CN1149364C - Refrigerator - Google Patents

Abstract

To lower the temperature of a condenser on the side of vapor phase, eliminate a temperature difference between condenser peripheral temperature on the vapor phase side and on a liquid phase side, and hence prevent condenser internal pressure from being raised by increasing a heat exchange amount at a refrigerant inlet side of the condenser of a refrigerator apparatus using a hydrofluorocarbon mixed refrigerant higher than that at an outlet side. A refrigerant apparatus is adapted such that respective devices of a compressor 1, a condenser 2, a throttle device 3, and an evaporator 4 are connected in order to form a refrigerant circuit for circulating a refrigerant, and mixture refrigerant is used which is yielded by mixing several kinds of hydrofluorocarbons in a refrigerant. In the refrigerant apparatus, a heat exchange amount on the side of a refrigerant inlet 2a of the condenser 2 is more increased increased than on the side of a refrigerant outlet 2b. For this, a fan is provided on the condenser 2 with which fan an air amount to the condenser 2 is more increased at the refrigerant inlet side 2a of the condenser 2 than at the refrigerant outlet side 2b. Further, for a heat exchange piping of the condenser 2 there is used one having a larger heat transfer surface area and a high heat transmission rate at the refrigerant inlet side 2a than at the refrigerant outlet side 2b (e.g. internal surface grooved pipe).

Description

Refrigerating plant

The present invention system is with the refrigerating plant of hydrogen fluorohydrocarbon as refrigerant about refrigerating plant used in display case, freezer, the insulating box.

In the past, this refrigerating plant has, disclosed device in for example real public clear 58-48987 communique.

This refrigerating plant as shown in Figure 30, is formed by connecting compressor 1, condenser 2, throttling arrangement 3, evaporimeter 4 with pipeline 5, and hair-dryer 6 is set near evaporimeter 4, and disposes temperature sensing tube 7 on evaporimeter 4 outlet side pipelines 5.

The action of this refrigerating plant is that the temperature of temperature sensing tube 7 also descended when for example the liquid refrigerant temperature in evaporimeter 4 descended, and the blast intensity of hair-dryer 6 is reduced, thereby makes storehouse temperature keep certain.

, when adopting said structure, for the situation of the non-vapor of mixture refrigerant that several hydrogen fluorohydrocarbons are mixed as refrigerant, its Mollier enthalpy-entropy diagram will become for example state shown in Figure 31.That is, exist thermograde between the mixing refrigerant that several hydrogen fluorohydrocarbons mix, in above-mentioned condenser crushing is arranged, so just become 55 ℃ in the gas-liquid two-phase gas phase side temperature partly of above-mentioned condenser, the liquid side temperature then is 52 ℃.Thereby, make the gas phase side of above-mentioned condenser different with the temperature difference of condenser environment temperature with liquid side, can not bring into play condenser performance to greatest extent or make the undue problem that raises of above-mentioned condenser internal pressure with regard to having, that is, the heat exchange amount Q in condenser is determined by following formula.

Q＝KAΔT

Wherein, K: be heat transfer coefficient,

A: heat transfer area,

Δ T: the temperature difference

Have in condenser under the situation of Δ T difference (the entrance side temperature difference is big, and outlet side has a narrow range of temperature), because outlet side has a narrow range of temperature, its heat exchange amount diminishes, thereby the heat exchange amount of whole condenser is diminished, so often can not bring into play the performance of condenser to greatest extent.

Under the situation that condenser performance can not get bringing into play to greatest extent, in order to increase the heat exchange amount of condenser, even the device running just produced the too high part of condensation temperature, and condensing pressure uprises excessively also so that Δ T increases.

In addition, owing to exist thermograde in the refrigerant that mixes with several hydrogen fluorohydrocarbons, and on above-mentioned evaporimeter, crushing is arranged, will make, for example shown in Figure 31, the temperature of above-mentioned evaporator inlet side is-20 ℃, and the gas phase side temperature of gas-liquid two-phase portion is-18 ℃.Thereby make the interior refrigerant temperature of the above-mentioned evaporator inlet side and the evaporimeter of the gas phase side of gas-liquid two-phase portion different, frosting is different and become inhomogeneous frosting, then the not frosting of evaporimeter partly produces heat loss when defrosting, or makes the defrosting time lengthening, also can bring problems such as making the storehouse temperature rising.

And, when the refrigerant of the hydrogen fluorohydrocarbon that hydrogen fluorohydrocarbon (HCFC) the refrigerant R22 that the ozone layer destroying effect is arranged is changed into the ozone free destruction, in transformation period, R22 respectively has requirement with evaporimeter and hydrogen fluorohydrocarbon refrigerant with evaporimeter, above-mentioned two kinds of refrigerants, its refrigerant characteristic difference can not a shared evaporimeter, so must produce two kinds of evaporimeters, increase the machine problem in addition.

In addition, when using hydrogen fluorohydrocarbon refrigerant, also exist the problem of comparing its refrigeration output deficiency with the refrigerant R22 in past.

So that for example R404A uses as the hydrogen fluorohydrocarbon, will be as shown in Mollier enthalpy-entropy diagram and Figure 33 among Figure 32, under the situation of carrying out thermal control, its effective capacity (refrigeration effective capacity) that makes full use of evaporimeter is 3530Kcal/h for R22, to R404A then is 3401Kcal/h, can force rate be 96.3%, so the problem of refrigerating capacity deficiency is arranged.In addition, improve its refrigerating capacity and will make the exhaust temperature of compressor too high, also can make the reliability of compressor become problem.

The present invention proposes in order to solve the above problems, its objective is when using the mixing refrigerant that mixes by several hydrogen fluorohydrocarbons, the heat exchange amount that makes the condenser inlet side is greater than outlet side, the gas phase side temperature of above-mentioned condenser is descended, and make as much as possible in the gas phase side of above-mentioned condenser and the temperature difference of liquid side and condenser environment temperature and do not exist, thereby bring into play the performance of condenser to greatest extent, prevent that above-mentioned condenser internal pressure from rising.

Its purpose also is, and is little of required Min. by the difference that makes refrigerant temperature in condensator outlet side condenser environment temperature and condenser, and brings into play the performance of condenser to greatest extent, prevents that above-mentioned condenser internal pressure from rising.

The present invention also aims to, the control part of the above-mentioned condenser air quantity of control is set, so that the signal of temperature checkout part by detecting Temperature Distribution in the condenser and said temperature detecting element makes the uniformity of temperature profile in the condenser, thereby bring into play the performance of condenser to greatest extent and prevent that above-mentioned condenser internal pressure from rising.

Its another purpose be under the situation of using the refrigerant mix by several hydrogen fluorohydrocarbons in the evaporimeter refrigerant temperature even substantially, to prevent inhomogeneous frosting.

The present invention also aims to, even using under the refrigerant situation that mixes by several hydrogen fluorohydrocarbons, also can shared original equipment such as evaporimeter.

In addition, the present invention also aims to, in the refrigerating plant that uses a kind of or several hydrogen fluorohydrocarbons, can also improve its refrigeration output by supercooling control, suck gas at compressor simultaneously and wait the too high or oily temperature of the discharge temperature that prevents compressor too high, thereby guarantee the reliability of compressor above ending above-mentioned supercooling control under the situation of set point of temperature.

Refrigerating plant of the present invention is to connect various devices such as compressor, condenser, throttling arrangement and evaporimeter successively, refrigerant is circulated therein and form the refrigerant loop, and in the refrigerating plant of the mixing refrigerant that uses several hydrogen fluorohydrocarbons to mix, make the heat exchange amount of above-mentioned condenser inlet side be higher than outlet side.

In addition, on condenser, also be provided with hair-dryer, and make the air quantity of sending into above-mentioned condenser become the state of the refrigerant entrance side of condenser greater than the refrigerant exit side.

In addition, also make the condenser heat exchange use the heat transfer area of pipeline entrance side and heat exchanging fluid greater than outlet side.

Use the entrance side of pipeline to use the material bigger in the heat exchange of condenser than outlet side heat transfer coefficient.

Heat exchange amount for the condenser of obtaining regulation, for being benchmark with pipeline shape, the set heat transfer coefficient that decisions such as state are set and heat transfer area, with the outlet side of condenser, heat exchange is set on the required Min. in the permissible range with the temperature difference between fluid by heat exchange.

Make refrigeration loop that refrigerant circulates therein various devices such as compressor, condenser, throttling arrangement and evaporimeter being connected successively and form, in the refrigerating plant of the refrigerant that use is mixed by several hydrogen fluorohydrocarbons, be provided with condenser with pressure fan and control the pressure fan control part that above-mentioned pressure fan makes uniformity of temperature profile in the condenser by means of the signal of temperature checkout part that detects Temperature Distribution in the above-mentioned condenser and said temperature detecting element.

Make refrigeration loop that refrigerant circulates therein each equipment such as compressor, condenser, throttling arrangement and evaporimeter being connected in turn and form, in the refrigerating plant of the refrigerant that use is mixed by several hydrogen fluorohydrocarbons, the crushing in the above-mentioned evaporimeter makes the thermograde of refrigerant become essentially identical state.

In addition, also set the pipeline crushing of evaporimeter with pipeline shape and length.

Set the crushing of evaporator pipeline again with refrigerant flow rate in the control piper.

In addition, also be equipped with evaporimeter, its refrigerating capacity that makes when this evaporimeter is arranged in selected R404A for hydrogen fluorohydrocarbon mixing refrigerant is roughly the common port number of the port number of maximum evaporator heat exchanger as R404A and refrigerant R22.

And then, each equipment such as compressor, condenser, throttling arrangement and evaporimeter is being connected successively, and form the refrigeration loop that refrigerant is circulated therein, and use in the refrigerating plant of hydrogen fluorohydrocarbon as refrigerant, also be provided with the supercooling heat exchanger that high-pressure liquid refrigerant and low pressure gaseous coolant carry out heat exchange.

In device, use hydrogen fluorohydrocarbon R404A or hydrogen fluorohydrocarbon R507 as refrigerant.

Wherein, also use dual pipe, flow through the low pressure gaseous coolant in the interior pipe, flow through the high-pressure liquid refrigerant in the annulus as the supercooling heat exchanger that high-pressure liquid refrigerant and low pressure gaseous coolant carry out heat exchange.

In addition, the supercooling heat exchanger that also makes high-pressure liquid refrigerant and low pressure gaseous coolant carry out heat exchange can be connected with the low pressure gas tube connector at the high pressure liquid tube connector midway midway, to become the other parts that improve refrigerating capacity.

And then, wherein also be provided with the refrigerant control device that the coolant quantity of this supercooling heat exchanger is flow through in control.

Fig. 1 is the structure chart of the present invention's the 1st embodiment refrigerating plant.

Fig. 2 is the condenser stereogram of the present invention's the 1st embodiment refrigerating plant.

Fig. 3 is the condenser pipe sectional view of the present invention's the 2nd embodiment refrigerating plant.

Fig. 4 is the structure chart of the present invention's the 4th embodiment refrigerating plant.

Fig. 5 is the condenser stereogram of the present invention's the 5th embodiment refrigerating plant.

Fig. 6 is the Mollier enthalpy-entropy diagram of the explanation usefulness of the present invention's the 5th embodiment refrigerating plant.

Fig. 7 is the refrigerating plant structure chart of the present invention the 6th embodiment.

Fig. 8 is the pipeline structure figure of evaporimeter of the refrigerating plant of the present invention the 7th embodiment.

Fig. 9 is the refrigerating plant evaporimeter number of vias of the present invention the 7th embodiment and the graph of a relation of refrigeration output.

Figure 10 is the refrigerating plant structure chart of the present invention the 8th embodiment.

Figure 11 is the explanation Mollier enthalpy-entropy diagram of the refrigerating plant of the present invention the 8th embodiment.

Figure 12 is the refrigeration output table of the refrigerating plant of expression the 8th embodiment.

Figure 13 is the refrigerating plant structure chart of the present invention the 9th embodiment.

Figure 14 is the explanation Mollier enthalpy-entropy diagram of the refrigerating plant of the present invention the 9th embodiment.

Figure 15 is the refrigerating plant structure chart of the present invention the 10th embodiment.

Figure 16 is the refrigerating plant structure chart of the present invention the 11st embodiment.

Figure 17 is the present invention's the 12nd embodiment refrigerating plant structure chart.

Figure 18 is the present invention's the 13rd embodiment refrigerating plant structure chart.

Figure 19 is the present invention's the 14th embodiment refrigerating plant structure chart.

Figure 20 is the present invention's the 15th embodiment refrigerating plant structure chart.

Figure 21 is the present invention's the 16th embodiment refrigerating plant structure chart.

Figure 22 is the present invention's the 17th embodiment refrigerating plant structure chart.

Figure 23 is the Mollier enthalpy-entropy diagram of its refrigerant cycles action of expression of the present invention's the 17th embodiment refrigerating plant.

Figure 24 is the chart of the refrigeration output of expression the present invention the 17th embodiment refrigerating plant.

Figure 25 is the another kind of structure chart of expression the present invention the 17th embodiment refrigerating plant.

Figure 26 is the structure chart of the present invention's the 18th embodiment refrigerating plant.

Figure 27 is another structure chart of the present invention's the 18th embodiment refrigerating plant.

Figure 28 is the another structure chart of the present invention's the 18th embodiment refrigerating plant.

Figure 29 is the other another structure chart of the present invention's the 18th embodiment refrigerating plant.

Figure 30 is the structure chart of existing refrigerating plant.

Figure 31 is the explanation Mollier enthalpy-entropy diagram of existing refrigerating plant.

Figure 32 is the Mollier enthalpy-entropy diagram that the refrigerating capacity of the existing refrigerating plant of explanation is used.

Figure 33 is the refrigeration output chart of the existing refrigerating plant of expression.

(embodiment 1)

Below, with reference to the description of drawings embodiments of the invention.

Fig. 1 is the structure chart that the multiple hydrogen fluorohydrocarbon of the use of the present invention the 1st embodiment mixes the refrigerating plant of non-vapor of mixture refrigerant, an example of the condenser that the refrigerating plant of Fig. 2 presentation graphs 1 is used.

In Fig. 1, connect compressor 1, condenser 2, throttling arrangement 3, evaporimeter 4 with pipeline 5, pressure fan 6 is set near evaporimeter 4, on the outlet side pipeline 5 of evaporimeter 4, temperature sensing tube 7 is set.Make the heat exchange amount of its entrance side 2a greater than outlet side 2b at above-mentioned condenser 2.

In Fig. 2, the 8th, the heat exchanger of above-mentioned condenser 2, refrigerant flows to downside from upside.The 9th, the condenser pressure fan is installed in the upside at above-mentioned heat exchanger 8 centers, and makes the air quantity top of above-mentioned condenser 2 bigger than the bottom.

The action of this refrigerating plant should be when liquid refrigerant temperature in the evaporimeter 4 for example descends, and the temperature of temperature sensing tube 7 descends, and the blast intensity of pressure fan 6 is reduced, to keep storehouse temperature certain.

In addition, the non-vapor of mixture refrigerant that uses multiple hydrogen fluorohydrocarbon to mix in the present invention, the heat exchange amount that makes above-mentioned condenser inlet side 2a is greater than outlet side 2b, thereby the gas phase side temperature of above-mentioned condenser is descended, the temperature difference of above-mentioned condenser 2 gas phase side and liquid side and condenser environment temperature is not existed, make as required perhaps that condenser temperature and its environment temperature of homogenising have the temperature difference of suitable setting and guarantee to have sufficient heat exchange amount, with the performance of bringing into play condenser to greatest extent and prevent that above-mentioned condenser internal pressure from rising.

The refrigerating plant of the mixing refrigerant that use of the present invention is mixed by multiple hydrogen fluorohydrocarbon is brought into play the performance of condenser 2 to greatest extent by the air quantity that makes above-mentioned condenser 2 tops greater than the air quantity of bottom, and can prevent that above-mentioned condenser internal pressure from rising.

Air quantity as the top that makes above-mentioned condenser 2 (entrance side) then can be considered a plurality of fans are installed greater than the method for the air quantity of its underpart (outlet side), and to make the top fan be high wind running, and the bottom fan is weak wind running.In addition, also can make the air quantity of the top air quantity of above-mentioned condenser 2 even make the crushing of above-mentioned condenser 2 constitute wind path littlely greater than its underpart than the bottom on top.

(embodiment 2)

The heat exchange amount that makes condenser 2 entrance sides also can be following other method greater than the method for outlet side:

Fig. 3 illustrates the interior section configuration of pipeline 12 of the heat exchanger 8 of the condenser 2 among Fig. 2.

Fig. 3 (a) is inner fluted trough of belt pipe, (b) is inner level and smooth smooth tubes.

In Fig. 2,3, upside uses the pipeline coefficient of overall heat transmission the pipe that inside groove arranged higher than the center of heat exchanger 8, downside then uses the pipeline coefficient of overall heat transmission than the low smooth tubes in heat exchanger 8 centers, the heat exchange amount that makes above-mentioned condenser 2 entrance sides is greater than outlet side, thereby can bring into play the performance of condenser 2 to greatest extent, prevent that above-mentioned condenser internal pressure from rising.

In addition, can also to the smooth tubes of outlet side the groove of entrance side be increased from the interior barrel of heat exchanger 8 entrance sides, the groove of outlet side reduces.

And, also can make the entrance side heat transfer area make the method for the heat exchange amount of above-mentioned condenser 2 entrance sides greater than outlet side greater than the method conduct of outlet side.Promptly it is also conceivable that to make entrance side fin number, or use the high shutter of the coefficient of overall heat transmission to turn to fin, then use the low ring type fin of the coefficient of overall heat transmission at outlet side at entrance side more than outlet side.

In addition, suitably make up, then can improve its effect more if change the method and the method in the present embodiment of wind speed (air quantity) utilizing the pressure fan described in the embodiment 1.

(embodiment 3)

The refrigerating plant of present embodiment has structure as shown in Figure 1.

In Fig. 1, the heat exchange amount Q of condenser 2 is determined by following formula.

Q＝K·A·ΔT………………(1)

In the formula, K: heat transfer efficiency,

A: heat transfer area,

Δ T: the temperature difference of refrigerant temperature and condenser environment temperature.

So far, though Q is determined by the refrigeration output of installing, and K and A be by heat exchange with the shape of pipeline, decision such as state is set, and in the present embodiment, in order to obtain the Q value of required condenser, the setting of its Δ T, promptly the setting of refrigerant temperature is that benchmark carries out with the condensator outlet side in the condenser.

Because the mixing refrigerant that has used the hydrogen fluorohydrocarbon to mix in the present invention exists thermograde in condenser, condenser inlet one side compares the refrigerant temperature height with outlet side, and it is big that Δ T becomes.

Thereby, for requiring with the condensator outlet side is that Q that benchmark is set Δ T is the necessary Min. that is set in permissible range, thereby guarantee the required heat exchange amount Q of condenser, and the difference that makes outlet side refrigerant temperature and environment temperature becomes desired minimum of a value, just can be suppressed at the entrance side refrigerant temperature within the thermograde, prevent that the condenser internal pressure is too high.

Particularly in above-mentioned formula (1), if KA is increased, Δ T diminishes, and just can receive the heat exchange amount of guaranteeing condenser and prevent the remarkable result that the condenser internal pressure is too high.

(embodiment 4)

Fig. 4 is the structure chart of the refrigerating plant of the 4th embodiment, existing only the difference of it and the 1st embodiment is illustrated.

A plurality of condenser pressure fans are installed on above-mentioned condenser 2, are two condensers pressure fan 9a, 9b in this embodiment.10 for detecting the temperature checkout part of the Temperature Distribution in the above-mentioned condenser 2, and the 11st, control part, it makes according to the wind speed of the above-mentioned condenser 2 of the signal controlling of said temperature detecting element 10 and does not have Temperature Distribution in the condenser 2.

The action of this refrigerating plant for example is, signal according to said temperature detecting element 10, detect the Temperature Distribution in the above-mentioned condenser 2, near the condenser of being controlled by control part 11 the temperature eminence that makes in the condenser 2 strengthens with the wind speed of pressure fan 9a, and near the condenser the temperature lower diminishes with the wind speed of pressure fan 9b, thereby above-mentioned condenser 2 interior Temperature Distribution are reached unanimity.

Thereby, in the present embodiment, even under the situation of the refrigerant that the easy multiple hydrogen fluorohydrocarbon that produces Temperature Distribution of use mixes in condensation process, because be provided with the temperature checkout part that can detect Temperature Distribution in the condenser and according to the air quantity of a plurality of pressure fans of the above-mentioned condenser of signal controlling of temperature checkout part so that the control part of temperature distribution homogenization in the condenser, just can bring into play the performance of condenser to greatest extent, prevent hypertonia in the above-mentioned condenser.

Use the present invention, can make being evenly distributed of refrigerant temperature in the condenser,, also can not produce the too high part of temperature,, bring into play the ability of condenser fully so can prevent that the condenser internal pressure is too high even refrigerant temperature is risen in order to improve refrigeration output.

Though shown in Fig. 4 is the example that is provided with two pressure fans, be not limited thereto, when being provided with many, just can carry out thinner control and obtain corresponding effects.

In addition, use 1 or many its directions of pressure fan and intensity variable, make it in the high part of temperature to maximum, other parts change then more weakly also can obtain above-mentioned same effect.

(embodiment 5)

Fig. 1 is the structure chart of an example of expression present embodiment refrigerating plant.

Fig. 5 then is the stereogram of the evaporimeter 4 of presentation graphs 1 refrigerating plant.

Among the figure, the 13rd, the heat exchanger of evaporimeter 4, refrigerant flows to downside from upside, the 14th, the pipeline in the heat exchanger 13, shown in the Mollier enthalpy-entropy diagram among Fig. 6, pipeline crushing Δ ρ in the selected above-mentioned heat exchanger 13 make the refrigerant temperature gradient when pipeline does not have crushing be, for example, and refrigerant temperature gradient, (18 ℃)-(20 ℃)=2 ℃ essentially identical states of the heat exchanger 13 entrance side refrigerant temperatures of evaporimeter 4 from-20 ℃ to outlet side refrigerant temperature-18 ℃.

Concrete setting pipeline crushing can be extended, be made the internal diameter of pipe to reduce gradually uniformly or impedance etc. is set and in addition suitably selected in pipeline by the internal diameter with pipe.

In the present embodiment, the mixing refrigerant that uses multiple hydrogen fluorohydrocarbon to mix, because being the pipeline of selecting in the heat exchanger 13 14, the pipeline crushing in the above-mentioned heat exchanger 13 makes it to become the state identical substantially with the refrigerant temperature gradient, refrigerant temperature in the above-mentioned evaporimeter 4 is just basic identical, so can prevent inhomogeneous frosting.

(embodiment 6)

Fig. 7 is the structure chart of the 6th embodiment, the existing different piece that itself and the 1st embodiment only are described.

15 and 16 is respectively to detect the inlet in the above-mentioned evaporimeter 4, the refrigerant inlet temperature detecting element and the outlet refrigerant temperature detecting element of outlet side refrigerant temperature.17 is control part, and its control cold medium flux makes and do not have temperature difference between above-mentioned refrigerant inlet temperature detecting element 15 and the above-mentioned outlet refrigerant temperature detecting element 16.

Among this embodiment, even using the mixing refrigerant that mixes by multiple hydrogen fluorohydrocarbon, but because the refrigerant inlet temperature detecting element 15 that the inlet detect in the above-mentioned evaporimeter 4, outlet side refrigerant temperature be set and outlet refrigerant temperature detecting element 16 and control cold medium flux and make the control part 17 that between above-mentioned refrigerant inlet temperature detecting element 15 and outlet refrigerant temperature detecting element 16, does not have temperature difference, so can make above-mentioned evaporimeter 4 interior refrigerant temperatures even substantially, thereby can prevent inhomogeneous frosting.

Promptly, when the having a narrow range of temperature of above-mentioned evaporimeter refrigerant inlet temperature detecting element 15 and outlet refrigerant temperature detecting element 16, make refrigerant crushing minimizing in the evaporimeter by reducing cold medium flux, otherwise, when the temperature difference of above-mentioned refrigerant inlet temperature detecting element 15 and refrigerant exit detecting element 16 is big, then by increasing the crushing that cold medium flux increases refrigerant in the evaporimeter.

(embodiment 7)

Fig. 8 represents the example of pipeline structure of evaporator heat exchanger of the refrigerating plant of the 7th embodiment.The structure of its refrigerating plant is identical with Fig. 1.

In Fig. 8, the 13rd, the heat exchanger of evaporimeter 4, the 14th, heat exchange pipe, the quantity of heat exchange pipe is decided according to the capacity of heat exchanger.The 23rd, first termination, 24 that the refrigerant from evaporator inlet is distributed is provided in a side of second termination of compiling refrigerant of evaporator outlet side.First termination 23, second termination 24 are divided into 10 to pipeline 13,14, and 10 paths are arranged.Fig. 9 is when changing above-mentioned number of vias in the expression present embodiment, the refrigeration output variation diagram of hydrogen fluorohydrocarbon mixing refrigerant R404A and refrigerant R22.

Fig. 9 is when number of vias is changed, and makes the comparison diagram of refrigerant R22 and the refrigerating capacity variation of R404A under the cold medium flux change situation in the heat exchange pipe of inflow heat exchanger.

As shown in Figure 9, change number of vias, just can change refrigeration output by changing the cold medium flux that flows into heat exchange pipe 14, number of vias 10 makes refrigeration output reach maximum for the big physical efficiency of the shared situation of double-refrigerant.

Herein, refrigeration output Q represents with following formula

Q＝K·A·ΔT

Wherein, K: heat transfer coefficient,

A: heat transfer area,

Δ T: the temperature difference of refrigerant temperature and condenser environment temperature.

As for the relation between R404A and the R22, be identical then at evaporimeter, heat transfer area A is identical, and uses when high-volume compressor of same row is arranged, and R404A is substantially also identical with the in-tube evaporation coefficient of heat conduction of R22, so Coefficient K is substantially also identical.

So T makes refrigeration output according to Δ, just can set out for R404A and R22 and make its refrigeration output be roughly maximum co-channel number.

In the present embodiment, because the number of vias of the cold medium flux of the heat exchange pipe of the heat exchanger of setting inflow evaporator is common, and make the state that the refrigeration output separately of refrigerant R404A and R22 is all made it to become roughly maximum, refrigerant R404A and R22 can shared evaporimeters, in the refrigerant transition period to the ozone free destruction, just can deal with common evaporimeter with the both sides' of evaporimeter requirement with the R404A of evaporimeter and ozone free destruction for R22, so can reduce machine, very big economic effect is arranged.

(embodiment 8)

Figure 10 is the structure chart of the 8th embodiment, in the figure, with pipeline 5 compressor 1, condenser 2, throttling arrangement 3, evaporimeter 4 and supercooling heat exchanger 18 are coupled together, near evaporimeter 4, be provided with pressure fan 6, configuration temperature sensing tube 7 on evaporimeter 4 outlet side pipelines 5.Supercooling heat exchanger 18 carries out heat exchange with the refrigerant that comes out from evaporimeter 4 between condenser 2 and throttling arrangement 3.That is, supercooling heat exchanger 18 makes the high-pressure liquid refrigerant that comes out from condenser 2 and the low pressure gaseous coolant that comes out from evaporimeter 4 constitutes for example carrying out heat exchange between two pipelines.The 19th, detect the suction gas temperature detecting element of the suction gas temperature of above-mentioned compressor 1, refrigerant control part 20 as the refrigerant control device, under the situation of carrying out the supercooling operation with supercooling heat exchanger 18, the 25a of switch valve 25 is opened, 25b closes, gauge tap valve 25 then when the suction gas temperature that is detected by above-mentioned suction gas temperature detecting element 19 surpasses setting, 25a is closed, and 25b opens, and is controlled to the state that does not flow through refrigerant in the above-mentioned supercooling heat exchanger 18 that makes.

Figure 11 represents the state that utilizes supercooling heat exchanger 18 to turn round with solid line, is represented by dotted lines the Mollier enthalpy-entropy diagram of non-supercooling operating condition.

In Figure 11, make the liquid refrigerants supercooling with supercooling heat exchanger 18, make the enthalpy of evaporimeter only increase Δ i.

That is, the enthalpy difference of evaporator outlet and evaporator inlet is Δ I when non-supercooling is turned round, and becomes Δ I ' during by 18 runnings of supercooling heat exchanger, increases owing to the supercooling operation makes refrigeration output.

Shown in Figure 12 is to utilize the supercooling running to increase an example of refrigeration output, compare with refrigerant R22 (R22 only carries out the temperature that adds of Figure 33 and controls), the refrigeration output of R404A becomes 106.2% than (the relatively energy force rate that can be applied flexibly as the evaporimeter of R404A of R22), and with above-mentioned refrigeration output that adds the Figure 33 under temperature control (crossing thermal control) situation be 96.3% when comparing than (with respect to energy the force rate that can apply flexibly as the evaporimeter of R404A of R22), as seen refrigeration output has improved.

That is, can guarantee the refrigeration output that refrigerant R22 is in the past had by means of the supercooling running.

In addition, owing to can detect the temperature of gas that compressor sucks, when being higher than setting, it just ends the supercooling running, so can prevent that also the discharge temperature of compressor is too high.

Like this, in the refrigerating plant of the multiple hydrogen fluorohydrocarbon of use of the present invention mixing refrigerant, owing to be provided with supercooling heat exchanger and the suction gas temperature detecting element that detects the suction gas temperature of above-mentioned compressor, and be provided with sucking and then control the refrigerant control part that makes refrigerant not flow through above-mentioned supercooling heat exchanger when gas temperature surpasses the setting temperature, so can make the discharge temperature of above-mentioned compressor unlikely too high, can improve the refrigeration output of hydrogen fluorohydrocarbon mixing refrigerant, thereby be expected to improve the ability of this refrigerating plant.

In addition, suck detecting of gas temperature and be, can accomplish than being easier to and detecting at an easy rate as long as temperature checkout part contacted with suction line just can realize.

Modified example as present embodiment, also can replace switch valve among Figure 10 and the use traffic control valve, detect the temperature that compressor sucks gas with sucking gas temperature detecting element 19, control the cold medium flux that flows through supercooling heat exchanger 18 with refrigerant control part 20 by the aperture of regulating flow control valve 26a, 26b, make this temperature be no more than setting.By such operation, except obtaining the effect of using above-mentioned switch valve 25, can also improve control accuracy by the aperture of regulating flow control valve 26, make control become easy.

(embodiment 9)

Figure 13 is the structure chart of the refrigerating plant of the 9th embodiment, existing only the difference of itself and the 8th embodiment is illustrated.

The 21st, detect the suction pressure detecting element of suction pressure, the 22nd, determine the setting determination section of setting according to the suction pressure that detects by suction pressure detecting element 21.And, control with refrigerant control part 20, refrigerant did not flow through above-mentioned supercooling heat exchanger 18 when the feasible suction gas temperature that is detected by above-mentioned suction gas detecting element 19 surpassed by setting determination section 22 determined settings.

Figure 14 is the operating condition when representing to turn round by supercooling heat exchanger 18 with solid line, is represented by dotted lines the Mollier enthalpy-entropy diagram of non-supercooling operating condition.

Among the figure, the curve that chain-dotted line is represented is the setting curve, does not turn round by supercooling heat exchanger 18 in the fluctuation zone on this curve right side, and becomes non-supercooling operating condition.

In the present embodiment, owing to determine setting according to sucking refrigerant pressure, even it is identical to suck refrigerant temperature, discharge the situation that refrigerant temperature uprises and also handle for get over low compression ratio (high voltage/low voltage) high more the making that become because of pressure, promptly, thermoisopleth from Figure 14 shown in the double dot dash line and afore mentioned rules value curve as can be known, the temperature of side's afore mentioned rules value curve that pressure is low is also low, can carry out more high-precision control to discharge temperature is too high so just compare with the situation of the 8th embodiment.

In addition, also can be as the modified example of the 8th embodiment, also can use flow control valve 26 instead and control without switch valve 25.

In the refrigerating plant of the mixing refrigerant that the multiple hydrogen fluorohydrocarbon of use of the present invention mixes, be provided with and detect the suction gas temperature detecting element and the suction pressure detecting element that detects suction pressure that above-mentioned compressor sucks gas temperature, and determine setting according to the suction pressure that above-mentioned suction pressure detecting element is detected with the setting configuration part.With the refrigerant control part when the suction gas temperature that is detected by above-mentioned suction gas temperature detecting element surpasses by the determined setting of setting determination section, control by switch valve and to make refrigerant not flow through above-mentioned supercooling heat exchanger, so can prevent that the discharge temperature of above-mentioned compressor is too high with high accuracy more, and can improve the ability of refrigerating plant.

(the 10th embodiment)

Figure 15 is the structure chart of the 10th embodiment refrigerating plant, and now only the difference with regard to itself and the 8th embodiment describes.

The 23rd, detect the effluent air temp detecting element of compressor effluent air temp.

In addition, control with refrigerant control part 20, refrigerant did not flow through above-mentioned supercooling heat exchanger 18 when the feasible effluent air temp that is detected by above-mentioned effluent air temp detecting element 23 surpassed setting.

In the present embodiment, because the temperature of compressor discharge gas is detected, when surpassing setting, it just ends the supercooling running, so can prevent that the compressor discharge temperature is too high.

And when detecting effluent air temp, need only the temperature checkout part contact on discharge line, so can realize at an easy rate than being easier to detecting.And, owing to be directly to detect discharge temperature, so can control discharge temperature is too high with higher precision.

Like this, owing in the refrigerating plant of the mixing refrigerant of the multiple hydrogen fluorohydrocarbon of the use of present embodiment, be provided with supercooling heat exchanger and the effluent air temp detecting element that detects the effluent air temp of above-mentioned compressor, and be provided with the refrigerant control part, when effluent air temp is higher than setting, control and make refrigerant not flow through above-mentioned supercooling heat exchanger, so can make the discharge temperature of above-mentioned compressor unlikely too high, improve the refrigeration output of hydrogen fluorohydrocarbon mixing refrigerant, thereby can improve the refrigeration output of refrigerating plant.

Modified example as present embodiment, also can replace flow control valve 26 without the switch valve among Figure 15 25, detect the effluent air temp of compressor with effluent air temp detecting element 23, regulate the aperture of flow control valve 26a, 26b and control the cold medium flux that flows through supercooling heat exchanger 18 and make said temperature be no more than setting with refrigerant control part 20.So, except obtaining the effect of using above-mentioned switch valve 25, regulate by means of the aperture of flow control valve 26 and can also improve control accuracy, make control easily.

(the 11st embodiment)

Figure 16 is the structure chart of the refrigerating plant of the 11st embodiment, now only to the 8th embodiment in different part be illustrated.

The 24th, detect the oily temperature detecting element of compressor oil temperature.

Also control in addition, make that refrigerant did not flow through above-mentioned supercooling heat exchanger 18 when the oil temperature that is detected at above-mentioned oil temperature detecting element 24 surpassed setting with refrigerant control part 20.

Owing to be to detect the compressor oil temperature in the present embodiment, the supercooling running is ended, so can prevent that the compressor oil temperature is too high.

Directly detect owing to oily temperature again, thereby just may be for the warm too high higher control of precision of carrying out of oil.

In the refrigerating plant of the multiple hydrogen fluorohydrocarbon of the use of present embodiment mixing refrigerant, because supercooling heat exchanger and the oily temperature detecting element that detects above-mentioned compressor oil temperature are set, also be provided with the refrigerant control part, it is controlled and makes refrigerant not flow through above-mentioned supercooling heat exchanger when the oil temperature surpasses setting, just can make the oil temperature of above-mentioned compressor unlikely too high, the refrigeration output of hydrogen fluorohydrocarbon mixing refrigerant improves, so just can improve the ability of refrigerating plant.

Modified example as present embodiment, can use flow control valve 26 without the switch valve among Figure 16 25 instead, the oil that detects compressor with oil temperature detecting element 24 is warm, is regulated the aperture of flow control valve 26a, 26b and is controlled the cold medium flux that flows through supercooling heat exchanger 18 so that above-mentioned oily temperature is no more than setting by refrigerant control part 20.By this way, not only can obtain the effect of using above-mentioned switch valve 25, can also regulate making control accuracy higher by the aperture of flow control valve 26, control is easily.

(the 12nd embodiment)

Figure 17 is the structure chart of the 12nd embodiment refrigerating plant, existing itself and the different part of the 8th embodiment of only illustrating.

The 23rd, detect the effluent air temp detecting element of compressor effluent air temp, the 24th, detect the oily temperature detecting element of compressor oil temperature.

But also control with refrigerant control part 20, make that when the effluent air temp that is detected by above-mentioned effluent air temp detecting element 23 surpasses setting above-mentioned refrigerant did not flow through above-mentioned supercooling heat exchanger 18 when perhaps the oil temperature that is detected by above-mentioned oil temperature detecting element 24 surpassed setting.

Owing to be to detect compressor effluent air temp and compressor oil temperature in the present embodiment, and end therein that supercooling turns round during a setting that surpasses separately, so can prevent that the too high or oily temperature of compressor discharge temperature is too high.

In addition since detect effluent air temp and oil temperature both, so can prevent that the too high and oily temperature of discharge temperature is too high, thereby can carry out the control of higher temperature.

Like this, in the refrigerating plant of the multiple hydrogen fluorohydrocarbon of the use of present embodiment mixing refrigerant, supercooling heat exchanger and the oily temperature detecting element that detects the effluent air temp detecting element of above-mentioned compressor effluent air temp and detect above-mentioned compressor oil temperature are set, also be provided with the refrigerant control part, its control refrigerant makes it not flow through above-mentioned supercooling heat exchanger when effluent air temp is higher than setting or oily temperature and is higher than setting, thereby can make the discharge temperature of above-mentioned compressor and oil temperature unlikely too high, improve the refrigeration output of hydrogen fluorohydrocarbon mixing refrigerant, and can improve the ability of refrigerating plant.

Modified example as present embodiment, also can in Figure 17, replace switch valve 25 with flow control valve 26, detect the compressor effluent air temp with effluent air temp detecting element 23, detect the oil temperature of compressor with oil temperature detecting element 24, the aperture of regulating flow control valve 26a, 26b with refrigerant control part 20 flows through the cold medium flux of supercooling heat exchanger 18 with control, makes above-mentioned arbitrary value of detecting all be no more than setting.Do like this, except obtaining the effect of using above-mentioned switch valve 25, can also regulate by the aperture of flow control valve 26 and improve control accuracy more, make control easily.

(the 13rd embodiment)

Figure 18 is the structure chart of the refrigerating plant of the 13rd embodiment, now only its part different with the 8th embodiment is illustrated.

The 23rd, detect the effluent air temp detecting element of compressor effluent air temp, the 21st, detect the suction pressure detecting element of compressor suction pressure.

Control with refrigerant control part 20 in addition, make the suction pressure that is detected at above-mentioned suction pressure detecting element 21 be lower than under the setting situation, when the effluent air temp that is detected with above-mentioned effluent air temp detecting element 23 is higher than setting, or under suction pressure surpasses the situation of setting, and effluent air temp surpasses when setting the 2nd setting that is higher than the 1st setting for, and the control refrigerant makes it not flow through above-mentioned supercooling heat exchanger 18.

When suction pressure was lower than setting, storehouse temperature was lower than setting, though ended the supercooling running, storehouse temperature can not rise to not cold degree yet.

Thereby, effluent air temp is divided into the 1st setting, two stages of the 2nd setting, be lower than the occasion of setting for suction pressure, in the time of on becoming the 1st lower setting that surplus is arranged with respect to the 2nd setting as the higher side's of effluent air temp threshold value, termination supercooling running, make not cold state of the unlikely generation of storehouse temperature, can prevent that effluent air temp is too high, and in the occasion of suction pressure above setting, pay attention to the cooling of storehouse temperature and when above, end the supercooling running above the 2nd setting higher than the threshold value of discharging gas temperature higher side, also can not produce in the storehouse not cold state, and prevent that effluent air temp is too high.

Thereby, in the refrigerating plant of the mixing refrigerant that the multiple hydrogen fluorohydrocarbon of the use of the embodiment of the invention mixes, be provided with the supercooling heat exchanger and detect the effluent air temp detector of above-mentioned compressor effluent air temp and detect the suction pressure detecting element of above-mentioned compressor suction pressure, and be provided with the refrigerant control part, be lower than the occasion effluent air temp of setting on the 1st setting in suction pressure, and make effluent air temp not flow through above-mentioned supercooling heat exchanger so can make the discharge temperature of above-mentioned compressor unlikely too high being higher than the above time control refrigeration of the 2nd setting matchmaker that the 1st setting sets for the occasion that suction pressure surpasses setting, improve the refrigeration output of hydrogen fluorohydrocarbon mixing refrigerant, and can improve the ability of refrigerating plant.

Modified example as present embodiment, also can use the switch valve 25 among flow control valve 26 replacement Figure 18, detect suction pressure with suction pressure detecting element 21, detect the effluent air temp of compressor with effluent air temp detecting element 23, and regulate flow control valve 26a with refrigerant control part 20, the flow of supercooling heat exchanger 18 is flow through in the aperture control of 26b, with convenient suction pressure when setting is following, make above-mentioned effluent air temp be no more than above-mentioned the 1st setting, when suction pressure surpasses setting, make above-mentioned effluent air temp be no more than above-mentioned the 2nd setting.Do like this and not only can obtain the effect of using above-mentioned switch valve 25, can also rely on the aperture adjusting of flow control valve 26 that control accuracy is improved more, and make control become easy.

(the 14th embodiment)

Figure 19 is the structure chart of the refrigerating plant of the 14th embodiment, existing only the different piece of itself and the 8th embodiment is illustrated.

The 24th, detect the oily temperature detecting element of compressor oil temperature, the 21st, detect the suction pressure detecting element of compressor suction pressure.

Control with refrigerant control part 20 in addition, make in the oil temperature that is being lower than when the suction pressure that detects with above-mentioned suction pressure detecting element 21 that above-mentioned oil temperature detecting element 24 is detected under the setting situation when setting is above, and surpass under the setting situation and oily temperature becomes to surpass and is higher than the 2nd setting time control refrigeration matchmaker that the 1st setting sets and do not flow through above-mentioned supercooling heat exchanger 18 when suction pressure.

In the present embodiment, oily temperature is divided into the 1st setting and two stages of the 2nd setting, for the situation of suction pressure below setting, for the 2nd setting surplus is being arranged and becoming the 1st lower setting when above as the high lateral confinement dividing value of oil temperature, termination supercooling running, and the not cold state of unlikely generation storehouse temperature, can prevent that the oil temperature is too high, and for the situation of suction pressure above setting, pay attention to the cooling of storehouse temperature and when higher the 2nd setting that surpasses than the high lateral confinement dividing value of oil temperature, end the supercooling running, also can make not cold state of the unlikely generation of storehouse temperature, prevent that the oil temperature is too high.

Like this, in the refrigerating plant of the multiple hydrogen fluorohydrocarbon of the use of present embodiment mixing refrigerant, owing to supercooling heat exchanger and the oily temperature detecting element that detects above-mentioned compressor oil temperature are set and detect the suction pressure detecting element of above-mentioned compressor suction pressure, and be provided with the refrigerant control part, make and be lower than under the situation of setting more than oily Wen Zaidi 1 setting in suction pressure, perhaps when suction pressure surpasses the 2nd setting that is set in more than the 1st setting above oil under the setting situation is warm, its control refrigerant makes it not flow through the supercooling heat exchanger, so do not cause the oil temperature of above-mentioned compressor too high, improve the refrigerating capacity of hydrogen fluorohydrocarbon mixing refrigerant, thereby can improve the ability of refrigerating plant.

Modified example as present embodiment, the switch valve 25 that can use flow control valve 26 to replace among Figure 19, detect suction pressure with suction pressure detecting element 21, detect the compressor oil temperature with oil temperature detecting element 24, and regulate flow control valve 26a with refrigerant control valve 20, the aperture of 26b is with the cold medium flux in the control inflow supercooling heat exchanger 18, make that above-mentioned oily temperature was no more than the 1st setting when suction pressure was lower than setting, and when suction pressure surpasses setting, make above-mentioned oily temperature be no more than the 2nd setting, so, except can obtaining using the effect of switch valve 25, aperture adjusting by means of flow control valve 26 can make control accuracy improve more, and control easily.

(the 15th embodiment)

Figure 20 is the structure chart of the 15th embodiment refrigerating plant, existing only the difference of it and the 8th embodiment is illustrated.

The 23rd, detect the effluent air temp detecting element of the effluent air temp of compressor, the 24th, detect the oily temperature detecting element, the 21st of compressor oil temperature, detect the suction pressure detecting element of compressor suction pressure.

In addition, also control with refrigerant control part 20, make the suction pressure that is detected at above-mentioned suction pressure detecting element 21 under the situation below the setting, at least one side is more than the 1st setting in effluent air temp that above-mentioned effluent air temp detecting element 23 is detected and the oily temperature that detected by above-mentioned oil temperature detecting element 24, perhaps surpass under the situation of setting in the suction pressure that is detected by above-mentioned suction pressure detecting element 21, at least one side surpasses that the control switch valve cuts out 25a when being set in above the 2nd setting of the 1st setting in above-mentioned effluent air temp and the above-mentioned oily temperature, and 25b opens and refrigerant does not just flow through above-mentioned supercooling heat exchanger 18.

In the present embodiment, gas temperature and oily temperature are divided into the 1st setting respectively spuing, two stages of the 2nd setting, in suction pressure under the situation below the setting, when at least one side in effluent air temp and the oily temperature surpasses when with respect to the 2nd setting as effluent air temp and the high lateral confinement definite value of oil temperature lower the 1st setting of surplus being arranged, termination supercooling running, make the not cold situation of the unlikely generation of storehouse temperature, and can prevent effluent air temp and oily warm too high, perhaps, surpass under the situation of setting in suction pressure, pay attention to the cooling of storehouse temperature and when at least one side surpasses higher the 2nd setting as the warm high lateral confinement dividing value of effluent air temp and oil in effluent air temp and oily temperature, termination supercooling running, also can make not cold state of the unlikely generation of storehouse temperature, prevent that the too high and oily temperature of effluent air temp is too high.

Like this, in the refrigerating plant of the multiple hydrogen fluorohydrocarbon of the use of present embodiment mixing refrigerant, the supercooling heat exchanger is set and detects the effluent air temp detecting element of the effluent air temp of above-mentioned compressor, detect the oily temperature detecting element and the suction pressure detecting element that detects the above-mentioned compressor suction pressure of above-mentioned compressor oil temperature, and be provided with the refrigerant control part, it is lower than the occasion of setting in suction pressure, when at least one side surpasses the 1st setting in effluent air temp and the oily temperature, perhaps, be higher than in suction pressure under the situation of setting, when at least one side surpasses the 2nd setting that is set in more than the 1st setting in effluent air temp and the oily temperature, the control refrigerant makes it not flow through above-mentioned supercooling heat exchanger, just can make the discharge temperature and the oil temperature of above-mentioned compressor unlikely too high, improve the refrigeration output of hydrogen fluorohydrocarbon mixing refrigerant, thereby can improve the ability of refrigerating plant.

Modified example as present embodiment, also can use the switch valve 25 among flow control valve 26 replacement Figure 20, detect the compressor effluent air temp with effluent air temp detecting element 23, detect the compressor oil temperature with oil temperature detecting element 24, be lower than in the suction pressure that detects by suction pressure detecting element 21 under the situation of setting, regulate flow control valve 26a with refrigerant control valve 20, the cold medium flux of supercooling heat exchanger 18 is flow through in the aperture control of 26b, make above-mentioned any one value of detecting all be not less than the 1st setting separately, perhaps, surpass under the situation of setting in suction pressure, also can control above-mentioned arbitrary value of detecting and make it to be not more than the 2nd setting, so, except having the effect of using above-mentioned switch valve 25, by the aperture of regulating flow control valve 26 control accuracy is improved more, make control easily.

(the 16th embodiment)

Figure 21 is the structure chart of the 16th embodiment refrigerating plant, and now only the different piece with regard to itself and the 8th embodiment is illustrated.

The 19th, detect the suction gas temperature detecting element that compressor sucks gas temperature, the 21st, detect the suction pressure detecting element of compressor suction pressure.

In addition, also be lower than the situation of setting in the suction pressure that detects by above-mentioned suction pressure detecting element 21 with refrigerant control part 20, when the suction gas temperature that above-mentioned suction gas temperature detecting element 19 is detected is higher than the 1st setting, or under suction pressure surpasses the situation of setting, the suction gas temperature surpasses when setting the 2nd setting that is higher than the 1st setting for to be controlled, and makes refrigerant not flow through above-mentioned supercooling heat exchanger 18.

Be divided in the present embodiment and suck gas temperature the 1st setting, 2 stages of the 2nd setting, be lower than in suction pressure under the situation of setting, when surpassing the 2nd setting for the high side boundary value that sucks gas temperature lower the 1st setting of surplus being arranged, termination supercooling running, can make the unlikely generation of storehouse temperature not cold, and can prevent that effluent air temp is too high, perhaps, be higher than in suction pressure under the situation of setting, pay attention to the cooling of storehouse temperature and sucking gas temperature when the higher setting of high side is above, termination supercooling running also can make the not cold situation of the unlikely generation of storehouse temperature, prevents that the compressor effluent air temp is too high.

Like this, in the refrigerating plant of the multiple hydrogen fluorohydrocarbon of the use of present embodiment mixing refrigerant, suction gas temperature detecting element by supercooling heat exchanger and the suction gas temperature that detects above-mentioned compressor are set and detect the suction pressure detecting element of the suction pressure of above-mentioned compressor, and be arranged on and suck gas temperature under the situation that suction pressure is lower than setting greater than the 1st setting, perhaps surpass setting in suction pressure, suck gas temperature and surpass the refrigerant control part that the 2nd setting time control refrigeration matchmaker who is higher than the setting of the 1st setting makes it not flow through above-mentioned supercooling heat exchanger, just can make the discharge temperature of above-mentioned compressor unlikely too high, the refrigeration output of hydrogen fluorohydrocarbon mixing refrigerant can be improved, thereby the ability of refrigerating plant can be improved.

Modified example as present embodiment, also can use the switch valve 25 among flow control valve 26 replacement Figure 21, detect compressor suction gas temperature by sucking gas temperature detecting element 19, be lower than in the suction pressure that detects with suction pressure detecting element 21 under the situation of setting, the aperture of regulating flow control valve 26a, 26b by refrigerant control valve 20 is controlled the cold medium flux that flows through supercooling heat exchanger 18 and is made it to be no more than the 1st setting or controlled when suction pressure is higher than setting and make it not to be higher than the 2nd setting.The result who does like this except can obtaining to use the result of above-mentioned switch valve 25, also can improve control accuracy by the aperture of regulating flow control valve 26 more, and control easily.

And then, can also be the above-mentioned the 8th, 9,10,11,12,13,14,15, among 16 the embodiment, mix and use switch valve 25 and flow control valve 26, be configured in respectively on the pipeline of supercooling heat exchanger 18 sides and make on the pipeline of supercooling heat exchanger 18 bypasses, perhaps switch valve 25a on the pipeline that is configured in supercooling heat exchanger 18 sides or flow control valve 26a, as among the various embodiments described above figure, be not located on the supercooling heat exchanger 18 entrance side pipelines and be provided in outlet side, can obtain the described effect much at one of the various embodiments described above yet as variation.

(the 17th embodiment)

Figure 22 represents the present invention's the 17th embodiment refrigerating plant, it is that compressor 1, condenser 2, accumulator 3, throttling arrangement 4, evaporimeter 4, reservoir 31 etc. are connected with pipeline successively, and then the high pressure liquid portion of supercooling heat exchanger 18 is connected and is subjected between liquid portion 30 and the throttling arrangement 3, and the low pressure gas body is connected between evaporimeter 4 and the reservoir 31.That is, supercooling heat exchanger 18 be high-pressure liquid refrigerant that makes to come out from condenser 2 and the low pressure gaseous coolant that comes out from evaporimeter 4 for example, carry out heat exchange between two pipelines and constitute.Be to use the refrigerating plant of hydrogen fluorohydrocarbon R404A as refrigerant.Also can use hydrogen fluorohydrocarbon R507 as refrigerant.Figure 23 is illustrated in the operating point of the present embodiment freeze cycle on pressure one mollier diagram, and the theory of Figure 24 (a) expression R404A refrigeration output increases ratio, and the theory of the refrigeration output of Figure 24 (b) expression R22 increases ratio.Also can be supercooling heat exchanger 18 as the part of condenser 2 or evaporimeter 4 and be combined in the device.Arrow 32 expression refrigerants flow among the figure.

With Figure 23 its action is described now.1. the HTHP cold media gas of discharging from compressor 1 enters condenser 2 and condenses into the high-pressure liquid refrigerant therein 2. ', the high-pressure liquid refrigerant enters supercooling heat exchanger 18 by accumulator 30, with the low-pressure gas enthalpy difference 4.-4. ' cooling, enthalpy is from 2. ' to 2. reducing, and decompression and become the two-phase low pressure refrigerant 3. in throttling arrangement 3.Send into two-phase refrigerant in the evaporimeter 4 in evaporimeter 4, evaporate become low pressure gas attitude refrigerant 4. ' and enter supercooling interchanger 18.Therein,, make enthalpy from 4. by carrying out heat exchange with the high-pressure liquid refrigerant ' be increased to 4., suck again in the compressor 1.

Below, explain the refrigerant cycles action of supercooling heat exchanger 18.2. ', enthalpy 2. is respectively H3 ', H3,4. ', enthalpy 4. is respectively H4 ', H4,4. ', density 4. respectively is ρ 4 ', ρ 4, the refrigeration output of the refrigerant cycles in past is Q ', the refrigeration output of the refrigerant cycles of present embodiment then is Q.From the high-pressure liquid refrigerant of accumulator 30 in supercooling heat exchanger 18 from 2. ' move to 2., promptly, the enthalpy of evaporator inlet is reduced to H3 from H3 ', enthalpy difference in the evaporimeter 4 from H4 '-H3 ' be increased to H4 '-H3, low pressure gaseous coolant supercooling heat exchanger 18 from 4. ' shift to 4., the suction enthalpy that is compressor increases to H4 from H4 ', the cold media gas temperature that compressor 1 sucks rises, and cold media gas density is reduced to ρ 4 from ρ 4 ', and the result descends cold medium flux.The theoretical ratio that its refrigeration output increases when using same compressor can be represented approx by following formula.Wherein, H4-H4 ' does not comprise because not carry out the raise enthalpy calculate refrigeration output of refrigeration temperature poor.

$-\frac{Q}{Q\text{'}}=\frac{\mathrm{\ρ}4(H4\text{'}-H3)}{\mathrm{\ρ}4\text{'}(H4\text{'}-H3\text{'})}$

R404 is 40 ℃ of condensation temperatures in Figure 24 (a) expression, under ℃ situation of evaporating temperature-10～-40, when becoming supercooling degree 10 (degree) by supercooling heat exchanger 18, the ratio that enthalpy difference in the evaporimeter 4 increases, promptly (H4 '-H3)/(H4 '-H3 '), compressor sucks the ratio that gas coolant density reduces, i.e. ρ 4/ ρ 4 ', and the ratio that refrigeration output increases is the result that the theory of Q/Q ' is tried to achieve.In order to compare with present embodiment, Figure 24 (b) shows and uses R22 to make refrigerant, 40 ℃ of condensation temperatures, under ℃ situation of evaporating temperature-10～-40, enthalpy difference increase ratio in the evaporimeter 4 when making the supercooling degree be 10 (degree) by supercooling heat exchanger 18, promptly (H4 '-H3)/(H4 '-H3 '), it is ρ 4/ ρ 4 ' that compressor suction gas coolant density reduces ratio, it is Q/Q ' that refrigeration output increases ratio.

As can be seen, it is big that the increase ratio ratio piston compressor 1 suction gas coolant density of R404A enthalpy difference in evaporimeter reduces ratio from Figure 24 (a), and pretending is that all its refrigeration outputs increase.

On the other hand, from Figure 24 (b) as can be known since in the refrigerating plant in the past the used enthalpy difference of R22 in evaporimeter to increase ratio almost be identical with the reduction ratio of the suction gas coolant density of compressor 1, so can not improve refrigeration output.From as can be known above, be not suitable for R22, it is effective using R404A in the present embodiment.

As previously discussed, be not suitable for for the heat exchange of high-pressure liquid refrigerant and low-pressure gas refrigerant with R22, and be expected in the refrigerating plant of use R404A in high-pressure liquid refrigerant in the present embodiment and the heat exchange of low-pressure gas refrigerant in guaranteeing the scope of compressor reliability (not making the undue scope that rises of discharge temperature), to improve its refrigeration output.And then though the value of not shown in the present embodiment relevant R507, it also has the effect identical with R404A.

In addition,,, in supercooling heat exchanger 18, can reclaim heat, suppress because of returning the reduction of the refrigeration output that liquid causes so can expectation obtain even in evaporimeter 4, return the liquid phenomenon by means of supercooling heat exchanger 18.

And when supercooling heat exchanger 18 is assembled into refrigerating plant, even in evaporimeter 4, liquid takes place back, also can reclaims heat energy with supercooling heat exchanger 18 and become gas coolant, be expected to suppress because of returning the decline of the compressor reliability that liquid causes.

Among Figure 22, if make supercooling heat exchanger 18 be the double pipe structure, flow through the low-pressure gas refrigerant in the interior pipe, flow through the high-pressure liquid refrigerant in the annulus of the outside, when then low-pressure gas refrigerant (for example temperature-30 ℃) is flow through in the loss that causes because of the heat exchange (heat radiation) between annulus high-pressure liquid refrigerant (for example temperature is 40 ℃) and the outer gas (for example 20 ℃) than in annulus with outside the loss that causes of the heat exchange (heat absorption) of gas little, so can improve heat exchanger effectiveness between low-pressure gas refrigerant and the high-pressure liquid refrigerant.

Supercooling heat exchanger 18 is connected in the middle of high pressure liquid tube connector and the low pressure gas tube connector shown in Figure 25 is used to improve the other parts of performance.At this moment, compressor 1, condenser 2, accumulator 30, throttling arrangement 3, evaporimeter 4 etc. all can use structure in the past, just can obtain the advantage of improving refrigeration output as long as supercooling heat exchanger 18 is combined in the existing refrigerating plant.

(the 18th embodiment)

Figure 26 shows the 18th embodiment of the present invention, it is provided with the bypass liquid tube loop 33 18 bypasses of supercooling heat exchanger, reach the magnetic valve of for example using 34 in this loop, also be provided with the temperature sensor 36 of the exit gas refrigerant temperature that detects supercooling heat exchanger 18 as switch valve.When the magnetic valve 35 as switch valve for example is set in the liquid pipe outlet of linking up supercooling heat exchanger 18, in turning round usually, the magnetic valve 34 of bypass loop 33 cuts out, link up the magnetic valve 35 of the liquid pipe of supercooling heat exchanger and open, just can refrigeration output be improved with the 17th embodiment.Detect the gaseous coolant temperature of supercooling heat exchanger 18 outlets by temperature sensor 36, when it is higher than set point of temperature, the magnetic valve 34 of bypass circulation 33 is opened, magnetic valve 35 on the liquid pipe of communication heat exchanger cuts out, make refrigerant flow through bypass circulation 33 and the 1 suction gas temperature rising of inhibition compressor, so can guarantee the reliability of compressor 1.

Be provided with bypass tracheae loop 37 in the structure shown in Figure 27 18 bypasses of supercooling heat exchanger, reach the magnetic valve of in this loop, for example using 38, also be provided with the temperature sensor 36 of the gaseous coolant temperature that detects 18 outlets of supercooling heat exchanger as switch valve.The magnetic valve of for example using as switch valve 39 is set in the outlet of the tracheae of linking up supercooling heat exchanger 18.When turning round usually, the magnetic valve 38 of bypass circulation 37 cuts out, and magnetic valve 39 is opened on the tracheae of communication supercooling heat exchanger, also can obtain the effect that increases refrigeration output with the 17th embodiment the samely.Detect supercooling heat exchanger 18 outlet gaseous state refrigerant temperatures with temperature sensor 36, when it was higher than set point of temperature, the magnetic valve 38 of bypass 37 was opened, and magnetic valve 39 cuts out on the tracheae of communication heat exchanger, suck the gas temperature rising and suppress compressor 1, so can guarantee the reliability of compressor 1.

Be provided with the bypass tracheae loop 37 that makes 18 bypasses of supercooling heat exchanger in the structure shown in Figure 28, with the electric expansion valve 40 that for example is used as flow control valve in this bypass 37, also be provided with the temperature sensor 36 of the gaseous coolant temperature that detects supercooling heat exchanger 18.Link up the magnetic valve 39 that for example also is provided with in the tracheae outlet of supercooling heat exchanger 18 as switch valve.When turning round usually, electric expansion valve 40 full cut-offs, magnetic valve 39 is opened, and also can refrigeration output be increased with the 17th embodiment.Detect the cold media gas temperature of supercooling heat exchanger 18 outlets with temperature sensor 36, when it is higher than set point of temperature, regulate the aperture control bypass flow of the electric expansion valve 40 of bypass loop 37, and supercooling heat exchanger 18 is exported the adjustment of cold media gas below set point of temperature.Like this, just can suppress compressor and suck the gas temperature rising, guarantee the reliability of compressor 1, simultaneously, can similarly increase its refrigeration output with the 17th embodiment.Still can not reach set point of temperature at the aperture standard-sized sheet of electric expansion valve 40 when following, close magnetic valve 39, make gaseous coolant all flow through bypass circulation 37, suck gas temperature and rise, thereby guarantee the reliability of compressor 1 and suppress compressor.

In the structure shown in Figure 29, be provided with bypass tracheae loop 37 that made cool-heat-exchanger 18 bypasses and the magnetic valve 38 that for example on this loop, is used as switch valve, also be provided with the temperature sensor 36 that detected cool-heat-exchanger 18 gaseous coolant temperature.Electric expansion valve 41 as control valve for refrigerant flow for example is set in the tracheae outlet of linking up supercooling heat exchanger 18.When turning round usually, magnetic valve 38 cuts out, and electric expansion valve 41 standard-sized sheets also can increase its refrigeration output with the 17th embodiment the samely.Detect the outlet cold media gas temperature of supercooling heat exchanger 18 with temperature sensor 36, when it is higher than set point of temperature, magnetic valve 38 is opened, the aperture of regulating electric expansion valve 41 flows through the cold media gas flow of supercooling heat exchanger 18 with adjusting, thereby the outlet cold media gas temperature of supercooling heat exchanger 18 is controlled at below the set point of temperature, whereby, when the reliability of compressor 1 is guaranteed in the rising of inhibition compressor suction gas temperature, can as the 17th embodiment, increase refrigeration output.

And then, though in the refrigerating plant described in above-mentioned each inventive embodiments, compressor and evaporimeter etc. only is a structure shown in the embodiment, should not be limited to these, in order to finish main target of the present invention, not mediocre theory also comprises wider structure.

By above explanation, refrigerating plant in the 1st invention is to connect compressor successively, condenser, various device such as throttling arrangement and evaporimeter, formation makes the refrigerant loop of refrigerant circulation, in the refrigerating plant of the mixing refrigerant that uses multiple hydrogen fluorohydrocarbon to mix, because its structure makes heat exchange amount in above-mentioned condenser inlet side greater than outlet side, the temperature difference with the condenser environment temperature of condenser gas phase side and liquid side is not existed as much as possible, appropriate temperature difference is set also for as required the condenser temperature and the condenser environment temperature of homogenising, so can guarantee sufficient heat exchange, give full play to condenser performance, and can prevent the rising singularly of condenser internal pressure.

The refrigerating plant of the 2nd invention is to be provided with pressure fan on condenser, and make the air quantity that flows to above-mentioned condenser bigger than outlet side at the refrigerant entrance side of condenser, so can make the refrigerant entrance side of condenser stronger cooling be arranged than outlet side, can make condenser temperature even, can give full play to condenser performance, and can prevent that the condenser internal pressure from raising unusually.

The 3rd the invention in refrigerating plant be make condenser heat exchange pipe entrance side have than outlet side bigger with heat transfer area heat-exchange fluid, so just can make the heat exchange amount of entrance side bigger, make condenser temperature even than outlet side.

In the 4th refrigerating plant of the present invention, be to use the structure higher, so can make condenser temperature even than the outlet side coefficient of overall heat transmission at condenser heat exchange pipe entrance side.

Refrigerating plant in the 5th invention, be to connect compressor successively, condenser, each equipment of throttling arrangement and evaporimeter also circulates refrigerant therein and forms the refrigerant loop, and in the refrigerating plant that uses by multiple hydrogen fluorohydrocarbon mixing refrigerant, heat exchange amount for the regulation that obtains condenser, for by the heat exchange pipe shape, the thermal conductivity and the heat transfer area of the regulation of decisions such as state are set, with the condensator outlet side is benchmark and heat exchange is set at required Min. in permissible range with the temperature difference between fluid, so the minimum of a value that the difference of outlet side refrigerant temperature and environment temperature is necessitated.Also can be suppressed at the entrance side refrigerant temperature within the thermograde, can prevent hypertonia in the condenser.

The refrigerating plant of the 6th invention, be compressor, condenser, equipment such as throttling arrangement and evaporimeter links to each other successively, refrigerant is circulated therein and form the refrigerant loop, and in the refrigerating plant that uses multiple hydrogen fluorohydrocarbon mixing refrigerant, be provided with the condenser pressure fan, detect the temperature checkout part of Temperature Distribution in the condenser and according to the above-mentioned pressure fan of the signal controlling of said temperature detecting element so that the pressure fan control part of uniformity of temperature profile in the condenser, refrigerant temperature is evenly distributed in the condenser so can make, even when refrigerant temperature is risen, can not produce the too high part of temperature yet, thereby can prevent that the condenser internal pressure is too high, open the ability that to give full play to condenser.

The refrigerating plant of the 7th invention, be that each equipment of compressor, condenser, throttling arrangement and evaporimeter is connected in turn, refrigerant is circulated therein and form the refrigerant loop, and in the refrigerating plant that uses multiple hydrogen fluorohydrocarbon mixing refrigerant, owing to the pipeline crushing of the heat exchanger that makes above-mentioned evaporimeter is identical substantially with the thermograde of refrigerant, refrigerant temperature is uniformly substantially in the evaporimeter so make, and can prevent inhomogeneous frosting.

In the refrigerating plant in the 8th invention, owing to setting out the evaporator pipeline crushing, so by making pipeline have suitable shape and length just can accomplish to make the thermograde of crushing in the evaporimeter and refrigerant basic identical by pipeline shape and length.

In the refrigerating plant in the 9th invention, owing to the pipeline crushing of evaporimeter is to set with the control of refrigerant flow rate in the pipeline, under the situation about having a narrow range of temperature of evaporimeter refrigerant inlet temperature and outlet refrigerant temperature, just can reduce refrigerant crushing in the evaporimeter by reducing cold medium flux, otherwise, under the big situation of the temperature difference of above-mentioned refrigerant inlet temperature and outlet temperature, just can increase refrigerant crushing in the evaporimeter by increasing cold medium flux, can make the interior refrigerant temperature of evaporimeter even substantially.

Refrigerating plant in the 10th invention, be to connect compressor successively, condenser, throttling arrangement and evaporimeter various device, refrigerant is circulated therein and form the refrigerant loop, and in the refrigerating plant that uses multiple hydrogen fluorohydrocarbon mixing refrigerant, it selectes R404A as hydrogen fluorohydrocarbon mixing refrigerant, and be provided with so that refrigeration output is roughly the evaporimeter of the number of vias of maximum evaporator heat exchanger as the common number of vias of R404A and refrigerant R22, because it is common having set the number of vias of cold medium flux of the heat exchange pipe of the heat exchanger that feeds evaporimeter, and the refrigeration output that can make refrigerant R404A and R22 respectively reaches maximum substantially, so refrigerant R404A and R22 be the shared evaporimeter of energy just, in the refrigerant transition period to the ozone free destruction, just can deal with the requirement of using evaporimeter two aspects for R22 with the R404A of evaporimeter and ozone free destruction with common evaporimeter, so can reduce machine, bigger economic benefit is arranged.

Refrigerating plant in the 11st invention, be to connect equipment such as compressor, condenser, throttling arrangement and evaporimeter successively, make the refrigerant circulation and form the refrigerant loop, and in the refrigerating plant that uses multiple hydrogen fluorohydrocarbon mixing refrigerant, because it is provided with the supercooling heat exchanger that makes high-pressure liquid refrigerant and low pressure gaseous coolant carry out heat exchange, even when using the hydrogen fluorohydrocarbon as refrigerant, by the heat exchange between supercooling heat exchanger mesohigh liquid refrigerants and low pressure gaseous coolant, make the enthalpy difference of evaporator outlet and inlet increase, thereby increase its refrigeration output.

The refrigerating plant of the 12nd invention owing to use hydrogen fluorohydrocarbon R404A or R507 to make refrigerant, is expected to improve the refrigeration output of refrigerating plant.

Refrigerating plant in the 13rd invention, because the supercooling heat exchanger that makes high-pressure liquid refrigerant and low pressure gaseous coolant carry out heat exchange is the double pipe structure, flow through the low pressure gaseous coolant in the pipe in it, flow through the high-pressure liquid refrigerant in the annulus, so can make the low pressure gaseous coolant of supercooling heat exchanger and the heat exchanger effectiveness height between the high-pressure liquid refrigerant.

Refrigerating plant in the 14th invention, be to be connected the supercooling heat exchanger that high-pressure liquid refrigerant and low pressure gaseous coolant carry out heat exchange in the middle of the high pressure liquid tube connector with the centre of low pressure gas tube connector as the other parts that improve refrigeration output, as long as be assembled in the existing freezing equipment, just can improve the refrigeration output of the refrigerating plant that uses hydrogen fluorohydrocarbon refrigerant.

Refrigerating plant in the 15th invention, be provided with control and flow through the refrigerant control device of the coolant quantity of supercooling heat exchanger, by making refrigerant flow through the refrigeration output that the supercooling heat exchanger can improve refrigerating plant, simultaneously can be when flowing through the supercooling heat exchanger because of refrigerant and produce certain and do not want, the control cold medium flux just can be eliminated this improper.

Claims (1)

1. refrigerating plant, it is compressor, and various devices such as condenser, throttling arrangement and evaporimeter in turn connect, and refrigerant is circulated therein and form the refrigerant loop, wherein use the mixing refrigerant that is mixed by multiple hydrogen fluorohydrocarbon, it is characterized in that having:

Refrigerant inlet temperature test section and outlet refrigerant temperature test section are used for detecting respectively the refrigerant temperature of above-mentioned evaporator inlet side and outlet side;

Control part is used for cold medium flux being reduced, and when described temperature difference is big, cold medium flux being increased in the temperature difference of above-mentioned refrigerant inlet temperature test section and outlet refrigerant temperature test section hour.

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