CN1769813A - Air attemperation apparatus - Google Patents
Air attemperation apparatus Download PDFInfo
- Publication number
- CN1769813A CN1769813A CN 200510117091 CN200510117091A CN1769813A CN 1769813 A CN1769813 A CN 1769813A CN 200510117091 CN200510117091 CN 200510117091 CN 200510117091 A CN200510117091 A CN 200510117091A CN 1769813 A CN1769813 A CN 1769813A
- Authority
- CN
- China
- Prior art keywords
- unit
- refrigerant flow
- gas
- liquid separator
- decompressing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
-
- 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
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
Abstract
Aimed is to implement optimal injection even when a resisting value of a pressure reducer is changed by individual difference of a pressure reduction adjusting means and accumulation of dusts, in an air conditioner wherein a refrigerant is injected from a gas-liquid separator 4 to a refrigerant outlet portion of a lower stage-side compressing portion 1b of a compressor 1, and controlling the injection by a pressure reducing means on a downstream side of the gas-liquid separator 4. The pressure reduction by the pressure reducing means 3, 5 on the downstream side of the gas-liquid separator 4 are determined on the basis of the difference between a lower stage-side compressing portion discharge temperature 8 and a higher stage-side compressing portion suction temperature 7 of a two-stage compressor 1 having the lower stage-side compressing portion 1b and the higher stage-side compressing portion 1a.
Description
Technical field
The present invention relates to a kind of air attemperation apparatus, and spray relevant with gas.
Background technology
As the technology of relevant air attemperation apparatus power saving, well-known, gas injection system is arranged, promptly in compression process, spray the gas coolant that is helpless to evaporability, reduce the gas injection system of compression power.That is, have: compressor; Refrigerant flow direction switch unit, it is connected with this compressor, switches the refrigerant flow direction in the running of cold air operation and heating installation; The 1st heat exchanger, it is connected with this refrigerant flow direction switch unit; First decompressing unit, it is connected with the 1st heat exchanger; Gas-liquid separator, it is connected with this first decompressing unit; Second decompressing unit, it is connected with this gas-liquid separator; The 2nd heat exchanger, the one side is connected with this first decompressing unit, and opposite side is connected with described refrigerant flow direction switch unit; Spray pipe arrangement, it connects the middle splenium branch of described gas-liquid separator and described compressor; Two-way valve, it is arranged on this injection pipe arrangement.By adjusting the decompression amount of first decompressing unit and second decompressing unit, will be in the gas-liquid separator as pressing in the middle of compressor suction pressure and the discharge pressure, partly spray the gas coolant that is helpless to evaporability to the intermediate pressure of compressor.
Gas sprays, and according to the first time and secondary decompression amount of decompressing unit, determines the pressure in the gas-liquid separator, and according to this pressure, emitted dose or gas-liquid separation performance change, and are accompanied by these, and the efficient of air attemperation apparatus changes.That is, the pressure of gas-liquid separator has suitable value, as the method for this suitableization, records the method for decompression amount of controlling the decompressing unit in downstream according to compressor revolution and outer temperature degree in the patent documentation 1.
Patent documentation 1: the spy opens the 2002-81769 communique.
For the pressure of suitableization gas-liquid separator, patent documentation 1 disclosed air conditioner, according to Compressor revolution and outer temperature degree are controlled the decompression amount of the decompressing unit in downstream. But, because root not The state of the freeze cycle on border is controlled factually, so can not be with the adjustment decompression amount of decompressing unit The variation correspondence of the stream resistance value that the individual difference XOR causes because of accumulations such as rubbish, therefore, sometimes decompression Decompression amount in the unit may not be best gas spray regime.
Summary of the invention
The object of the present invention is to provide a kind of air attemperation apparatus, it sprays near best gas when carrying out the gas injection.Air attemperation apparatus of the present invention has: two sections compressors, and it has low-pressure side compression unit and high-pressure side compression unit; Second heat exchanger, two sections compressors of itself and this are connected; Second decompressing unit, it is connected with this second heat exchanger, can regulate aperture; Gas-liquid separator, it is connected with this second decompressing unit; First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture; Freeze cycle, it has a side and is connected first heat exchanger that opposite side is connected with described two sections compressors with this first decompressing unit; With spray pipe arrangement, it connects the middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of low-pressure side compression unit of described gas-liquid separator and described compressor and high side compressors portion.In this air attemperation apparatus, compare with the connecting portion of described injection pipe arrangement with described middle refrigerant flow, realize above-mentioned purpose by partly being provided with high band side inlet temperature detecting unit in suction near the high band side compression unit.
Air attemperation apparatus of the present invention has: two sections compressors, and it has low-pressure side compression unit and high-pressure side compression unit, has middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of this low-pressure side compression unit and this high-pressure side compression unit; Second heat exchanger, two sections compressors of itself and this are connected; Second decompressing unit, it is connected with this second heat exchanger, can regulate aperture; Gas-liquid separator, it is connected with this second decompressing unit; First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture; Freeze cycle, it has a side and is connected first heat exchanger that opposite side is connected with described two sections compressors with this first decompressing unit; With the injection pipe arrangement, it connects described gas-liquid separator and described middle refrigerant flow.Refrigerant flow has the outer coolant piping of closed container that is exposed to described two sections compressors in the middle of described, in this air attemperation apparatus, with described injection pipe arrangement and be exposed to described in the middle of the connecting portion of the outer coolant piping of the closed container of refrigerant flow compare, be provided with a high section inlet temperature detecting unit by the coolant piping place the described closed container that is exposed to refrigerant flow direction downstream outside and realize above-mentioned purpose.
Air attemperation apparatus of the present invention has: two sections compressors, and it has low-pressure side compression unit and high-pressure side compression unit; Refrigerant flow direction switch unit, two sections compressors of itself and this are connected; Indoor heat converter, it is connected with this refrigerant flow direction switch unit; Second decompressing unit, it is connected with this indoor heat converter, can regulate aperture; Gas-liquid separator, it is connected with this second decompressing unit; First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture; Freeze cycle, it has a side and is connected the outdoor heat converter that opposite side is connected with described refrigerant flow direction switch unit with this first decompressing unit; With spray pipe arrangement, it connects the middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of low-pressure side compression unit of described gas-liquid separator and described compressor and high side compressors portion.In this air attemperation apparatus, compare with the connecting portion of described injection pipe arrangement with described middle refrigerant flow, realize above-mentioned purpose by partly being provided with high band side inlet temperature detecting unit in suction near the high band side compression unit.
Air attemperation apparatus of the present invention has: two sections compressors, and it has low-pressure side compression unit and high-pressure side compression unit, has middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of this low-pressure side compression unit and this high-pressure side compression unit; Refrigerant flow direction switch unit, two sections compressors of itself and this are connected; Indoor heat converter, it is connected with this refrigerant flow direction switch unit; Second decompressing unit, it is connected with this indoor heat converter, can regulate aperture; Gas-liquid separator, it is connected with this second decompressing unit; First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture; Freeze cycle, it has a side and is connected the outdoor heat converter that opposite side is connected with described refrigerant flow direction switch unit with this first decompressing unit; With the injection pipe arrangement, it connects described gas-liquid separator and described middle refrigerant flow.In this air attemperation apparatus, with described injection pipe arrangement and be exposed to described in the middle of the connecting portion of the outer coolant piping of the closed container of refrigerant flow compare, be provided with a high section inlet temperature detecting unit by the coolant piping place the described closed container that is exposed to refrigerant flow direction downstream outside and realize above-mentioned purpose.
Can provide a kind of air attemperation apparatus according to above invention, it sprays near best when carrying out the gas injection.
Description of drawings
Fig. 1 relates to the refrigeration cycle diagram of the air attemperation apparatus of a kind of embodiment of the present invention.
Fig. 2 relates to the control flow chart of a kind of embodiment of the present invention.
Fig. 3 is the schematic diagram of the relation of explanation downstream expansion valve opening and compressor temperature.
Fig. 4 is the schematic diagram of the relation of explanation compressor temperature and COP.
Fig. 5 is the schematic diagram of the relation of explanation expansion valve opening and compressor temperature.
Fig. 6 is the schematic diagram of the relation of explanation upstream side expansion valve opening and COP.
Fig. 7 is the schematic diagram of the relation of explanation compressor revolution and compressor temperature.
Fig. 8 relates to the longitudinal section of two sections compressors of a kind of embodiment of the present invention.
Symbol description
1... two sections compressors, 2... outdoor heat converter, 3... first electric expansion valve, 4... gas-liquid separator, 5... second electric expansion valve, 6... indoor heat converter, 7... high band side inlet temperature sensor, 8... low band side discharge temperature sensor, 9... high band side discharge temperature sensor, 10... arithmetic unit, 11... injection pipe arrangement, 12... two-way valve, the outdoor air-supply air blast of 13..., the indoor air-supply air blast of 14....
The specific embodiment
Below, describe one embodiment of the present of invention with reference to the accompanying drawings in detail.Fig. 1 is the freeze cycle that has in the air attemperation apparatus that gas sprays, the refrigerant flow direction the during running of expression heating installation.Two sections compressors 1 are the compressors with high band side (high side compressors portion) 1a and low band side (low-pressure side compressor section) 1b2 compression unit, the detailed content aftermentioned.As the outdoor heat converter 2 of first heat exchanger, when turning round, heating installation plays a role as evaporimeter (during cold air operation as condenser).Second electric expansion valve 5 is the variable decompressing unit of decompression amount that are arranged at refrigerant flow direction upstream (being the downstream during cold air operation).First electric expansion valve 3 is the variable decompressing unit of decompression amount that are positioned at refrigerant flow direction downstream (being the upstream during cold air operation).Gas-liquid separator 4 is arranged between first electric expansion valve 3 and second expansion valve 5, has the function of divided gas flow refrigerant and liquid coolant.As the indoor heat converter 6 of second heat exchanger, when turning round, heating installation plays a role as condenser (during cold air operation as evaporimeter).
The liquid that is separated by gas-liquid separator 4 or the refrigerant of low mass dryness fraction are constituted as to first electric expansion valve 3 and flow.In addition, the discharge portion that is constituted as to the low band side compression unit 1b of two sections compressors 1 by the refrigerant of 4 gas separated of gas-liquid separator or high mass dryness fraction flows.High band side inlet temperature sensor 7 is inlet temperature detecting units of the high band side 1a of two sections compressors 1, and low band side discharge temperature sensor 8 is discharge temperature detecting units of the low band side 1b of two sections compressors 1.In addition, the inlet temperature detecting unit of the high band side 1a of 9 two sections compressors 1 of high band side discharge temperature sensor.Arithmetic unit 10 has control program as shown in Figure 2.Two-way valve 12 can be set in and spray " the opening " or " pass " that is provided with on the pipe arrangement 11.In addition, the 13rd, outdoor air-supply air blast, the 14th, indoor air-supply air blast.
According to Fig. 1 and the as above operation of the air attemperation apparatus of formation of Fig. 2 explanation.When step 101 running beginning (being illustrated as the heating installation running), if two-way valve 12 is opened then and closed, the aperture that makes first electric expansion valve 3 and second electric expansion valve 5 is an initial set value (step 102).If two sections compressors 1 of starting under this state, the cold media gas of the HTHP that compressed of two sections compressors 1 then, arrive indoor heat converters 6 by four-way valve 15, to the air heat release of blowing and condensation by indoor air-supply air blast as refrigerant flow direction switch unit.Reduce pressure till the pressure in the middle of becoming with respect to discharge pressure and suction pressure by second electric expansion valve 5, arrive gas-liquid separator 4.At this moment because two-way valve 12 is closed,, become the refrigerant of low-temp low-pressure so whole refrigerants reduces pressure by first electric expansion valve 3 again.The refrigerant of the gas-liquid two-phase state of low-temp low-pressure from being evaporated by the air heat absorption of outdoor air-supply air blast 13 air-supplies, turns back to two sections compressors 1 at outdoor heat converter 2 once more.
Then, if open two-way valve 12 (step 103), then given the discharge portion of the low band side compression unit 1b of two sections compressors 1 by shunting by two-way valve 12 by 4 gas separated refrigerants of gas-liquid separator.Afterwards, the output (step 104) of low band side discharge temperature sensor 8 and high band side inlet temperature sensor 7 is read in s operation control portion 10, computing low band side discharge temperature and high band side inlet temperature poor.And when (low band side discharge temperature)-(high band side inlet temperature) not do not spent greater than 1, promptly the difference of low band side discharge temperature and high band side inlet temperature was smaller or equal to once the time, and being judged to be also is not liquid mist injection (step 105).
At this, use Fig. 8 that two sections compressors 1 are elaborated.Two sections compressors 1 have the closed container 41 that is made of bottom 21 and cap 40 and cylindrical portion 22.Above closed container 41 inside, be provided with motor 44 with stator 42 and rotor 43.The rotating shaft 45 that is connected with motor 44 has 2 eccentric parts 46 (46a, 46b), is subjected to 19 supportings of base bearing 47 and supplementary bearing.With respect to this rotating shaft 45, from motor 44 sequentially the base bearing 47, high pressure of lamination with the 48a of end plate portion with (high band side) compression key element 1a, central dividing plate 49, low pressure with (low band side) compression key element 1b and supplementary bearing 19 with the 19a of end plate portion, integrated by fastening key elements such as bolt (figure does not show).
The 48a of end plate portion is fixed by welding on the inwall of cylindrical portion 22, and supporting spindle holds 47.The 19a of end plate portion supports supplementary bearing 19.In addition, though present embodiment uses stiff end board 19a such as bolt,, also can be fixed by welding on the cylindrical portion 22.
Each compresses key element 1a and the following formation of 1b.Low pressure compression key element 1b is made of supplementary bearing 19, cylinder cylindraceous (cylinder) 50a, cylinder cylindraceous (roller) 51a that is entrenched in eccentric part 46a periphery and central dividing plate 49, and the space that surrounds these becomes discharge chambe 23a.In addition, high pressure compressed key element 1a is made of base bearing 47, cylinder 50b cylindraceous, the cylinder 51b cylindraceous and the central dividing plate 49 that are entrenched in eccentric part 46b periphery, and the space that surrounds these becomes discharge chambe 23b.These discharge chambes 23a, 23b, contact the motion of also advancing and retreat simultaneously on the periphery by flat blade (figure do not show) and cylinder 51a, 51b, and discharge chambe 23a, 23b are divided into compression stroke and suck the space, the such active force of this blade and helical spring gives the unit and is connected, and this cylinder 51a, 51b rotate with the eccentric motion of eccentric part 46a, 46b.
As shown in Figure 8, eccentric part 46a and eccentric part 46b 180 ° of phasic differences mutually, the phase difference of the compression section of compression key element 1a, 1b is 180 °.Promptly the compression section of 2 compression key elements is an antiphase.
The arrow of use Fig. 8 is represented flowing as the gas coolant of working fluid.The gas coolant of the low pressure Ps that is supplied with by pipe arrangement 31 is drawn into low pressure with in the compression key element 20a by the suction inlet 25a that is connected with pipe arrangement 31, presses Pm in the middle of being compressed to by the eccentric rotation of cylinder 51a.If the pressure in the discharge chambe 23a reaches predefined pressure, then the dump valve 28a of opening presses the Pm opening in the centre, presses the gas coolant of Pm to be discharged to the discharge space 33 that is communicated with outlet 26a in the middle of becoming.This discharges space 33, is the space that is isolated by the confined space 29 in supplementary bearing 19 and shell 35 and the closed container 13, presses Pm in the middle of its internal pressure is essentially.Intermediate flow passage 30 is to be communicated with the stream of discharging space 33 and suction inlet 25a, about U word shape outside a part of closed container 40.By the space of discharging the connection that space 33 and intermediate flow passage 30 and suction inlet 25a constitute, be to separate with closed container 13, internal pressure is middle intermediate space 32 (part that with dashed lines is placed among Fig. 1) of pressing Pm.Therefore, from the gas coolant of the discharge pressure Pm of outlet 26a institute of dump valve 28a opening, be discharged to discharge space 33 after, by intermediate flow passage 30, arrive the suction inlet 25b that is communicated with the 23b of balancing gate pit of high-pressure key element 20b.
Then, be drawn into the gas coolant of high pressure by suction inlet 25b, be compressed into high pressure P d by cylinder 51b revolution with the middle Pm of pressure in the compression key element 1a by intermediate flow passage 30.If the pressure in the discharge chambe 23b reaches predefined pressure, then the dump valve 28b of opening is with high pressure P d opening, and gas coolant is discharged to confined space 29 as the inner space of closed container 41 from outlet 26b.This is discharged to the gas coolant of confined space 29, is discharged by discharge pipe 27 by the gap of motor 14.
And, be provided with low band side discharge temperature sensor 8 in the low pressure of intermediate flow passage 30 with the discharge portion of compression key element 1b, be provided with high band side inlet temperature sensor 7 at the high pressure of intermediate flow passage 30 with the suction portion that compresses key element 1a.In addition, be connected with the injection pipe arrangement 11 that is connected with gas-liquid separator 4 at the low band side discharge temperature sensor 8 of intermediate flow passage 30 with stream between the high band side inlet temperature sensor 7.That is, the intermediate flow passage 30 in the intermediate flow passage 30 and the refrigerant flow direction upstream of the connecting portion that sprays pipe arrangement 11 is provided with low band side discharge temperature sensor 8, is provided with high band side inlet temperature sensor 7 in downstream intermediate flow 30.
In the present embodiment, utilize the temperature difference of low band side discharge temperature sensor 8 and high band side inlet temperature sensor 7, judge that the refrigerant that is sprayed from injection pipe arrangement 11 is gas coolant or mixes the refrigerant that liquid is arranged.Promptly, from spraying the refrigerant that pipe arrangement 11 sprays because be because the refrigerant of the electric expansion valve of upstream after expanding, institute thinks low temperature, flows into intermediate flow passage 30 if particularly mixed the refrigerant of liquid coolant, then with from the gas coolant mixed refrigerant temperature of low pressure with compression key element 1b reduces.Promptly utilize following situation: the output valve of high band side inlet temperature sensor 7 is lower than the output valve of low band side discharge temperature sensor 8.
Use Fig. 3 that this principle is described.Fig. 3 represents to spray the phase state of refrigerant with (a low section discharge temperature)-(the high section inlet temperature) at the aperture of first electric expansion valve 3 on curve top, this first electric expansion valve 3 is in the downstream in the freeze cycle shown in Figure 1.Tighten first electric expansion valve 3 more, (low section discharge temperature)-(high section inlet temperature) is big more.This be because, tighten the downstream expansion valve more, the pressure of gas-liquid separator 4 increases, the mass dryness fraction that flows into the refrigerant of gas-liquid separator 4 becomes big, so refrigerant becomes instability, causes the gas-liquid separation performance to reduce.Therefore, the refrigerant of the low temperature that fluid density is big is sneaked in a large number and is sprayed in the refrigerant, and high band side inlet refrigerant temperature is lower than low band side discharge refrigerant temperature.
Turn back to Fig. 2, when (low section discharge temperature)-(high section inlet temperature) when being not more than 1 ℃, promptly when being judged as the gas injection, controlled in step 106, so that tighten the downstream expansion valve.This be because, as shown in Figure 4, distinguish that (low section discharge temperature)-(high section inlet temperature) and COP become maximum COP in (low section discharge temperature)-(high section inlet temperature) when being 1 ℃, when (low section a discharge temperature)-(high section inlet temperature)＞1 ℃, dwindle the aperture of downstream electric expansion valve 5, improve expulsion pressure, control and make its approaching maximum COP.
At this, why think that be maximum COP in (low section a discharge temperature)-(high section inlet temperature) when being about 1 ℃, be because if expulsion pressure is low, then the differential pressure with low section discharge pressure of two sections compressors 1 diminishes, and emitted dose reduces.In addition, if the reason that expulsion pressure height then COP reduce as previously mentioned, is because the big refrigerant of fluid density has turned back to compressor in spraying refrigerant, so the coolant quantity that causes circulating in evaporimeter reduces.
But some liquid coolants are sneaked into the cooling effect with compressor, and maximum COP determines according to these influences, in the present embodiment, become maximum COP during with (a low section discharge temperature)-(high section inlet temperature)=1 ℃ and implement control as prerequisite.
Get back to Fig. 2, when satisfying step 105, enter step 111.In step 111, when (low section a discharge temperature)-(high section inlet temperature)＞15 ℃, be judged as the injection of the liquid that has carried out comprising suitable volume, abandon control based on electric expansion valve 3,5, close two-way valve 12, interrupt spraying (step 112).When the injection of the liquid that has carried out comprising so suitable volume, interrupt the reason of injection, be because if spraying the liquid incorporation rate of refrigerant uprises, then cause liquid compression, so liquid compression is owing to being to cause the reason of compressor damage or noise to prevent at a high section compressor.
Afterwards, significantly open first electric expansion valve 3, reduce expulsion pressure, make it to become the state (step 113) that carries out gas-liquid separation easily as downstream valve.Turn back to step 103 afterwards, open two-way valve 12, restart to spray.
When in step 111 (low section a discharge temperature)-(high section inlet temperature) during not greater than 15 ℃, promptly when temperature difference be during from 1 ℃ to 15 ℃, judgement is that the few liquid of harmful effect is sneaked into injection, open downstream electric expansion valve (is first electric expansion valve 3 at this), reduce expulsion pressure (step 114) slightly.
Step 107～109 owing to be the control of second electric expansion valve 5 of relevant expansion valve as the upstream, so control, are the target high band side discharge temperature determined of approach in addition so that the high band side discharge temperature becomes.
As shown in Figure 5, this reason is, and is also less to the influence of (a low section discharge temperature)-(high section inlet temperature) even the electronic valve opening in upstream changes aperture, also less to the influence of the phase state that sprays refrigerant.But as shown in Figure 6, upstream side electric expansion valve aperture influences the high band side discharge temperature, and influences the high band side discharge temperature and influence COP.And as shown in the figure, because this COP has peak value, so the aperture of upstream side electric expansion valve has suitable value.
In addition, the reason of carrying out high band side compressor temperature control (step 108～110) after emitted dose control (step 105,106,111,112,113,114) suitableization is in order to prevent: because the liquid of volume is injected, cause compressor to be cooled, when the high band side discharge temperature reduced, erroneous judgement was decided to be the decompression quantity not sufficient at upstream side electric expansion valve 3.
But, in the present embodiment, though detect the low band side discharge temperature in step 104, whether the ratio of judging liquid mixing jetting whether or liquid combined amount in step 105 is optimum value, but, can detect operating conditions such as compressor revolution, high band side discharge temperature, outer temperature degree, indoor temperature, condensation temperature, evaporating temperature, air blast revolution, its low band side discharge temperature is determined on not computing detected value ground.
For example, when downstream electric expansion valve during by suitable control, according to compressor revolution and outer temperature degree, the low band side discharge temperature during can be roughly unique definite cold air operation.Can store these relation in advance, give the low band side discharge temperature according to detected compressor revolution and outer temperature degree.Promptly, as shown in Figure 7, compressor revolution and low band side discharge temperature can be come additional relationships as parameter with outer temperature degree, and these values are stored in memory cell in the arithmetic unit 10 in advance, obtain the low band side discharge temperature according to detected compressor revolution and outer temperature degree.At this moment, because do not need low band side discharge temperature detecting sensor, can provide cheap air attemperation apparatus.In addition, can also the processing of step 105 be carried out as (target high band side inlet temperature)＞(high band side inlet temperature) with (low band side discharge temperature)-(1 ℃) as target high band side inlet temperature.At this moment can realize the simplification of arithmetic element.
In Fig. 2, pass through high band side compressor discharge temperature sensor 9 detected high band side compressor discharge temperatures in step 107, if than desired value height (step 108), open the upstream side expansion valve in step 110, control to the direction that COP uprises, if lower than desired value, then in step 109 by tightening the upstream side expansion valve, come the direction control that uprises to COP.
Can know by above-mentioned explanation, in the present embodiment, by high band side inlet temperature sensor 7 is set, can carry out as inferior control: i.e. poor according to high band side inlet temperature and benchmark high band side inlet temperature, or low band side discharge temperature and high band side inlet temperature is poor, determines the decompression amount of downstream decompressing unit.Has following effect thus:, also can carry out Optimal Control even when the resistance change that accumulation caused of individual difference XOR rubbish because of decompression amount adjustment unit etc. is arranged.
Claims (9)
1. air attemperation apparatus, it has:
Two sections compressors, it has low-pressure side compression unit and high-pressure side compression unit;
Second heat exchanger, two sections compressors of itself and this are connected;
Second decompressing unit, it is connected with this second heat exchanger, can regulate aperture;
Gas-liquid separator, it is connected with this second decompressing unit;
First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture;
Freeze cycle, it has a side and is connected first heat exchanger that opposite side is connected with described two sections compressors with this first decompressing unit; With
Spray pipe arrangement, it connects the middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of low-pressure side compression unit of described gas-liquid separator and described compressor and high side compressors portion;
Compare with the connecting portion of described injection pipe arrangement with described middle refrigerant flow, partly be provided with high band side inlet temperature detecting unit in suction near the high band side compression unit.
2. air attemperation apparatus, it has:
Two sections compressors, it has low-pressure side compression unit and high-pressure side compression unit, has middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of this low-pressure side compression unit and this high-pressure side compression unit;
Second heat exchanger, two sections compressors of itself and this are connected;
Second decompressing unit, it is connected with this second heat exchanger, can regulate aperture;
Gas-liquid separator, it is connected with this second decompressing unit;
First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture;
Freeze cycle, it has a side and is connected first heat exchanger that opposite side is connected with described two sections compressors with this first decompressing unit; With
Spray pipe arrangement, it connects described gas-liquid separator and described middle refrigerant flow;
Refrigerant flow has the outer coolant piping of closed container that is exposed to described two sections compressors in the middle of described,
With described injection pipe arrangement and be exposed to described in the middle of the connecting portion of the outer coolant piping of the closed container of refrigerant flow compare, the coolant piping place outside the described closed container that is exposed to refrigerant flow direction downstream is provided with high band side inlet temperature detecting unit.
3. air attemperation apparatus according to claim 1 and 2, wherein,
According to the output of described high band side inlet temperature detecting unit, regulate the decompression amount of described first decompressing unit that becomes the downstream decompressing unit.
4. air attemperation apparatus, it has:
Two sections compressors, it has low-pressure side compression unit and high-pressure side compression unit;
Refrigerant flow direction switch unit, two sections compressors of itself and this are connected;
Indoor heat converter, it is connected with this refrigerant flow direction switch unit;
Second decompressing unit, it is connected with this indoor heat converter, can regulate aperture;
Gas-liquid separator, it is connected with this second decompressing unit;
First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture;
Freeze cycle, it has a side and is connected the outdoor heat converter that opposite side is connected with described refrigerant flow direction switch unit with this first decompressing unit; With
Spray pipe arrangement, it connects the middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of low-pressure side compression unit of described gas-liquid separator and described compressor and high side compressors portion;
Compare with the connecting portion of described injection pipe arrangement with described middle refrigerant flow, partly be provided with high band side inlet temperature detecting unit in suction near the high band side compression unit.
5. air attemperation apparatus, it has:
Two sections compressors, it has low-pressure side compression unit and high-pressure side compression unit, has middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of this low-pressure side compression unit and this high-pressure side compression unit;
Refrigerant flow direction switch unit, two sections compressors of itself and this are connected;
Indoor heat converter, it is connected with this refrigerant flow direction switch unit;
Second decompressing unit, it is connected with this indoor heat converter, can regulate aperture;
Gas-liquid separator, it is connected with this second decompressing unit;
First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture;
Freeze cycle, it has a side and is connected the outdoor heat converter that opposite side is connected with described refrigerant flow direction switch unit with this first decompressing unit; With
Spray pipe arrangement, it connects described gas-liquid separator and described middle refrigerant flow;
With described injection pipe arrangement and be exposed to described in the middle of the connecting portion of the outer coolant piping of the closed container of refrigerant flow compare, the coolant piping place the described closed container that is exposed to refrigerant flow direction downstream outside is provided with high section inlet temperature detecting unit.
6. according to claim 4 or 5 described air attemperation apparatus, wherein,
According to the output of described high band side inlet temperature detecting unit, regulating becomes described first decompressing unit of downstream decompressing unit or the decompression amount of described second decompressing unit.
7. air attemperation apparatus, it has:
Two sections compressors, it has low-pressure side compression unit and high-pressure side compression unit, has middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of this low-pressure side compression unit and this high-pressure side compression unit;
Second heat exchanger, two sections compressors of itself and this are connected;
Second decompressing unit, it is connected with this second heat exchanger, can regulate aperture;
Gas-liquid separator, it is connected with this second decompressing unit;
First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture;
Freeze cycle, it has a side and is connected first heat exchanger that opposite side is connected with described two sections compressors with this first decompressing unit; With
Spray pipe arrangement, it connects described gas-liquid separator and described middle refrigerant flow;
Refrigerant flow has the outer coolant piping of closed container that is exposed to described two sections compressors in the middle of described, with described injection pipe arrangement and be exposed to described in the middle of the connecting portion of the outer coolant piping of the closed container of refrigerant flow compare, coolant piping place outside the described closed container that is exposed to refrigerant flow direction downstream is provided with high band side inlet temperature detecting unit, and the coolant piping place outside the described closed container that is exposed to refrigerant flow direction upstream is provided with low band side discharge temperature detecting unit.
8. air attemperation apparatus, it has:
Two sections compressors, it has low-pressure side compression unit and high-pressure side compression unit, has middle refrigerant flow between the refrigerant suction portion of the refrigerant discharge portion of this low-pressure side compression unit and this high-pressure side compression unit;
Refrigerant flow direction switch unit, two sections compressors of itself and this are connected;
Indoor heat converter, it is connected with this refrigerant flow direction switch unit;
Second decompressing unit, it is connected with this indoor heat converter, can regulate aperture;
Gas-liquid separator, it is connected with this second decompressing unit;
First decompressing unit, it is connected with this gas-liquid separator, can regulate aperture;
Freeze cycle, it has a side and is connected the outdoor heat converter that opposite side is connected with described refrigerant flow direction switch unit with this first decompressing unit; With
Spray pipe arrangement, it connects described gas-liquid separator and described middle refrigerant flow;
With described injection pipe arrangement and be exposed to described in the middle of the connecting portion of the outer coolant piping of the closed container of refrigerant flow compare, coolant piping place outside the described closed container that is exposed to refrigerant flow direction downstream is provided with high band side inlet temperature detecting unit, and the coolant piping place outside the described closed container that is exposed to refrigerant flow direction upstream is provided with low band side discharge temperature detecting unit.
9. according to claim 7 or 8 described air attemperation apparatus, wherein,
According to the output of described high band side inlet temperature detecting unit and described low band side discharge temperature detecting unit, regulate the decompression amount that becomes the decompressing unit in refrigerant flow direction downstream among described first decompressing unit and described second decompressing unit.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004317458A JP2006125793A (en) | 2004-11-01 | 2004-11-01 | Air conditioner |
| JP2004317458 | 2004-11-01 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1769813A true CN1769813A (en) | 2006-05-10 |
| CN100498122C CN100498122C (en) | 2009-06-10 |
Family
ID=36720707
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005101170918A Expired - Fee Related CN100498122C (en) | 2004-11-01 | 2005-11-01 | Air attemperation apparatus |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2006125793A (en) |
| CN (1) | CN100498122C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101479535B (en) * | 2006-07-06 | 2013-02-20 | 大金工业株式会社 | Air conditioning system |
| CN110312902A (en) * | 2017-02-28 | 2019-10-08 | 三菱重工制冷空调系统株式会社 | The operation method of turborefrigerator and turborefrigerator |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4845605B2 (en) * | 2006-06-20 | 2011-12-28 | 三洋電機株式会社 | Refrigeration cycle apparatus and heat pump water heater |
| JP4887929B2 (en) * | 2006-06-21 | 2012-02-29 | ダイキン工業株式会社 | Refrigeration equipment |
| JP4716935B2 (en) * | 2006-06-27 | 2011-07-06 | 三洋電機株式会社 | Refrigeration cycle apparatus and heat pump water heater |
| KR100845847B1 (en) * | 2006-11-13 | 2008-07-14 | 엘지전자 주식회사 | Control Metheod for Airconditioner |
| KR101392316B1 (en) | 2007-12-24 | 2014-05-08 | 엘지전자 주식회사 | Air conditioning system |
| KR101450544B1 (en) * | 2007-12-26 | 2014-10-15 | 엘지전자 주식회사 | Air conditioning system |
| KR101450543B1 (en) * | 2007-12-26 | 2014-10-17 | 엘지전자 주식회사 | Air conditioning system |
| KR101450545B1 (en) * | 2007-12-26 | 2014-10-15 | 엘지전자 주식회사 | Air conditioning system |
| CN105371514B (en) * | 2015-12-10 | 2018-05-18 | 珠海格力电器股份有限公司 | Compressibility, air-conditioning system with second vapor injection and its judge control method |
| KR20210048161A (en) | 2019-10-23 | 2021-05-03 | 엘지전자 주식회사 | Gas-liquid separator and air-conditioner having the same |
-
2004
- 2004-11-01 JP JP2004317458A patent/JP2006125793A/en active Pending
-
2005
- 2005-11-01 CN CNB2005101170918A patent/CN100498122C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101479535B (en) * | 2006-07-06 | 2013-02-20 | 大金工业株式会社 | Air conditioning system |
| CN110312902A (en) * | 2017-02-28 | 2019-10-08 | 三菱重工制冷空调系统株式会社 | The operation method of turborefrigerator and turborefrigerator |
| CN110312902B (en) * | 2017-02-28 | 2021-08-13 | 三菱重工制冷空调系统株式会社 | Turbo refrigerator and method for operating turbo refrigerator |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100498122C (en) | 2009-06-10 |
| JP2006125793A (en) | 2006-05-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1769813A (en) | Air attemperation apparatus | |
| CN1119528C (en) | Scroll compressor and air conditioner | |
| CN101441006B (en) | Cooling unit and compressor | |
| US7674097B2 (en) | Rotary expander | |
| CN1118672C (en) | Parallel type refrigerator | |
| JPH09196478A (en) | Refrigerating cycle | |
| CN1808016A (en) | Refrigeration cycle apparatus | |
| CN102597524B (en) | The method of operation of heat pump system, compound compressor and heat pump system | |
| CN1193199C (en) | Air conditioning system with two compressors and method for operating the same | |
| CN1840986A (en) | Refrigerating device and refrigerator | |
| CN1892154B (en) | Return-oil control method of multi-gang air-conditioner | |
| WO2008072575A1 (en) | Freezing apparatus, and expander | |
| CN201561599U (en) | Multifunctional constant-temperature air-conditioning syhandle in swimming pool | |
| CN1045291A (en) | The compressor and the operating method thereof that are used for heat pump | |
| CN1811290A (en) | Capacity-variable air conditioner | |
| CN100547318C (en) | Air regulator | |
| CN200982767Y (en) | Jet expansion two-section evaporation steam jet type refrigeration device | |
| CN1804514A (en) | Rotary and centrifugal type flash vaporization groove energy saving device | |
| CN1609451A (en) | Compressor | |
| CN207004814U (en) | Rotary compressor and there is its refrigerating plant | |
| CN107228070A (en) | Compressor and the refrigeration system with it | |
| CN1782621B (en) | Freezing circulation device and its control method | |
| JP2002286257A (en) | Refrigeration cycle | |
| CN111486609A (en) | Air conditioning system and control method | |
| CN1793754A (en) | Air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090610 Termination date: 20111101 |