CN1174294A - Refrigerant compressor and refrigeration cycle device equipped with the same - Google Patents
Refrigerant compressor and refrigeration cycle device equipped with the same Download PDFInfo
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- CN1174294A CN1174294A CN97114523A CN97114523A CN1174294A CN 1174294 A CN1174294 A CN 1174294A CN 97114523 A CN97114523 A CN 97114523A CN 97114523 A CN97114523 A CN 97114523A CN 1174294 A CN1174294 A CN 1174294A
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 16
- 239000003507 refrigerant Substances 0.000 title claims abstract description 14
- 239000002826 coolant Substances 0.000 claims description 82
- RWRIWBAIICGTTQ-UHFFFAOYSA-N difluoromethane Chemical compound FCF RWRIWBAIICGTTQ-UHFFFAOYSA-N 0.000 claims description 28
- GTLACDSXYULKMZ-UHFFFAOYSA-N pentafluoroethane Chemical compound FC(F)C(F)(F)F GTLACDSXYULKMZ-UHFFFAOYSA-N 0.000 claims description 16
- 230000033228 biological regulation Effects 0.000 claims description 10
- 230000007246 mechanism Effects 0.000 claims description 2
- 238000007906 compression Methods 0.000 description 36
- 230000006835 compression Effects 0.000 description 35
- 238000003825 pressing Methods 0.000 description 18
- 239000003921 oil Substances 0.000 description 14
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 12
- 230000008859 change Effects 0.000 description 10
- 239000003795 chemical substances by application Substances 0.000 description 10
- 238000005096 rolling process Methods 0.000 description 10
- 238000005461 lubrication Methods 0.000 description 9
- 239000000758 substrate Substances 0.000 description 8
- 229910052742 iron Inorganic materials 0.000 description 6
- 239000007788 liquid Substances 0.000 description 6
- 239000000203 mixture Substances 0.000 description 6
- 230000004907 flux Effects 0.000 description 5
- 230000002093 peripheral effect Effects 0.000 description 5
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 4
- 230000008602 contraction Effects 0.000 description 4
- 229910052802 copper Inorganic materials 0.000 description 4
- 239000010949 copper Substances 0.000 description 4
- 238000005755 formation reaction Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000005059 dormancy Effects 0.000 description 3
- 230000002500 effect on skin Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 241000555745 Sciuridae Species 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 238000009795 derivation Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000006698 induction Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 239000000178 monomer Substances 0.000 description 2
- 238000009987 spinning Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- LVGUZGTVOIAKKC-UHFFFAOYSA-N 1,1,1,2-tetrafluoroethane Chemical compound FCC(F)(F)F LVGUZGTVOIAKKC-UHFFFAOYSA-N 0.000 description 1
- UJPMYEOUBPIPHQ-UHFFFAOYSA-N 1,1,1-trifluoroethane Chemical compound CC(F)(F)F UJPMYEOUBPIPHQ-UHFFFAOYSA-N 0.000 description 1
- NPNPZTNLOVBDOC-UHFFFAOYSA-N 1,1-difluoroethane Chemical compound CC(F)F NPNPZTNLOVBDOC-UHFFFAOYSA-N 0.000 description 1
- 229940051271 1,1-difluoroethane Drugs 0.000 description 1
- 208000035874 Excoriation Diseases 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000005660 chlorination reaction Methods 0.000 description 1
- 229910052801 chlorine Inorganic materials 0.000 description 1
- 125000001309 chloro group Chemical group Cl* 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 description 1
- 230000009931 harmful effect Effects 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 125000004435 hydrogen atom Chemical class [H]* 0.000 description 1
- 238000007914 intraventricular administration Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000001932 seasonal effect Effects 0.000 description 1
- 238000009958 sewing Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/021—Inverters therefor
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Control Of Electric Motors In General (AREA)
Abstract
The invention relates to the bad performance such as inferior performance and SEER of a refrigerant compressor. In a refrigerant compressor which is used in a refrigeration cycle and carries out variable speed drive by changing a frequency supplied from a power source, the compressor has a predetermined operational frequency range at steady operation except for at a start-up, and the operational frequency range has a minimum operational frequency which is not less than a frequency near to the frequency of the power supply.
Description
The present invention relates to use in the refrigeration cycle, carry out the coolant compressor of variable speed drives by utilizing change driving power frequencies such as phase inverter, also relate to the operating frequency that utilizes control coolant compressors such as phase inverter, the refrigerating circulatory device that carries out the variable speed drives of coolant compressor.
So far, open as described in the flat 7-294030 communique as the spy, about utilizing minimum operating frequency that phase inverter etc. carries out the coolant compressor that uses in the refrigerating circulatory device of variable speed drives of coolant compressor as 28Hz, also lower than the frequency (in Japan being 60Hz or 50Hz) of industrial power.
In addition, the coolant compressor that uses in the refrigerating circulatory device as the variable speed drives of carrying out coolant compressor is generally rotary compressor shown in Figure 7 or the scroll compressor that uses in recent years shown in Figure 10.
Fig. 7 is the sectional arrangement drawing of one of rotary compressor example, shows its simple structure.Fig. 8 is the drawing in side sectional elevation of the compression member among Fig. 7.Compression member 2 and motor 3 are housed in seal container 1, and this motor 3 is corresponding with the variable velocity by this compression member 2 of bent axle 4 variable speed drives.The 5th, be used for the duty cryogen is sucked the suction pipe of above-mentioned compression member 2, it is communicated with the oil hydraulic cylinder 6 that forms pressing chamber 11.As shown in Figure 8, in oil hydraulic cylinder 6, be provided with the inlet hole 7 with the low pressure chamber 11a UNICOM of suction pipe 5 and pressing chamber 11 (as the inner space of oil hydraulic cylinder 6), in oil hydraulic cylinder 6, also be provided with the rolling piston 8 that can roll along the inner side surface of oil hydraulic cylinder 6, drive by the rotation of bent axle 4.The 9th, install in the valve groove 10 that can in oil hydraulic cylinder 6, form along the reciprocating valve of radial direction, it can often contact with the circumferential lateral surface of rolling piston 8, and pressing chamber is divided into hyperbaric chamber 11b and low pressure chamber 11a.In addition, valve 9 oil hydraulic cylinders of an inlet hole 7 and an opposite side thereof partly form tap hole 12 near being positioned at, and it and hyperbaric chamber 11b UNICOM are used for compressed duty cryogen is discharged in the seal container 1, and this tap hole 12 is closed by expulsion valve 13.
In the rotary compressor that constitutes like this, be compressed to the pressure of regulation at leisure because the off-centre of the rolling piston 8 that is driven by bent axle 4 rotatablely moves by inlet hole 7, the duty cryogen that is drawn among the low pressure chamber 11a with suction pipe 5, and opening expulsion valve 13 backs, be discharged in the seal container 1 by tap hole 12 from hyperbaric chamber 11b.
Fig. 9 represent with a Vorticose scroll wrap stationary fixing, make another Vorticose scroll wrap not around the center of the scroll wrap of stationary fixing from then make revolution motion, the basic comprising parts and the contraction principle of revolution type rotary compressor that the duty cryogen is compressed.Among the figure, the 21st, with respect to the fixed scroll of space stationary fixing, it has Vorticose scroll wrap 21a.The 22nd, make the rotation vortex of revolution motion, it has, and it is opposite with fixed scroll tooth 21a around direction, with the Vorticose scroll wrap 22a with respect to the combinations of states of 180 ° of phase places of fixed scroll tooth 21a skew.The shape of these Vorticose scroll wrap 21a, 22a is a kind of with the shape after the combinations such as involute and camber line.The 23rd, suction chamber, the 24th, tap hole, the 25th, pressing chamber.
Secondly, the working condition of parts shown in Figure 9 is described.Rotation vortex 22 does not change its attitude, promptly do not make spinning motion but be rotated around the center of fixed scroll tooth 21a to make revolution motion, the operating position by 0 °, 90 °, 180 °, 270 ° shown in Fig. 9 (a) and (b), (c), (d) moves successively.Under 0 ° of state shown in Fig. 9 (a), finish the process that the duty cryogen in the suction chamber 23 is shut up, between fixed scroll tooth 21a and rotation scroll wrap 22a, formed the pressing chamber 25 of three life shapes.Along with the revolution motion of rotation vortex 22, pressing chamber 25 reduces its volume successively then, the duty cryogen is compressed near the center of fixed scroll 21, discharges from tap hole 24.
The concrete structure and the working condition of rotary compressor then, are described.Figure 10 is the sectional arrangement drawing of an example of expression revolution type rotary compressor, and 21 is that Vorticose scroll wrap 21a is located at fixed scroll on the substrate 21b among the figure, is fixed on the body frame 26.The 22nd, the Vorticose scroll wrap 22a with said fixing scroll wrap 21a combination is located at rotation vortex on the substrate 22b, forming thrust face 22c and shaking bearing 22d on the substrate 22b with on the side opposing end faces that is provided with scroll wrap 21a, above-mentioned thrust face 22c is used for bearing the thrust that is produced by the compressive load that acts on the rotation vortex 22, and the above-mentioned bearing 22d that shakes is used for supporting by acting on the radially loads such as centrifugal force that compressive load on the rotation vortex 22 or revolution motion derive from.Above-mentioned body frame 26 is fixed in the seal container 27, forms thrust-bearing 26a on body frame 26, is bearing in vertically sliding freely on the thrust face 22c of rotation vortex 22.The 28th, the motor of the speed change correspondence of available speed change rotation drive main spindle 29 is made of stator 28a and rotor 28b.Rotor 28b is fixed on the main shaft 29 through shrink fit, and balancing stand 30a, 30b are used to revolt the centrifugal force by the revolution motion derivation of rotation vortex 22, and the balance that the system that is rotated is all is installed in the upper and lower respectively.Main shaft 29 is driven by motor 28 rotation, is used in main bearing 26b that forms on the body frame 26 and the supplementary bearing 31a that forms on subframe 31, radially supports clamping motor 28 both sides.The 32nd, Euclidean ring (オ Le ダ system リ Application グ) carries out linear reciprocating motion with respect to rotation vortex 22 and body frame 26.Eccentric shaft 29a is located at the upper end of main shaft 29, eccentric shaft 29a utilizes the rotation of main shaft 29 to drive, by shaking bearing 22d rotary driving force is delivered on the rotation vortex 22, rotation vortex 22 utilizes the linear reciprocating motion constraint rotation of Euclidean ring 32, so carry out revolution motion with respect to fixed scroll 21, as mentioned above, the duty cryogen is compressed.In addition, the bottom of seal container 27 constitutes lubricating oil tank 33, utilization is installed in the displacement pump 34 of main shaft 29 lower ends, and the oil circuit 29b by forming on main shaft 29 supplies with each bearing 22d of, 26a, 26b, 31a and other sliding parts with the lubricant oil in the lubricating oil tank 33.
Coolant compressors such as aforesaid rotary compressor or scroll compressor, open as described in the flat 7-294030 communique as the spy, during except starting, in the time of in normal operating limit, with the low frequency run of 28Hz geometric ratio industrial power frequency, the performance of coolant compressor is compared remarkable decline with the industrial power frequency or than the high frequency run of industrial power frequency the time.
Its reason is that at first, during low-speed running, leakage loss increases with respect to the ratio of theoretical compression work.This be because, in the compression process or the duty cryogen of compression after finishing have nothing to do with rotating speed (being operating frequency) by the internal leakage amount of leading near unit time of the various clearance leakages of the pressing chamber of low voltage side.Therefore, rotating speed is low more, and the 1 needed time of circle of rotation is long more, so leak volume increases in the process of rotation 1 circle, under identical contractive condition, leakage loss increases with respect to the ratio of theoretical compression work, and efficiency factor descends.In rotary compressor, the various gaps of sewing as generation, in a single day for example as being discharged into the path that the interior duty cryogen with discharge pressure of seal container drains to hyperbaric chamber and low pressure chamber both sides, the axial clearance that the upper-end surface of the gap of valve and valve groove side and rolling piston is arranged, as the leakage path that leads to low pressure chamber from the hyperbaric chamber, the radial clearance of inner peripheral surface of the outer circumferential face of rolling piston and oil hydraulic cylinder and the axial clearance of valve upper-end surface are arranged.In scroll compressor, as the leakage path that leads to the adjacent pressing chamber lower than pressing chamber pressure itself, have scroll wrap the increment face and and the substrate end-face of the vortex of its unification side that matches between axial clearance and the radial clearance between the side of both sides' scroll wrap.Moreover, in scroll compressor, also have duty cryogen in the pressing chamber that most peripheral forms to drain to the leakage path of outside of the pressing chamber of most peripheral from above-mentioned leakage path at the compression stroke initial stage, therefore, volumetric efficiency also descends significantly when low-speed running.
The 2nd reason, during low-speed running, the loss of motor is big with respect to the ratio of theoretical compression work.The motor that carries out the coolant compressor of variable speed drives with the frequency of change driving powers such as phase inverter uses the three phase squirrel cage induction machine usually.In the three phase squirrel cage induction machine, when being certain value at the Magnetic flux density in the gap of the Magnetic flux density of the electromagnetic steel plate that constitutes stator and rotor or stator and rotor and frequency-independent, be necessary to make the relation of voltage and frequency proportional, but at this moment frequency is low more, it is more little that detent torque becomes, particularly be lower than under the low frequency situation of industrial frequency the problem that exists detent torque sharply to descend.Therefore, be higher than when turning round under industrial frequency and the equal pressure condition frequency low more (low speed) in frequency, turn round torque more near detent torque, so, in order to increase current value, iron loss increases (iron loss and current value square be directly proportional), causes efficiency of motor decline.That is, the motor loss becomes big with respect to the ratio of theoretical compression work.Therefore, during the low frequency that particularly diminishes, be lower than industrial frequency in detent torque, adopt the high method of magnitude of voltage that voltage ratio is determined by the aforementioned proportion relation in order to increase detent torque, therefore, electric efficiency increases than above-mentioned efficient, even but in this case, because voltage increases, cause the Magnetic flux density in the gap of the Magnetic flux density of the electromagnetic steel plate that constitutes stator and rotor or stator and rotor to increase, iron loss (iron loss and current value square be directly proportional) has also just increased.Like this, than the low low frequency of industrial frequency the time, the efficient of efficiency of motor during than the frequency more than industrial frequency is low, and the motor loss becomes big with respect to the ratio of theoretical compression work.
In addition, during with the low frequency run of 28Hz geometric ratio industrial power frequency, the revolution motion of the thrust-bearing of particularly revolution type scroll compressor is the different peculair motion of thrust-bearing a kind of and the general spinning motion of supporting, its turning radius is the revolution radius, therefore with supporting spindle the holds rotation of etc.ing spool the bearing of radial load compare, turning radius is little, thereby Sliding velocity diminishes, greasy property descends, and there is harmful effect the reliability aspects such as durability of coolant compressor.The decline of greasy property also can cause can not keep lubricated by Liquid Lubrication Condition decision, and becomes boundary lubrication condition, has strengthened wearing and tearing, even can cause the friction burn in the worst case, causes coolant compressor so fatal problem that can not turn round.In addition, under boundary lubrication condition,, cause bearing loss to increase, problem is also arranged at aspect of performance because friction factor increases.
As mentioned above, from season, under near the setting value at room temperature of growing in the running the environment, in order to obtain better comfort, make coolant compressor carry out low-speed running with the low frequency that is lower than industrial power, in the existing refrigerating circulatory device of the variable speed drives of accurately controlling of carrying out coolant compressor, the performance of the performance (efficiency factor) of the coolant compressor during such low-speed running during than the frequency that is higher than industrial power is low, and therefore seasonal energy consumption efficient (following note is made SEER) descends.In addition, if it is long to be lower than running time of frequency of industrial power, then bearing performance degenerates, so, the problem that exists the durability of coolant compressor to descend.
The present invention finishes in order to address the above problem, its purpose is the coolant compressor that carries out variable speed drives that a kind of SEER height is provided, can also improves durability, in addition, a kind of refrigerating circulatory device that can obtain the also high variable speed drives of carrying out coolant compressor of enough travelling comfortes, SEER height and reliability is provided, moreover, provide a kind of and have that volume is little, the refrigerating circulatory device of lightweight coolant compressor.
Relevant the 1st aspect of the present invention, a kind of frequency of using in refrigeration cycle of passing through the change driving power is carried out the coolant compressor of variable speed drives, above-mentioned coolant compressor is except when starting, the operating frequency that has regulation when running well makes the minimum operating frequency in above-mentioned operating frequency district be higher than near the frequency of industrial power frequency.
In addition, relevant the 2nd aspect of the present invention, invention the 1st aspect in, coolant compressor is the scroll compressor that a pair of Vorticose scroll wrap is combined the duty cryogen is compressed.
In addition, relevant the 3rd aspect of the present invention, invention the 1st aspect or in the 2nd aspect, adopt the mix refrigerant that difluoromethane (HFC32) and pentafluoroethane (HFC125) are mixed as the duty cryogen.
In addition, relevant the 4th aspect of the present invention, a kind of refrigerating circulatory device that coolant compressor, heat exchanger, expansion mechanism etc. is coupled together with pipeline, above-mentioned coolant compressor is except when starting, the operating frequency that has regulation during normal operation, make the minimum operating frequency in above-mentioned operating frequency district be higher than near the frequency of industrial power frequency,, carry out variable speed drives by changing the frequency of driving power.
In addition, relevant the 5th aspect of the present invention, invention the 4th aspect in, coolant compressor is the scroll compressor that a pair of Vorticose scroll wrap is combined the duty cryogen is compressed.
In addition, relevant the 6th aspect of the present invention, invention the 4th aspect or in the 5th aspect, adopt the mix refrigerant that difluoromethane (HFC32) and pentafluoroethane (HFC125) are mixed as the duty cryogen.
Fig. 1 is the basic block diagram of refrigerating circulatory device of the variable speed drives of carrying out coolant compressor of expression one embodiment of the invention.
Fig. 2 is the sectional arrangement drawing of structure of the coolant compressor (revolution type scroll compressor) of expression one embodiment of the invention.
Fig. 3 is the explanatory drawing of leakage clearance of pressing chamber of the scroll compressor of expression one embodiment of the invention.
Fig. 4 is the comparison diagram of monomer performance of the coolant compressor (revolution type scroll compressor) of expression one embodiment of the invention and conventional example.
Fig. 5 is the sectional arrangement drawing of structure of the coolant compressor (two rotary type scroll compressor) of expression one embodiment of the invention.
Fig. 6 is the explanatory drawing of the contraction principle of the two rotary type scroll compressors of expression.
Fig. 7 is the sectional arrangement drawing of the structure of the existing coolant compressor of expression (rotary compressor).
Fig. 8 is the drawing in side sectional elevation of the compression member of expression rotary compressor.
Fig. 9 is the explanatory drawing of the contraction principle of expression revolution type scroll compressor.
Figure 10 is the sectional arrangement drawing of the structure of the existing coolant compressor of expression (revolution type scroll compressor).
Embodiment 1
Below describe embodiments of the invention in detail with regard to accompanying drawing.Fig. 1 is the basic block diagram of refrigerating circulatory device of the variable speed drives of carrying out coolant compressor of expression one embodiment of the invention.
Among the figure, the 100th, coolant compressor, the 101st, outdoor heat converter, the 102nd, indoor heat converter, the 103rd, four-way valve, the 104th, outdoor expansion valve, the 105th, indoor expansion valve, the 106th, accumulator couples together the formation cooling cycle system with them.The 107th, industrial power, converter plants such as phase inverter 108 are connected on this industrial power 107, and the output terminal of this converter plant 108 is connected with the motor of coolant compressor 100.Electric current from industrial power 107 carries out variable voltage variable frequency control, variable speed drives coolant compressor 100 by converter plant 108.
Fig. 2 be expression as the sectional drawing of the scroll compressor shown in the coolant compressor among Fig. 1 100, the scroll compressor of the revolution type that the duty cryogen is compressed by a pair of Vorticose scroll wrap is combined constitutes.Fig. 9 of the basic structure of coolant compressor and working condition and conventional example, scroll compressor shown in Figure 10 are identical, are marked with the symbol identical with conventional example, and its explanation is omitted.
In above-mentioned structure, during except coolant compressor 100 startings, minimum operating frequency in the normal operation frequency zones is near the frequency of frequency (being 60Hz or 50Hz in Japan) of industrial power 107, or with the equal above frequency of the frequency of industrial power 107, make the normal operation frequency zones from the past district integrally to high frequency one side shifting.Specifically, except when starting, the minimum operating frequency in the normal operation frequency zones is 60Hz, and the normal operation frequency zones is 60Hz～240Hz.This is that to make in the past normal operation frequency zones be that the coolant compressor of 30Hz～120Hz increases and is twice the speed pairing frequency zones that turns round, owing to become this capacity, the swept volume of coolant compressor 100 can reduce half, and this just can make the shape miniaturization of two scroll wrap 21a, 22a.When Vorticose scroll wrap was formed by involute, swept volume can calculate with following formula.
V
st＝(2N-1)πp(p-2t)h
In the formula, V
St: swept volume
N: the number of turns
P: tooth pitch p=2 π A A: the Base radius of involute
T: transverse tooth thickness
H: tooth depth
As can be known, if change number of turns N and transverse tooth thickness t, then can reduce tooth depth h and tooth pitch p.With respect to being the existing coolant compressor of operating range with 30Hz～120Hz, the reducing of tooth depth h can seek to sew reducing of flow path area by what the radial clearance between the side of binary vortices tooth shown in Figure 3 formed, in addition, tooth pitch p reduce can seek equally to reduce to sew flow path area by what the axial clearance between the substrate end-face of the front-end face of scroll wrap shown in Figure 3 and the vortex that matches formed.Therefore, when the leakage loss low-limit frequency high with respect to the ratio of theoretical compression work turns round, be that the existing coolant compressor of operating range turns round with 30Hz promptly with 30Hz～120Hz, then as mentioned above, to be that coolant compressor that the swept volume of the existing coolant compressor of operating range reduces the embodiment of half is when turning round under same pressure condition with low-limit frequency 60Hz with 60Hz～240Hz, though capacity is identical (if volumetric efficiency is identical, then refrigerating capacity is identical, theoretical compression work is identical), but it is little to sew the little embodiment's of area leakage loss.Moreover, in an embodiment, owing to sew reducing of area, duty cryogen in the pressing chamber that most peripheral forms also is leaked to the pressing chamber outside slightly at the compression stroke initial stage, and the theoretical intake (frequency * swept volume) in the unit time is identical with conventional example, so volumetric efficiency has improved than conventional example.And theoretical compression work has increased with the raising degree of volumetric efficiency big or small accordingly, as mentioned above, leakage loss descends, so embodiment's leakage loss can reduce than conventional example with the ratio of theoretical compression work, compressor performance when turning round with low-limit frequency 30Hz with the extra high conventional example of the ratio of leakage loss is compared, and the compressor performance during the turning round with low-limit frequency 60Hz of embodiment increases substantially.Certainly, even when other frequency, by the same token, if under identical pressure condition, the frequency of same capability is compared, embodiment's volumetric efficiency is also than the height of conventional example, and can reduce the ratio of leakage loss with respect to theoretical compression work.Therefore in addition, can make the shape miniaturization of two scroll wrap 21a, 22a, promptly mean the miniaturization of fixed scroll 21 and rotation vortex 22, can also seek to accommodate the miniaturization of rotation vortex 22 and body frame 26 that fixed scroll 21 is fixing.And the miniaturization of these two vortexs 21,22 can also reduce the load that acts on thrust-bearing 26a and the main bearing 26b etc.
In addition, under identical pressure condition, the driving torque of the needed motor 28 of compression work refrigeration agent is the value of theoretical compression work divided by (2 π * frequency) gained.Therefore, in the present embodiment, under identical pressure condition, the driving torque of the needed motor 28 of compression work refrigeration agent was 2 times of frequency when the same theory compression work was same refrigerating capacity, can reduce half than conventional example as can be known.And in an embodiment, the low frequency running to be lower than the industrial power frequency that causes detent torque sharply to descend is not implemented in normal operating limit, so, do not produce the problem of the described motor loss of the problem to be solved in the present invention.That is, even during with the running of the low-limit frequency of normal operation frequency zones, also can be with the time with other frequency equal Magnetic flux density running, so, compare when turn round with low-limit frequency in the conventional example, can reduce iron loss, the raising electric efficiency.Therefore, compare when turning round with low-limit frequency (30Hz) with conventional example, embodiment can reduce the ratio of motor loss with respect to theoretical compression work when turning round with low-limit frequency (60Hz), can improve compressor performance.Here, if ignore motor 2S miniaturization, adopt motor same, the torque of then turning round is extremely low to the ratio of detent torque, can seek to increase substantially electric efficiency, if rating of machine is excessive, it is big to remain the advantage of seeking miniaturization.The low-limit frequency that makes the normal operation frequency zones like this be near the industrial power frequency frequency or with the equal above frequency of industrial power frequency, the rapid problem that descends of detent torque that then in the district that runs well, does not have motor, therefore when turn round with low-limit frequency, can eliminate owing to the current value increase causes the copper loss increase or sets voltage to such an extent that highly cause degradation factor under the electric efficiency such as iron loss increase.So can increase substantially the electric efficiency when turning round, can greatly improve the compressor performance when turning round with low-limit frequency with low-limit frequency.
Next thrust-bearing 26a is described.In an embodiment, as mentioned above,, seeks swept volume the miniaturization of two vortexs 21,22 by being reduced by half, so, the compressive load of the thrust direction that is taken place by the compression and the duty cryogen of frequency-independent can reduce the part that reduces with tooth pitch p size accordingly.Therefore, the miniaturization of thrust-bearing 26a is possible.And, because the low-limit frequency in the normal operation frequency zones becomes 2 times of conventional example, so Sliding velocity increases.The revolution radius of rotation vortex 22 can calculate with following formula.
The revolution radius R
c=p/2-t
In the formula, p: tooth pitch p=2 π A A: the Base radius of involute
T: transverse tooth thickness
Reduce by half when carrying out the miniaturization of Vorticose scroll wrap 21a, 22a by swept volume, not only to reduce tooth pitch p in an embodiment, but tooth depth h also reduces in the lump, so the radius that not only revolves round the sun reduces half, and the value of the existing radius of revolution radius ratio after reducing by half is also big a lot.Therefore, during minimum operating frequency, can be with respect to the Sliding velocity of thrust-bearing 26a than existing increase.Thereby, can make thrust-bearing 26a miniaturization, from whole season, running time, the greasy property of thrust-bearing 26a during long minimum operating frequency also can be than existing improve, the lubricating status of fluid can be guaranteed reliably, the durability of coolant compressor can be greatly improved.In addition, under Liquid Lubrication Condition, the increase Sliding velocity will cause the increase of slippage loss, operating frequency is high more, the slippage loss of thrust-bearing is big more, even therefore in the prior embodiment, in the frequency zones that makes fluid lubrication really, in the embodiment's corresponding with it frequency zones, the slippage loss of thrust-bearing might increase., the turning radius of original thrust-bearing and revolution radius are just little, so if by fluid lubrication, its slippage loss is just little with respect to the ratio of theoretical compression work.Therefore, when embodiment's high frequencies such as 240Hz, Sliding velocity increases, if compare during with the high frequencies such as 120Hz of corresponding conventional example, the part that the slippage loss of thrust-bearing 26a increases only is equivalent to compressor performance and descends little by little.On the other hand, when low-limit frequency,, compare, can reduce friction factor, can not only improve reliability, and can seek to reduce slippage loss with boundary lubrication condition in the past by guaranteeing reliable Liquid Lubrication Condition.
In addition, main bearing 26b, supplementary bearing 31a, shake the bearing (being referred to as radial bearing) of radial load that this class of bearing 22d supports the axle of relative rotation, its turning radius (being exactly bearing radius itself) is bigger, Sliding velocity is compared with thrust-bearing 26a, it is big or small accordingly to have increased the part that goes out greatly with turning radius, even so in the prior embodiment, when minimum operating frequency, also can guarantee sufficient greasy property.Therefore, if embodiment when the minimum oil film thickness of pairing each bearing part forms than the minimum operating frequency of conventional example during with identical pressure condition, low-limit frequency the minimum oil film thickness of each radial bearing part thick or identical with it, even then also can guarantee sufficient greasy property in an embodiment.Equally, the foregoing description is with respect to conventional example, seek the miniaturization of two vortexs 21,22 by reducing by half of swept volume,, can reduce the compressive load of the thrust direction that the duty cryogen by compression and frequency-independent taken place effectively particularly by reducing tooth depth h.Wherein tooth pitch reduces also to have contribution.In addition, it is lightweight that the rotation vortex 22 of derivation centrifugal force is miniaturized, therefore and then the revolution radius of rotation vortex 22 also is reduced, and also can seek to be used for offsetting the centrifugal force that is derived from by revolution motion, the balancing stand 30a that carries out the balance of all rotary systems, the miniaturization and of 30b.In addition, because the miniaturization of motor 28, distance between main bearing 26b and the supplementary bearing 31a and the distance between balancing stand 30a, the 30b also can shorten.Therefore, it is thick or identical when if the minimum oil film thickness of each radial bearing forms than the minimum operating frequency 30Hz of conventional example during embodiment's low-limit frequency 60Hz with it, then centrifugal force is square increase of frequency with rotating speed, and above-mentioned reason is that the influence of centrifugal force is little because frequency is low, so embodiment one can reduce the radial load that acted on, and frequency doubles, and Sliding velocity increases, so, compare with conventional example, each radial bearing can miniaturization.Suppose that with the such miniaturization that reduces by half of bearing radius even doubling frequency so, Sliding velocity is also constant, but can alleviate load, so even carry out such miniaturization, greasy property also descends unlike conventional example, and can have sufficient durability.In addition, in the high side of the big frequency of the influence of centrifugal force, centrifugal force is with square increase of frequency, so even there is above-mentioned such radial load to alleviate parts, also opposite with the low side of frequency, the radial load that acts on each radial bearing is bigger than high frequency one side of pairing conventional example., because with each radial bearing miniaturization, so can reduce friction factor.And, in an embodiment, seek miniaturization based on each radial bearing that dwindles bearing diameter, so turning radius is reduced, even frequency doubles, Sliding velocity also increases hardly.By such processing, the slippage loss the when slippage loss of the radial bearing of high frequency one side can be suppressed in than the frequency corresponding with conventional example is lacked or is equal with it.Therefore, in an embodiment, even its frequency increases be twice, the ratio with respect to theoretical compression work of high frequency side is compared with the past, and the slippage loss of the radial bearing that the ratio with respect to theoretical compression work of high frequency one side is high can identical and minimizing.
Fig. 4 represents revolution type scroll compressor that present embodiment is used and is the comparison of the compressor monomer performance of revolution type scroll compressor under identical conditions of normal operation frequency zones as conventional example with 30～120Hz.The efficiency factor COP (Coefficient of performance) that the longitudinal axis of this figure will have the 60Hz of compressor now as 1, expression and its ratio.Transverse axis is represented frequency, and the frequency of the correspondence of conventional example and present embodiment (being between the identical frequency of capacity) is at same position.As shown in Figure 4, according to above-mentioned reason, the COP during low-limit frequency improves very big.Frequency is high more, embodiment is low more with respect to the superiority of conventional example, but when it being carried out between the pairing frequency compare, the advantage of the reduction of embodiment's leakage loss is because except above-mentioned thrust-bearing 26a as can be known, is called the discharge crushing of overshoot loss and the increase of the secondary copper loss that produced by the skin effect of motor 28 offsets.Even when highest frequency, also be embodiment's COP height.Frequency is high more, and the overshoot loss is also high more with respect to the ratio of theoretical compression work.Embodiment's swept volume reduces by half, and the displaced volume flow also reduces by half, but the influence of doubling frequency is big, when comparing between the frequency with correspondence, embodiment one side's overshoot loss is with respect to the ratio height of theoretical compression work, more in high frequency one side, compare with conventional example, its ratio is high more.In addition, though skin effect is arranged, this is the phenomenon that the secondary resistance that causes when the CURRENT DISTRIBUTION that flows through rotor 28b is inhomogeneous and secondary inductance change, and frequency is high more, and particularly the secondary copper loss is big more.
As mentioned above, in high frequency one side, compressor performance improves for a short time, except that when starting, the minimum operating frequency in operating frequency district is 60Hz, the normal operation frequency zones is 60Hz～240Hz, by like this to high frequency one side shifting, from whole season, running time long, the performance of coolant compressor 100 can increase substantially when turning round with low-limit frequency, so the SEER of coolant compressor has improved, the SEER that its refrigerating circulatory device that carries out variable speed drives is installed also can improve.And, under near the environment the room temperature that sets, carry out refined control also resembling in the past in low-limit frequency when running of carrying out the operating frequency district.In addition, owing to can improve the greasy property of the thrust-bearing 26a in low-limit frequency when running, so can improve the durability of coolant compressor 100, reliability is also high.Moreover, as mentioned above, because can be with each part miniaturization, so coolant compressor 100 all energy miniaturization ands, its cost also can reduce.In the scroll compressor that uses in Fig. 4, embodiment is with respect to conventional example, and the compressor external diameter is reduced to 88%, and the compressor height is reduced to 78%, and compressor weight also is relieved to 65%.In addition, this means the miniaturization that can make the refrigerating circulatory device that this coolant compressor 100 is installed and reducing cost.
Here, the advantage of use scroll compressor as coolant compressor 100 has been described.Scroll compressor simultaneously and suck continuously, compress, discharge, in addition, the pressing chamber of intermediate pressure forms between sucking and discharging, so rate of pressure rise is slow, so the torque variation is very little.And almost be to discharge with the form of Continuous Flow, so the variation in pressure of the duty cryogen of discharging is little.Therefore vibrate low, be suitable for when high frequency, turning round, therefore even with near the frequency the frequency of industrial power 107 or than the low-limit frequency of the high or equal frequency of the frequency of industrial power 107 as the normal operation frequency zones with it, with the normal operation frequency zones integrally than in the past to high frequency one side shifting, also can turn round with high frequency.In addition, not necessarily expulsion valve must be arranged, so, there are not the problems such as followability of the noise that causes by expulsion valve when turning round, breakage, valve with high frequency.
In the above-described embodiments, as this scroll compressor, though used with a vortex stationary fixing, make another vortex around the center of the vortex of stationary fixing not from then make the scroll compressor of the revolution type of revolution motion, but in scroll compressor, be with two vortex eccentric combination, make the scroll compressor of two vortexs along the two-volute of same direction rotation, compression work refrigeration agent.Fig. 5 is the sectional arrangement drawing of the scroll compressor of this two-volute, Fig. 6 is the explanatory drawing of contraction principle of the scroll compressor of expression two-volute, the part identical or suitable with the scroll compressor of above-mentioned revolution type is marked with identical symbol, and its explanation is omitted.41 is to drive vortex among this figure, it is Vorticose scroll wrap 41a vertically to be located at substrate 41b go up, connecting live axle 42 formations on the face of its opposite side, 43 driven vortexs, it is Vorticose scroll wrap 43a vertically to be located at substrate 43b go up, connecting driven shaft 44 formations on the face of its opposite side, and two scroll wrap 41a, 43a are combined prejudicially.Drive above-mentioned live axle 42 with motor 28 rotations, therefore the driving vortex 41 that is connected just carries out rotation.In case drive vortex 41 rotations, the driveshaft 45 that vertically is located on the substrate 41b that drives vortex 41 just is fitted in the groove 46 that radially extends that forms on driven vortex 43, so, driven vortex 43 also with drive vortex 41 along same direction rotation.Two of eccentric combination vortexs 41,43 are along same direction rotation like this, and as shown in Figure 6, the pressing chamber 25 of the three life shapes that form between two scroll wrap 41a, 43a just reduces its volume successively, and the compression work refrigeration agent is discharged from tap hole 24.If will drive vortex 41 forms to such an extent that make the center of gravity that drives vortex 41 concentric with live axle 42, then do not carry out eccentric motion with respect to the driving bearing 47 of supporting driving shaft 42 radially, in addition, if form driven vortex 43 to such an extent that make the center of gravity of driven vortex 43 concentric with driven shaft 44, then do not carry out eccentric motion with respect to the driven bearing 48 that radially supports driven shaft 44, therefore whole rotary system is configured so that complete equilibrium, does not need to install balanced body.
The scroll compressor of this two-volute is used as coolant compressor 100, during except that starting, with near the frequency the frequency of industrial power 107 or than the low-limit frequency of the high or equal frequency of the frequency of industrial power 107 as the normal operation frequency zones, with the normal operation frequency zones integrally than in the past to high frequency one side shifting, can obtain and the same effect of the foregoing description, and because rotary system is configured so that complete equilibrium, so can seek lower vibration when turning round with high frequency.
When coolant compressor 100 stopped for a long time, the duty cryogen was condensing in seal container 27, accumulates under liquid state, caused so-called dormancy phenomenon.In scroll compressor, the amount of the liquid refrigerant of dormancy even also has been full of liquid refrigerant for a long time in the pressing chamber 25, just begins starting from such state sometimes.At this moment, if with the high frequency starting, then the volume of pressing chamber is big with respect to the variance ratio of time, so, particularly sharply rise at middle pressure intraventricular pressure, promptly produce pressure pulse, therefore there is the problem that causes Vorticose scroll wrap breakage.Therefore, though present embodiment with near the frequency the frequency of industrial power 107 be higher than the frequency of industrial power 107 or the frequency equal with it as the low-limit frequency of normal operation frequency zones, but for example begin to carry out slow start, make the stepped rising of frequency during starting, the generation of the pressure pulse when having prevented the dormancy starting from low frequencies such as 10Hz.
Embodiment 2
Consider to use the situation of rotary compressor as coolant compressor 100, when low-limit frequency turns round, the same with scroll compressor, by reduce swept volume, particularly by reducing to sew area by the side clearance of valve and valve groove and by what the gap of the radial direction of rolling piston outer circumferential face and oil hydraulic cylinder inner peripheral surface formed, seek to reduce leadkage loss, in addition, about, the motor loss also can obtain same effect, so can greatly improve compressor performance.But rotary compressor is different with scroll compressor, in the process of rotating a circle because the stroke that sucks, compress, discharge, rate of pressure rise is big, so, torque change than scroll compressor greatly, because this point and need expulsion valve etc., this compressor is not suitable for running up resemble the scroll compressor.Therefore, compare with scroll compressor, be restricted in high frequency one side, the operating frequency district is narrower than the scroll compressor.In addition, the maximum reason that hinders rotary compressor to run up is considered to the slip of valve and rolling piston outer circumferential face, this sliding parts often is in boundary lubrication condition, if carry out the high frequency running, then the friction of valve front end and rolling piston outer circumferential face becomes very violent.But designed in recent years valve and rolling piston are the rotary compressor that formation integrally, valve and rolling piston outer circumferential face are non-sliding mode, can solve the friction problem of this part.
Embodiment 3
In recent years from the viewpoint of environmental protection; duty cryogen as refrigerating circulatory device uses the hydrogen fluorocarbon (to call HFC class refrigeration agent in the following text) that does not contain the chlorine atom that damages the ozone layer in its structure of molecule gradually, and decision is abolished the main chlorination difluoromethane (to call HCFC22 in the following text) that uses in the present air-conditioning fully in nearer future.The refrigeration agent of this HCFC22 instead, for example have: difluoromethane (HFC32), pentafluoroethane (to call HFC125 in the following text), 1,1,1,2 HFC-134a (to call HFC134a in the following text), 1,1,1 HFC-143a (to call HFC143a in the following text), 1,1 Difluoroethane HFC such as (to call HFC152a in the following text) series refrigeration agent uses them separately or multiple mixing is used.Be hopeful most with HFC32, HFC125 and three kinds of HFC32/125/134a refrigeration agents that mix of HFC134a or with the refrigeration agent of HFC32 and two kinds of HFC32/125 that mix of HFC125.HFC32/125 particularly, HFC22 compares with high-pressure refrigerant, and is quite high with respect to the full resultant pressure of same temperature.Therefore, with identical in the past temperature conditions under, the height pressure difference is big more a lot of than HCFC22.On the other hand, because density is also big than HCFC22, so the refrigerating capacity in order to obtain to equate when using HCFC22, swept volume is little just passable during than use HCFC22.
Duty cryogen as the refrigerating circulatory device that carries out the variable speed drives coolant compressor, if use this HFC32/125, as mentioned above, the height pressure difference increases than HCFC22, so leadkage loss increases, particularly leakage loss significantly descends with respect to the ratio existing compressor performance high, when turning round with low-limit frequencies such as 30Hz of theoretical compression work.Therefore adopt the present invention promptly to use scroll compressor to constitute coolant compressor 100, during except that starting, if with near the frequency the frequency of industrial power 107 be higher than the frequency of industrial power 107 or the frequency equal with it as the low-limit frequency of normal operation frequency zones, with the normal operation frequency zones integrally than in the past to high frequency one side shifting, owing to aforesaid reason, can reduce leakage loss especially effectively, the compressor performance in the time of improving the low-limit frequency running significantly.In addition, compare during with HCFC22, can reduce swept volume,, can reduce the overshoot loss so the displaced volume flow in high frequency when running reduces.Therefore,, can make compressor performance, in other words, can make COP near smooth in the district's equilibrium of whole operating frequency even also can seek to improve compressor performance in high frequency one side.Therefore, can improve the SEER of coolant compressor 100, also can improve the SEER that it is housed, carry out the refrigerating circulatory device of variable speed drives.
In an embodiment of the present invention, although understand operating frequency district with 60Hz～240Hz regulation when running well, but the operating frequency district of regulation is not limited to 60Hz～240Hz during of the present invention the normal operation, be that minimum operating frequency can select to be higher than near the frequency of industrial power frequency, promptly as the explanation to solve problem the time described, select the big frequency of frequency than the point that detent torque is sharply descended, in addition, the transport maximum frequency can be chosen in the slippage loss that does not produce when running up because of bearing part, the increase of overshoot loss or the losses such as secondary copper loss that produced by the skin effect of motor and cause the frequency of the problem of decreased performance can suitably selection between these two frequencies.
The present invention is because the operating frequency district of the regulation when determining as above that coolant compressor runs well, thus can with low cost provide a kind of miniaturization and and SEER height, durability might as well the coolant compressor that carries out variable speed drives.
In addition, can be with the refrigerating circulatory device that carries out the variable speed drives coolant compressor that low cost provides a kind of miniaturization and and travelling comfort is good, SEER is high, reliability is also high.
As mentioned above, aspect the of the present invention the 1st in, advancing by the frequency that changes driving power In the coolant compressor of row variable speed drives, above-mentioned coolant compressor is except when starting, The operating frequency that has regulation during normal operation makes the low-limit frequency of above-mentioned operating frequency be higher than industry Near the supply frequency frequency, so, when the low-limit frequency running of normal operation frequency zones, energy Make the loss of leakage loss or motor little with respect to the ratio of theoretical work done during compression, from whole season, The performance of the coolant compressor in the time of making the minimum operating frequency of growing the duration of runs is carried significantly Height, so, the SEER of coolant compressor can be improved. And, carrying out the operating frequency district Low-limit frequency when running, under the environment of the near room temperature that sets, carry out essence also resembling in the past Thin control. In addition, the miniaturization of compression function, lightweight can reduce cost.
In addition, aspect the of the present invention the 2nd in since aspect the of the present invention the 1st in, the refrigeration The agent compressor combines a pair of Vorticose scroll wrap the duty cryogen is compressed Scroll compressor is so except the effect of the 1st invention, can also improve minimum operating frequency The time the greasy property of bearing portion of compressor, improve the durability, reliable of coolant compressor The property. In addition, can also obtain the compressor that the pressure variation is little when high-frequency turns round, vibration is low.
In addition, aspect the of the present invention the 3rd in owing to will be higher than near the industrial power frequency In the compressor of frequency as minimum operating frequency, use the mixing system of HFC32 and HFC125 Cryogen is as the duty cryogen, so, can relax especially the leakage that causes owing to the use high-pressure refrigerant Let out the increase of loss. In addition, owing to use the mix refrigerant conduct of HFC32 and HFC125 The duty cryogen so can also improve the compressor performance of high-frequency one side, can make by frequency to produce The poor performance of coolant compressor for just, can the performance of compressor be connect in whole operating frequency district Be bordering on smoothly, more can improve the SEER of coolant compressor.
In addition, aspect the of the present invention the 4th in because in refrigerating circulatory device, cold-producing medium is pressed In the contracting machine, coolant compressor is except when starting, the running that has regulation when running well Frequency makes the low-limit frequency of above-mentioned operating frequency be higher than near the frequency of industrial power frequency, by The frequency that changes driving power carries out variable speed drives, so, can improve refrigerating circulatory device SEER. In addition, by miniaturization and is installed coolant compressor, can make kind of refrigeration cycle The device miniaturization and can reduce cost.
In addition, aspect the of the present invention the 5th in owing in aspect the of the present invention the 4th, use Scroll compressor is as coolant compressor, thus improved durability, reliability, in addition, Even when high-frequency turns round, also can change compressor little, that vibration is low by working pressure, so energy Acquisition reliability height, the refrigerating circulatory device that performance is good.
In addition, aspect the of the present invention the 6th in because aspect the of the present invention the 4th or the 5th side In the face, owing to be to adopt difluoromethane (HFC32) and pentafluoroethane (HFC125) are mixed Close the mix refrigerant that forms as the scroll compressor of duty cryogen, so, can relax by In the increase of the leakage loss of using high-pressure refrigerant to cause, and owing to use the high system of SEER The cryogen compressor is so can obtain the refrigerating circulatory device that performance is good, SEER is high.
Claims (6)
1. coolant compressor that in refrigeration cycle, use, carry out variable speed drives by the frequency that changes driving power, it is characterized in that: described coolant compressor is except when starting, the operating frequency that has regulation when running well makes the minimum operating frequency in described operating frequency district be higher than near the frequency of industrial power frequency.
2. coolant compressor according to claim 1 is characterized in that: coolant compressor is the scroll compressor that a pair of Vorticose scroll wrap is combined the duty cryogen is compressed.
3. coolant compressor according to claim 1 and 2 is characterized in that: adopt the mix refrigerant that difluoromethane (HFC32) and pentafluoroethane (HFC125) are mixed as the duty cryogen.
4. refrigerating circulatory device that coolant compressor, heat exchanger, expansion mechanism etc. is coupled together with pipeline, it is characterized in that: described coolant compressor is except when starting, the operating frequency that when running well, has regulation, make the minimum operating frequency in described operating frequency district be higher than near the frequency of industrial power frequency, by changing the frequency of driving power, carry out variable speed drives.
5. coolant compressor according to claim 4 is characterized in that: coolant compressor is the scroll compressor that a pair of Vorticose scroll wrap is combined the duty cryogen is compressed.
6. according to claim 4 or 5 described coolant compressors, it is characterized in that: adopt the mix refrigerant that difluoromethane (HFC32) and pentafluoroethane (HFC125) are mixed as the duty cryogen.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8182310A JPH1026425A (en) | 1996-07-11 | 1996-07-11 | Refrigerant compressor driving at variable speed and refrigeration cycle device provided with the same refrigerant compressor |
| JP182310/96 | 1996-07-11 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1174294A true CN1174294A (en) | 1998-02-25 |
Family
ID=16116070
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97114523A Pending CN1174294A (en) | 1996-07-11 | 1997-07-10 | Refrigerant compressor and refrigeration cycle device equipped with the same |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPH1026425A (en) |
| KR (1) | KR980010247A (en) |
| CN (1) | CN1174294A (en) |
| GB (1) | GB2315299B (en) |
| IT (1) | IT1292487B1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100335782C (en) * | 2003-02-12 | 2007-09-05 | 松下电器产业株式会社 | Electric compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101736861B1 (en) * | 2010-05-12 | 2017-05-17 | 엘지전자 주식회사 | Scorll compressor |
| JP5772811B2 (en) * | 2012-12-28 | 2015-09-02 | ダイキン工業株式会社 | Refrigeration equipment |
| JP6269756B1 (en) * | 2016-09-02 | 2018-01-31 | ダイキン工業株式会社 | Refrigeration equipment |
| WO2023223467A1 (en) * | 2022-05-18 | 2023-11-23 | 三菱電機株式会社 | Air conditioning device |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0683590B2 (en) * | 1984-07-04 | 1994-10-19 | 株式会社東芝 | Air conditioner |
| DE3642729C3 (en) * | 1986-12-13 | 1997-05-07 | Grundfos Int | Pump unit for conveying liquids or gases |
| JPH02118362A (en) * | 1988-10-26 | 1990-05-02 | Hitachi Ltd | Capacity control air conditioner |
| US5316074A (en) * | 1990-10-12 | 1994-05-31 | Nippondenso Co., Ltd. | Automotive hair conditioner |
| JP3167372B2 (en) * | 1991-10-11 | 2001-05-21 | 東芝キヤリア株式会社 | Air conditioner |
| JPH05256299A (en) * | 1992-03-13 | 1993-10-05 | Toshiba Corp | Blower |
-
1996
- 1996-07-11 JP JP8182310A patent/JPH1026425A/en active Pending
-
1997
- 1997-07-04 IT IT97MI001600A patent/IT1292487B1/en active IP Right Grant
- 1997-07-10 GB GB9714547A patent/GB2315299B/en not_active Expired - Fee Related
- 1997-07-10 KR KR1019970032022A patent/KR980010247A/en not_active Application Discontinuation
- 1997-07-10 CN CN97114523A patent/CN1174294A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100335782C (en) * | 2003-02-12 | 2007-09-05 | 松下电器产业株式会社 | Electric compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| ITMI971600A1 (en) | 1999-01-04 |
| IT1292487B1 (en) | 1999-02-08 |
| GB2315299B (en) | 1999-02-17 |
| JPH1026425A (en) | 1998-01-27 |
| GB9714547D0 (en) | 1997-09-17 |
| ITMI971600A0 (en) | 1997-07-04 |
| KR980010247A (en) | 1998-04-30 |
| GB2315299A (en) | 1998-01-28 |
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