CN1793754A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
- Publication number
- CN1793754A CN1793754A CN 200510093243 CN200510093243A CN1793754A CN 1793754 A CN1793754 A CN 1793754A CN 200510093243 CN200510093243 CN 200510093243 CN 200510093243 A CN200510093243 A CN 200510093243A CN 1793754 A CN1793754 A CN 1793754A
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- mentioned
- pipe arrangement
- compressor
- intermediate space
- pressure
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- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
Abstract
The invention relates to an air conditioner with freezing circular function. The object of the invention lies in improving efficiency of jet circulation. The air conditioner is characterized in that when pulse wavelength generated in the middle space of the suction side of a high pressure compression unit (20b) on the discharge side of a low-pressure compression unit (20a) in a rotary two-stage compressor (1) is set as Lambada, a section area reducing part (34) for reducing section area of the flow passage of a jet tube (17) is arranged in a position with a tubing distance of L from the joint part between the middle space (32) of the rotary two-stage compressor (1) and the jet tube (17) so as to improve COP; and L is equal to ((2n -1)/4 plus or minus 1/8)Lambada (wherein, n=1, 2, 3 ellipsis).
Description
Technical field
The present invention relates to a kind of air conditioner that possesses freeze cycle.
Background technology
Known for everyone as seeking one of means that improve freeze cycle efficient, spraying cycle.Patent documentation 1-Japanese kokai publication hei 5-133368 communique discloses a kind of spraying cycle, and it has been to use the rotary split-compressor of the split-compressor structure that the suction side of the discharge side of low-pressure stage (low-pressure side) compression unit and hiigh pressure stage (high-pressure side) compression unit is connected in series by interface channel (center-aisle).Promptly, the spraying cycle of record is that secondary coolant compressor, condenser, the 1st swollen expansion device, gas-liquid separator, the 2nd swollen expansion device, evaporimeter are connected with pipeline successively, and with the interface channel (center-aisle) of injection channel connection gas-liquid separator and split-compressor midway.
And, following technology is disclosed: the throughput deficiency that produces between the suction cylinder volume owing to refrigerant gas volume of discharging from low pressure compression unit mechanism and high pressure compressed unit mechanisms, pressure fluctuation takes place in the center-aisle that is communicated with between two compression units, and the refrigerant gas of center-aisle is back in the gas-liquid separator, thereby normal freeze cycle running can not be carried out, to this problem, configuration only allows fluid from the technology of gas-liquid separator to the check valve apparatus of interface channel inflow in the way of injection channel.
For improving the efficient of spraying cycle, importantly guarantee suitable expulsion pressure to compressor.When using rotary split-compressor to spray, the interface channel of low-pressure side compression unit and high-pressure side compression unit is sprayed.But the situation of distinguishing is: when using the rotary split-compressor of patent documentation 1 record, utilize the situation of the effect of spraying the existing cycle efficieny that can fully be improved, the situation that can not obtain this effect is also arranged.
Summary of the invention
In view of the above problems, the objective of the invention is to seek to improve the efficient of spraying cycle.
For achieving the above object, air conditioner of the present invention has: the cold-producing medium of discharging with compression unit from low pressure is drawn into high pressure with the compression unit and the split-compressor of discharging to the outside by intermediate space, the condenser that is connected with this split-compressor, first mechanism of decompressor that cold-producing medium from this condenser is reduced pressure, be connected in the gas-liquid separator of this first mechanism of decompressor, be connected in second mechanism of decompressor of this gas-liquid separator, be connected in this second mechanism of decompressor on one side, and another side is connected in the evaporimeter of above-mentioned split-compressor, connects the injection pipe arrangement of above-mentioned gas-liquid separator and above-mentioned intermediate space; It is characterized in that: on the position of the distance L of representing with following formula from the above-mentioned injection pipe arrangement of above-mentioned intermediate space, have the littler long-pending part of dwindling of cross section of fluid channel of sectional area of the above-mentioned injection pipe arrangement of the position of sectional area ratio from above-mentioned intermediate space to this distance L; Wherein,
L={ (2n-1)/4 ± 1/8} λ (wherein, n=1,2,3 ...)
Particularly, distance L is:
L={ (2n-1)/4 ± 1/16} λ (wherein, n=1,2,3 ...)
According to the present invention, can realize improving the efficient of spraying cycle.
Description of drawings
Fig. 1 is the profilograph of the rotary split-compressor of one embodiment of the present of invention.
Fig. 2 is the loop structure figure of the air conditioner of one embodiment of the present of invention.
Fig. 3 is an expression pipe arrangement distance and the graph of a relation of circulation COP.
Fig. 4 is the method to set up figure that pipe arrangement is sprayed in expression.
Fig. 5 is the compression cover and the graph of a relation that spray pipe arrangement of expression when observing from the top of Fig. 4.
The specific embodiment
With reference to the description of drawings embodiments of the invention, the rotary split-compressor of present embodiment is described with Fig. 1 at first.
The 9a of end plate portion is by being fixedly welded on the inwall of pars intermedia 22, and supporting spindle holds 9.The 19a of end plate portion is supported on the supplementary bearing 19.Also have,, also can be fixed on the pars intermedia 22 by the side of welding though the 19a of end plate portion of present embodiment is fixing with bolt etc.
Each compression unit 20a and 20b are constructed as follows.Low pressure compression unit 20a is by supplementary bearing 19, and cylinder 10a cylindraceous is engaged in the rotor cylindraceous 11 of the periphery of eccentric part 5a, and central dividing plate 15 constitutes discharge chambe 23a.In addition, high pressure compressed unit 20b is by base bearing 9, and cylinder 10b cylindraceous is engaged in the rotor cylindraceous 11 of eccentric part 5b periphery, and central dividing plate 15 constitutes discharge chambe 23b.These discharge chambes 23a, 23b, by applying the flat slide plate 18 that the mechanism of spring force is connected with helical spring and so on, eccentric motion along with eccentric part 5a, 5b, contact is on the periphery of rotor rotated 11a, 11b on one side, do the advance and retreat motion on one side, thereby discharge chambe 23a, 23b are divided into compression stroke and suck the space.
Compression unit 20 drives rotor 11 by the off-centre rotation of eccentric part 5.As shown in Figure 1, the phase difference of the compression station of eccentric part 5a and 180 ° of eccentric part 5b phase differences, compression unit 20a, 20b is 180 °.That is, the compression station of 2 compression units is an antiphase.
Represent flow direction with the arrow of Fig. 1 as the gas refrigerant of working fluid.The low pressure Ps gas refrigerant of being supplied with by pipe arrangement 31 sucks low pressure with in the compression unit 20a by the suction inlet 25a that is connected with pipe arrangement 31, rotates by means of the off-centre of rotor 11a to be compressed to intermediate pressure Pm.The dump valve 28a that pressure one in the discharge chambe 23a reaches predetermined pressure, opening is because of intermediate pressure Pm opening, thereby makes the gas refrigerant that has reached intermediate pressure Pm just to discharge space 33 discharges that are communicated with outlet 26a.This discharge space 33 is the spaces that separate by the confined space 29 in supplementary bearing 19 and lid 35 and the closed container 13, and its internal pressure is essentially intermediate pressure Pm.Intermediate flow channel 30 is to be communicated with the runner of discharging space 33 and suction inlet 25b.By discharge that space 33 and intermediate flow channel 30 and suction inlet 25b constitute one space that has been communicated with, be to separate with closed container 13 and internal pressure is the intermediate space 32 (part that with dashed lines impales among Fig. 1) of intermediate pressure Pm.Thereby the pressure that the outlet 26a behind dump valve 28a opening discharges is after the gas refrigerant of Pm is discharged to discharge space 33, to drain into the suction inlet 25b that is communicated with the 23b of balancing gate pit of high-pressure unit 20b by intermediate flow channel 30.
Then, being drawn into high pressure by intermediate flow channel 30 by suction inlet 25b is that the gas refrigerant of Pm is because the revolution of rotor 11b is compressed into high pressure P d with the intermediate pressure in the compression unit 20b.The dump valve 28b that pressure one in the discharge chambe 23b reaches preset pressure, opening is because of high pressure P d opening, and gas refrigerant is just from outlet 26b is discharged to confined space 29 as the inner space of closed container 13.The gas refrigerant that is discharged in this confined space 29 is discharged from discharge pipe 27 by the gap of motor 14.In addition, be injected in the intermediate space 32 by spraying pipe arrangement 17 by the gas refrigerant of not shown gas-liquid separator separates.
Secondly, Fig. 2 represents to have the structure of the freeze cycle of spraying cycle.In addition, identical with Fig. 1 label is represented identical structure.In addition, the cross valve that switches cooling operation and heating running does not give diagram.Thereby condenser 3 is outdoor heat converter when cooling operation, and becomes indoor heat converter when the heating running.Equally, evaporimeter 16 is heat exchanger when cooling operation, and becomes outdoor heat converter when the heating running.
The high pressure P d refrigerant gas of discharging from rotary split-compressor 1 by condenser 3 condensations after, swollenly rise that the 4a of mechanism is swollen to rise by the 1st, and pressure is decompressed to intermediate pressure Pm.This refrigerant gas that is depressurized is separated into gas and liquid by gas-liquid separator 6.After the 2nd swollen 4b of mechanism that rises in the downstream of the liquid refrigerant after the separation by being positioned at gas-liquid separator 6 further is decompressed to low pressure Ps, become gas refrigerant by evaporimeter 16 evaporations.The gas refrigerant of low pressure Ps is drawn into low pressure with in the compression unit 20a by suction inlet 25a, and by cooperates with eccentric part 5a the revolution of rotor 11a be compressed into intermediate pressure Pm, and to intermediate space 32 discharges.
The gas refrigerant of intermediate space 32 mixes with the gas refrigerant of the intermediate pressure Pm that the injection pipe arrangement 17 that is communicated with from gas-liquid separator 6 and intermediate flow channel 30 imports.Thereafter, be drawn into the gas refrigerant of high pressure with the intermediate pressure Pm in the compression unit 20b by suction inlet 25b, the revolution of doing by the rotor 11 that cooperates with eccentric part 5b is compressed into high pressure P d, and discharges from discharge pipe 27.
Such spraying cycle because gas refrigerant bypass that heat transfer property is low in evaporimeter 16, thereby reduces unnecessary circular flow to low-pressure side compression unit 20a, reduces compression work, thereby improves the efficiency factor COP of air conditioner.
So, with regard to the gas spraying cycle that adopts so rotary split-compressor, distinguish low phenomenon when high when COP produces.
Expression that shown in Figure 3 is from middle space 32 and the junction surface of spraying pipe arrangement 17 to the experimental result of the relation of the COP of the distance L of motor-driven valve 34 and circulation.As shown in Figure 3, circulation COP has periodic peak value by the pipe arrangement distance L, and this peak value reaches and causes with pressure fluctuation that the pipe arrangement of resonance grows up to cause and equate.
It is ignorant to anticipate according to this result, by will be from middle space 32 and the junction surface of spraying pipe arrangement 17 to the distance of motor-driven valve 34 as the distance that improves COP, can realize the raising of COP thus.
In the present embodiment, when the wavelength of establishing pressure wave (pressure fluctuation) is λ, by being in distance L: (2n-1)/4 ± 1/8} λ (wherein, n=1,2,3 ...) the position on motor-driven valve 34 is set, utilize the covibration that causes by pressure fluctuation, circulation COP can be brought up to more than the mean value.
In addition, pipe arrangement distance L one is long, and injection flow then reduces because of the pressure loss of pipe arrangement, and circulation COP reduces.Thereby, wish the most when we can say n=1.Have again, by distance L is made as: (2n-1)/4 ± 1/16} λ (wherein, n=1,2,3 ...), can make COP reach high zone.Particularly for 1/4 λ by it is controlled at ± 1/16 scope in, can obtain extra high effect.
Study obtaining as mentioned above the reason of effect.At first with regard to its reason, the influence of the pressure fluctuation of the intermediate space 32 that can be speculated as that the chances are.Promptly, in the intermediate space 32 of rotary split-compressor 1, reach high pressure by the cold-producing medium of discharging from low-pressure side compression unit 20a after owing to sucked by high-pressure side compression unit 20b, thereby pressure reduces gradually, to produce pressure fluctuation with the corresponding cycle of the revolution of compressor.In the discharge end-of-job stage of low-pressure side compression unit 20a, low-pressure side compression unit 20a and intermediate space 32 are cut off, because therefore 180 ° of the phase deviations of high-pressure side compression unit 20b, are in the suction process in this stage.Owing to the volume of high-pressure side compression unit 20b is added to volume in the intermediate space 32 in this stage for minimum, so the pressure of the intermediate space 32 in this stage reaches the highest.And phase place one is leading, because high-pressure side compression unit 20b suction work shifts to an earlier date, volume increases, thereby the pressure of intermediate space 32 reduces along with the revolution of rotor 11.Can think that this pressure fluctuation also propagates into sprays in the pipe arrangement, and jeting effect is affected.
Below, discuss when motor-driven valve 34 location-appropriate is set the time COP raising reason.Being located at the motor-driven valve 34 that sprays in pipe arrangement 17 ways and the injection pipe arrangement 17 of intermediate space 32 sides, to compare its sectional area littler.The pressure wave of the pressure fluctuation of intermediate space 32 is sprayed littler motor-driven valves 34 reflections of pipe arrangement 17 by sectional area ratio, and and intermediate space 32 between pipe arrangement in produce standing wave.Therefore, can consider it whether is the manifesting of pressurized effect of the ejector refrigeration agent that causes of pressure fluctuation.
, control to a certain degree though such pressure fluctuation can increase by the volume that makes intermediate space 32, if will make it very during smoothing, then the machine volume will increase.In addition for prevent cold-producing medium from middle space 32 to the backflow of spraying pipe arrangement 17, even can not the be inhibited effect of pressure fluctuation of check-valves is set on spray circuits.
In the present embodiment, owing to be provided with the long-pending part of dwindling of cross section of fluid channel of the back wave generation that makes the pressure wave of in spraying pipe arrangement 17, propagating become the standing wave that stiff end is arranged in spraying pipe arrangement 17, promptly be provided with motor-driven valve 34 in the present embodiment, thereby utilize the inertia effect of spraying fluid, can guarantee stable performance.
As being provided with the long-pending position that dwindles part of cross section of fluid channel, as previously mentioned, when the injected resulting value of fluid velocity of sound of revolution removal with compressor is made as λ, intermediate space 32 from rotary split-compressor 1 is being made as with the pipe arrangement distance L that the junction surface of spraying pipe arrangement 17 begins: L={ (2n-1)/4 ± 1/8} λ (wherein, n=1,2,3 ...) the position on, the long-pending part of dwindling of the cross section of fluid channel that sprays pipe arrangement is set.Like this, just can utilize covibration to increase the inertia supercharging effect of the injection fluid that causes because of the internal pressure piping pulsation.Therefore, there is desire that the flow of injection fluid is increased, improves the effect that causes because of injection, so can improve the COP of spraying cycle.
, in the big occasion of the pressure loss of spraying pipe arrangement 17, because the increased pressure of gas-liquid separator 6, the aridity of gas-liquid separator 6 reduces, and the reduction of the ratio of refrigerant gas, thereby injection flow reduces.Therefore, the efficient of circulation reduces.Here, the pipe arrangement distance L is { 1/4 ± 1/8} λ when the n in the above-mentioned condition is made as n=1.Like this, as mentioned above, spray the increase that pipe arrangement can reduce pressure and lose, and can suppress the reduction of efficient by lengthening.In addition, as mentioned above, { 1/4 ± 1/16} λ can use in the highest zone of the effect of raising the efficiency by the pipe arrangement distance L is made as.
Have again, can be with motor-driven valve 34 as the long-pending part of dwindling of cross section of fluid channel; The spray circuits of this motor-driven valve 34 can open and close, and long-pending littler than the sectional area that sprays pipe arrangement at the cross section of fluid channel of the state of opening.At this moment, owing to can will carry out motor-driven valve and the shared same part of sectional area change device that spray circuits opens and closes, thereby can reduce the part number, and enlarged the free degree of design.Compare with the pipe arrangement diameter before the distance L, the long-pending part of being located on this distance L part of dwindling of cross section of fluid channel can be played the pipe arrangement reduced that gas-liquid separator 6 ends from distance L.Also have, both can block up the pipe arrangement of distance L part, also can connect the little pipe arrangement of sectional area of other part.Have again, even be not motor-driven valve, so long as what valve of the valve that sectional area diminishes all can.In addition, motor-driven valve 34 both can be 2 logical valves as open and close valve, also can be expansion valve.
In addition, in this example, spray pipe arrangement 17 and be made of two pipeline 17a and 17b arranged side by side, its structure is made by one of only opening among the motor-driven valve 34a that is disposed at each pipeline and the 34b side, just can switch these pipelines.In addition, each motor-driven valve 34a and 34b are configured in from middle space 32 and spray on the different position of distance that the joint portion of pipe arrangement 17 begins.Though the length of only injection pipe arrangement becomes with the revolution of compressor.But in the present embodiment, switch two pipelines that spray pipe arrangement, can obtain very high jeting effect by using motor-driven valve 34a and 34b.For example, usually, the heating running more needs ability than cooling operation, and the revolution of compressor increases.Therefore, use motor-driven valve 34a during by cooling operation, use motor-driven valve 34b during the heating running, thereby can raise the efficiency.In addition, the same with present embodiment, spray pipe arrangement 17 by constituting, and change pipe arrangement diameter separately by two pipelines, also can obtain same effect.
In addition, the internal diameter of injection pipe arrangement 17 is preferably in 2.0mm in the 7.0mm scope.Promptly, when the pipe arrangement diameter is meticulous, the pressure loss of spraying fluid becomes big, just reduction of Xun Huan efficient as previously mentioned.On the other hand, the pipe arrangement diameter is crossed when thick, and the amplitude of pulsation diminishes, because the pressurized effect that causes because of pulsation diminishes, for this reason, preferably selected suitable pipe arrangement diameter.In the present embodiment, be decided to be about 5.0mm, therefore, utilize the effect of spraying generation just can improve performance owing to will spray the internal diameter of pipe arrangement 17.
Fig. 4 represents to be provided with piping methods in off-premises station.When in addition, Fig. 5 represents to observe from the top of Fig. 4 with the graph of a relation of compression cover.As shown in Figure 4; make that the straight-tube portion that sprays pipe arrangement 17 is S-shaped to be disposed along vertical direction; as shown in Figure 5; by being clamped in, pipe arrangement is wound between the compressor protective layer and protective layer on every side; new fixture of no use etc. just can be fixed pipe arrangement at an easy rate; simultaneously, can prevent to wait the breakage that causes pipe arrangement because of vibration.In addition; carry out heat exchange though spray pipe arrangement with protective layer and ambient air; but usually; because the temperature of protective layer inboard is higher than the temperature of the cold-producing medium that sprays; therefore; even the occasion that liquid refrigerant sprays pipe arrangement because of inflows exceedingly such as load changes also can make liquid refrigerant utilize the heat that is brought by compressor to be evaporated in protective layer.Therefore, owing to usually can gasify the cold-producing medium that sprays, so, the problem that can avoid liquid refrigerant because the liquid compression that injection causes etc. reduced the reliability of compressor, thus reliability also can improve.
Claims (4)
1. air conditioner, it has: the cold-producing medium of discharging with compression unit from low pressure is drawn into high pressure with the compression unit and the split-compressor of discharging to the outside by intermediate space, the condenser that is connected with this split-compressor, first mechanism of decompressor that cold-producing medium from this condenser is reduced pressure, be connected in the gas-liquid separator of this first mechanism of decompressor, be connected in second mechanism of decompressor of this gas-liquid separator, be connected in this second mechanism of decompressor on one side, and another side is connected in the evaporimeter of above-mentioned split-compressor, connects the injection pipe arrangement of above-mentioned gas-liquid separator and above-mentioned intermediate space; It is characterized in that: on the position of the distance L of representing with following formula from the above-mentioned injection pipe arrangement of above-mentioned intermediate space, have the littler long-pending part of dwindling of cross section of fluid channel of sectional area of the above-mentioned injection pipe arrangement of the position of sectional area ratio from above-mentioned intermediate space to this distance L; Wherein,
L={ (2n-1)/4 ± 1/8} λ (wherein, n=1,2,3 ...).
2. air conditioner, it has: the cold-producing medium of discharging with compression unit from low pressure is drawn into high pressure with the compression unit and the split-compressor of discharging to the outside by intermediate space, the condenser that is connected with this split-compressor, first mechanism of decompressor that cold-producing medium from this condenser is reduced pressure, be connected in the gas-liquid separator of this first mechanism of decompressor, be connected in second mechanism of decompressor of this gas-liquid separator, be connected in this second mechanism of decompressor on one side, and another side is connected in the evaporimeter of above-mentioned split-compressor, connects the injection pipe arrangement of above-mentioned gas-liquid separator and above-mentioned intermediate space; It is characterized in that: on the position of the distance L of representing with following formula from the above-mentioned injection pipe arrangement of above-mentioned intermediate space, have the littler long-pending part of dwindling of cross section of fluid channel of sectional area of the above-mentioned injection pipe arrangement of the position of sectional area ratio from above-mentioned intermediate space to this distance L; Wherein,
L={ (2n-1)/4 ± 1/16} λ (wherein, n=1,2,3 ...).
3. air conditioner according to claim 1 and 2, it is characterized in that: above-mentioned cross section of fluid channel is long-pending, and to dwindle part be the littler sectional area of sectional area that has than the above-mentioned injection pipe arrangement of the position from above-mentioned intermediate space to above-mentioned distance L, can open and close the motor-driven valve of above-mentioned injection pipe arrangement.
4. air conditioner according to claim 1 and 2 is characterized in that: be made of along the pipe arrangement of vertical direction configuration the S-shaped straight-tube portion that makes to the injection pipe arrangement of above-mentioned distance L, and be fixed in the protective layer inboard that is centered around around the above-mentioned split-compressor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004370376 | 2004-12-22 | ||
| JP2004370376A JP4102799B2 (en) | 2004-12-22 | 2004-12-22 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1793754A true CN1793754A (en) | 2006-06-28 |
| CN100376847C CN100376847C (en) | 2008-03-26 |
Family
ID=36731857
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100932435A Expired - Fee Related CN100376847C (en) | 2004-12-22 | 2005-08-19 | Air conditioner |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP4102799B2 (en) |
| KR (1) | KR100646288B1 (en) |
| CN (1) | CN100376847C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102338514A (en) * | 2010-07-15 | 2012-02-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary type compressor and gas-liquid separator thereof |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103362807B (en) * | 2012-04-10 | 2016-06-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, the air conditioning system with this compressor and heat pump water heater system |
| JP6141349B2 (en) * | 2015-04-16 | 2017-06-07 | 本田技研工業株式会社 | Program and application control method |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2699723B2 (en) * | 1991-11-12 | 1998-01-19 | 松下電器産業株式会社 | Two-stage compression refrigeration system with check valve device |
| JP4016659B2 (en) * | 2002-01-15 | 2007-12-05 | 株式会社デンソー | Air conditioner |
| JP3903342B2 (en) * | 2003-03-13 | 2007-04-11 | 株式会社日立製作所 | Air conditioner |
| JP2004293896A (en) * | 2003-03-26 | 2004-10-21 | Aisin Seiki Co Ltd | Air conditioner |
-
2004
- 2004-12-22 JP JP2004370376A patent/JP4102799B2/en not_active Expired - Fee Related
-
2005
- 2005-08-19 KR KR20050076014A patent/KR100646288B1/en not_active IP Right Cessation
- 2005-08-19 CN CNB2005100932435A patent/CN100376847C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102338514A (en) * | 2010-07-15 | 2012-02-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary type compressor and gas-liquid separator thereof |
| CN102338514B (en) * | 2010-07-15 | 2013-10-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary type compressor and gas-liquid separator thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20060071845A (en) | 2006-06-27 |
| JP4102799B2 (en) | 2008-06-18 |
| JP2006177595A (en) | 2006-07-06 |
| CN100376847C (en) | 2008-03-26 |
| KR100646288B1 (en) | 2006-11-23 |
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Granted publication date: 20080326 Termination date: 20100819 |