CN1721786A - Air conditioner and rotary compressor thereof - Google Patents
Air conditioner and rotary compressor thereof Download PDFInfo
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- CN1721786A CN1721786A CNA2004100119784A CN200410011978A CN1721786A CN 1721786 A CN1721786 A CN 1721786A CN A2004100119784 A CNA2004100119784 A CN A2004100119784A CN 200410011978 A CN200410011978 A CN 200410011978A CN 1721786 A CN1721786 A CN 1721786A
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- compressing member
- compressor
- low pressure
- pressure
- speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-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
- F04C18/34—Rotary-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
- F04C18/356—Rotary-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
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides an air conditioner which is equipped with the refrigeration cycle of a rotary compressor and a control part for controlling the rotation of the compressor. The rotary compressor is equipped with a rotating compression element which is provided with both a low voltage compression element and a high voltage compression element and an intermediate space which is connected with the low voltage compression element and the high voltage compression element. And the phase difference of the compression process of the low voltage compression element and the high voltage compression element is 180 degrees. The coefficient of performance (COP) is improved in the whole action range of the air conditioner carrying a rotary second grade compressor through maintaining the ratio of the volume (Vm) of the intermediate space to the stroke volume (V1) of the low voltage compression element within a specific range compared with the minimum rotation speed (Nmin) used by the compressor and the maximum rotation speed (Nmax) used by the compressor. Therefore, coefficient of high performance can be obtained within the rotation range.
Description
Technical field
The present invention relates to a kind of air regulator with freeze cycle.
Background technology
In the past, as employed rotary 2 stage compressors in the freeze cycle, known for example had that the spy opens the structure of being announced in the clear 60-128990 communique (hereinafter referred to as patent documentation 1).The compressor of the conventional art in the inside of closed container, has the motor that is made of stator and rotor on top.The rotating shaft that is connected with motor has 2 eccentric parts.As the compressing mechanism corresponding,, be provided with high pressure successively in the inside of closed container with compressing member and low pressure compressing member from motor side with these eccentric parts.
Each compressing member utilizes the off-centre rotation of the eccentric part of rotating shaft to make cylinder carry out revolution motion.180 ° of the phase phasic differences of these eccentric parts, the phase difference of the compression section of each compressing member are 180 °.That is, the compression section phase place of 2 compressing members is opposite.
Gas refrigerant as the action fluid is inhaled under low pressure Ps in the low pressure usefulness compressing member, and being compressed and raising is that Pm is pressed in the centre.The gas refrigerant of pressing Pm to be ejected in the centre is sprayed to intermediate flow passage.Then, the middle gas refrigerant of Pm of pressing is inhaled into high pressure with in the compressing member through intermediate flow passage, be compressed into high pressure P d.
, after the device condensation that is condensed, be inflated mechanism and be decompressed to low pressure from the gas refrigerant of the high pressure P d of compressor ejection., in evaporimeter evaporate, become gas refrigerant and be inhaled into low pressure with in the compressing member thereafter.
Patent documentation 1: the spy opens clear 60-128990 communique (the 5th page, the 1st figure)
Rotary 2 stage compressors described in conventional art, owing to compare with the compressor of single-stage, the pressure ratio of each compressing member (=ejection pressure/suction pressure) diminishes, so the reductions such as leakage loss of cold-producing medium.Reduce the input electric energy of compressor thus, the coefficient of performance COP of air regulator (coefficient of performance) improves.Here, so-called coefficient of performance COP is meant, with the refrigeration of input electric energy deacration adjuster or the value of the warm ability of system.
But in rotary 2 stage compressors in the past, high pressure uses compressing member and low pressure with the pressure between the compressing member, promptly is inhaled into the pressure meeting change of high pressure with the refrigerant gas the compressing member from low pressure with the compressing member ejection.Low pressure is accompanied by the variation of angle (hereinafter referred to as the crank angle) that eccentric part leaves the eccentric direction of fin (vane) with the pressure P 1 of the discharge chambe of compressing member, presses Pm in the middle of being compressed into from low pressure Ps.Connect low pressure and use the pressure (hereinafter referred to as intermediate space pressure P 3) in the space of compressing member with compressing member and high pressure, because the phase difference of the off-centre of 2 compressing members rotation is 180 °, therefore (the low pressure compression section of compressing member) under the situation that the ejection valve of low-pressure side compressing member cuts out, because the high pressure suction of compressing member, the gas refrigerant deficiency is pressed Pm in the middle of being lower than.On the contrary, under the situation that low pressure is opened with the ejection valve of compressing member, because the ejection of low-pressure side compressing member, gas refrigerant is too much, presses Pm in the middle of intermediate space pressure P 3 is higher than.So, from low pressure with ejection the compressing member after soon the intermediate space pressure P 3 of refrigerant gas change with respect to the crank angle corrugate.
In addition, from low pressure with ejection the compressing member after soon in the middle of press Pm because by intermediate space, therefore with the suction of compressing member not long ago at high pressure, the slow Δ τ of phase place.Even the phase difference of each compressing member is set at 180 °, 2 stages ground carries out the rotating speed of compressor for compressing because with 2 compressing members of rotating shaft driving,, also can produce the rising sequential of suction intermediate space pressure P 3 not long ago and the suction of discharge chambe and begin the consistent of sequential with in the compressing member at high pressure.At this moment, because high pressure is with the compression initiation pressure height of compressing member, so the input of compressor increases severely, and causes the reduction of compression efficiency, caused using the reduction of coefficient of performance COP of the air regulator of rotary 2 stage compressors then.
Summary of the invention
The objective of the invention is to, solve described problem, be implemented in the air regulator that can obtain high-performance coefficient COP in its operating range.In addition, other purpose of the present invention is that realization can prevent rotary 2 stage compressors that high pressure reduces with the performance in the compressing member.
In addition, in order to reach purpose of the present invention, air regulator of the present invention possesses: with rotary compressor, condensation from the condenser of the gas refrigerant of the high pressure of this rotary compressor ejection, freeze cycle that the cold-producing medium that is condensed expansion mechanism that is expanded to low pressure and the evaporimeter that makes dilated cold-producing medium evaporation are connected successively, and the control part of controlling the rotating speed of described compressor; By this control part in the front and back of the rotary speed area of regulation to the control of turning round of described compressor, wherein above-mentioned rotary compressor possesses in closed container: motor, by this Motor Drive and have the rotating shaft of 2 eccentric parts, rotate the rotation compressing member that the low pressure of the cylinder that carries out revolution motion is provided with every demarcation strip with the compressing member folder with compressing member and high pressure with in discharge chambe, having the off-centre of utilizing described eccentric part respectively, the intermediate space that is connected with the discharge chambe of compressing member with the discharge chambe of compressing member and high pressure with described low pressure and separates with the inner space of described closed container, and described low pressure is approximately 180 ° with compressing member and described high pressure with the phase difference of the compression section of compressing member.
In addition, in order to reach described purpose, air regulator of the present invention possesses: with rotary compressor, condensation from the condenser of the gas refrigerant of the high pressure of this rotary compressor ejection, freeze cycle that the cold-producing medium that is condensed expansion mechanism that is expanded to low pressure and the evaporimeter that makes dilated cold-producing medium evaporation are connected successively, and the control part of controlling the rotating speed of described compressor; This control part has the minimum speed of the running rotating speed that stores described compressor and the storage part of maximum (top) speed, from the minimum speed and maximum (top) speed of described compressor, with the coefficient of performance (COP) of avoiding making this air regulator rotation speed operation for the rotating speed (Ns) of minimum described compressor, wherein above-mentioned rotary compressor possesses in closed container: motor, by this Motor Drive and have the rotating shaft of 2 eccentric parts, rotate the rotation compressing member that the low pressure of the cylinder that carries out revolution motion is provided with every demarcation strip with the compressing member folder with compressing member and high pressure with in discharge chambe, having the off-centre of utilizing described eccentric part respectively, the intermediate space that is connected with the discharge chambe of compressing member with the discharge chambe of compressing member and high pressure with described low pressure and separates with the inner space of described closed container, and described low pressure is approximately 180 ° with compressing member and described high pressure with the phase difference of the compression section of compressing member.
In addition, the ratio V1/Vm of the swept volume V1 of the described low pressure usefulness compressing member of rotary compressor and the volume V m of described intermediate space, the minimum of described rotary compressor running rotating speed is being made as Nmin[1/ second] and the transport maximum rotating speed is made as Nmax[1/ second] time, be preferably (V1/Vm)≤1.4 * 10
-5Nmin
2And 2.6 * 10
-5Nmax
2≤ (V1/Vm).
In addition, in the air regulator of the present invention, first expansion mechanism that described expansion mechanism will expand by being decompressed to intermediate pressure by the cold-producing medium of described condenser condenses, make the cold-producing medium expansion of the intermediate pressure that is expanded by this first expansion mechanism and second expansion mechanism formation of supplying with to described evaporimeter, possesses the gas-liquid separator that is connected with described second expansion mechanism with described first expansion mechanism and gas refrigerant is separated with liquid refrigerant, the injection stream that is communicated with this gas-liquid separator and described intermediate space and gas refrigerant is shunted, the flow path cross sectional area of this injection stream gets final product less than the minimum flow path cross sectional area of described intermediate space.
In order to reach other purpose of the present invention, rotary 2 stage compressors of the present invention are provided with motor in closed container, by this Motor Drive and have the rotating shaft of 2 eccentric parts, rotate the rotation compressing member that the low pressure of the cylinder that carries out revolution motion is provided with every demarcation strip with the compressing member folder with compressing member and high pressure with in discharge chambe, having the off-centre of utilizing described eccentric part respectively, with the intermediate space that is connected with the discharge chambe of compressing member with the discharge chambe of compressing member and high pressure with described low pressure and separates with the inner space of described closed container, described low pressure is approximately 180 ° rotary compressor with the phase difference of the compression section of compressing member with compressing member and described high pressure, utilize the minimum running rotational speed N min[1/ second of this compressor] and transport maximum rotational speed N max[1/ second], the volume V m of described intermediate space and low pressure are made as (V1/Vm)≤1.4 * 10 with the ratio V1/Vm of the swept volume V1 of compressing member
-5Nmin
2And 2.6 * 10
-5Nmax
2≤ (V1/Vm).The phase difference of the compression section of each compressing member also can adopt with 180 ° be the center, from 150 ° to 210 ° scope.
According to the present invention, can obtain to use the air regulator that can prevent rotary 2 stage compressors that the performance in the high pressure usefulness compressing member reduces and can in whole actuating ranges, realize high-performance coefficient COP.
Description of drawings
Fig. 1 is the profilograph of rotary 2 stage compressors of an embodiment of the invention.
Fig. 2 has been to use the pie graph of air regulator of rotary 2 stage compressors of an embodiment of the invention.
Fig. 3 is the figure of the pressure oscillation of explanation each discharge chambe of 2 stage compressors and intermediate space.
Fig. 4 is the figure of the relation of expression rotational speed N and coefficient of performance COP.
Fig. 5 is the figure of the relation of (V1/Vm) of compressor of expression an embodiment of the invention and rotational speed N s.
Fig. 6 is the figure of the relation of the rotational speed N of compressor of expression an embodiment of the invention and coefficient of performance COP.
Fig. 7 is the block diagram of control circuit of the air regulator of expression an embodiment of the invention.
Fig. 8 is the figure of the relation of the rotational speed N of air regulator of expression an embodiment of the invention and coefficient of performance COP.
Fig. 9 is other the pie graph of air regulator of embodiment of the present invention.
Among the figure: 1-compressor, 2-rotating shaft, 5-eccentric part, 10-cylinder, 11-cylinder, 14-motor, 20-compressing member, 23-discharge chambe, 25-suction inlet, 32-intermediate space.
The specific embodiment
Use accompanying drawing that embodiments of the present invention are described.At first, among Fig. 1, compressor 1 has the closed container 13 that is made of bottom 21, cap 12 and tube portion 22.Above closed container 13 inside, be provided with motor 14 with stator 7 and rotor 8.The rotating shaft 2 that is connected with motor 14 has 2 eccentric parts 5, is supported by base bearing 9 and supplementary bearing 19.On this rotating shaft 2, from motor 14 sides, stack gradually base bearing 9 with the 9a of end plate portion, high pressure with compressing member 20b, intermediate section dividing plate 15, low pressure with compressing member 20a and have the supplementary bearing 19 of the 19a of end plate portion, integrated by Connection Elements such as bolt (not shown).
The 9a of end plate portion is fixed on the inwall of a portion 22 by welding, and supports main shaft holds 9.The 19a of end plate portion is supported by supplementary bearing 19.And, though present embodiment also can be utilized to be weldingly fixed in the portion 22 with stiff end board 19a such as bolts.
Each compressing member 20a and the following formation of 20b.Low pressure constitutes discharge chambe 23a with compressing member 20a with supplementary bearing 19, cylinder 10a cylindraceous, the cylinder cylindraceous 11 that is entrenched in the periphery of eccentric part 5a, intermediate section dividing plate 15.In addition, high pressure constitutes discharge chambe 23b with compressing member 20b with base bearing 9, cylinder 10b cylindraceous, the cylinder cylindraceous 11 that is entrenched in the periphery of eccentric part 5b, intermediate section dividing plate 15.These discharge chambes 23a, 23b, are divided into discharge chambe 23a, 23b compression stroke and suck the space while contacting the motion of advancing and retreat on the periphery that cooperates the cylinder 11a, the 11b that rotate with the eccentric motion of eccentric part 5a, 5b by the flat fin 18 that is connected with the elastic force applying mechanism of helical spring and so on.
Compressing member 20 carries out the off-centre rotation and head roll 11 by eccentric part 5.As shown in Figure 1,180 ° of the phasic differences mutually of eccentric part 5a and eccentric part 5b, the phase difference of the compression section of compressing member 20a, 20b is 180 °.That is, the compression section phase place of 2 compressing members is opposite.
To represent as the mobile arrow of gas refrigerant of action fluid with Fig. 1.The gas refrigerant of the low pressure Ps that passes pipe arrangement 31 and supply with is inhaled into low pressure with in the compressing member 20a from the suction inlet 25a that is connected with pipe arrangement 31, carries out the off-centre rotation by cylinder 11a, presses Pm in the middle of being compressed into.Ejection valve 28a that will opening when the pressure in the discharge chambe 23a reaches predefined pressure presses the gas refrigerant of Pm to spray to the ejection space 33 that is communicated with ejiction opening 26a after the Pm under shed is pressed in the centre in the middle of reaching.This ejection space 33 be by supplementary bearing 19 and outer cover 35 and with the space that the confined space 29 in the closed container 13 is isolated, press Pm in the middle of its internal pressure reaches basically.Intermediate flow passage 30 is the streams with ejection space 33 and suction inlet 25b connection.The space of a connection that is made of ejection space 33 and intermediate flow passage 30 and suction inlet 25b is to separate with closed container 13 and internal pressure is pressed the intermediate space 32 (among Fig. 1 by the part of dotted line) of Pm in the middle of being.So, by after 33 ejections of ejection space,, reach the suction inlet 25b that is communicated with the 23b of balancing gate pit of high-pressure element 20b through intermediate flow passage 30 from the gas refrigerant of the pressure P m of the ejiction opening 26a ejection of ejection valve 28a opening.
Then, being inhaled into high pressure through intermediate flow passage 30 from suction inlet 25b presses the gas refrigerant of Pm to be compressed into high pressure P d owing to cylinder 11b revolves round the sun in the middle of in the compressing member 20b.Ejection valve 28b that will opening when the pressure in the discharge chambe 23b reaches predefined pressure is behind high pressure P d under shed, and gas refrigerant will be from ejiction opening 26b to confined space 29 ejections as the inner space of closed container 13.Sprayed by bleed pipe 27 by the space of motor 14 by gas refrigerant to this confined space 29b ejection.
To use the formation of the freeze cycle of rotary 2 stage compressors illustrated in fig. 1 to be illustrated among Fig. 2.The gas refrigerant of the high pressure P d of ejection is inflated mechanism 4 and is decompressed to low pressure Ps after device 3 condensations that are condensed from compressor 1.Thereafter, evaporation becomes gas refrigerant in evaporimeter 16, is sucked low pressure from suction inlet 25a with in the compressing member 20a.The gas refrigerant of compressor 1 the process that moves in each discharge chambe 23 as use Fig. 1 illustrated.To use Fig. 2 below, the relation of each discharge chambe 23a, 23b will be described.
Rotary compressor along with the crank angle of eccentric part 5a is that benchmark changes with the position of fin 18, and changes the volume of discharge chambe 23, carries out the compression of cold-producing medium.Among this Fig. 2, low pressure is positioned at the position of 180 ° of crank angles with compressing member 20a.Separated by fin 18, in discharge chambe 23a, have 2 spaces, be i.e. compression stroke and suction space.On the other hand, the crank angle of high pressure compressed element 20b is 0 ° (360 °), with low pressure compressing member 20a 180 ° the phase place that staggers.The state of this high pressure compressed element 20b is that the volume of compression stroke reaches minimum state basically in the middle of two spaces that exist in low pressure compressing member 20a, is that the volume that sucks the space reaches maximum state basically.That is, to be high pressure compressed element 20b with suction inlet 25b moment ground as the part of intermediate space 32 disconnect is connected, is communicated with before soon state and suck the space with the next one.
To change the continuous pressure of each compressing member 20 of rotary 2 stage compressors 1 below and describe.Among Fig. 3, the pressure P 1 of hypomere and intermediate space pressure P 3 are represented the variation of low pressure with the pressure of the variation of the pressure of compressing member 20a and intermediate space 32 respectively.The pressure of the central portion of pressure P 3 ' the expression intermediate space 32 in the stage casing of Fig. 3 changes.In addition, pressure P 3 " and pressure P 2 represents respectively that the pressure of the suction inlet 25b of intermediate space 32 changes and high pressure with the variation of the pressure in the discharge chambe 23b of compressing member 20b.
Shown in the hypomere of Fig. 3, low pressure is accompanied by the variation of crank angle with the pressure P 1 of the discharge chambe 23a of compressing member 20a, presses Pm in the middle of changing to from low pressure Ps.By low pressure with the intermediate space pressure P 3 of compressing member 20a compression because the phase difference of each compressing member 20 is 180 °, therefore when low pressure is closed with the ejection valve 28a of compressing member 20a (compression section of low pressure usefulness compressing member 20a), because high pressure is with the suction of compressing member 20b, gas refrigerant is not enough and reduce (with reference to hypomere, the pressure P 3 of Fig. 3).On the contrary, when ejection valve 28a opens (the low pressure ejection operation of compressing member 20a), after the intermediate space pressure P 3 of pressure Pm rises to the middle Pm of pressure in the middle of being lower than, owing to the ejection of low pressure with compressing member 20a, gas refrigerant is too much, thereby intermediate space pressure P 3 presses Pm to begin to rise from the centre.So, after the ejection of discharge chambe 23a soon in the middle of press Pm to change with respect to the crank angle corrugate.Here, the dotted line of Fig. 3 is pressed Pm in the middle of being, is the mean value of intermediate space pressure P 3.
In addition, after the ejection of discharge chambe 23a soon in the middle of press Pm because by intermediate space 32, therefore not long ago in the suction of discharge chambe 23b, the slow Δ τ of phase place.So,, because the running rotating speed of compressor 1, also can produce consistent that the suction of the rising of suction intermediate space pressure P 3 not long ago and discharge chambe 23b begins in compressing member 20b sometimes at high pressure even the phase difference of each compressing member 20 is set at 180 °.At this moment, because the compression initiation pressure P3 of discharge chambe 23b is higher, so the input of compressor sharp increase, cause the reduction of compression efficiency.In addition, when making compressor operation, also can cause using the reduction of coefficient of performance COP of the refrigerating plant of this compressor with the rotating speed that brings this kind state.
This high pressure depends on the rotational speed N of the circular flow of cold-producing medium and volume V m of intermediate space 32 (hereinafter referred to as middle volume) and compressor with the interference of the suction phase place at interval of the rise interval of the intermediate space pressure P 3 among the compressing member 20b and gas refrigerant.Because the circular flow of cold-producing medium and low pressure are roughly proportional with swept volume V1 and the rotational speed N of compressing member 20a, therefore the performance reduction that is caused by interference uses swept volume V1, the rotational speed N of compressing member relevant with middle volume V m, low pressure, forms the characteristic of Fig. 4.
The transverse axis of Fig. 4 is a rotational speed N, and the longitudinal axis is the coefficient of performance COP of air regulator.To use the coefficient of performance COP of the air regulator of rotary 2 stage compressors 1 to represent with C2.Among Fig. 4, the coefficient of performance COP of single-stage compressor is also represented simultaneously with C1.
The coefficient of performance COP of single-stage compressor is accompanied by the increase of rotational speed N and has maximum, reduces lentamente thereafter.In 2 stage compressors 1, coefficient of performance COP is roughly the same with regard to maximum for the dependence of rotational speed N.On the whole, the coefficient of performance COP of 2 stage compressors 1 increases.But, with respect to specific the low pressure swept volume of compressing member and the ratio (V1/Vm) of middle volume, specific rotational speed N s with previous described high pressure amplifies with the interference of the phase place among the compressing member 20b expresses coefficient of performance COP and reaches minimizing characteristic.The reduction of this performance is nearly about 3 to 8%, and the performance of air regulator is reduced significantly.Scope basis that performance reduces and the comparison of the coefficient of performance COP of the compressor of single-stage as rotational speed N, are the scope of center from 0.85Ns to 1.15Ns with specific rotation speeds Ns.
Shown in the dotted line of Fig. 4, when changing specific volume than (V1/Vm), specific rotation speeds Ns changes.This is because because when specific volume changes than (V1/Vm), phase delay delta τ promptly changes, so the interference state that the suction of the change of intermediate space pressure P 3 and discharge chambe 23b begins the interval changes.Here, specific rotation speeds Ns as shown in Figure 4, specific volume than (V1/Vm) for the domination parameter, can ignore the influence of pressure condition.
So, be suitable for air regulator of the present invention not the rotating speed of the front and back that comprise specific rotational speed N s at least, coefficient of performance COP turns round in than the also low rotary speed area of the coefficient of performance COP of single-stage compressor.Specifically, improve the rotating speed of 2 stage compressors, surmount the maximum of coefficient of performance COP after, cross specific rotary speed area with the in fact very short time, make it speedup to the rotating speed that surpasses this rotary speed area.When from state, with than the lower rotation speed operation of this rotary speed area the time, change rotating speed according to the mode of crossing this rotary speed area with time shorter equally than other zone with the rotation speed operation that surpasses this rotary speed area.By carrying out the rotating speed control of 2 stage compressors like this, just can greatly reduce the duration of runs in the rotary speed area that coefficient of performance COP reduces, thereby can improve the performance of air regulator.
Use accompanying drawing that an embodiment of the invention are described more specifically below.For example in rotary 2 stage compressors 1, use cold-producing medium R410A as the action fluid, and with it as the compressor that uses in the air regulator.At this moment, the rotational speed N of compressor 1 is by Frequency Converter Control, and the ratio of maximum (top) speed Nmax, the minimum speed Nmin of action is more than 1.4.
The basic formation of rotary 2 stage compressors 1 of present embodiment as shown in Figure 1.By minimum speed Nmin[1/ second with respect to this compressor 1 of running] and maximum (top) speed Nmax[1/ second], middle volume V m and low pressure are made as (V1/Vm)≤1.4 * 10 with the specific volume of the swept volume V1 of compressing member 20a than (V1/Vm)
-5Nmin
2, 2.6 * 10
-5Nmax
2≤ (V1/Vm), then can when being equipped on compressor 1 on the air regulator, in whole running rotating speeds, coefficient of performance COP be improved.Here, for the situation of cold-producing medium R410A, though need the condition of the ratio (Nmax/Nmin)＞1.4 of rotating speed, this condition is general condition in the air regulator with the rotating speed of Frequency Converter Control compressor.In the compressor 1 of present embodiment, specifically, adopt (Nmax/Nmin)=6, (V1/Vm)=2.6 * 10
-5Nmax
2
Describe for the relation of described specific volume than (V1/Vm) and minimum and maximum compression machine rotating speed.At first, as shown in Figure 4, in the specific volume of rotary 2 stage compressors than (V1/Vm) with make coefficient of performance COP set up dependency relation among the minimum specific rotation speeds Ns.Among Fig. 5, the expression specific volume is than the relation of (V1/Vm) and specific rotation speeds Ns.As shown in Figure 5, both relations can be used Ns=230 (V1/Vm)
0.5Be similar to, specific rotation speeds Ns changes than (V1/Vm) corresponding to specific volume.In addition, as shown in Figure 4, because in the scope from 0.85Ns to 1.15Ns, performance reduces, so the specific volume of compressor 1 adopts suitable with Ns=1.18Nmax (Nmax=0.85Ns) 2.6 * 10 than the higher limit of (V1/Vm)
-5Nmax
2, so that do not reduce in the following performance of Nmax.
On the contrary, the specific volume of compressor 1 is suitable with Ns=0.87Nmin (Nmin=1.15Ns) 1.4 * 10 than the lower limit of (V1/Vm)
-5Nmin
2, not reduce in the above performance of Nmin.When their relation is represented than (V1/Vm) with specific volume, then be (V1/Vm)≤1.4 * 10
-5Nmin
2, 2.6 * 10
-5Nmax
2≤ (V1/Vm).
Among Fig. 6, the rotational speed N of the compressor 1 of expression present embodiment and the relation of the coefficient of performance COP of the air regulator that has carried this compressor 1.Compressor 1 is owing to be made as 2.6 * 10 with specific volume than (V1/Vm)
-5Nmax
2, therefore making coefficient of performance COP is that minimum rotational speed N s just becomes 1.18Nmax (Nmax=0.85Ns).Till employed maximum (top) speed Nmax, the interference of the phase place among the discharge chambe 23b is suppressed, thereby compressor 1 is moved expeditiously.
In this Fig. 6, will be as the specific volume of the application examples of present embodiment than (V1/Vm)=1.4 * 10
-5Nmin
2Characteristic dot.At this moment, on the contrary, make coefficient of performance COP reach minimum rotational speed N s and become 0.87Nmin (Nmin=1.15Ns).From this application examples, can see, in the whole actuating ranges more than employed minimum speed Nmin, compressor 1 is moved expeditiously.
Use Fig. 7 and Fig. 8 to describe below.The air regulator of an embodiment of the invention is to control on the basis of running to maximum (top) speed in the minimum speed from compressor, study with the relation of the volume (Vm) of the intermediate space between the compressing member rotational speed N s with compressing member and high pressure with the swept volume (V1) of compressing member, low pressure according to low pressure the compressor of the coefficient of performance COP that considered air regulator, rotary 2 stage compressors 1 of (V1/Vm) of regulation are moved with minimum speed Nmin≤Ns≤maximum (top) speed Nmax, thereby improved the device of the versatility of design.That is, purpose is, even under the different situation of maximum capacity, the minimum ability of air regulator, also can use identical rotary 2 stage compressors 1 to improve coefficient of performance COP.
Though the formation of the air regulator of present embodiment is identical with Fig. 1, in the control of compressor 1 and its rotational speed N, feature is arranged.
The control circuit of the rotational speed N of compressor 1 is illustrated among Fig. 7.The user of air regulator imports the indoor temperature or the setting value of humidity or air quantity from indicating devices such as remote controller or input terminal (not shown).The signal receiving part 201 of control circuit receives this input signal.At the input signal that signal receiving part 201 conversion are received, become the control signal of the decompression amount of expansion mechanism or blower speed and to the control signal of compressor 1 and send.
Control signal to compressor 1 is the command value T of indoor temperature specifically
*, transmitted downstream with poor Δ T from the measured value that is arranged on the Temperature Detector 202 on the indoor set (not shown).Thereafter, according to roughly with the proportional mode of Δ T, carry out transformation of speed with transformation of speed portion 203, transmit tach signal Δ N.Δ N with from the measured value N's of revolution detector 204 with become tach signal N
*
In the 1st judging part 205, according to the minimum running rotating speed and the transport maximum rotating speed that are stored in the compressor 1 in the not shown storage part, as tach signal N
*More than the 0.85Ns and when 1.15Ns is following, in the 2nd judging part 206, carry out judgement to Δ N.Specifically, more than 0, promptly increase under the situation of rotational speed N, adopt N at Δ N
*The 1.17Ns that=1.15Ns is above, promptly reduces under the situation of rotational speed N below 0 at Δ N, adopts and compares N
*The 0.83Ns that=0.85Ns is littler comes figure signal.In the 1st judging part 205, as tach signal N
*During less than 0.85Ns or greater than 1.15Ns, do not carry out tach signal N
*Conversion.Have in the air regulator of present embodiment of this control circuit, make compressor 1 with these tach signals N
*Action.Here, N
*=1.17Ns, N
*=0.83Ns considers the control sensitivity of the detection error of temperature or rotating speed or rotating speed and the value of 1.15Ns, 0.85Ns having been carried out increase and decrease.
Like this in the air regulator of Kong Zhi present embodiment, as shown in Figure 8, actuating range will be less than 0.85Ns (action A) or greater than 1.15Ns (action B), in the minimum Ns that performance is reduced (0.85Ns≤rotational speed N≤1.15Ns) compressor 1 is moved.So therefore the air regulator of an embodiment of the invention can realize the high performance in whole operating ranges owing to can use 2 grades of formula compressors 1 of rotation expeditiously.
Below other the embodiment that is suitable for air regulator of the present invention is described.This air regulator uses spraying cycle.As shown in Figure 9, in condenser 3, after the condensation, in first expansion mechanism 4, expand, press Pm in the middle of pressure is depressurized to from refrigerant gas as the high pressure P d of ejection 2 grades of formula compressors 1 of rotation of an embodiment of the invention.Refrigerant gas after this is depressurized is separated into gas and liquid in gas-liquid separator 6.Separated liquid refrigerant is further depressurized to low pressure Ps in the 2nd expansion mechanism 4 in the downstream that is positioned at gas-liquid separator 6 after, evaporation becomes gas refrigerant in evaporimeter 16.The gas refrigerant of low pressure Ps is sucked low pressure with in the compressing member 20a from suction inlet 25a, the cylinder 11a that is entrenched on the eccentric part 5a revolves round the sun, thereby presses Pm in the middle of being compressed into, to intermediate space 32 ejections.
The gas refrigerant of intermediate space 32 with import from the injection stream 17 that is communicated with intermediate flow passage 30 with gas-liquid separator 6 in the middle of press the gas refrigerant of Pm to mix., by the cylinder 11b that be entrenched in eccentric part 5b on revolve round the sun, be inhaled into high pressure from suction inlet 25b and in the middle of in the compressing member 20b, press the gas refrigerant of Pm to be compressed into high pressure Pd, from bleed pipe 27 ejections thereafter.
Therefore this kind spraying cycle has reduced the unnecessary circular flow to low-pressure side compressing member 20a, thereby has reduced compression work owing to gas refrigerant shunting in evaporimeter 16 that heat transfer property is low, has improved the coefficient of performance COP of air regulator.In addition, also can adopt the following formation that can switch, promptly, in the way of spraying cycle stream 17, the two-way valve 34 that opens and closes stream 17 is set, when opening two-way valve 34, just become spraying cycle, when closing two-way valve 34, just become common freeze cycle shown in Figure 2.
In the air regulator of present embodiment, make the minimum flow path cross sectional area of the flow path cross sectional area of injection stream 17 less than intermediate space 32.The minimum flow path cross sectional area of intermediate space 32 is flow path cross sectional areas (with reference to Fig. 1) of intermediate flow passage 32 and suction inlet 25b.Utilize present embodiment, can limit too much gas refrigerant from spraying the inflow and outflow of stream 17 to intermediate space 32.In addition, can greatly suppress the variation of the intermediate space 32 that causes by the internal volume that sprays stream 17.So, the phase delay delta τ of the middle Pm of pressure shown in Figure 3 is sprayed with changing.Therefore, just can make full use of the characteristic of compressor 1, obtain the effect of spraying cycle.
Claims (9)
1. air regulator is characterized in that possessing:
With rotary compressor, condensation from the condenser of the gas refrigerant of the high pressure of this rotary compressor ejection, freeze cycle that the cold-producing medium that is condensed expansion mechanism that is expanded to low pressure and the evaporimeter that makes dilated cold-producing medium evaporation are connected successively, and
Control the control part of the rotating speed of described compressor;
By this control part in the front and back of the rotary speed area of regulation to the control of turning round of described compressor,
Wherein above-mentioned rotary compressor possesses in closed container: motor, by this Motor Drive and have the rotating shaft of 2 eccentric parts, rotate the rotation compressing member that the low pressure of the cylinder that carries out revolution motion is provided with every demarcation strip with the compressing member folder with compressing member and high pressure with in discharge chambe, having the off-centre of utilizing described eccentric part respectively, the intermediate space that is connected with the discharge chambe of compressing member with the discharge chambe of compressing member and high pressure with described low pressure and separates with the inner space of described closed container, and described low pressure is approximately 180 ° with compressing member and described high pressure with the phase difference of the compression section of compressing member.
2. air regulator according to claim 1 is characterized in that, described control part is to remove the rotating speed of described rotary speed area with described compressor control.
3. air regulator according to claim 1, it is characterized in that, the ratio (V1/Vm) of the swept volume (V1) of the described low pressure usefulness compressing member of described rotary compressor and the volume (Vm) of described intermediate space, the minimum of described rotary compressor running rotating speed is being made as Nmin[1/ second], the transport maximum rotating speed is made as Nmax[1/ second] time, be (V1/Vm)≤1.4 * 10
-5Nmin
2And 2.6 * 10
-5Nmax
2≤ (V1/Vm).
4. according to claim 1, any described air regulator in 2 or 3, it is characterized in that, described expansion mechanism is by will be by first expansion mechanism of the cold-producing medium puffing of described condenser condenses to intermediate pressure, the cold-producing medium of the intermediate pressure that will be expanded by this first expansion mechanism expands and second expansion mechanism supplied with to described evaporimeter constitutes, possesses the gas-liquid separator that is connected with described second expansion mechanism with described first expansion mechanism and gas refrigerant is separated with liquid refrigerant, with the gas refrigerant zone of this gas-liquid separator and the injection stream of described intermediate space connection, this sprays the minimum flow path cross sectional area of the flow path cross sectional area of stream less than described intermediate space.
5. air regulator is characterized in that possessing:
With rotary compressor, condensation from the condenser of the gas refrigerant of the high pressure of this rotary compressor ejection, freeze cycle that the cold-producing medium that is condensed expansion mechanism that is expanded to low pressure and the evaporimeter that makes dilated cold-producing medium evaporation are connected successively, and
Control the control part of the rotating speed of described compressor;
This control part has the minimum speed of the running rotating speed that stores described compressor and the storage part of maximum (top) speed, from the minimum speed and maximum (top) speed of described compressor, with the coefficient of performance (COP) of avoiding making this air regulator rotation speed operation for the rotating speed (Ns) of minimum described compressor
Wherein above-mentioned rotary compressor possesses in closed container: motor, by this Motor Drive and have the rotating shaft of 2 eccentric parts, rotate the rotation compressing member that the low pressure of the cylinder that carries out revolution motion is provided with every demarcation strip with the compressing member folder with compressing member and high pressure with in discharge chambe, having the off-centre of utilizing described eccentric part respectively, the intermediate space that is connected with the discharge chambe of compressing member with the discharge chambe of compressing member and high pressure with described low pressure and separates with the inner space of described closed container, and described low pressure is approximately 180 ° with compressing member and described high pressure with the phase difference of the compression section of compressing member.
6. air regulator according to claim 5, it is characterized in that, described control part is according to the volume (Vm) of the intermediate space of the minimum speed of the running rotating speed of described compressor and maximum (top) speed and described rotary compressor and the low pressure relation with the ratio of the swept volume (V1) of compressing member, try to achieve the coefficient of performance (COP) that makes this air regulator rotating speed (Ns), to avoid the rotation speed operation of this rotational speed N s for minimum described compressor.
7. air regulator according to claim 6, it is characterized in that, the ratio (V1/Vm) of the swept volume (V1) of the described low pressure usefulness compressing member of described rotary compressor and the volume (Vm) of described intermediate space, the minimum of described rotary compressor running rotating speed is being made as Nmin[1/ second], the transport maximum rotating speed is made as Nmax[1/ second] time, be (V1/Vm)≤1.4 * 10
-5Nmin
2And 2.6 * 10
-5Nmax
2≤ (V1/Vm).
8. according to claim 5, any described air regulator in 6 or 7, it is characterized in that, described expansion mechanism is by will be by first expansion mechanism of the cold-producing medium puffing of described condenser condenses to intermediate pressure, the cold-producing medium of the intermediate pressure that will be expanded by this first expansion mechanism expands and second expansion mechanism supplied with to described evaporimeter constitutes, possesses the gas-liquid separator that is connected with described second expansion mechanism with described first expansion mechanism and gas refrigerant is separated with liquid refrigerant, with the gas refrigerant zone of this gas-liquid separator and the injection stream of described intermediate space connection, this sprays the minimum flow path cross sectional area of the flow path cross sectional area of stream less than described intermediate space.
9. rotary compressor, in closed container, possess: motor, by this Motor Drive and have the rotating shaft of 2 eccentric parts, rotate the rotation compressing member that the low pressure of the cylinder that carries out revolution motion is provided with every demarcation strip with the compressing member folder with compressing member and high pressure with in discharge chambe, having the off-centre of utilizing described eccentric part respectively, the intermediate space that is connected with the discharge chambe of compressing member with the discharge chambe of compressing member and described high pressure with described low pressure and separates with the inner space of described closed container, and described low pressure is approximately 180 ° with compressing member and described high pressure with the phase difference of the compression section of compressing member, it is characterized in that, when the minimum of this compressor running rotating speed is Nmin[1/ second], the transport maximum rotating speed is Nmax[1/ second] time, the ratio (V1/Vm) of the swept volume (V1) of low pressure usefulness compressing member and the volume (Vm) of described intermediate space is (V1/Vm)≤1.4 * 10
-5Nmin
2And 2.6 * 10
-5Nmax
2≤ (V1/Vm).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004204057A JP4719432B2 (en) | 2004-07-12 | 2004-07-12 | Air conditioner and rotary two-stage compressor used therefor |
| JP2004204057 | 2004-07-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1721786A true CN1721786A (en) | 2006-01-18 |
| CN100547318C CN100547318C (en) | 2009-10-07 |
Family
ID=35895768
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100119784A Expired - Fee Related CN100547318C (en) | 2004-07-12 | 2004-09-27 | Air regulator |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP4719432B2 (en) |
| KR (1) | KR100653815B1 (en) |
| CN (1) | CN100547318C (en) |
| MY (1) | MY137946A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101666314A (en) * | 2008-09-03 | 2010-03-10 | 富士通将军股份有限公司 | Injectible two-stage rotary compressor |
| CN101482117B (en) * | 2008-01-10 | 2013-03-06 | 富士通将军股份有限公司 | Two-stage rotary compressor |
| CN104632624A (en) * | 2013-12-25 | 2015-05-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-cylinder double-stage compressor |
| CN105587663A (en) * | 2015-12-29 | 2016-05-18 | 西安交通大学 | Vertical two-stage rotating compressor for refrigerator and work method of vertical two-stage rotating compressor |
| CN108138780A (en) * | 2015-09-29 | 2018-06-08 | 株式会社电装 | Motor compressor |
| CN106091455B (en) * | 2016-08-04 | 2018-07-10 | 青岛大学 | A kind of quasi- two stage compression refrigeration system of piston compressor intermediate injection |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009079492A (en) * | 2007-09-25 | 2009-04-16 | Fujitsu General Ltd | Two-stage rotary compressor |
| JP5253909B2 (en) * | 2008-07-25 | 2013-07-31 | 株式会社東芝 | Washing and drying machine |
| KR101528645B1 (en) * | 2009-04-09 | 2015-06-15 | 엘지전자 주식회사 | 2-stage rotary compressor |
| KR20130081107A (en) * | 2012-01-06 | 2013-07-16 | 엘지전자 주식회사 | Hemetic compressor |
| CN105298840B (en) * | 2015-11-23 | 2017-07-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Multi-cylinder Dual-level enthalpy adding compressor and air-conditioner, Teat pump boiler and control method |
| CN106382227A (en) * | 2016-11-18 | 2017-02-08 | 广东美芝制冷设备有限公司 | Multi-stage compression type rotary compressor and refrigerating circulating device provided with same |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2555464B2 (en) * | 1990-04-24 | 1996-11-20 | 株式会社東芝 | Refrigeration cycle equipment |
| JPH05256286A (en) * | 1992-03-13 | 1993-10-05 | Toshiba Corp | Multicylinder rotary compressor |
| JPH1082391A (en) * | 1996-07-19 | 1998-03-31 | Ishikawajima Harima Heavy Ind Co Ltd | Control device of two-stage screw compressor |
| JP2000087892A (en) * | 1998-09-08 | 2000-03-28 | Daikin Ind Ltd | Two-stage compressor and air conditioner |
| JP3389539B2 (en) | 1999-08-31 | 2003-03-24 | 三洋電機株式会社 | Internal intermediate pressure type two-stage compression type rotary compressor |
| JP2003021089A (en) * | 2001-07-03 | 2003-01-24 | Kobe Steel Ltd | Two-stage compression refrigerating machine, and its operating method |
| JP4024056B2 (en) | 2002-03-04 | 2007-12-19 | 三洋電機株式会社 | Rotary compressor |
| JP4045154B2 (en) * | 2002-09-11 | 2008-02-13 | 日立アプライアンス株式会社 | Compressor |
| JP4079736B2 (en) * | 2002-09-30 | 2008-04-23 | 三洋電機株式会社 | Refrigerant cycle equipment |
-
2004
- 2004-07-12 JP JP2004204057A patent/JP4719432B2/en not_active Expired - Fee Related
- 2004-09-24 KR KR1020040076732A patent/KR100653815B1/en active Pre-grant Review Request
- 2004-09-27 CN CNB2004100119784A patent/CN100547318C/en not_active Expired - Fee Related
- 2004-09-29 MY MYPI20044001A patent/MY137946A/en unknown
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101482117B (en) * | 2008-01-10 | 2013-03-06 | 富士通将军股份有限公司 | Two-stage rotary compressor |
| CN101666314A (en) * | 2008-09-03 | 2010-03-10 | 富士通将军股份有限公司 | Injectible two-stage rotary compressor |
| CN104632624A (en) * | 2013-12-25 | 2015-05-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-cylinder double-stage compressor |
| CN108138780A (en) * | 2015-09-29 | 2018-06-08 | 株式会社电装 | Motor compressor |
| CN105587663A (en) * | 2015-12-29 | 2016-05-18 | 西安交通大学 | Vertical two-stage rotating compressor for refrigerator and work method of vertical two-stage rotating compressor |
| CN106091455B (en) * | 2016-08-04 | 2018-07-10 | 青岛大学 | A kind of quasi- two stage compression refrigeration system of piston compressor intermediate injection |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20060039043A (en) | 2006-05-08 |
| MY137946A (en) | 2009-04-30 |
| KR100653815B1 (en) | 2006-12-05 |
| JP4719432B2 (en) | 2011-07-06 |
| CN100547318C (en) | 2009-10-07 |
| JP2006029085A (en) | 2006-02-02 |
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Effective date of registration: 20160901 Address after: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee after: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. Address before: Tokyo, Japan Patentee before: Hitachi Appliances, Inc. |
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Effective date of registration: 20180704 Address after: Tokyo, Japan Patentee after: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, Inc. Address before: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee before: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. |
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