing this, control unit 610 can be controlled selector 620 before switch element 650 is switched on, and perhaps control unit 610 still keeps original state when cooling system is shut down.Simultaneously, be connected in common 621 under the state of first contact 623, if switch element 650 is switched on, then motor begins with the first moment of torsion work.Be connected in common 621 under the state of second contact 622, if switch element is switched on, then motor begins with the second moment of torsion work.
If drive motor, then cooling system is started working.If the cooling system work scheduled time, then the temperature in this room also changes.Temperature transducer 660 detects the temperature in this room, then, detection information is sent to control unit 610.Whether then, whether control unit 610 is determined the method for work of cooling system, that is, with current torque cooling system is worked on, cooling system is shut down, and perhaps whether makes cooling system work with the moment of torsion that changes.At this moment, if control unit 610 is determined the moment of torsion work of cooling system to change, then control unit 610 sends to switch element 650 with control signal, thus cut-off switch unit 650.Then, control unit 610 sends to selector 620 with control signal, thereby changes the coupled condition between common 621 and other contacts 622 and 623.After having changed coupled condition, switch element 650 conductings.Afterwards, compressor is according to the torque characteristics work that changes.Therefore, in an embodiment of the present invention, according to the state of the object that will cool off, cooling system can suitably be worked.The following describes the method that is used to control the compressor of cooling system according to the embodiment of the invention.
Simultaneously, with reference to figure 3, the system that is used to control compressor in accordance with another embodiment of the present invention comprises: control unit 610, selector 620, power generator 10 and switch element 670.At this because the structure of control unit 610, selector 620 and power generator 10 is with shown in Figure 2 identical, so detailed they.
In the system that is used for controlling compressor in accordance with another embodiment of the present invention, as shown in Figure 3, switch element 670 comprises thermostat, and the contact of this thermostat connects or disconnects according to the temperature of the object that will cool off.At this, this thermostat is provided with, for example, bimetallic strip.For example, deploy switch unit 670 is connected this contact, and disconnect this contact when this temperature is lower than predeterminated level when being higher than predeterminated level with the temperature at the interior space or buttery.Switch element 670 with above-mentioned structure is according to the condition drive motor in room or motor is shut down, and need not the control of control unit 610.In this case, by the check elapsed time, control unit 610 control selectors 620 are so that cooling system is effectively worked.
Simultaneously, the system that is used to control compressor in accordance with another embodiment of the present invention comprises the device that is used to determine whether to connect motor.At this, this determines that device is provided with current sensor 690, is used to detect the electric current by switch element 670.In this case, thus make switch element 670 conductings or when disconnecting, current sensor 690 detects motors and whether works, and corresponding information is sent to control unit 610 when raising in the temperature in this room or reducing.Utilize the job information of motor, control unit 610 check elapsed times are also controlled selector 620, therefore, and can more effective control cooling system.
Simultaneously, system further comprises second switch unit 680 in accordance with another embodiment of the present invention, and it is connected in series to switch element 670.Different with switch element 670, the control of the conducting of second switch unit 680 and the controlled unit 610 of disconnection.In this case, control unit 610 can be controlled selector 620 according to elapsed time, and can control second switch unit 680, so that force to make motor to be shut down.At this, during drive motor, by disconnecting the contact of second switch unit 680, control unit 610 can force to make motor to be shut down.Yet between the motor down period, control unit 610 can not be forced machine operation.At this, the situation of drive motor is not the situation that one of switch element 670 and second switch unit 680 are disconnected.If switch element 670 is disconnected, even then switch element 610 makes the make contact of second switch unit 680, also drive motor not.Therefore, in system in accordance with another embodiment of the present invention, control unit 610 check elapsed times, and during drive motor are according to the information control compressor of time of experience.
Below with the brief description work of system in accordance with another embodiment of the present invention.
For example, if the temperature in this room raises, then switch element 670 automatic conductings are with drive motor.Certainly, identical with the embodiment who describes with reference to figure 2, before motor was driven, common 621 was connected to any one of other contacts.If supposition common 621 is connected to first contact 623, in case then switch element 670 conductings just utilize the first torque drive motor.If drive motor, then current sensor 690 is driven notice control unit 610 with motor.When recognizing drive motor, the time of control unit 610 check experience.After at the fixed time control signal is sent to second switch unit 680, perhaps by after motor is shut down control signal being sent to selector 620, control unit 610 can change torque characteristics.After selector 620 had changed the torque characteristics of motor, control unit 610 can be controlled second switch unit 680, with drive motor again.Certainly, at the fixed time after because the operation of thermostat, the contact of switch element 670 may be by automatic disconnection, so motor is shut down.According to the present invention, because the cooling system temperature in this room that makes an immediate response, suitably work according to condition so be used to control the system of compressor.Certainly, being used to control the system of compressor in accordance with another embodiment of the present invention need be based on the complicated control algorithm of time of motor driving and experience.To be described in more detail the work of the system that is used to control compressor according to another embodiment of the present invention below.
To describe structure in detail referring to accompanying drawing below according to the compressor in the cooling system of the present invention.
Fig. 4 illustrates according to the Fig. 2 of the embodiment of the invention and the schematic representation of compressor shown in Figure 3.Fig. 5 is the perspective exploded view that the compression unit of compressor shown in Figure 4 is shown.
As shown in Figure 4, rotary compressor of the present invention comprises: shell 1; Be positioned at the power generator 10 of shell 1, that is, and motor; And compression unit 20.With reference to figure 4, power generator 10 is positioned at the top of compressor, and compression unit 202 is positioned at the bottom of compressor.Yet, if desired, can change their position.Upper cover plate 3 and lower cover plate 5 are mounted respectively in the upper and lower of shell 1, with the definition sealed inner.The suction pipe 7 that is used for the suction operation fluid is installed in the side of shell 1, and is connected to and is used for liquid-storage container 8 that oiling agent is separated with refrigerant.The discharge tube 9 that is used to discharge the fluid of compression is installed in the center of upper cover plate 3.On lower cover plate 5, inject the oiling agent " 0 " of predetermined quantity, with parts lubricated and that cooling is frictionally moved.At this, the end of live axle 13 is immersed in the oiling agent.
Power generator 10 comprises: stator 11, and it is fixed in the shell 1; Rotor 12, it rotatably is supported in the stator 11; And live axle 13, it forces to insert in the rotor 12.Rotor 12 is because electromagnetic force is rotated, and then, live axle 13 is delivered to compression unit 20 with the rotating force of rotor.For stator 20 is supplied with external power, mounting terminal 4 on upper cover plate 3.
Compression unit 20 comprises: cylinder 21, and it is fixed on the shell 1; Cylinder 22, it is positioned at cylinder 21; And upper bearing 24 and lower bearing 25, it is installed in the upper and lower of cylinder 21 respectively.To be described in more detail compression unit 20 with reference to figure 2,3 and 4.
Cylinder 21 has predetermined inner space, and its intensity is enough to bear the pressure of fluid.Cylinder 21 holds eccentric part 13a, and this eccentric part 13a is formed on the live axle 13 that is positioned at the inner space.Eccentric part 13a is a kind of eccentric cam, its rotating center intended distance of its misalignment.Cylinder 21 has the groove 21b that extends predetermined depth from its inner circumferential.The blade 23 that will describe below is installed in the groove 21b.The length of groove 21b is enough to hold fully blade 23.Shown in Figure 4 and 5, on cylinder 21, form the suction inlet 27 that is communicated with fluid chamber 29.Suction inlet 27 is directed to the fluid of compression in the fluid chamber 29.Suction inlet 27 is connected to suction pipe 7, and the fluid of compressor outside can incoming fluid chamber 29.More particularly, by connecting tube 7, suction pipe 7 is connected to suction inlet 27, therefore fluid before the compression can be delivered to fluid chamber 29.
Cylinder 22 is annular elements, and its external diameter is less than the internal diameter of cylinder 21.As shown in Figure 4, the inner circumferential of cylinder 22 contact cylinders 21, and be rotatably connected to eccentric part 13a.Therefore, cylinder 22 rolls on the inner circumferential of cylinder 21, and when live axle 13 rotations, spins on the exterior periphery of eccentric part 13a.Because eccentric part 13a rotates so cylinder 22 leaves rotating center " O " intended distance, carry out rolling motion simultaneously.Because because the exterior periphery of the cause cylinder 22 of eccentric part 13a contacts inner circumferential all the time, so the inner circumferential of the exterior periphery of cylinder 22 and cylinder forms independent fluid chamber 29 in the inner space.In rotary compressor, fluid chamber 29 is used for sucking and compressed fluid.
Blade 23 is installed in the groove 21b of cylinder 21, as mentioned above.Elastic member 23a is installed in the groove 21b, is used for flexibly support blade 23.Blade 23 continues contact cylinder 22.In other words, the end of elastic member 23a is fixed on the cylinder 21, and the other end links to each other with blade 23, then, pushes blade 23 to cylinder 22 sides.Therefore, blade 23 is divided into two separate space 29a and 29b with fluid chamber 29, as shown in Figure 4.When live axle 13 rotations, perhaps when cylinder 22 rotated, the volume of space 29a and 29b complementally changed.In other words, if cylinder 22 turns clockwise, then space 29a diminishes, and another space 29b becomes big.Yet the total volume of space 29a and 29b is fixed, and basic identical with the volume of predetermined fluid chamber 29.At live axle 13 during with a direction (clockwise or counterclockwise) rotation, one of space 29a and 29b be with the suction chamber that acts on the suction stream body, and another is with the pressing chamber that acts on relative compressed fluid.Therefore, as mentioned above, according to the rotation of cylinder 22, the pressing chamber of space 29a and 29b diminishes, and compressing the fluid of previous suction, and suction chamber enlarges, to suck new relatively fluid.If the sense of rotation of cylinder 22 is inverted, then the function of space 29a and 29b is also exchanged.In other words, if cylinder 22 rotates counterclockwise, then the rightward space 29b of cylinder 22 is pressing chambers, if but cylinder 22 clockwise rotates, and then the leftward space 29a of cylinder 22 is discharging units.
As shown in Figure 4, upper bearing 24 and lower bearing 25 are mounted respectively in the upper and lower of cylinder 21, and utilize the through hole 24b and the 25b of the inside formation of sleeve pipe and this sleeve pipe, and rotatably supporting driving shaft 12.More particularly, upper bearing 24, second bearing 25 and cylinder 21 comprise a plurality of attachment hole 24a, 25a and the 21a that forms in correspondence with each other respectively.The connected element of utilization such as screw bolt and nut is connected to each other cylinder 21, upper bearing 24 and lower bearing 25 together, and with sealing cylinder internal space, particularly fluid chamber 29.
On upper bearing 24, form exhaust port 26a and 26b.Exhaust port 26a and 26b are communicated with fluid chamber 29, make to discharge compressed fluid.Exhaust port 26a and 26b can directly be communicated with fluid chamber 29, also can be communicated with fluid chamber 29 by the predetermined fluid path 21d that is formed on cylinder 21 and the clutch shaft bearing 24.Expulsion valve 26c and 26d are installed on the upper bearing 24, to open and close exhaust port 26a and 26b.Only when the pressure of fluid chamber 29 was greater than or equal to predetermined pressure, expulsion valve 26c and 26d just optionally opened exhaust port 26a and 26b.For realizing this, wish that expulsion valve 26c and 26d are reeds, the one end be fixed on exhaust port 26a and 26b near, and its other end can free deformation.As shown in the figure, the retainer 26e of the distortion of limiting valve and the top that 26f is installed in expulsion valve 26c and 26d in order to make the valve stable operation.Retainer 26e and 26f are set, guaranteeing expulsion valve 26c and 26d stable operation, and its contact expulsion valve 26c and 26d are set, with the opening degree of control expulsion valve 26c and 26d.If do not have retainer 26e and 26f, then expulsion valve 26c and 26d may be out of shape because of high pressure, so the reliability of expulsion valve 26c and 26d worsens.
Baffler 140 is set on the upper bearing 24.Baffler 140 reduces the noise that produces when discharging compressed fluid.For this reason, comprise the upper space of exhaust port 26a and 26b in the baffler 140, and form additional exhaust port 141 in a side of baffler 140.
Simultaneously, in a preferred embodiment of the invention, the position of the sense of rotation of cylinder 22 and suction inlet 27 is the important factors that are used for determining compression volume.To be described in more detail their relation below.
Fig. 6 A is the sectional view of the cylinder that the is illustrated in compressor shown in Figure 4 cylinder internal when rotating counterclockwise.As shown in the figure, blade 23 and cylinder 22 are divided into two space 29a and 29b with fluid chamber 29.Exhaust port 26a and 26b lay respectively at the both sides of blade 23, continuing compressed fluid, and ignore the sense of rotation of cylinder 22.In other words, do not consider the sense of rotation of cylinder, between suction inlet 27 and blade 23, open exhaust port 26a and 26b at least one of them.At this moment, blade 23 is preferably identical with the distance between blade 23 and the exhaust port 27b with distance between the exhaust port 26a.
At this, pressing chamber 200 is divided into: pumping unit is used to utilize blade 23 and cylinder 22 to come to suck gas by suction inlet 27; And discharge section, be used for discharging fluid gas by one of exhaust port 26a and 26b.At this moment, according to the sense of rotation of cylinder 22, determine pumping unit and discharge section.In other words, when cylinder 22 rotates counterclockwise, become discharge section with respect to the rightward space 210 of cylinder 22, and when cylinder 22 clockwise rotated, leftward space 220 became discharge section.
Simultaneously, utilize the volume of discharge section 29a and 29b to determine the compression volume of compressor.From suction inlet 27 to blade 23, the volume of discharge section 29a and 29b is determined in the space that utilizes cylinder 50 and cylinder 22 to surround.Therefore, utilize the position of suction inlet 27 to determine compression volume.
For example, when suction inlet 27 was positioned at from the extended imaginary line of the transverse axis of blade 23, in other words, when the position of suction inlet 27 and blade 23 left about 180 ° of angular distances, the volume of exhaust port 29a was identical with the volume of exhaust port 29b.Therefore, this compressor can obtain same capacity, and irrelevant with the sense of rotation of cylinder 22.
Yet when suction inlet 27 was positioned on a side of the extended imaginary line of transverse axis of blade 23, the discharge section 29a of pressing chamber 29 was different with the volume of 29b.That is, shown in Fig. 6 a, pressing chamber 29 is split into leftward space 29a and rightward space 29b.Utilize the counterclockwise angular distance definition leftward space 29a between blade 23 and the suction inlet 26, and utilize the clockwise angular distance definition rightward space 29b between blade 23 and the suction inlet 26, this counterclockwise angular distance is less than this clockwise angular distance.At this moment, according to the sense of rotation of cylinder 22, space 29a and 29b are small capacity and big capacity discharge section 29b and 29a.This illustrates that rotary compressor of the present invention has the double volume amount.
Then, utilize the compression ratio of big capacity discharge section and small capacity discharge section 29b and 29a to determine the position of suction inlet 27.For example, the present invention supposes the clockwise angular distance that has about 180-300 ° between blade 23 and the suction inlet 27.When the clockwise angular distance between blade 23 and suction inlet 26 was 180 °, the compression ratio between space 29b and the 29a was 50: 50.When the clockwise angular distance between blade 23 and suction inlet 27 was 270 °, the compression ratio between space 29b and the 29a was 75: 25.
Illustrate in greater detail the running of rotary compressor of the present invention now.
The continuous operation step of rotary compressor when Fig. 6 A to 6C is illustrated in cylinder and rotates counterclockwise.Fig. 6 A illustrates initial fluid and sucks step, and Fig. 6 B illustrates fluid compression/discharge step, and Fig. 6 C illustrates the discharge completing steps.
When live axle 13 rotation, cylinder 22 rotations and rotate counterclockwise along the inner circumferential of cylinder 50.In this processing procedure, suction inlet 27 is opened, and therefore, by suction inlet 27, fluid is inhaled into fluid chamber.Then, cylinder 22 makes fluid enter big capacity discharge section 29b, as shown in Figure 6A.
When cylinder 22 further rotated, the volume of big capacity discharge section 29b reduced, to compress this fluid.In this processing procedure, when fluid was continued to deliver to big capacity discharge section 29b by suction inlet 27, blade 23 kept this big capacity discharge section 29b of sealing, utilized spring 23a and cylinder 22 to realize to-and-fro motion simultaneously.
After this, be elevated to when being higher than predeterminated level at the pressure of big capacity discharge section 29b, the expulsion valve 26d of big capacity discharge section 29b is opened.Therefore, the fluid in the big capacity discharge section 29b begins to be discharged to baffler by exhaust port 26b, shown in Fig. 6 B.
Then, when cylinder further rotated, the fluid in the big capacity discharge section 29b was discharged to baffler fully by exhaust port 26b, then, utilizes it from elastic force, and expulsion valve 26d closes exhaust port 26b, shown in Fig. 6 C.
When Fig. 7 A and 7B are illustrated in cylinder and clockwise rotate, the continuous running step of rotary compressor.Fig. 7 A illustrates initial fluid and sucks step, and Fig. 7 B illustrates fluid compression/discharge step.
When live axle 13 rotation, cylinder 22 rotations and clockwise rotate along the inner circumferential of cylinder 21.In this processing procedure, suction inlet 27 is opened, and makes fluid be sucked fluid chamber by suction inlet 27.At this moment, cylinder 22 makes fluid enter small capacity discharge section 29a.
When cylinder 22 further rotated, the volume of small capacity discharge section 29a reduced, to compress this fluid, meanwhile, by suction inlet 27 sustainable supply fluids.
After this, be elevated to when being higher than predeterminated level at the pressure of small capacity discharge section 29a, the expulsion valve 26c of small capacity discharge section 29a is opened.Therefore, the fluid in the small capacity discharge section 29a begins to be discharged to baffler by exhaust port 26a, shown in Fig. 7 B.
Then, when cylinder 22 further rotated, the fluid in the small capacity discharge section 29a was discharged to baffler fully by exhaust port 26a, after this, utilizes it from elastic force, and expulsion valve 26c closes exhaust port 26a.
After this, when cylinder 22 further rotated, by above-mentioned suction, compression and discharge step, fluid further was discharged to baffler.
As shown in Figure 4, the pressurized gass in the baffler 140 are entered shell 1 by exhaust port 141, then, by the space between rotor 12 and the stator 11, the perhaps space between stator 11 and the shell 1, the destination of its arrival requirement.
Simultaneously, in Fig. 8, the compressor of compressor control system in accordance with another embodiment of the present invention is shown.Describe compressor in accordance with another embodiment of the present invention below in detail.Fig. 8 is the transverse sectional view of compressor arrangement, and Fig. 9 is the perspective exploded view of the compression unit of compressor, and Figure 10 is the sectional view of compression unit.
With reference to figure 8, compressor comprises in accordance with another embodiment of the present invention: power generator 10 and compression unit 20, and compression unit 20 comprises: cylinder 21, upper bearing and lower bearing 24 and 25 and valve assembly 100.In this embodiment, omitted the structure identical with Fig. 4 to 7B illustrated embodiment.
Upper bearing 24 provides exhaust port 26a and the 26b that is communicated with fluid chamber 29, to discharge the fluid that flows out from fluid chamber 29.Exhaust port 26a and 26b can directly be communicated with fluid chamber 29, also can be communicated with fluid chamber 29 by the fluid passage 21d that is formed on cylinder 21 and the upper bearing 24.Utilization is installed in expulsion valve 26c and the 26d on the upper bearing 24, and the opening and closing operation of exhaust port 26a and 26b is controlled.Only when the pressure of fluid chamber 29 was elevated to greater than predeterminated level, expulsion valve 26c and 26d just optionally opened exhaust port 26a and 26b.For realizing this, needing expulsion valve 26c and 26d is reed, the one end be fixed on exhaust port 26a and 26b near, and its other end can free deformation.Although not shown, the retainer of the distortion of limiting valve is installed in the top of expulsion valve 26c and 26d in order to make the valve stable operation.In addition, the baffler (not shown) can be set on the top of upper bearing 24, the noise that produces when discharging compressed fluid to reduce.
On lower bearing 25, form suction inlet 27a, 27b and the 27c that is communicated with fluid chamber 29.Suction inlet 27a, 27b and 27c are directed to fluid chamber 29 with compressed fluid.Suction inlet 27a, 27b and 27c are connected to suction pipe 7, make that the fluid of compressor outside can incoming fluid chamber 29.More particularly, suction pipe 7 is branched to a plurality of auxiliary tube 7a, and they are connected respectively to suction inlet 27.If desired, exhaust port 26a and 26b can be formed on the lower bearing 25, and pumping unit 27a, 27b and 27c can be formed on the upper bearing 24.
Simultaneously, the pumping chamber 200 that is communicated with and has stored fluid in advance with suction inlet 27a, 27b and 27c is set preferably, therefore, fluid can be supplied with the fluid chamber 29 of cylinder 21.
Suction pumping chamber 200 directly is communicated with all suction inlet 27a, 27b and 27c, to supply with fluid.Therefore, near suction inlet 27a, 27b and 27c, suction pumping chamber 200 is installed in the bottom of lower bearing 25.Although the 27a of suction inlet shown in the figure, 27b and 27c are formed on the lower bearing 25, if desired, they can also be formed on the upper bearing 24.In this case, suction pumping chamber 200 is installed on the upper bearing 24.Suction pumping chamber 200 can directly be fixed on the lower bearing 25 by welding.In addition, can utilize connected element will aspirate pumping chamber 200 links together with cylinder 21, upper bearing 24 and lower bearing 25 and valve assembly 100.For lubricated live axle 13, the sleeve pipe 25d of lower bearing 25 should be immersed in the oiling agent that is contained in the shell 1.Therefore, suction pumping chamber 200 comprises the through hole 200a of sleeve pipe.The volume of suction pumping chamber 200 is 1 times to 4 times of volume of fluid chamber 29 preferably, with the stable supplying fluid.Suction pumping chamber 200 is also connected to suction pipe 7, with storing fluid.More particularly, suction pumping chamber 200 can be connected to suction pipe 7 by the predetermined fluid path.In this case, as shown in figure 10, fluid passage passes cylinder 21, valve assembly 100 and lower bearing 25.In other words, fluid passage comprises the suction hole 21c of cylinder 21, the suction hole 122 of second valve and the suction hole 25c of lower bearing 25.
This suction pumping chamber 200 forms the space of the fluid of storing predetermined amount all the time, therefore, has cushioned the variation in pressure of the fluid of suction, thereby to suction inlet 27a, 27b and 27c stable supplying fluid.In addition, suction pumping chamber 200 can hold the oil that extracts from the fluid of storage, therefore, can assist or replace liquid-storage container 8.
Suction inlet 26 and exhaust port 27 become the key factor of the compression volume of determining rotary compressor, will they be described with reference to Figure 11.In order to be clearly shown that suction inlet 27, Figure 11 illustrates the cylinder that does not have valve assembly 100 and link to each other with lower bearing 25.
At first, compressor of the present invention comprises two exhaust port 26a and 26b at least.As shown in the figure, even cylinder 22 rotates with any direction, should be between suction inlet on the rotation path and blade 23, there being an exhaust port, to discharge compressed fluid.Therefore, each sense of rotation needs an exhaust port.Can make compressor of the present invention discharge fluid like this, and irrelevant with the sense of rotation (that is the sense of rotation of live axle 13) of cylinder 22.Simultaneously, as mentioned above, during near blade 23, the pressing chamber of space 29a and 29b becomes littler, with compressed fluid at cylinder 22.Therefore, near blade 23, preferably form exhaust port 26a and 26b, to discharge maximum compressed fluids with facing one another.In other words, as shown in the figure, exhaust port 26a and 26b lay respectively at the both sides of blade 23.If possible, exhaust port 26a and 26b be preferably located in blade 23 near.
Correct location suction inlet 27, so as between exhaust port 26a and 26b and cylinder 22 compressed fluid.In fact, on the rotation path of cylinder 22, from suction inlet to the exhaust port compressed fluid.In other words, determine compression volume, therefore,, utilize different suction inlet 27, can obtain two compression volumes according to sense of rotation corresponding to the relative position of the suction inlet of exhaust port.Therefore, compressor of the present invention has first and second suction inlet 27a and the 27b that correspond respectively to two exhaust port 26a and 26b, and with respect to the center O of two different compression volumes, suction inlet predetermined angle separated from each other.
Preferably, the first suction inlet 27a be positioned at blade 23 near.Therefore, with the rotation of direction the time (being counterclockwise among the figure), 22 pairs on the cylinder fluid from the first suction inlet 27a that is positioned at blade 23 both sides to the second exhaust port 26b compresses.Because the cause of the first suction inlet 27a, so cylinder 22 utilizes whole fluid chamber 29 compressed fluids, therefore, this compressor has the maximum compression capacity in the counterclockwise direction.In other words, can the as many fluid of compressed fluid chamber 29 volumes.In fact the first suction inlet 27a separates 10 ° angle in clockwise or counter clockwise direction with blade 23.Accompanying drawing of the present invention is illustrated in counterclockwise the separately first suction inlet 27a of angle theta 1.At this angle of departure θ 1, can utilize whole fluid chamber 29 compressed fluids, and need not the participation of blade 23.
With respect to the center, the second suction inlet 27b and the first suction inlet 27a separate predetermined angle.When rotating in a counter-clockwise direction, the fluid of cylinder 20 compressions from the second suction inlet 27b to the first exhaust port 26a.Because the second suction inlet 27b and blade 23 are separated sizable angle in the clockwise direction, so cylinder 22 utilizes segment fluid flow chamber 29 compressed fluids, therefore, the compression volume that this compressor has is littler than the compression volume that is rotated counterclockwise when moving.In other words, fluid that can compressed fluid chamber 29 partial volume amounts.The second suction inlet 27b separates the 90-180 ° of angle theta 2 in the scope at clockwise or counterclockwise preferred and blade 23.The second suction inlet 27b is preferably placed at the opposite of the first suction inlet 27a, therefore, the difference between the compression volume can be set correctly, and can avoid being subjected to the influence of each sense of rotation.
As shown in figure 11, suction inlet 27a and 27b are normally circular.In order to improve the aspiration of fluid, the suction inlet 27a and the 27b of several shapes that comprise rectangle can also be set.In addition, shown in Figure 12 A and 12B, suction inlet 27a and 27b can be the rectangles with predetermined curvature.In this case, in operating process, can be with adjacent miscellaneous part, particularly the influence of cylinder 22 is reduced to minimum.
Simultaneously, in order to obtain the compression volume that requires in each direction respectively, should be single at any one available suction inlet of sense of rotation.If on the rotate path of cylinder 22, have two suction inlets, then between suction inlet, can not compress.In other words, if the first suction inlet 27a opens, then the second suction inlet 27b should be closed, and vice versa.Therefore, for the sense of rotation according to cylinder 22 is only optionally opened one of suction inlet 27a and 27b, valve assembly 100 is installed on compressor of the present invention.
Valve assembly 100 comprises first and second valves 110 and 120, and they are installed between cylinder 21 and the lower bearing 25, so that it is facing to suction inlet.If form suction inlet 27a, 27b and 27c on upper bearing 24, then first valve and second valve 110 and 120 are installed between cylinder 21 and the upper bearing 24.
First valve 110 is disk components, and it is installed, to compare the more accurate eccentric part 13a that contacts with live axle 13.Therefore, if live axle 13 rotations (that is, cylinder 22 rotates), then first valve 110 is with same direction rotation.The diameter of first valve 110 is preferably more than the internal diameter of cylinder 21.Cylinder 21 is supported part first valve 110, and therefore, first valve 110 can be stablized rotation.
First valve 110 comprises: first opening 111 and second opening 112 are communicated with the first suction inlet 27a and 27b respectively in specific sense of rotation; And through hole 110a, live axle 13 inserts in it.More particularly,, be communicated with the first suction inlet 27a by rotating first valve, 110, the first openings 111, and the main body of first valve 110 makes the second suction inlet 27b closure during at cylinder 22 in a clockwise direction with arbitrary rotation of counter clockwise direction.Cylinder 22 in a clockwise direction with another when rotation of counter clockwise direction, second opening 112 is communicated with the second suction inlet 27b.At this moment, the main body of first valve 110 makes the first suction inlet 27a closure.First opening 111 and 112 can be circular or polygonal shape.In addition, shown in Figure 12 A and 12B, opening 111 and 112 can be the rectangle with predetermined curvature.Therefore, opening is exaggerated, so that sucks fluid glibly.If near the center of first valve 110, form this opening 111 and 112, then may increase the influence between cylinder 22 and the eccentric part 13a.In addition, may be along live axle 13 leak fluid, this be because opening 111 and 112 and cylinder 22 and eccentric part 13a between spatial communication.Because these reasons, opening 111 and 112 be preferably located in first valve exterior periphery near.Simultaneously, by regulating the corner of first valve 110, in each sense of rotation, first opening 111 all can be opened first and second suction inlet 27a and the 27b respectively.In other words, during in a clockwise direction with arbitrary rotation of counter clockwise direction, first opening 111 is communicated with the first suction inlet 27a, makes the second suction inlet 27b closure simultaneously at live axle 13.Live axle 13 in a clockwise direction with another when rotation of counter clockwise direction, first opening 111 is communicated with the second suction inlet 27b, makes the first suction inlet 27a closure simultaneously.Because the structure of first valve 110 is simpler, need utilize so single opening 111 each suction inlet of control.
Second valve 120 is fixed between cylinder 21 and the lower bearing 25, to transmit rotatablely moving of first valve 110.Second valve 120 is to have scene (site) part 121 annular element of (it rotatably holds first valve 110).Second valve 120 further comprises: attachment hole 120a, it utilizes connected element by this attachment hole 120a second valve 120 and cylinder 21 and clutch shaft bearing 24 and second bearing 25 to be linked together.Second valve 120 preferably has same thickness with first valve 110, realizes stable support in case the fluid stopping body leaks.In addition, because first valve 110 is supported by cylinder 21 parts,, make the gap of second valve, 120 smooth rotations with formation so the thickness of first valve 110 is slightly less than the thickness of second valve 120.
Simultaneously, with reference to Figure 11, for turning clockwise, when cylinder 22 rotates from blade 23 to second suction inlet 27b, fluid does not take place between blade 23 and cylinder 22 suck or discharge.Therefore, regional V becomes vacuum state.Vacuum area V causes the power loss of live axle 13, and produces big noise.Therefore, in order to overcome the problem of vacuum area V, the 3rd suction inlet 27c is set on lower bearing 25.The 3rd suction inlet 27c is formed between the second suction inlet 27b and the blade 23, be used for fluid is delivered in the space between cylinder 22 and the blade 23, with at cylinder 22 by before the second suction inlet 27b, do not form vacuum state.The 3rd suction inlet 27c preferably be formed on blade 23 near so that eliminate vacuum state rapidly.Yet, because the 3rd suction inlet 27c with the sense of rotation work different with the first suction inlet 27a, locatees the 3rd suction inlet 27c facing to the first suction inlet 27a.In fact, in the clockwise direction or counterclockwise, separate about 10 ° angle (θ) location the 3rd suction inlet 27c with blade 23.In addition, shown in Fig. 5 A and 5B, the 3rd suction inlet 27c can be circular or crooked rectangle.
Because the 3rd suction inlet 27c works with the second suction inlet 27B, so at cylinder 22 during in a clockwise direction with arbitrary rotation of counter clockwise direction, suction inlet 27b and 27c should open simultaneously.Therefore, first valve 110 further comprises the 3rd opening, disposes the 3rd opening, so that when the second suction inlet 27b is opened, is communicated with the 3rd suction inlet 27c simultaneously.According to the present invention, can form the 3rd opening 113 separately.Yet, because the first suction inlet 27a and the 3rd suction inlet 27c are adjacent each other, thus wish corner by increase first valve 110, and open the first and the 3rd suction inlet 27a and 27c simultaneously according to the sense of rotation of first opening 111.
According to the sense of rotation of cylinder 22, first valve 110 can be opened suction inlet 27a, 27b and 27c, but the compression volume in order to obtain to require should accurately be opened corresponding suction inlet.By controlling the corner of first valve, can control the accurately degree of opening of suction inlet.Therefore, valve assembly 100 preferably further comprises the device of the corner that is used to control first valve 110, below with reference to Figure 12 A and 12B it is elaborated.For this control gear clearly is described, Figure 12 A illustrates the valve assembly that links to each other with second bearing 25 with 12B.
Can be provided with this control gear: projection 115, it is formed on first valve 110, and at the radial protrusion of first valve; And groove 123, it is formed on second valve 220, is used for holding movably this projection.At this, groove 123 is formed on second valve 220, so that be exposed in the inner space of cylinder 21.Therefore, in cylinder, do not form void volume (deadvolume).In addition,, can be provided with this control gear although not shown: projection, it is formed on second valve 120, and at the radial protrusion of second valve 120; And groove, it is formed on first valve 110, and holds projection 124 movably.
If use this control gear, shown in Figure 12 A, if then live axle 13 rotation counterclockwise, projection 115 and 124 is latchable to an end of groove 123 and 116 respectively.Therefore, first opening 111 is communicated with the first suction inlet 27a, with the suction fluid, and the second and the 3rd suction inlet 27b and 27c is closed.On the contrary, as shown in figure 12, if live axle 13 rotates in a clockwise direction, then projection 115 and 124 is latchable to the other end of groove 123 and 116 respectively, and first opening 111 and second opening 112 are opened the 3rd and second suction inlet 27c and 27b simultaneously, to allow to suck fluid.First valve 110 cuts out the first suction inlet 27a.
To describe work below in detail according to rotary compressor of the present invention.
Figure 13 A to 13C is the sectional view that is illustrated in cylinder work of rotary compressor when counterclockwise rotating.
At first, in Figure 13 A, the state of each element of cylinder internal when showing live axle 13 and rotating in a counter-clockwise direction.At first, the first suction inlet 27a is communicated with first opening 111, and remaining second suction inlet 27b and the 3rd suction inlet 27c close.Because they are illustrated above, the state of each suction inlet elaborated when omission was rotated counter clockwise direction.
Under the state that the first suction inlet 27a opens, because the rotation of live axle 13, cylinder 22 rotates counterclockwise, and rotates along the inner circumferential of cylinder simultaneously.When cylinder 22 was rotated further, the size of space 29b reduced, and therefore, the fluid that has sucked is compressed.In this stroke, elastic member 23a moves blade 23 elasticity up and down, thereby fluid chamber 29 is divided into two seal space 29a and 29b.Meanwhile, by first suction inlet 27, new fluid is continued to suck space 29a, so that be compressed in next one circulation.
When the hydrodynamic pressure in the 29b of space was higher than predetermined value, the second expulsion valve 26d opened.Therefore, the fluid in the 29b of space is discharged by the second exhaust port 26b.When cylinder 22 was rotated further, all fluids in the 29b of space were discharged by the second exhaust port 26b.After fluid is discharged fully, utilize its own elasticity, the second expulsion valve 26d closes the second exhaust port 26c.
Therefore, after a loop ends, cylinder 22 continues to rotate counterclockwise, and then, discharges fluid by repeating same circulation.In circulating counterclockwise, cylinder 22 compressed fluids turn to the second exhaust port 26b from the first suction inlet 27a simultaneously.As mentioned above, because the first suction inlet 27a and the second exhaust port 27b are positioned near the to face with each other of blade 23,, therefore obtained the maximum compression capacity so in circulating counterclockwise, utilize this fluid of space compression of whole fluid chamber 29.
Figure 14 A to 14C is according to the sectional view of the sequence of operation of rotary compressor of the present invention when being illustrated in cylinder and clockwise rotating.
At first, in Figure 14 A, the state of each element of cylinder internal when showing live axle 13 and rotating in a clockwise direction.The first suction inlet 27a closes, and the second suction inlet 27b and the 3rd suction inlet 27c are communicated with second opening 112 and first opening 111 respectively.If first valve 110 also has the 3rd opening 113 in addition, then the 3rd suction inlet 27c is communicated with the 3rd opening 113.Because they are illustrated above, the state of each suction inlet elaborated when omission was rotated clockwise direction.
Under the state that the second suction inlet 27b and the 3rd suction inlet 27c open, because the turning clockwise of live axle 13, cylinder 22 begins to clockwise rotate, and the inner circumferential along cylinder rotatablely moves simultaneously.In this initial rotation stage, cylinder 22 arrives the fluid that sucks before the second suction inlet 27b and is not compressed, and utilizes cylinder 22, and the outside of this fluid being forced to be discharged to cylinder 21 by the second suction inlet 27b is shown in Figure 14 A.Therefore, by behind the second suction inlet 27b, this fluid begins to be compressed, as shown in Figure 14B at cylinder 22.Meanwhile, make the space between the second suction inlet 27b and the blade 23, that is, space 29b is in vacuum state.Yet as mentioned above, when cylinder 22 began to rotate, the 3rd suction inlet 27c was communicated with first opening 111, and therefore, it is opened to suck fluid.Therefore, the fluid of suction has been removed the vacuum state of space 29b, has restricted generation noise and power loss.
When cylinder 22 was rotated further, the size of space 29a reduced, and therefore, the fluid that has sucked is compressed.In this compression stroke, elastic member 23a moves blade 23 elasticity up and down, thereby fluid chamber 29 is divided into two seal space 29a and 29b.In addition, by the second suction inlet 27b and the 3rd suction inlet 27c, new fluid is continued to suck space 29b, so that be compressed at next stroke.
When the hydrodynamic pressure in the 29b of space was higher than predetermined value, the first expulsion valve 26c shown in Figure 5 opened.Therefore, the fluid in the 29b of space is discharged by the first exhaust port 26a.After finishing this fluid of discharge, utilize its own elasticity, the first expulsion valve 26c closes the first exhaust port 26a.
Therefore, after a stroke finished, cylinder 22 continued to clockwise rotate, and then, discharged fluid by repeating same stroke.In circulating counterclockwise, cylinder 22 compressed fluids turn to the first exhaust port 26a from the second suction inlet 27b simultaneously.Therefore, in counterclockwise stroke, utilize the part of whole fluid chamber 29 to compress this fluid, therefore, compression volume is less than clockwise compression volume.
In above-mentioned stroke (that is, stroke and stroke clockwise counterclockwise), the compressed fluid of discharge upwards flows by rotor 12 in the shell 1 and the space between the space between the stator 11 and stator 1 and the shell 1.Therefore, compressed fluid is discharged compressor by discharge tube 9.
To describe the controlling method of the compressor of cooling system referring to accompanying drawing in detail below with above-mentioned structure.Figure 15 illustrates the flow chart that is used to control the method for cooling system compressor according to the embodiment of the invention.In this embodiment, control unit receives information about the temperature variation in room from being installed in temperature transducer in the room, then, and the control compressor.Certainly, according to the sense of rotation of live axle, the motor that is installed in the compressor has different torque characteristicses.In the following description, phrase " utilizes the first moment of torsion work " and means and utilizes the high pulling torque Driven Compressor, but also produce big output (perhaps big cooling Power), phrase " utilizes the second moment of torsion work " and means and utilizes little torque drive compressor, and produce little output (perhaps, little cooling Power).
With reference to Figure 15, in the initial start step, compressor starts is with the first torque characteristics work, in the embodiment shown in Figure 2, in the initial start stage, if the information that control unit 610 receives about room temperature from the temperature transducer 660 that is installed in the room, and would determine to make cooling system work, then control unit 610 sends to switch sections 650 with control signal, thereby makes the make contact of switch sections 650.Power is sent to motor, and live axle 13 is with the first moment of torsion work.Certainly, the common at selector 620 is connected under the state of first contact 623 switch sections 650 closures.As mentioned above, the method that the common 621 of selector 620 is connected to first contact 623 before drive motor has two kinds.A kind of method is before the make contact that makes switch sections 650, to receive the control unit 610 control selectors 620 of information from temperature transducer 660.Another kind method is that in the initial start stage, design makes the common 621 of selector 620 keep coupled condition with first contact 623 all the time.Certainly, under latter instance,, then can dispose it, so that its former state keeps coupled condition if motor is opened under the reformed situation of coupled condition of the contact of selector 620.Compressor utilizes the reason of the first driving torque work to be in the initial start stage, because the object that will cool off, promptly, the temperature height of the buttery of refrigerator or the interior space, and in the initial start stage, the temperature height of the refrigerant of cooling system, the compressor of refrigerant pipeline is in high temperature, so the load of compressor is bigger.Under compressor is in high load condition, in the initial start stage, need be with very high torque characteristics, that is, and the first torque drive compressor.At this moment, if utilize the second torque drive compressor littler than first moment of torsion, then start-up function failure, even perhaps it has been worked for a long time, but the cooling Power of refrigerant is still not enough, therefore can not cool off this object well.
After utilizing the first moment of torsion initial start, as shown in figure 15, check the drive pattern of this motor.Certainly, check at initial start stage compression machine with the first torque mode work.The following describes the drive pattern determining step; carry out the drive pattern determining step; with state according to the room; determine whether to have changed in the work drive pattern of compressor; after it is shut down; when compressor starts was worked, which kind of method of work work compressor utilized with which kind of pattern work and compressor.
As definite result of drive pattern,, then check when compressor operating, whether to satisfy first condition if with the first torque characteristics Driven Compressor.If satisfy first condition, compressor shutdown then.At this, as shown in figure 15, when whether check satisfies first condition, wish the absolute value (P) of the mean temperature variance ratio of calculating scheduled time inside room.Reason is the basis whether absolute value (P) changes as the drive pattern of determining compressor.Certainly, if use other factors, for example, the time of experience, determine the drive pattern of compressor then to need not to calculate absolute value (P).Simultaneously, in this embodiment, first condition is the temperature of object, that is, whether the temperature in room (t) is lower than the lower limit (t-) of setting temperature.At this,, as shown in figure 15, then continue to calculate absolute value (P) if temperature (t) is higher than the lower limit (t-) of setting temperature.If temperature (t) is lower than the lower limit (t-) of setting temperature, then compressor shutdown.In the embodiment shown in Figure 2; if the temperature in the room that temperature transducer 660 provides is lower than the lower limit (t-) of setting temperature; and control unit 610 continuation calculating absolute values (P), then control unit 610 sends to switch sections 650 with control signal, so that motor is shut down.
Under the situation of compressor shutdown, determine whether to be suitable for continuing to utilize first torque characteristics to make compressor operating.As definite result, if be fit to, then keep the driving torque characteristic of motor, if be not suitable for, be second torque characteristics then with this driving torque feature change.If satisfy second condition, then compressor is driven again.To elaborate to this with reference to figure 2.
At first, under the situation of compressor shutdown, control unit 610 is determined the torque characteristics change condition of motor.In this embodiment, as shown in figure 15, the torque characteristics change condition of motor is whether absolute value (P) is greater than the critical value (P+) of the rate of temperature change absolute value of torque characteristics change.In other words, if the absolute value (P) that calculates is greater than critical value (P+), then control unit 610 sends to selector 620 with control signal, so that common 621 links to each other with second contact 623, therefore, the driving torque characteristic of motor changes to second torque characteristics from first torque characteristics.At this, absolute value (P) means greater than critical value (P+), because the rate of temperature change height in room, that is, when compressor operating, it is very many that temperature descends, and need be with strong cooling Power drive motor.Therefore, in this case, need stop the work under the first very high driving torque pattern of energy consumption, and make compressor with the second driving torque pattern work.Because this reason, control unit 610 control selectors 620 are to change the driving torque characteristic.Simultaneously, if do not satisfy torque characteristics change condition, then the rate of temperature change in room is low.In other words, this means that the reduction of room temperature is little.Therefore, in this case, should utilize strong cooling Power to continue this room of cooling.Therefore, former state keeps first torque characteristics, and does not change the driving torque characteristic.
After having determined driving torque change characteristic, change drive pattern, then, determine whether to satisfy second condition.At this, second condition is the temperature of the object that will cool off, that is, whether the temperature in this room is higher than the upper limit (t+) of the setting temperature in this room.In other words, because compressor is in outage state, cooling system is not worked in the given time.Therefore, as time goes by, the temperature in this room raises gradually.If the temperature in this room (t) surpasses the upper limit (t+) of setting temperature, then control unit 610 sends to switch sections 650 with control signal, so that this make contact, thereby drive motor.In this case, although moment of torsion is little, to have the second driving torque drive motor of high energy efficiency.At this moment very many because the temperature in room descends, can be with the second driving torque drive motor, and to its permissible range of compressor loads for driving the load of this compressor with second driving torque.With the second driving torque drive motor time, improved the efficiency of cooling system.Simultaneously,, still can check the temperature in this room even keep this torque characteristics owing to not satisfying driving torque change condition, thus Driven Compressor in the same way.If the temperature in this room (t) is lower than the upper limit (t+) of setting temperature, then it continues the check temperature.
If compressor is worked, as shown in figure 15, then determine the drive pattern of compressor again after having finished said process.In this case, can utilize two kinds of situations to determine the drive pattern of compressor.A kind of situation is, when carrying out said process, the temperature in the room descends and changes drive pattern very for a long time, and another kind of situation is, because the temperature in room lacking of descending keeps this drive pattern.After having kept this drive pattern, Driven Compressor is determined the drive pattern of compressor to repeat said process then.The following describes the another kind of method of control compressor behind the drive pattern of having determined compressor.
With reference to Figure 15, if determine with the second torque characteristics drive motor, then according to the state of the object that will cool off, that is, the temperature in this room and the absolute value of variance ratio, control unit 610 determines whether motors are suitable for the second torque characteristics work.Then, make compressor shutdown.To do explanation to this with reference to figure 2.
At first, control unit 610 then, when compressor operating, calculates the absolute value (P) of the mean temperature variance ratio of the scheduled time from the temperature transducer 660 real-time temperature that receive this room.Determine that this absolute value (P) is whether less than the absolute value (P-) of minimum temperature variance ratio.
At this, if this absolute value (P) less than absolute value (P+), then control unit 610 sends to switch sections 650 with control signal, opening the contact of switch sections 650, thereby motor is shut down.This absolute value (P) means less than absolute value (P+), although cooling system with the second moment of torsion work scheduled time because the cooling Power deficiency, it is so much that the temperature in this room does not reduce minimum necessary level.In this case, if cooling system does not then apply necessary cooling Power to this room with the second moment of torsion work, therefore, can not effectively cool off this room.Therefore, if determine that absolute value (P) is absolute value (P+), then be unsuitable for making motor with the second torque characteristics work.Therefore, in order to cool off this room, be first torque characteristics with the driving torque feature change with big cooling Power.In this case, as shown in figure 15, control unit 610 control switch parts 650 are so that compressor shutdown.
If compressor shutdown, then after having postponed the scheduled time, control unit 610 sends to selector 620 with control signal, thereby the common 621 and first contact 623 are connected to each other together.Therefore, the driving torque feature change with motor is first torque characteristics.If finished the torque characteristics that changes motor, then control unit 610 sends to switch sections 650 with control signal, so that the make contact of switch sections 650, thereby drive motor.With the first driving torque Driven Compressor, make and cool off this room with big cooling Power.If with the first driving torque Driven Compressor, as shown in figure 15, determine again then compressor with which kind of drive pattern is being worked.
Simultaneously, if absolute value (P) greater than absolute value (P+), the temperature information that provides according to temperature transducer 660 then, control unit 610 determines whether to be suitable for making motor with the second torque characteristics work.As shown in figure 15, this determines that condition is, the temperature of the object that cool off, that is and, whether the temperature in this room (t) is lower than the lower limit (t-) of setting temperature.If the temperature in this room (t) is lower than the lower limit (t-) of setting temperature, then control unit 610 determines whether to be suitable for making motor with the second torque characteristics work, then, control signal is delivered to switch sections 650, so that motor is shut down.At this, the lower limit (t-) that the temperature in this room (t) is lower than setting temperature means because temperature (t-) is enough low, even the rate of temperature change in this room is very low, also do not need big cooling Power, and cooling system can continue with little cooling Power work.Therefore, in this case, under the situation that the drive performance of motor remains unchanged, motor is shut down.Simultaneously, if the temperature in this room (t) is higher than the lower limit (t-) of setting temperature, then control unit 610 continues to calculate this absolute value (P), and two absolute values (P) (P+) are compared, and then, according to comparative result, repeats said process.
When making compressor shutdown because the temperature (t) in this room is lower than the lower limit (t-) of setting temperature, as shown in figure 15, the temperature of definite object that will cool off, that is, whether the temperature in this room (t) satisfies the upper limit (t+) of setting temperature.If this temperature (t+) satisfies the upper limit (t+) of setting temperature, drive motor then, then, this processing procedure enters the step of determining drive pattern.
In the method that is used for controlling compressor according to the present invention, control unit control compressor is with the temperature variation in this room of real-time check, then, according to the temperature variation of check, export the cooling Power and the required moment of torsion of Driven Compressor in this room, thereby make compressor obtain best effort all the time.
Figure 16 is the flow chart that the method for the compressor that is used for controlling cooling system according to another embodiment of the present invention is shown.In this embodiment, according to the length of time of the driving process of motor and experience, control unit control compressor.To describe this embodiment of the present invention in detail with reference to figure 3.Omit explanation and identical content embodiment illustrated in fig. 15.
With reference to Figure 16, in the initial start stage, compressor is started working with first moment of torsion.Again with reference to figure 3, according to the switch sections 670 of the temperature on/off contact in room with automatic drive motor.In other words, switch sections 670 comprises the thermostat that utilizes bimetallic strip work, and deploy switch part 670 making make contact when being higher than first temperature, and opens the contact when being lower than second temperature.If being elevated to, the temperature in room is higher than first temperature, the make contact of switch sections 670 then, therefore, compressor operating.After compressor starts work, this processing procedure enters the step of determining drive pattern.
Determine the result as drive pattern, when work, satisfy first condition if compressor, is then determined compressor with the first torque characteristics work.At this moment, if satisfy first condition, compressor shutdown then.In this embodiment, first condition is whether compressor shuts down.With reference to figure 3, utilize switch sections 670 according to the temperature on/off in room, compressor opens automatically or cuts out.Therefore, if compressor works long hours, so that the temperature in room is reduced to and is lower than second temperature, and then the contact of switch sections 670 disconnects, so that compressor shutdown.The current sensor 690 of connecting with switch sections 670 detects compressor shutdown, then, and with this notice control unit 610.In other words, if current sensor 690 does not detect electric current, then control unit 610 is determined the motor shutdown.
Simultaneously, in order to determine drive pattern change condition, when compressor operating,, will be explained below drive pattern change condition to time (T) counting of experience.If compressor is not shut down, then continue the time (T) of counting experience.Certainly, if compressor shutdown then stops time (T) counting to experience.
If determine compressor shutdown, then under the compressor shutdown state, determine whether to be suitable for making compressor with the first torque characteristics work.If be fit to, then keep this driving torque characteristic, if be not suitable for, be second torque characteristics then with this driving torque feature change.After keeping or having changed the driving torque characteristic of motor, determine whether to satisfy second condition, if satisfy second condition, compressor operating then.To elaborate to this with reference to figure 2.
At first, under the situation of compressor shutdown, control unit 610 is determined the condition of the torque characteristics of change motor.At this, torque characteristics change condition be the experience time (T) whether less than presetting the shortest time (T-).In other words, if the experience time (T) less than shortest time (T-), then control unit 610 is determined to be unsuitable for to determine compressor with first drive pattern.The time (T) of experience means that less than the shortest time (T-) temperature in this room in the very short time is reduced to the temperature of requirement, because cooling Power is enough, perhaps the temperature in this room is low.Therefore, need be with big cooling Power Driven Compressor.At this moment, need to reduce energy consumption, drive this system effectively by changing torque characteristics.On the contrary, if the experience time (T) greater than shortest time (T-), then control unit 610 is determined to be suitable for the first drive pattern Driven Compressor, therefore, keeps this driving torque characteristic.In this embodiment, shortest time (T-) can be set to about 10 minutes.
If the time (T) of experience, then control unit 610 sent to selector 620 with control signal less than shortest time (T-),, thereby be second torque characteristics with the driving torque feature change of motor so that the common 621 and second contact 622 link together.After having changed the driving torque characteristic of motor, the time (T) that control unit 610 resets and experiences.On the contrary, if the time of experience less than shortest time (T-), then under the situation that the driving torque characteristic is kept intact, reset time (T) of this experience of control unit 610, as shown in figure 16.
After the time of this experience that resetted (T), control unit 610 is determined second conditions, that is, and and Driven Compressor whether.Certainly, current sensor 690 is used for determining second condition.If determine that compressor is driven, as shown in figure 15, then this processing procedure enters the step of the drive pattern of determining motor.On the contrary, if determine that compressor is not driven, then control unit 610 continues to determine second condition.
Simultaneously, identical with embodiment shown in Figure 15, after said process, determine that the step of the drive pattern of compressor provides two kinds of results.If determine then to repeat said process, and if determine that with the second torque drive motor, then compressor is with diverse ways work with the first torque drive compressor.The following describes situation with the second torque drive motor.
At first, then, determine whether to be suitable for making motor with the second torque characteristics drive motor if determine with the second torque characteristics work according to the time of experience.At this, the time and the preset time of the experience by with compressor operating the time compare, and carry out this deterministic process.After having finished this deterministic process, compressor shutdown elaborates to this below with reference to Fig. 3.
When compressor is driven, the time (T) of 610 pairs of experience of control unit counting, as shown in figure 16.Then, control unit 610 is determined the driving torque change condition of compressor.At this, driving torque change condition has two kinds of situations.A kind of situation is, whether the time of experience (T) surpasses the longest time limit (T+), and another kind of situation is, whether the time of experience (T) successfully determines the time (Tt) less than the starting of compressor.In this embodiment, the longest time limit (T+) can be set to about 30 minutes, determine that successfully the time (Ty) is set to about 10 minutes and will start.If satisfy one of two conditions, then control unit 610 is determined to be unsuitable for making compressor with the second torque characteristics work.Reason is as follows.
At first, the time of experience, (T) meaned greater than the longest time limit (T+), and compressor does not need for a long time with the second torque characteristics work.Because the cooling Power deficiency of cooling system, perhaps because around or the temperature height in this room, compressor works long hours with second torque characteristics.Therefore, temperature reduces enough low, with the switch sections 670 of opening installation in this room.In this case, because it is more effective to drive cooling system with big cooling Power, so determine to be not suitable for making compressor with the second torque characteristics work.
If the time (T) of experience is successfully determined time (Tt), then compressor malfunction less than starting.In addition, this means that after just having driven compressor with second torque characteristics, compressor is just shut down.In other words, when compressor is worked with second torque characteristics, if the moment of torsion of output is less than driving required moment of torsion, then motor overload when starting with second moment of torsion.Therefore, for example, overload protective device 640 makes the motor autostop.In this case, owing to this means that the moment of torsion of live axle 13 with the second torque characteristics drive motor time is little, so should be with bigger torque drive motor.
As mentioned above, if determine to be unsuitable for the second torque characteristics drive motor, then control unit 610 sends to second switch part 680 with control signal, opening the contact, thereby forces motor to be shut down.After the compressor shutdown, as shown in figure 16, control unit 610 delay scheduled times, and control selector 620 are first torque characteristics with the driving torque feature change with compressor.After having changed torque characteristics, the time of this experience that resets (T).Control unit 610 control second switch parts 680, with Driven Compressor, then, this processing procedure enters the step of determining mode.
Simultaneously, if the compressor with the second moment of torsion work does not satisfy moment of torsion change condition, in other words,, starts the time (Tt) of successfully determining the time of experience if surpassing, and less than the longest time limit (T+), then control unit 610 is determined to be fit to the second torque drive compressor.This means, the starting success of carrying out with second moment of torsion, and also the room temperature in this room is reduced to and is lower than second temperature.Carried out this determine after, whether current sensor 690 detects compressors and is switched on.At this moment,, then when the time (T) of check experience, determine moment of torsion change condition again, then, carry out corresponding processing procedure if compressor at work.
If determine compressor shutdown, then mean, the driving success of carrying out with second moment of torsion, and also the temperature in this room is reduced to the target temperature of requirement, that is, second temperature, compressor is with the second moment of torsion work simultaneously.After compressor shutdown, reset time (T) of this experience of control unit 610.In addition, because cooling system is not worked after the compressor shutdown, so the temperature in this room raises gradually.If the temperature in this room is higher than first temperature, then switch sections 670 auto-closings and motor rotation, Driven Compressor thus.If temperature is lower than first temperature, switch sections 670 is held open state, and therefore, compressor keeps outage state.Simultaneously, as shown in figure 16, driven compressor after, this processing procedure enters the step of the drive pattern of determining compressor.
According to the system that is used to control cooling system,, control compressor according to the automatic on/off motor of the temperature in room by time according to experience.Therefore, can provide responsive and be fit to the moment of torsion and the cooling Power of the condition in this room to the temperature conditions in room.
Those skilled in the art understand, can carry out various modifications and changes to the present invention.Therefore, if these modifications and changes fall in the scope of claims and equivalent thereof, then the present invention attempts to contain various modifications and changes of the present invention.
For example, the method that is used to control the compressor of cooling system according to the present invention is not limited only to above-mentioned compressor.In other words, the present invention can be applied to be used for cooling system and have any compressor of the motor that can export two kinds of different moments of torsion.Yet different with compressor of the present invention, the shortcoming of these compressors is that they can not export two kinds of different moments of torsion and two kinds of different capacity, perhaps cooling Powers simultaneously.In this case, if to this compressor application method of the present invention, then this compressor can be exported the moment of torsion of the state of the suitable object that will cool off, thus the efficiency that is improved.Simultaneously, the invention provides a kind of method that is used to control the compressor that to export two kinds of different moments of torsion and double volume amount.
Commercial Application
Compressor with above-mentioned structure has following effect.
At first, according to prior art, in order to realize the double-volume contracting, several devices are combined in Together. For example, in order to obtain two compression volumes, with interchanger with have different compression volumes Compressor bank is combined. In this case, complex structure, and increased cost. So And, according to the present invention, only utilize a compressor just can realize the double-volume contracting. Particularly, Reduce to minimum by the parts with traditional rotary compressor, the present invention can realize the double volume amount Compression.
Secondly, the traditional compressor with single compressed capacity can not provide be suitable for air-conditioner or The compression volume of the various conditions of work of refrigerator. In this case, unnecessarily waste power Consume. Yet the present invention can provide the compression volume of the condition of work that is fit to equipment.
The 3rd, according to rotary compressor of the present invention, can utilize the fluid chamber of traditional design Two compression volumes are provided. This means, the compression volume of compressor of the present invention at least with have The compression volume of traditional rotary compressor of onesize cylinder and fluid chamber is identical. In other words Say that rotary compressor of the present invention can replace traditional rotary compressor, and need not to revise The design of the basic element of character, for example, the size of cylinder. Therefore, rotary compressor of the present invention Can freely be applied to the system that requires, and need not the considering compression capacity and increase production of units and become This.
The 4th, according to the method for the control compressor of the present invention, can export different moments of torsion All compressors and double-volume compressor all can be according to the condition of the object that will cool off with Good moment of torsion work. Therefore, compared with prior art, can make cooling system more economical, effective Ground work.

Claims (29)

1. system that is used to control the compressor of cooling system, this control system comprises:
Compressor, it has the live axle of can be clockwise and being rotated counterclockwise, and makes this compressor operating by the power of exporting the motor of different torque characteristicses according to the sense of rotation of live axle;
Selector, it is used to select the output torque characteristic of motor;
Switch sections, it is used to open or close motor; And
Control unit, thus it is used to control the torque characteristics Driven Compressor of selector with the suitable object that will cool off,
Wherein, this motor comprises:
First winding, it connects first end and common port, and live axle is rotated with first torque characteristics; And
Second winding, it connects second end and common port, and live axle is rotated with second torque characteristics.
2. the system as claimed in claim 1 further comprises the detection device that is used to detect about the information of the object that will cool off, and wherein this control unit is based on the information control selector and the switch sections that send from this detection device.
3. system as claimed in claim 2, wherein, this detection device comprises the temperature transducer of the temperature that is used to measure the object that will cool off.
4. the system as claimed in claim 1 further comprises overload protective device, and it is set between motor and the switch sections.
5. the system as claimed in claim 1, wherein, this selector comprises:
First contact, it links to each other with first end;
Second contact, it links to each other with second end; And
Common, it links to each other with power supply, and selected first contact or second contact of being connected to.
6. the system as claimed in claim 1, wherein, this switch sections comprises the thermostat that its contact connects or disconnects according to the temperature of the object that will cool off.
7. system as claimed in claim 6 further comprises being used for determining that motor is opened or pent definite device.
8. system as claimed in claim 7, wherein, this determines that device comprises the current sensor that is used to detect by the electric current of switch sections.
9. system as claimed in claim 7, wherein, this control unit is opened according to motor or the time that disconnects and experience is controlled selector.
10. system as claimed in claim 6 further comprises the second switch part that is connected in series with switch sections, and wherein this control unit is controlled selector and second switch part according to the length of the time of experience.
11. the system as claimed in claim 1, wherein, this compressor comprises:
Live axle, it has the eccentric part of pre-sizing, and can clockwise and be rotated counterclockwise;
Cylinder, it forms predetermined internal volume;
Cylinder, the inner circumferential ground rotation of its contact cylinder is rotatably installed on the exterior periphery of eccentric part, carries out rolling motion along the inner circumferential of cylinder, and forms fluid chamber to suck and compressed fluid with the inner circumferential of cylinder;
Blade, it is resiliently mounted in the cylinder, thereby continues the contact cylinder, and is two separate space with fluid chamber's subregion;
Upper bearing and lower bearing, it is mounted respectively at the upside of cylinder and downside, is used for rotatably supporting driving shaft and the internal volume that seals cylinder;
Exhaust port, it is communicated with fluid chamber;
Expulsion valve, it is used for opening each exhaust port with predetermined pressure or the pressure higher than predetermined pressure; And
At least one suction inlet, it is communicated with fluid chamber.
12. system as claimed in claim 11, wherein, this suction inlet and exhaust port are formed in the cylinder.
13. system as claimed in claim 12, wherein, this exhaust port is separated intended distance to face one another about blade.
14. system as claimed in claim 13, wherein, this suction inlet be its position by above the imaginary line of blade to the suction inlet of blade.
15. system as claimed in claim 13, wherein, this suction inlet is positioned at by the side on the imaginary line of blade.
16. system as claimed in claim 11, wherein, this suction inlet is formed in the upper bearing, exhaust port is formed in the lower bearing, and described system further comprises valve assembly, is used for optionally opening one of each suction inlet according to the sense of rotation of live axle.
17. system as claimed in claim 11, wherein, this suction inlet is formed in the lower bearing, exhaust port is formed in the upper bearing, and described system further comprises valve assembly, is used for optionally opening one of each suction inlet according to the sense of rotation of live axle.
18. as claim 16 or 17 described systems, wherein, this exhaust port comprises first exhaust port and second exhaust port that the position faces one another about blade.
19. system as claimed in claim 16, wherein, this suction inlet comprises:
First suction inlet, it is positioned at and the blade position adjacent; And
Second suction inlet, its center about cylinder separates predetermined angle with first suction inlet.
20. system as claimed in claim 17, wherein, this suction inlet comprises:
First suction inlet, it is positioned at and the blade position adjacent; And
Second suction inlet, its center about cylinder separates predetermined angle with first suction inlet.
21. as claim 16 or 17 described systems, wherein, this cylinder utilizes whole fluid chamber compressed fluid when live axle only rotates in a clockwise direction or counterclockwise.
22. as claim 16 or 17 described systems, wherein, this cylinder utilizes segment fluid flow constant pressure contracted flow body when live axle only rotates in a clockwise direction or counterclockwise.
23. system as claimed in claim 19, wherein, this valve assembly comprises:
First valve, it is rotatably installed between cylinder and the described upper bearing, and has the through hole that inserts live axle by it; And
Second valve, it is fixed between cylinder and the described upper bearing, has the situ part that holds first valve, and this second valve is used to guide rotatablely moving of first valve.
24. system as claimed in claim 20, wherein, this valve assembly comprises:
First valve, it is rotatably installed between cylinder and the described lower bearing, and has the through hole that inserts live axle by it; And
Second valve, it is fixed between cylinder and the described lower bearing, has the situ part that holds first valve, and this second valve is used to guide rotatablely moving of first valve.
25. as claim 23 or 24 described systems, wherein, this first valve comprises disc member, thereby the eccentric part of its contact live axle is with the sense of rotation rotation of live axle.
26. as claim 23 or 24 described systems, wherein, this first valve comprises:
First opening, it is communicated with first suction inlet when live axle rotation one of in a clockwise direction or counterclockwise; And
Second opening, its live axle in a clockwise direction or another when rotation of counter clockwise direction be communicated with second suction inlet.
27. system as claimed in claim 26, wherein, this suction inlet further comprises the 3rd suction inlet, and it is positioned on second suction inlet and the blade, and firm the 3rd suction inlet of opening of first opening, and second suction inlet just is opened.
28. as claim 23 or 24 described systems, wherein, this valve assembly further comprises and is used to control the corner of first valve so that accurately open the device of corresponding suction inlet about each sense of rotation.
29. system as claimed in claim 28, wherein, this control gear comprises:
Projection, it is at the radially protrusion of first valve; And
Groove, it is formed in second valve, and holds this projection movably.
CNB2004800201791A 2003-05-13 2004-04-27 Be used to control the system and the controlling method thereof of the compressor of cooling system Expired - Fee Related CN100540904C (en)

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WO2004102006A1 (en) 2004-11-25
US20070180841A1 (en) 2007-08-09
KR100525412B1 (en) 2005-11-02
CN1823228A (en) 2006-08-23

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