CN103851817A - Refrigerating device - Google Patents
Refrigerating device Download PDFInfo
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- CN103851817A CN103851817A CN201310627518.3A CN201310627518A CN103851817A CN 103851817 A CN103851817 A CN 103851817A CN 201310627518 A CN201310627518 A CN 201310627518A CN 103851817 A CN103851817 A CN 103851817A
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Abstract
The invention provides a refrigerating device capable of properly controlling valve opening degree of an expansion valve when a compressor is started and reducing a starting load. The refrigerating device (R) is characterized in that the compressor (11), an air cooler (28), the expansion valve (32) and an evaporator (33) are formed to be a refrigerant loop (1), a high-pressure side of which is formed to be super-critical pressure; the refrigerating device is provided with a controlling device used for controlling the compressor (11) and the expansion valve (32); and the controlling device is used for changing valve opening degree of the expansion valve (32) when the compressor (11) is started based on external temperature of air and for expanding valve opening degree of the expansion valve (32) in the case of the high temperature of external air and lessening valve opening degree of the expansion valve (32) in the case of the low temperature of external air.
Description
Technical field
The present invention relates to form refrigerant loop and high-pressure side by compressor, gas cooler, expansion valve, evaporimeter and become the refrigerating plant of supercritical pressure.
Background technology
At present, this refrigerating plant forms refrigerant loop by compressor, gas cooler, expansion valve, evaporimeter etc., utilize gas cooler to make by the refrigerant loses heat after compressor compresses and after utilizing expansion valve decompression, utilize evaporimeter to make cold-producing medium evaporation, carry out cooling surrounding air by the evaporation of cold-producing medium now.In recent years, in this refrigerating plant, due to natural environmental stress etc., can not re-use freon class cold-producing medium.Therefore, as the substitute of freon refrigerant, the just carbon dioxide as natural refrigerant at application.Be well known that, this carbon dioxide coolant is the large cold-producing medium of height pressure reduction, and critical pressure is low, makes the high-pressure side of refrigerant circulation become supercriticality (for example,, with reference to patent documentation 1) by compressing.
In addition, because patent documentation 1 is for from refrigeration machine to the refrigerating plant of many showcases (load equipment) the supply system cryogen that is arranged on the shops such as supermarket, so the low-pressure lateral pressure of the running control of compressor that is arranged at refrigeration machine based on refrigerant loop carries out.In addition, by controlling the valve opening of expansion valve, the degree of superheat of evaporimeter is controlled to appropriate value.
Patent documentation 1:(Japan) JP 2011-133204 communique
At this, the rising cooled dose (gas refrigerant) of the high side pressure of the refrigerant loop when compressor start of this refrigerating plant affects significantly to the inflow resistance of the evaporimeter of the showcase as load equipment.And this inflow resistance is determined by the valve opening of expansion valve.
But this expansion valve (electric expansion valve) is failure to actuate under the speed of variation that can follow high side pressure.Therefore, in the past, predetermined the standard valve aperture of expansion valve, in the time of compressor start, controlled the inflow resistance to evaporimeter using the valve opening of expansion valve as this standard valve aperture, but equalizing pressure in the refrigerant loop of compressor after stopping is according to changing season.
Therefore, in summer, standard valve aperture is too small, when startup, cold-producing medium is stopped and is caused the rising of high side pressure to the inflow of evaporimeter, in the winter time, standard valve aperture is excessive and flow into too much cold-producing medium to evaporimeter on the contrary, by the unnecessary cooling capacity being caused by it, low-pressure lateral pressure is reduced, and has the problem that produces the so-called short circulation that compressor stops immediately.
Summary of the invention
The present invention sets up in order to solve above-mentioned existing technical task, and its object is to provide a kind of valve opening of the expansion valve can suitably control compressor start time, reduces the refrigerating plant that starts load.
The refrigerating plant of first aspect present invention, form refrigerant loop by compressor, gas cooler, expansion valve and evaporimeter, its high-pressure side becomes supercritical pressure, wherein, possesses the control module of controlling compressor and expansion valve, the valve opening of expansion valve when this control module changes compressor start based on ambient atmos temperature.
The refrigerating plant of second aspect present invention, on the basis of above-mentioned first aspect, control module expands the valve opening of expansion valve, the valve opening of dwindling expansion valve in the situation that extraneous gas temperature is low in the situation that extraneous gas temperature is high.
The refrigerating plant of third aspect present invention, on the basis of above-mentioned each side, comprising: refrigeration machine, and it has compressor and gas cooler; Load equipment, it has evaporimeter and expansion valve, and control module has: refrigeration pusher side control module, it is located at refrigeration machine, and compressor is controlled; Load equipment side control module, it is located at load equipment, and expansion valve is controlled, and by carry out the standard valve aperture of the expansion valve that modified load equipment side control module has based on ambient atmos temperature, thereby changes the valve opening of expansion valve.
The refrigerating plant of fourth aspect present invention, on basis aspect above-mentioned, control module is by the pusher side control module that freezes, load equipment side control module and with this refrigeration pusher side control module and load equipment side control module carry out data sending and receiving main control unit form, this main control unit receives the data about the standard valve aperture of expansion valve from load equipment side control module, and receive the data about ambient atmos temperature from refrigeration pusher side control device, standard valve aperture is revised, and the data of this revised valve opening about expansion valve are sent to load equipment side control module, the data of the valve opening about expansion valve of load equipment side control module based on sending from main control unit are controlled expansion valve.
The refrigerating plant of fifth aspect present invention, on the basis of the above-mentioned third aspect or fourth aspect, load equipment side control module has the standard valve aperture of the expansion valve after standard valve aperture, the compressor start of the expansion valve in compressor start moment, and each standard valve aperture is revised respectively.
The refrigerating plant of sixth aspect present invention, on the basis of above-mentioned each side, uses and has carbon dioxide as cold-producing medium.
According to the present invention, due to by compressor, gas refrigeration device, expansion valve and evaporimeter form refrigerant loop and high-pressure side are become in the refrigerating plant of supercritical pressure, there is the control module of controlling compressor and expansion valve, the valve opening of expansion valve when this control module changes compressor start based on ambient atmos temperature, so as second aspect present invention, high at extraneous gas temperature, under the high situation of the equalizing pressure of refrigerant loop, the valve opening expansion of expansion valve is prevented to the abnormal ascending of high side pressure, can reduce the startup load of compressor, and low at extraneous gas temperature, under the low situation of equalizing pressure, dwindle the valve opening of expansion valve and can prevent the generation of the short circulation being caused by the surplus of cooling performance.
In addition, as third aspect present invention and fourth aspect by refrigeration pusher side control module, load equipment side control module, the main control unit that carries out the sending and receiving of data with these control modules forms control module, load equipment side control module has the data relevant to the standard valve aperture of expansion valve, the data about ambient atmos temperature of main control unit based on receiving from refrigeration pusher side control module are revised the words of standard valve aperture, even if there is the situation of communication abnormality etc. between main control unit and load equipment side control module, load equipment side control module also can be made as expansion valve standard valve aperture without barrier.
In addition, as fifth aspect present invention the standard valve aperture of the expansion valve after standard valve aperture, the compressor start of the expansion valve of load equipment side control module while thering is compressor start, each standard valve aperture is revised respectively, can to starting, all be carried out without barrier the control of expansion valve from the Startup time of compressor.Above aspect is effective in the refrigerating plant taking carbon dioxide as cold-producing medium especially.
Brief description of the drawings
Fig. 1 is the refrigerant loop figure that is suitable for the refrigerating plant of one embodiment of the invention;
Fig. 2 is the block diagram of the control device of the refrigerating plant of Fig. 1;
Fig. 3 is the figure of the control device of the key diagram 2 operating frequency control to compressor;
Fig. 4 is the figure of the valve opening control of the control device of key diagram 2 expansion valve during to compressor start.
Description of symbols
C: control device (control module)
R: refrigerating plant
1: refrigerant loop
3: refrigeration machine
4: showcase
8,9: refrigerant piping
11: compressor
24: intercooler
28: gas cooler
32: expansion valve
33: evaporimeter
34: refrigeration machine side controller (refrigeration pusher side control module)
35: master controller (main control unit)
36: showcase side controller (showcase side control module)
Detailed description of the invention
Below, with reference to accompanying drawing, embodiments of the present invention are described in detail.Fig. 1 is the refrigerant loop figure that is suitable for the refrigerating plant R of the embodiment of object of the present invention.Refrigerating plant R in the present embodiment is arranged on the shops such as supermarket, there is refrigeration machine 3 and in shop, be provided with one or more showcase 4(load equipment), these refrigeration machines 3 and showcase 4 utilize refrigerant piping 8 and 9 and link via unit outlet 6 and unit entrance 7, form the refrigerant loop 1 of regulation.
This refrigerant loop 1 uses carbon dioxide that on high-tension side refrigerant pressure (high-pressure) becomes its critical pressure above (overcritical) as cold-producing medium.This carbon dioxide coolant is the natural refrigerant useful to environment of having considered combustibility and toxicity etc.In addition, as the oil of lubricating oil, for example, use the poly-alkylene ethylene glycol of mineral oil (mineral oil), alkylbenzene oil, ether oil, ester oil, PAG() etc. existing oil.
Refrigeration machine 3 possesses compressor 11.In the present embodiment, compressor 11 is multi-stage compression formula rotary compressors, by cylindric closed container 12, form as electric element 13 and the portion of rotary compression mechanism of driving element, closed container 12 is made up of steel plate, driving element 13 is configured the top of the inner space that is accommodated in closed container 12, and portion of rotary compression mechanism is by being configured in the downside of electric element 13 and consisting of rotation shaft-driven first (rudimentary side) rotary compression element (the first compressing member) 14 and second (senior side) rotary compression element (the second compressing member) 16.
The first rotary compression element 14 of compressor 11 compresses the low pressure refrigerant that sucks compressor 11 from the low-pressure side of refrigerant loop 1 via refrigerant piping 9, after boosting to middle pressure, discharge, the second rotary compression element 16 again sucks the middle compression refrigerant that is compressed rear discharge by the first rotary compression element 14 to compress, boost to high pressure, discharge to the high-pressure side of refrigerant loop 1.Compressor 11 is compressors of frequency conversion type, by changing the operating frequency of electric element 13, can control the rotating speed of the first rotary compression element 14 and the second rotary compression element 16.
Be formed with in the side of the closed container 12 of compressor 11 the rudimentary side draught entrance 17 that is communicated with the first rotary compression element 14, with the interior rudimentary side outlet 18 being communicated with of closed container 12, the senior side draught entrance 19 and the senior side outlet 21 that are communicated with the second rotary compression element 16.The rudimentary side draught entrance 17 of compressor 11 is connected with cold-producing medium ingress pipe 22 and is connected with refrigerant piping 9.
The refrigerant gas that is drawn into the low pressure (LP: be 2.6Mpa left and right under normal operation) of the low voltage section of the first rotary compression element 14 by rudimentary side draught entrance 17 boosts to after middle pressure (MP: be 5.5Mpa left and right under normal operation), to the interior discharge of closed container 12 by this first rotary compression element 14.Thus, in closed container 12, become middle pressure (MP).
And pressure goes out pipe arrangement 23 and is connected with one end of intercooler 24 during the rudimentary side outlet 18 of each compressor 11 that the middle compression refrigerant gas in closed container 12 is discharged connects.This intercooler 24 carries out air cooling to compression refrigerant discharging from the first rotary compression element 14, is connected with middle pressure suction line 26 at the other end of this intercooler 24, presses suction line 26 to be connected with the senior side draught entrance 19 of compressor 11 in this.
The refrigerant gas that is drawn into the middle pressure (MP) of the second rotary compression element 16 by senior side draught entrance 19 carries out second level compression by this second rotary compression element 16 becomes the refrigerant gas of HTHP (HP: be the supercritical pressure about 9Mpa under normal operation).
And, being connected with high pressure and discharging one end of pipe arrangement 27 at the senior side outlet 21 of the second rotary compression element 16 of being located at compressor 11, the other end is connected with the entrance of gas cooler (radiator) 28.The 20th, be folded in this high pressure and discharge the oil eliminator in pipe arrangement 27.Oil eliminator 20 separates the oil the cold-producing medium of discharging from compressor 11 make its oily path 25A via oil cooler 25 and motor-driven valve 25B and returns in the closed container 12 of compressor 11.In addition, the 55th, the float switch of the fuel head in detection compressor 11.
On the other hand, showcase 4 is arranged in the shop such as supermarket and convenience store, is connected with refrigerant piping 8 and 9.Be provided with expansion valve (electric expansion valve) 32 and evaporimeter 33 at showcase 4, between refrigerant piping 8 and refrigerant piping 9, be connected successively (expansion valve 32 is in refrigerant piping 8 sides, and evaporimeter 33 is in refrigerant piping 9 sides).Evaporimeter 33 and pressure fan 53(Fig. 2 for the circulating cold air of blowing to this evaporimeter 33) in abutting connection with arranging.And, refrigerant piping 9 as described abovely via cold-producing medium ingress pipe 22 with and the rudimentary side draught entrance 17 that is communicated with of the first rotary compression element 14 of compressor 11 be connected.Thus, form the refrigerant loop 1 of the refrigerating plant R in the present embodiment.In addition, the mark 37 in figure, for to make the check-valves that oil eliminator 20 sides are positive direction, is located in high pressure and discharges in pipe arrangement 27.
In addition, the refrigerant loop 1 of the refrigerating plant R of embodiment, for cutting apart circulation, comprising: the first rotary compression element (rudimentary side) 14 of compressor 11, intercooler 24, conduct make interflow device 41, the second rotary compression element (senior side) 16 of compressor 11, gas cooler 28, by-passing type heat exchanger 29, current divider 42, auxiliary expansion valve (auxiliary electric expansion valve) 43, expansion valve 32, the evaporimeter 33 of the converging device at the mobile interflow of two fluids.
Major loop in Fig. 1 refers to, the ring-type refrigerant loop being formed by the first rotary compression element 14, intercooler 24, interflow device 41, the second rotary compression element 16, check-valves 37, oil eliminator 20, gas cooler 28, the second stream 29B of by-passing type heat exchanger 29, current divider 42, expansion valve 32, evaporimeter 33, subsidiary loop refers to, arrives successively the loop of interflow device 41 from current divider 42 via the first stream 29A of auxiliary expansion valve 43, by-passing type heat exchanger 29.
The cold-producing medium of discharging from the first rotary compression element 14 of compressor 11 has carried out air cooling at intercooler 24, is inhaled into the second rotary compression element 16 compressed of compressor 11 via interflow device 41.And, from the second rotary compression element 16 discharge and via the second stream 29B(second refrigerant stream of check-valves 37, oily current divider 20, gas cooler 28, by-passing type heat exchanger 29), current divider 42 and arrive expansion valve 32.Therefore, cold-producing medium flows into evaporimeter 33 and evaporates after being depressurized.Under heat-absorbing action at this moment, bring into play cooling capacity.The degree of superheat of this evaporimeter 33 is controlled at appropriate value by expansion valve 32.
Aux. control valve 43 is by the first cold-producing medium stream decompression of shunting at current divider 42 and flowing at subsidiary loop.The heat exchanger of by-passing type heat exchanger 29 for the second refrigerant stream that is flowed and flowed out from gas cooler 28 by the first cold-producing medium of auxiliary expansion valve 43 post-decompression subsidiary loops is carried out to heat exchange.Be provided with relation that can heat exchange the second stream 29B, the first stream 29A that above-mentioned the first cold-producing medium stream flows that second refrigerant stream flows at this by-passing type heat exchanger 29, second refrigerant stream passes through at the second stream 29B of this by-passing type heat exchanger 29, the the first cold-producing medium stream being flowed at the first stream 29A is cooling, so can reduce the specific enthalpy in evaporimeter 33.
In addition, in the high-pressure side that becomes supercritical pressure in refrigeration machine loop 1, in the present embodiment for the by-passing type heat exchanger 29 of refrigeration machine 3 and the downstream of current divider 42, be connected with refrigerant amount regulating tank 52 via the first connected loop 51.In the first connected loop 51, be folded with the expansion valve (electric expansion valve) 56 in order to regulate refrigeration machine yield with regulation function.
In addition, be connected with on the top of this refrigerant amount regulating tank 52 in this refrigerant amount regulating tank 52 and the second connected loop 58 of the middle pressure regional connectivity of refrigerant loop 1.In the present embodiment, the other end of the second connected loop 58 is as an example in middle nip territory, is communicated with the middle pressure suction line 26 of the outlet side of the intercooler 24 of refrigerant loop 1.In this second connected loop 58, be folded with magnetic valve 59.
In addition, be connected with in the bottom of this refrigerant amount regulating tank 52 the third connecting loop 62 of the middle pressure regional connectivity of this interior bottom of refrigerant amount regulating tank 52 and refrigerant loop 1.In the present embodiment, the other end in third connecting loop 62 is connected with the downstream of above-mentioned auxiliary expansion valve 43 as the example in middle nip territory, and the middle pressure suction line 26 of the outlet side of the intercooler 24 of final and refrigerant loop 1 is communicated with.In this third connecting loop 62, be folded with magnetic valve 63 and capillary (throttling unit) 64.
The expansion valve 56 of this refrigerant amount regulating tank 52 and magnetic valve 59,63 are controlled by above-mentioned refrigeration machine side controller 34, the rising of high side pressure HP based on refrigeration machine loop 1, the valve opening of expansion valve 56 is expanded, magnetic valve 59 is opened, magnetic valve 63 cuts out, at the interior recovery refrigeration machine of refrigerant amount regulating tank 52, based on the reduction of high side pressure HP, magnetic valve 59 cuts out, magnetic valve 63 is opened and refrigeration machine is discharged.Thus, the circularly cooling dosage in refrigerant loop 1 is controlled to appropriate value, prevents that high side pressure HP from rising too much due to too much circularly cooling dosage.
In addition, be provided with the bypass circulation 71 being communicated with for cold-producing medium ingress pipe 22 for the low-pressure side of above-mentioned the second connected loop 58 of being connected with the outlet side of this intercooler 24 and refrigerant loop 1, in the present embodiment by the middle nip territory of the refrigerant loop of the outlet side of the intercooler of refrigerating plant R 24 1, in the present embodiment.And, be folded with in the time that compressor 11 starts open and for improving the magnetic valve 72 of startability at this bypass circulation 71.
In addition, in Fig. 1, PS1 discharges with high pressure that pipe arrangement 27 is connected and the discharge pressure that detects compressor 11 is the high pressure sensor of the high side pressure HP of refrigerant loop 1, PS2 is connected with cold-producing medium ingress pipe 22 and the suction pressure that detects compressor 11 is the low pressure sensor of the low-pressure lateral pressure LP of refrigerant loop 1, and PS3 is the intermediate pressure sensor that is connected and detects the intermediate pressure MP of refrigerant loop 1 with middle pressure suction line 26.
In addition, in Fig. 1, TS1 discharges with high pressure the discharge temperature sensor that pipe arrangement is connected and detects the discharging refrigerant temperature of compressor 11, TS2 is the gas refrigerant outlet temperature sensor that is connected and detects the refrigerant temperature flowing out from gas cooler 28 with the outlet of gas cooler 28, TS3 is the by-passing type outlet temperature sensor being connected with the outlet of the first stream 29A of by-passing type heat exchanger 29, TS4 is the outlet temperature sensor of refrigeration machine 3, TS5 is the inlet temperature sensor of refrigeration machine 3, TS6 is the ambient atmos temperature sensor that detects ambient atmos temperature.
Then, Fig. 2 is the block diagram as the control device C of the control module of refrigerating plant R.In the figure, 35 are arranged on the master controller as main control unit of the caretaker room in shop etc., the 34th, be located at the refrigerating device controller of the above-mentioned refrigeration pusher side control module of the conduct of refrigeration machine 3, the 36th, be located at respectively the above-mentioned showcase side controller as showcase side control module of each showcase.Arbitrary controller forms by general microcomputer, master controller 35 with these refrigeration machine side controllers 34 and showcase side controller 36(one or more) carry out the reception of data and the mode of transmission utilizes order wire to be connected.
The input of refrigeration machine side controller 34 has each sensors such as connecting above-mentioned ambient atmos temperature sensor TS6 (being represented by S as representative in Fig. 2), in addition, the output of refrigeration machine side controller 34 has the compressor 11(of connection electric element 13), auxiliary expansion valve 43, pressure fan 31 for gas cooler, expansion valve 56, each magnetic valve 59,63, motor-driven valve 25B etc.The input of showcase side controller 36 is connected with the in-cabinet temperature sensor 60 of the in-cabinet temperature that detects showcase 4 etc., and the output of showcase side controller 36 is connected with expansion valve 32 and above-mentioned circulating cold air pressure fan 53 etc.
The set points of temperature that the various setting datas such as the design temperature of showcase side controller 36 based on sending from master controller 35 and in-cabinet temperature sensor 53 detect etc. are controlled expansion valve 32 and pressure fan 60 for circulating cold air.In addition, the information of itself being set and operating condition, the data that alarm is relevant send to master controller 35.The compressor 11 that refrigeration machine side controller 34 temperature that also the various setting datas based on sending from master controller 35 (target zone that comprises low-pressure lateral pressure LP described later and stop value) detect with each sensor S and pressure control are connected with output and expansion valve 43,56, each magnetic valve 59,63 etc., carry out the recovery of the refrigeration machine of the above-mentioned control of cutting apart circulation and use refrigerant amount regulating tank 52, the control of discharge.
(A) control of the operating frequency of compressor
Then, use Fig. 3 to refrigeration machine side controller 34 to compressor 11(electric element 13) the control of operating frequency describe.The low-pressure lateral pressure LP in refrigeration machine loop 1 that the refrigeration machine side controller 34 of refrigeration machine 3 detects based on low pressure sensor PS2 controls compressor 11(electric element 13) operating frequency.
The in the situation that of this embodiment, refrigeration machine side controller 34 is carried out Region control as shown in Figure 3.That is, the low-pressure lateral pressure LP detecting at low pressure sensor PS2 is than the high region 1 of the higher limit of define objective scope, and the operating frequency that makes compressor 11 was every stipulated time t1(for example 10 seconds) rising 1Hz.In addition, by the control limit upper limit specifying, the rising of this operating frequency is tended towards stability.In addition, at low-pressure lateral pressure LP, in the region 3 lower than the lower limit of above-mentioned target zone, the operating frequency that makes compressor 11 is every than the short stipulated time t2(of afore mentioned rules time t1 for example 1 second) decline 1Hz., make compressor 11 operating frequency decline underspeed than make its rise time the rate of climb fast.This is in order to prevent that as much as possible low-pressure lateral pressure LP from reaching the value that stops described later.Also by the control limit lower limit specifying, the reduction of this operating frequency is tended towards stability.
In addition, the region 2 at low-pressure lateral pressure LP more than lower limit, below higher limit, low-pressure lateral pressure LP, in target zone, does not change the operating frequency of compressor 11.Thus, the mode becoming in target zone with the low-pressure lateral pressure LP of refrigerant loop 1 in the time conventionally turning round makes the operating frequency of compressor 11 rise or decline.
In addition, for example, because the expansion valve 32 of whole showcases 4 connecting cuts out etc., even if pass through the control of the operating frequency of compressor 11, low-pressure lateral pressure is also lower than lower limit and be reduced to the stopping below value of the regulation lower than lower limit, become in the situation in region 4, refrigeration machine side controller 34 stops compressor 11.
If compressor 11 stops, refrigeration machine side controller 34 (restarts and forbids the time) startup of forbidding compressor 11 at the appointed time.During this period, the high-pressure side in refrigerant loop 1 and the pressure of low-pressure side become equalizing pressure.Afterwards, due to in-cabinet temperature rising of showcase 4 etc. and expansion valve 32 is opened, low-pressure lateral pressure LP restarts in the situation that value (routine higher limit described above) rises higher than regulation, forbids that to have passed through to restart the time is as condition, and refrigerating device controller 34 starts compressor 11.
(B) Stabilization Control when compressor start
Then, Stabilization Control when compressor 11 starts is described.As previously mentioned, refrigerating device controller 34 carries out the mode in target zone with low-pressure lateral pressure LP makes the operating frequency of compressor 11 rise or decline, the control that compressor 11 is stopped, but the equalizing pressure in the refrigerant loop 1 after compressor 11 stops is according to ambient atmos temperature and difference, in extraneous gas temperature high summer, equalizing pressure uprises, in extraneous gas temperature low winter, and equalizing pressure step-down.
And if start compressor 11 under the high state of equalizing pressure,, because low-pressure lateral pressure LP is in region 1, the operating frequency of compressor 11 rises to high value immediately.On the other hand, because the evaporimeter 33 of showcase 4 turns cold, stop value so low-pressure lateral pressure LP sharply reduces and reaches, compressor 11 is stopped.Therefore, compressor 11 start and stop continually repeatedly (so-called short circulation), and the so-called overshoot of operating frequency also becomes greatly, and high side pressure P also rises singularly.
On the contrary, if start compressor 11 under the low state of equalizing pressure, the load of showcase 4 sides (cold air load) also diminishes and evaporimeter 33 also turns cold, and stops value and makes compressor 11 be absorbed in the state of repeatedly starting and stopping continually so low-pressure lateral pressure LP sharply reduces still to reach.
Therefore, refrigeration machine side controller 34 of the present invention is after compressor 11 starts, monitor the variation of the low-pressure lateral pressure LP of the refrigerant loop 1 of low pressure sensor PS2 detection, in the case of more than being judged as the setting that the decrease speed of low-pressure lateral pressure LP is regulation (die-offing), even if low-pressure lateral pressure LP, in above-mentioned zone 1, also forbids the rising of the operating frequency of compressor 11.
Thus, after starting compressor 11 under state for equalizing pressure in refrigerant loop 1, under the situation reducing sharp at low-pressure lateral pressure LP, forbid the rising of the operating frequency of compressor 11, so can be by the sharply reduction of the low-pressure lateral pressure LP after being accompanied by compressor 11 and starting, this low-pressure lateral pressure L reaches the unfavorable condition that stops value and stop immediately and prevents trouble before it happens.Therefore, refrigerating plant R compressor 11 problem of frequent start-stop repeatedly in the time starting can be eliminated, operating condition stabilisation can be made early.
(C) the valve opening control of expansion valve when compressor start
The control of the expansion valve 32 when then, compressor 11 startup describes.The rising cooled dose (gas refrigerant) of the high side pressure HP of the refrigerant loop 1 when compressor 11 starts as described above affects significantly to the inflow resistance of the evaporimeter 33 of showcase 4, but this inflow resistance is determined by the valve opening of expansion valve 32.But this expansion valve (electric expansion valve) 32 does not move under the speed of variation that can not follow high side pressure HP.
Therefore, preset the standard valve aperture of expansion valve 32 in the past, in the time that starting, compressor 11 controls the inflow resistance to evaporimeter 33 using the valve opening of expansion valve 32 as this standard valve aperture, but as described above, because the equalizing pressure in the refrigerant loop 1 of compressor 11 after stopping is according to changing season, so in summer, standardization valve opening is too small and cause the rising of high side pressure HP, in the winter time, standard valve aperture is excessive and make too much cold-producing medium flow into evaporimeter 33 on the contrary, cause low-pressure lateral pressure LP to reduce by too much cooling capacity, make as previously mentioned compressor 11 stop immediately (short circulation).
Therefore, master controller 35 is revised this standard valve aperture based on ambient atmos temperature, the valve opening of the expansion valve 32 when change compressor 11 starts.Fig. 4 represents the situation of valve opening control.First, the standard valve aperture of the expansion valve 32 in this embodiment of expression of the right side of Fig. 4 central authorities, following table is shown with correction value (variable quantity) thereon.The left side of Fig. 4 represents the transition of ambient atmos temperature.
The in the situation that of embodiment, the valve opening that the standard valve aperture of expansion valve 32 is divided into compressor 11 Startup times (, valve opening when startup) and start after valve opening, the in the situation that of this showcase 4, the standard valve aperture of Startup time is 150 pulses, standard valve aperture after startup is 120 pulses, is provided with in advance showcase side controller 36.In addition, this umber of pulse represents that electric expansion valve is the valve opening of expansion valve 32, under full-shut position, is zero (0), and umber of pulse is larger, and valve opening more expands.
When master controller 35 is connected with refrigerant piping 8,9 at showcase 4 and showcase side controller 36 is connected with main control 35, receive and read the data relevant to this standard valve aperture from showcase side controller 36.In addition, receive and read from refrigeration machine side controller 34 data about ambient atmos temperature that ambient atmos temperature sensor TS6 detects.
And, the ambient atmos temperature of master controller 35 based on receiving from refrigeration machine side controller 34, in the situation that extraneous gas temperature is high, by the standard valve aperture reading from showcase side controller 36 to direction of expansion correction, in the situation that extraneous gas temperature is low, standardization valve opening is also changed to dwindling adjustment in direction.The in the situation that of embodiment, ambient temperature rises and arrives when more than 30 DEG C, in standard valve aperture after standard valve aperture and the startup of Startup time, add respectively 150 pulses (variable quantity), while reaching below 10 DEG C in extraneous gas temperature reduction, the standard valve aperture from standard valve aperture and the startup of Startup time deducts respectively 50 pulses (variable quantity).
That is, be (equalizing pressure is high) more than 30 DEG C in the situation that at extraneous gas temperature, the standard valve aperture of Startup time expands 300 pulses to, and the standard valve aperture after startup expands 280 pulses to.On the other hand, be (equalizing pressure is low) below 10 DEG C in the situation that at extraneous gas temperature, the standard valve aperture of Startup time narrows down to 100 pulses, and the standard valve aperture after startup narrows down to 70 pulses.
In addition, ambient atmos temperature rise and further rise and reach before 30 DEG C and ambient atmos temperature declines and rise from the state 25 DEG C below is further and reached before 10 DEG C from more than 15 DEG C states, master controller 35 does not carry out above-mentioned control.In addition, the diagram that the arrow mark in Fig. 4 left side does not overlap means sluggishness.
And when refrigeration machine side controller 34 starts compressor 11 as previously mentioned, this refrigeration machine side controller 34 sends the data that start advance notice (starting advance notice) to master controller 35.Master controller 35 receives and starts when advance notice from this refrigeration machine side controller 34, and the data relevant to the valve opening of the Startup time of revised expansion valve 32 as described above or uncorrected valve opening (being standard valve aperture) are sent to showcase side controller 36.Showcase side controller 36 is controlled to expansion valve 32 at the Startup time (in fact before it) of compressor 11 valve opening of the Startup time of the expansion valve 32 receiving from master controller 35, and after startup, expansion valve 32 is controlled to the valve opening after the startup receiving.
Like this, the valve opening of the expansion valve 32 while startup based on ambient atmos temperature change compressor 11, under the high situation of equalizing pressure high at extraneous gas temperature and refrigerant loop 1, expand the valve opening of expansion valve 32 and can prevent the abnormal ascending of high side pressure HP, can reduce the startup load of compressor 11, and under and situation that equalizing pressure is low low at extraneous gas temperature, the valve opening that can dwindle expansion valve 32, prevents the generation of the short circulation that the surplus of cooling performance causes.
In addition, showcase side controller 36, in the case of not receiving the data relevant to revised valve opening from master controller 35, utilizes the standardization valve opening control expansion valve 32 self being provided with.; the in the situation that of embodiment; the standard valve aperture of expansion valve 32 has the showcase side control valve 36 of showcase 4; so produced the situation of communication abnormality etc. between master controller 35 and showcase side controller 36; from the Startup time of compressor 11, to startup, showcase side controller 36 also can be made as standard valve aperture by expansion valve 32 without barrier.
In addition, in an embodiment, utilize Region control that low-pressure lateral pressure LP is controlled in target zone, but be not limited to this, control as desired value even control to wait by so-called PID, the present invention is also effective.In addition, the each numerical value shown in embodiment is not limited to this, should suitably change according to the scale of refrigerating plant and purposes.
Claims (6)
1. a refrigerating plant, forms refrigerant loop by compressor, gas cooler, expansion valve and evaporimeter, and its high-pressure side becomes supercritical pressure, it is characterized in that,
Possess the control module of controlling described compressor and expansion valve,
The valve opening of described expansion valve when described control module changes described compressor start based on ambient atmos temperature.
2. refrigerating plant as claimed in claim 1, is characterized in that,
Described control module expands the valve opening of described expansion valve, the valve opening of dwindling described expansion valve in the situation that extraneous gas temperature is low in the situation that extraneous gas temperature is high.
3. refrigerating plant as claimed in claim 1 or 2, is characterized in that,
Comprise: refrigeration machine, it has described compressor and gas cooler; Load equipment, it has described evaporimeter and expansion valve,
Described control module has: refrigeration pusher side control module, and it is located at described refrigeration machine, and described compressor is controlled; Load equipment side control module, it is located at described load equipment, described expansion valve is controlled,
By revise the standard valve aperture of the described expansion valve that described load equipment side control module has based on ambient atmos temperature, thereby change the valve opening of described expansion valve.
4. refrigerating plant as claimed in claim 3, is characterized in that,
Described control module forms by described refrigeration pusher side control module, described load equipment side control module and with the main control unit that this refrigeration pusher side control module and load equipment side control module carry out the sending and receiving of data,
This main control unit receives the data about the standard valve aperture of described expansion valve from described load equipment side control module, and receive the data about ambient atmos temperature from described refrigeration pusher side control device, described standard valve aperture is revised, and the data of this revised valve opening about described expansion valve are sent to described load equipment side control module
The data of the valve opening about described expansion valve of described load equipment side control module based on sending from described main control unit are controlled described expansion valve.
5. the refrigerating plant as described in claim 3 or 4, is characterized in that,
Described load equipment side control module has the standard valve aperture of the described expansion valve after standard valve aperture, the described compressor start of the described expansion valve in described compressor start moment, and each standard valve aperture is revised respectively.
6. the refrigerating plant as described in any one in claim 1～5, is characterized in that,
Use and have carbon dioxide as cold-producing medium.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-261088 | 2012-11-29 | ||
| JP2012261088A JP6206787B2 (en) | 2012-11-29 | 2012-11-29 | Refrigeration equipment |
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| Publication Number | Publication Date |
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| CN103851817A true CN103851817A (en) | 2014-06-11 |
| CN103851817B CN103851817B (en) | 2017-06-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310627518.3A Active CN103851817B (en) | 2012-11-29 | 2013-11-29 | Refrigerating plant |
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| JP (1) | JP6206787B2 (en) |
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| CN108603697A (en) * | 2016-02-08 | 2018-09-28 | 松下知识产权经营株式会社 | Refrigerating plant |
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| CN108195097A (en) * | 2017-12-27 | 2018-06-22 | 安徽环球星新能源科技有限公司 | A kind of total assembling structure of CO 2 trans-critical heat pump |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN103851817B (en) | 2017-06-13 |
| JP6206787B2 (en) | 2017-10-04 |
| JP2014105962A (en) | 2014-06-09 |
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