CN1677017A

CN1677017A - Refrigeration circulation device and control method thereof

Info

Publication number: CN1677017A
Application number: CN 200510062849
Authority: CN
Inventors: 冈座典穗; 目方雅人; 中谷和生
Original assignee: Matsushita Electric Industrial Co Ltd
Current assignee: Panasonic Holdings Corp
Priority date: 2004-03-31
Filing date: 2005-03-31
Publication date: 2005-10-05
Anticipated expiration: 2025-03-31
Also published as: JP2005291622A; JP3708536B1; CN100513930C

Abstract

The invention provides a refrigeration circulation device and control method thereof. The refrigerating cycle operation is performed without lowering operating efficiency and capacity within various operating ranges by maintaining optimum high-pressure side pressure even if there is a restriction to keep constant a density ratio in a refrigerating cycle device using an expander. This refrigerating cycle device comprises a compression mechanism, an expansion mechanism, a drive source driving the compression mechanism connected to the expansion mechanism through one shaft, a radiator cooling a refrigerant discharged from the compression mechanism, an evaporator heating the refrigerant flowing out from the expansion mechanism, a bypass flow passage bypassing the expansion mechanism, a bypass valve installed in the bypass flow passage, a pre-pressure reducing valve reducing the pressure of the refrigerant flowing into the expansion mechanism, and an operating device controlling the bypass valve and the pre-pressure reducing valve. By operating the degrees of openings of the bypass valve and the pre-pressure reducing valve based on the delivery temperature or the degree of superheat of the refrigerating cycle to control the high-pressure side pressure to a desirable one, an efficient operation can be performed over a wide operating range.

Description

Freezing cycle device and control method thereof

Technical field

The present invention relates to have the freezing cycle device and the control method thereof of decompressor.

Background technology

Use the ozone layer destroying coefficient be zero and the also especially little carbon dioxide of global warming coefficient than freon class (below be called CO ₂) gazed in recent years as the freezing cycle device of refrigerant, but CO ₂Refrigerant, critical-temperature is low to reach 31.06 ℃, under the situation of utilizing the temperature high than this temperature, in the high-pressure side of freezing cycle device (compressor outlet～radiator～pressure reducer enters the mouth), does not become and CO can occur ₂The supercriticality of the condensation of refrigerant is compared with existing refrigerant, and the operational efficiency of freezing cycle device (COP) reduces.So, using CO ₂In the freezing cycle device of refrigerant, the unit that COP is improved is important.

As this unit, propose to be provided with decompressor and replaced pressure reducer, the pressure during with expansion can be as the freeze cycle of power recovery.Herein, pass through in the freezing cycle device of an Axile connection structure at compressor and decompressor positive displacement, when the volume of cylinder that with the cylinder of compressor volume is VC, decompressor is VE, decide the ratio of the volume internal circulating load that flows through compressor, decompressor respectively by VC/VE (design volumetric ratio).With the density of the refrigerant of evaporator outlet (flowing into the refrigerant of compressor) as the density of the refrigerant (flowing into the refrigerant of decompressor) of DC, radiator outlet during as DE, because flowing through the quality internal circulating load of compressor, decompressor respectively equates, " VC * DC=VE * DE ", in other words, the relation of " VC/VE=DE/DC " is set up.Because VC/VE (design volumetric ratio) is the constant of determining when Machinery Design, make DE/DC (density ratio) often keep certain, will carry out balance to freeze cycle.(followingly this point is called " density is than certain restriction ".)

Yet because the service condition of freezing cycle device might not be certain, the density in design volumetric ratio that prefers when design and the actual running status is not than not simultaneously, because " density is than certain restriction ", very difficult adjustment becomes optimal high side pressure.

So, proposed to make the shunting stream of decompressor shunting by setting, flow into the coolant quantity of decompressor by control, be adjusted into optimum on high-tension side structure and control method (such as, with reference to patent documentation 1 (the Japan Patent spy opens the 2000-234814 communique) and patent documentation 2 (the Japan Patent spy opens the 2001-116371 communique)).

Summary of the invention

But, in above-mentioned patent documentation, recorded and narrated density under the running status of reality than less than design during volumetric ratio, the shunting stream that decompressor is shunted by refrigerant is flow through, can be adjusted into the formation and the control method of optimal high side pressure, when comparing greater than the design volumetric ratio, for formation that is adjusted into optimal high side pressure and control method, without any record for the density under the running status of reality.In addition, there is not to record and narrate the value how to set the design volumetric ratio for well yet.

In addition, when comparing less than the design volumetric ratio for the density under the running status of reality, can not surpass under a certain amount of situation for the coolant quantity that flows through the shunting stream, in other words, for making the aperture that is arranged at the flow divider on the shunting stream become maximum occasion or the like, how to do better and also do not record and narrate.Therefore, just be created in density under the actual running status than the time, when perhaps becoming maximum or the like, can not be adjusted into the problem that operational efficiency that optimal high side pressure makes freezing cycle device reduces for the aperture of flow divider greater than the design volumetric ratio.

So, no matter the objective of the invention is to the density under the running status of reality than greater than the time still less than the design volumetric ratio, a kind of formation and control method thereof that can be adjusted into optimal high side pressure is provided, improves the operational efficiency (COP) of freezing cycle device.

In addition, its purpose is to provide a kind of freezing cycle device that can have the design volumetric ratio of the good operation of efficient under various running statuses.

The described freezing cycle device of first technical scheme of the present invention, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that comprising: the shunting stream that makes above-mentioned expansion mechanism shunting; The flow divider that on above-mentioned shunting stream, is provided with; The pre-pressure-reducing valve that the refrigerant that flows into above-mentioned expansion mechanism is reduced pressure; And the operator of controlling above-mentioned flow divider and above-mentioned pre-pressure-reducing valve based on discharge temperature or the degree of superheat.

The described freezing cycle device of second technical scheme of the present invention, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that comprising: the shunting stream that makes above-mentioned expansion mechanism shunting; The flow divider that on above-mentioned shunting stream, is provided with; And the operator of controlling the rotating speed of above-mentioned flow divider and above-mentioned drive source based on discharge temperature or the degree of superheat.

The described freezing cycle device of the 3rd technical scheme of the present invention, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that the refrigerant that flows out from above-mentioned expansion mechanism is heated is characterized in that comprising: the shunting stream that makes above-mentioned expansion mechanism shunting; The flow divider that on above-mentioned shunting stream, is provided with; Fan to above-mentioned evaporimeter air-supply; And the operator of controlling the rotating speed of above-mentioned flow divider and said fans based on discharge temperature or the degree of superheat.

The described freezing cycle device of the 4th technical scheme of the present invention, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that: the volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is roughly consistent with value maximum among the ratio of each outlet refrigerant density of above-mentioned radiator and above-mentioned evaporimeter under the running status of freezing cycle device.

The described freezing cycle device of the 5th technical scheme of the present invention, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that: the volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is roughly consistent for ratio of each outlet refrigerant density of above-mentioned radiator under the running status of maximum freezing cycle device and above-mentioned evaporimeter with refrigerant density in the outlet of above-mentioned radiator.

The described freezing cycle device of the 6th technical scheme of the present invention, have compressing mechanism, when expansion mechanism and drive source connect by an axle, radiator that will be cooled off and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out from the refrigerant that the above-mentioned compressor structure is discharged, it is characterized in that: the volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is with minimum in the environment temperature of above-mentioned evaporimeter, and the water temperature that flows into above-mentioned radiator is minimum, and the ratio of each outlet refrigerant density of above-mentioned radiator under the running status of the freezing cycle device that the hot water temperature of flowing out from above-mentioned radiator is the highest and above-mentioned evaporimeter is roughly consistent.

The described freezing cycle device of the 7th technical scheme of the present invention, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out from the refrigerant that the above-mentioned compressor structure is discharged, use carbon dioxide to use as refrigerant and as hot water machine, it is characterized in that: the volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is more than or equal to 10.

The described freezing cycle device of the 8th technical scheme of the present invention, have compressing mechanism, when expansion mechanism and drive source connect by an axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that: the volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is with minimum in the air themperature of blowing to above-mentioned evaporimeter, and the air themperature to above-mentioned radiator air-supply is minimum, and the ratio of each outlet refrigerant density of above-mentioned radiator under the running status of the freezing cycle device that the air themperature that blows out from above-mentioned radiator is the highest and above-mentioned evaporimeter is roughly consistent.

The described freezing cycle device of the 9th technical scheme of the present invention, it is characterized in that have compressing mechanism, expansion mechanism and drive source connected by axle in, radiator that will be cooled off and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out from the refrigerant that the above-mentioned compressor structure is discharged, use carbon dioxide to use as refrigerant and as air conditioner, it is characterized in that: the volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is more than or equal to 8.

The control method of the described freezing cycle device of the tenth technical scheme of the present invention, have compressing mechanism, expansion mechanism and drive source connected by axle in, the radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged; The evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out; Make the shunting stream of above-mentioned expansion mechanism shunting; The flow divider that on above-mentioned shunting stream, is provided with; And in the freezing cycle device of the pre-pressure-reducing valve that the refrigerant that flows into above-mentioned expansion mechanism is reduced pressure, it is characterized in that: control above-mentioned flow divider and above-mentioned pre-pressure-reducing valve based on the discharge temperature or the degree of superheat.

The control method of the described freezing cycle device of the 11 technical scheme of the present invention, have compressing mechanism, expansion mechanism and drive source connected by axle in, the radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged; The evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out; Make the shunting stream of above-mentioned expansion mechanism shunting; In the freezing cycle device of the flow divider that on above-mentioned shunting stream, is provided with, it is characterized in that: the rotating speed of controlling above-mentioned flow divider and above-mentioned drive source based on discharge temperature or the degree of superheat.

The control method of the described freezing cycle device of the 12 technical scheme of the present invention, have compressing mechanism, expansion mechanism and drive source connected by axle in, the radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged; The evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out; Make the shunting stream of above-mentioned expansion mechanism shunting; The flow divider that on above-mentioned shunting stream, is provided with; And in the freezing cycle device of the fan of above-mentioned evaporimeter air-supply, it is characterized in that: the rotating speed of controlling above-mentioned flow divider and said fans based on discharge temperature or the degree of superheat.

The described freezing cycle device of the 13 technical scheme of the present invention has when the auxiliary compressor structure is connected by an axle with expansion mechanism the compressing mechanism of compression refrigerant; The auxiliary compressor structure that will recompress from the refrigerant that the above-mentioned compressor structure is discharged; Cooling is characterized in that comprising: the shunting stream that makes above-mentioned expansion mechanism shunting from the radiator and the evaporimeter of heating from the refrigerant of above-mentioned expansion mechanism outflow of the refrigerant of above-mentioned auxiliary compressor structure discharge; The flow divider that on above-mentioned shunting stream, is provided with.

The 14 technical scheme of the present invention is characterised in that and also comprises the pre-pressure-reducing valve that the refrigerant that flows into above-mentioned expansion mechanism is reduced pressure.

Described being characterised in that of the 15 technical scheme of the present invention also comprises the operator of controlling above-mentioned flow divider and above-mentioned pre-pressure-reducing valve based on the discharge temperature or the degree of superheat of this freezing cycle device.

The 16 technical scheme of the present invention is characterised in that the volumetric ratio that makes above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is roughly consistent with value maximum among the ratio of each outlet refrigerant density of above-mentioned radiator under the running status of freezing cycle device and above-mentioned compressor structure.

The 17 technical scheme of the present invention is characterised in that the volumetric ratio that makes above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is roughly consistent for ratio of each outlet refrigerant density of above-mentioned radiator under the running status of maximum freezing cycle device and above-mentioned compressor structure with refrigerant density in the outlet of above-mentioned radiator.

The 18 technical scheme of the present invention is characterised in that the volumetric ratio that makes above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is with minimum in the environment temperature of above-mentioned evaporimeter and to flow into ratio of each outlet refrigerant density of above-mentioned radiator under the running status of the minimum and freezing cycle device that hot water temperature that flow out from above-mentioned radiator is the highest of the water temperature of above-mentioned radiator and above-mentioned evaporimeter roughly consistent.

The 19 technical scheme of the present invention is characterised in that the volumetric ratio of setting above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is more than or equal to 4 in the freezing cycle device that uses as hot water machine that uses carbon dioxide as refrigerant.

Freezing cycle device of the present invention and control method thereof are even using owing to density is difficult to adjust in the freezing cycle device of the decompressor that becomes optimal high side pressure than certain restriction; Also can in the range of operation of amplitude broad, obtain high power recovery effect, the freezing cycle device that can efficiently move and control method thereof.

Description of drawings

Fig. 1 is the structure chart that the freezing cycle device of embodiments of the invention 1 is shown.

Fig. 2 is the flow chart of control method that the freezing cycle device of embodiments of the invention 1 is shown.

Fig. 3 is the ideograph of association that the control module of embodiments of the invention 1 is shown.

Fig. 4 is the structure chart that the freezing cycle device of embodiments of the invention 2 is shown.

Fig. 5 is the flow chart of control method that the freezing cycle device of embodiments of the invention 2 is shown.

Fig. 6 is the structure chart that the freezing cycle device of embodiments of the invention 3 is shown.

Fig. 7 is the flow chart of control method that the freezing cycle device of embodiments of the invention 3 is shown.

Fig. 8 is the ideograph of association that the control module of embodiments of the invention 3 is shown.

Fig. 9 is the structure chart that the freezing cycle device of embodiments of the invention 4 is shown.

Figure 10 is the flow chart of control method that the freezing cycle device of embodiments of the invention 4 is shown.

Figure 11 is the ideograph of association that the control module of embodiments of the invention 4 is shown.

Figure 12 illustrates the density ratio of embodiments of the invention 5 and the correlation diagram of COP ratio.

Figure 13 illustrates the density ratio of embodiments of the invention 5 and the correlation diagram of refrigerant density.

Figure 14 is the structure chart that the freezing cycle device of embodiments of the invention 6 is shown.

Figure 15 illustrates the density ratio of embodiments of the invention 6 and the correlation diagram of COP ratio.

Figure 16 illustrates the density ratio of embodiments of the invention 6 and the correlation diagram of refrigerant density.

Figure 17 is the structure chart that the freezing cycle device of embodiments of the invention 7 is shown.

Figure 18 illustrates the density ratio of embodiments of the invention 8 and the correlation diagram of COP ratio.

Figure 19 illustrates the density ratio of embodiments of the invention 8 and the correlation diagram of refrigerant density.

The specific embodiment

1 freezing cycle device has the shunting stream that makes the expansion mechanism shunting according to the embodiment of the present invention; Be arranged at the flow divider on the shunting stream; Make the pre-pressure-reducing valve of the refrigerant decompression that flow into expansion mechanism; And based on the device of the operator of discharge temperature or degree of superheat control flow divider and pre-pressure-reducing valve.According to present embodiment, no matter be in density than less than or greater than the design volumetric ratio time, can provide a kind of can be adjusted into by the aperture operation of flow divider and pre-pressure-reducing valve desired high side pressure, can in wide cut degree scope, not make operational efficiency and ability reduce the freezing cycle device that moves.

2 freezing cycle device has the shunting stream that makes the expansion mechanism shunting according to the embodiment of the present invention; Be arranged at the flow divider on the shunting stream; And based on the device of the operator of the rotating speed of discharge temperature or degree of superheat control flow divider and drive source.According to present embodiment, can be adjusted into desired high side pressure by aperture and operating under the actual running status of drive source drives rotating speed to flow divider, even and be the occasion of standard-sized sheet in the aperture of flow divider, because by the drive source drives rotating speed is operated, can be adjusted into desired high side pressure, so the operational efficiency of freezing cycle device and ability are reduced.

3 freezing cycle device has the shunting stream that makes the expansion mechanism shunting according to the embodiment of the present invention; Be arranged at the flow divider on the shunting stream; Fan to the evaporimeter air-supply; And according to the device of the operator of the rotating speed of discharge temperature or degree of superheat control flow divider and fan.According to present embodiment, can be by the aperture of flow divider and the operating under the actual running status of rotating speed of fan be adjusted into desired high side pressure, even and be the occasion of standard-sized sheet in the aperture of flow divider, owing to operate by rotating speed to fan, can be adjusted into desired high side pressure, so the operational efficiency of freezing cycle device and ability are reduced.

4 freezing cycle device according to the embodiment of the present invention is the volumetric ratio that makes compressing mechanism and expansion mechanism and the maximum roughly consistent device of value among each the ratio of outlet refrigerant density of radiator and evaporimeter under the running status of freezing cycle device.According to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the freezing cycle device of high operational efficiency.

5 freezing cycle device according to the embodiment of the present invention is the volumetric ratio that makes compressing mechanism and expansion mechanism and outlet at radiator under the running status of freezing cycle device. refrigerant density be each the roughly consistent device of ratio of outlet refrigerant density of the radiator under the running status of maximum freezing cycle device and evaporimeter.According to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the freezing cycle device of high operational efficiency.

6 freezing cycle device according to the embodiment of the present invention, the radiator under the running status of and the freezing cycle device that hot water temperature that flow out from radiator is the highest minimum and the roughly consistent device of ratio of evaporimeter outlet refrigerant density separately for the environment temperature water temperature minimum and inflow radiator of the volumetric ratio that makes compressing mechanism and expansion mechanism and evaporimeter.According to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the freezing cycle device of high operational efficiency.

7 freezing cycle device according to the embodiment of the present invention, for the volumetric ratio that makes compressing mechanism and expansion mechanism more than or equal to 10 device.At freezing cycle device is the occasion of hot water machine, according to present embodiment, even the service condition difference, by using the volumetric ratio that does not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the hot water machine of high operational efficiency.

8 freezing cycle device according to the embodiment of the present invention is the volumetric ratio of compressing mechanism and expansion mechanism and the radiator under the running status of and to the air themperature of radiator air-supply minimum and freezing cycle device that air themperature that from radiator blow out the highest minimum to the air themperature of evaporimeter air-supply and the roughly consistent device of ratio of evaporimeter outlet refrigerant density separately.According to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the freezing cycle device of high operational efficiency.

9 freezing cycle device according to the embodiment of the present invention, for the volumetric ratio that makes compressing mechanism and expansion mechanism more than or equal to 8 device.At freezing cycle device is the occasion of air conditioner, and according to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, it is poor also can to improve the season that reduces COP raising rate, often keeps the air conditioner of high operational efficiency.

The control method of 10 freezing cycle device according to the embodiment of the present invention, for have compressing mechanism, expansion mechanism and drive source connected by an axle in, the radiator that will be cooled off from the refrigerant that compressing mechanism is discharged; The evaporimeter that the refrigerant that flows out from expansion mechanism is heated; Shunting stream with the expansion mechanism shunting; The flow divider that on the shunting stream, is provided with; And in the freezing cycle device of the pre-pressure-reducing valve that the refrigerant that flows into expansion mechanism is reduced pressure, based on the control method of discharge temperature or degree of superheat control flow divider and pre-pressure-reducing valve.According to present embodiment, no matter be density than less than or during greater than the design volumetric ratio, can be adjusted into by the aperture operation of flow divider and pre-pressure-reducing valve desired high side pressure, can in wide cut degree scope, not make operational efficiency and ability reduce the freezing cycle device that moves.

The control method of 11 freezing cycle device according to the embodiment of the present invention, for have compressing mechanism, expansion mechanism and drive source connected by an axle in, the radiator that will be cooled off from the refrigerant that compressing mechanism is discharged; The evaporimeter that the refrigerant that flows out from expansion mechanism is heated; Shunting stream with the expansion mechanism shunting; And in the freezing cycle device of the flow divider that shunting is provided with on the stream, based on the control method of the rotating speed of discharge temperature or degree of superheat control flow divider and drive source.According to present embodiment, no matter be density than less than or during greater than the design volumetric ratio, can be by operation to the rotating speed of the aperture of flow divider and drive source, be adjusted into desired high side pressure, even and be the occasion of standard-sized sheet in the aperture of flow divider, owing to operate, can be adjusted into desired high side pressure, so can in wide cut degree scope, under the situation of operational efficiency that does not make freezing cycle device and ability reduction, move by rotating speed to drive source.

The control method of 12 freezing cycle device according to the embodiment of the present invention, for have compressing mechanism, expansion mechanism and drive source connected by an axle in, the radiator that will be cooled off from the refrigerant that compressing mechanism is discharged; The evaporimeter that the refrigerant that flows out from expansion mechanism is heated; Shunting stream with the expansion mechanism shunting; The flow divider that on the shunting stream, is provided with; And in the freezing cycle device of the fan of evaporimeter air-supply, based on the control method of the rotating speed of discharge temperature or degree of superheat control flow divider and fan.According to present embodiment, no matter be density than less than or during greater than the design volumetric ratio, can be by operation to the rotating speed of the aperture of flow divider and fan, be adjusted into desired high side pressure, even and be the occasion of standard-sized sheet in the aperture of flow divider, owing to operate, can be adjusted into desired high side pressure, so can in wide cut degree scope, under the situation of operational efficiency that does not make freezing cycle device and capacity reduction, move by rotating speed to fan.

13 freezing cycle device gives the compressor for compressing structure having the auxiliary compressor structure with when expansion mechanism is connected by an axle with refrigerant according to the embodiment of the present invention; The auxiliary compressor structure that the refrigerant of discharging from compressing mechanism is compressed again; The freezing cycle device of radiator that will be cooled off and evaporimeter that the refrigerant that flows out from expansion mechanism is heated, have the device of the flow divider that is provided with on the shunting stream of expansion mechanism shunting and the shunting stream from the refrigerant that the auxiliary compressor structure is discharged.According to present embodiment, because density is than certain restriction, be difficult to keep in the freezing cycle device of decompressor of optimal high side pressure in use, because the variation of the density ratio under the running status of reality is little, even the design volumetric ratio that prefers during with design is different, by the aperture operation to flow divider, also can adjust becomes desired high side pressure, can move under the situation of operational efficiency that does not make freezing cycle device and ability reduction.

Embodiments of the present invention 14 are in the freezing cycle device of embodiments of the present invention 13, have the embodiment of the pre-pressure-reducing valve that makes the refrigerant decompression that flows into expansion mechanism.According to present embodiment, no matter be density than less than or during greater than the design volumetric ratio, can pass through the aperture operation to flow divider and pre-pressure-reducing valve, adjusting become desired high side pressure, can move under the situation of operational efficiency that does not make freezing cycle device and ability reduction.

Embodiments of the present invention 15 are in the freezing cycle device of embodiments of the present invention 14, have based on the discharge temperature of this freezing cycle device or the device of the degree of superheat control flow divider and the operator of pre-pressure-reducing valve.According to present embodiment, can pass through aperture operation to flow divider and pre-pressure-reducing valve, adjusting become desired high side pressure, can move under the situation of operational efficiency that does not make freezing cycle device and ability reduction.

Embodiments of the present invention 16 are in the freezing cycle device of embodiments of the present invention 13, make the volumetric ratio of auxiliary compressor structure and expansion mechanism and the roughly consistent device of value maximum among the ratio of the outlet refrigerant density separately of radiator and compressing mechanism under the running status of freezing cycle device.According to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the freezing cycle device of high operational efficiency.

Embodiments of the present invention 17 are in the freezing cycle device of embodiments of the present invention 13, and the volumetric ratio that makes auxiliary compressor structure and expansion mechanism is the radiator under the running status of maximum freezing cycle device and the roughly consistent device of ratio of compressing mechanism outlet refrigerant density separately with refrigerant density at radiator outlet.According to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the freezing cycle device of high operational efficiency.

Embodiments of the present invention 18 are in the freezing cycle device of embodiments of the present invention 13, the radiator under the running status of the volumetric ratio that makes auxiliary compressor structure and expansion mechanism and and the freezing cycle device that hot water temperature that flow out from radiator is the highest minimum in the environment temperature water temperature minimum and inflow radiator of evaporimeter and the roughly consistent device of ratio of evaporimeter outlet refrigerant density separately.According to present embodiment, even the service condition difference, by using the volumetric ratio do not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the operation of the freezing cycle device of high operational efficiency.

Embodiments of the present invention 19 are in the freezing cycle device of embodiments of the present invention 13, use carbon dioxide as the volumetric ratio of the auxiliary compressor structure of the freezing cycle device that uses as hot water machine of refrigerant and expansion mechanism more than or equal to 4 device.At freezing cycle device is the occasion with hot water machine of auxiliary compressor structure, according to present embodiment, even the service condition difference can be provided, by using the volumetric ratio that does not expand in advance as far as possible, the season that also can obtain reducing COP raising rate is poor, often keeps the freezing cycle device of high operational efficiency.

[embodiment 1]

With reference to the accompanying drawings embodiments of the invention are illustrated.

Fig. 1 is the structure chart that the freezing cycle device of embodiments of the invention 1 is shown.In addition, about the freezing cycle device of present embodiment, be to be that example describes with the hot water machine.In other words, the present invention is not limited to the hot water machine of present embodiment, also can be air conditioner or the like.

The freezing cycle device of present embodiment, have by compressing mechanism 1, radiator 2, expansion mechanism 3 and with outer gas and carry out refrigerant circulation circuit A that the evaporimeter 5 of heat exchange constitutes and the hot water supply closed circuit B that constitutes by feed pump 6, radiator 2 and hot water supply jar 7 by fan 4 air-supplies, in radiator 2, the refrigerant that utilization is discharged by compressing mechanism 1 is heated as hot water to the water from feed pump 6, and with the freezing cycle device (occasion at present embodiment be hot-water supply device) of this hot-water storage in hot water supply jar 7.

Compressing mechanism 1 is driven by drive sources such as motor 8.In addition, compressing mechanism 1 utilizes an axle 9 to be connected with the expansion mechanism 3 (decompressor) that pressure can be transformed to power, utilizes the input of the recovery power reduction drive source 8 of expansion mechanism 3.In addition, refrigerant circulation circuit A has the shunting stream 10 that makes expansion mechanism 3 shunting, regulates the flow divider 11 of the flow that flows through shunting stream 10 and is arranged at radiator 2 and the inlet of expansion mechanism 3 between the refrigerant to flowing into expansion mechanism 3 give decompression give pressure-reducing valve 12.Enclose carbon dioxide (CO ₂) as refrigerant.In addition, has the discharge temperature detecting unit 20 of the outlet temperature (discharge temperature of compressing mechanism) that detects compressing mechanism 1 and calculate flow divider 11 and give go forward side by side the 1st operator 21 of line operate of pressure-reducing valve 12 apertures based on the value that discharge temperature detecting unit 20 detects.

Below, with the volume of cylinder of compressing mechanism 1 as VC, with the volume of cylinder of expansion mechanism 3 as VE, with the outlet refrigerant density of evaporimeter 5 as DC (the inflow refrigerant density of compressing mechanism 1), the action during for the freezing cycle device running that as above constitutes is illustrated as DE (the inflow refrigerant density of expansion mechanism 3) with the outlet refrigerant density of radiator 2.At first, the density under the actual motion state is illustrated than the equal occasion of design volumetric ratio (VC/VE) that (DE/DC) roughly the time prefers with design.

Compressing mechanism 1 is compressed to refrigerant above critical pressure (high side pressure) always.This compressed refrigerant becomes high-temperature high-pressure state, when flowing through radiator 2, water-cooled is cooled off.In other words, send into the water on the current road of radiator 2 by feed pump 6 from the bottom of hot water supply jar 7, by the refrigerant heating of the refrigerant flow that flows through radiator 2.Thereafter, refrigerant is become by expansion mechanism 3 decompression and is the gas-liquid two-phase state.The pressure of refrigerant can be transformed to power in expansion mechanism 3, and this transmission of power is to axle 9.Owing to be delivered to this power of 9, the input of drive source 8 reduced.Refrigerant through expansion mechanism 3 decompressions flow into evaporimeter 5, and in this evaporimeter 5, refrigerant becomes gas-liquid two-phase or gaseous state by the air cooling., become the refrigerant of gas-liquid two-phase or gaseous state, be drawn into compressing mechanism 1 once again thereafter.

Below to being illustrated in the situation more different with the design volumetric ratio (VC/VE) that when designing, prefers of the density under the actual motion state than (DE/DC).At first, the action of the situation of the design volumetric ratio (VC/VE) that the density under the actual motion state time is preferred greater than design than (DE/DC) is illustrated.

In this case, because density is than certain restriction,, make freeze cycle under the state that high side pressure reduces, carry out balance for the refrigerant density (DE) of the outlet (inlet of expansion mechanism 3) that makes radiator 2 diminishes.But, high side pressure than the low state of desired pressure under, discharge temperature reduces and the heating efficiency of freezing cycle device is reduced and the efficient of freezing cycle device is reduced.Therefore, if flow divider 11 is not a full-shut position,, make the refrigerant of original inflow shunting stream 10 flow into expansion mechanism 3 to closing direction operation flow divider 11.Perhaps,, give pressure-reducing valve 12, make the refrigerant decompression that flows into expansion mechanism 3, refrigerant density is reduced to the closing direction operation if flow divider 11 is full-shut positions.By these actions, high side pressure is risen, because can adjust to desirable pressure, can carry out high efficiency operation.

Otherwise the action during design volumetric ratio (VC/VE) that the density under the actual motion state time is preferred less than design than (DE/DC) is illustrated.

In this case, because density is than certain restriction,, make freeze cycle under the state that high side pressure is risen, carry out balance for the refrigerant density (DE) of the outlet (inlet of expansion mechanism 3) that makes radiator 2 becomes big.But under the state that high side pressure rises than desired pressure, the operational efficiency of freezing cycle device reduces.Therefore, not full-gear if give pressure-reducing valve 12, give pressure-reducing valve 12 to opening direction operation, the refrigerant that flows into expansion mechanism 3 is not reduced pressure and refrigerant density is risen.Perhaps, are full-gears if give pressure-reducing valve 12, to opening direction operation flow divider 11, make the part of the refrigerant that flows into expansion mechanism 3 flow into shunting stream 10.By these actions, high side pressure is reduced, because can adjust to desirable pressure, can carry out high efficiency operation.

As mentioned above, in the freezing cycle device of embodiment 1, because density is than certain restriction, be difficult to keep in the freezing cycle device of decompressor of optimal high side pressure in use, when no matter the density under the running status of reality be the design volumetric ratio (VC/VE) that prefers during less than or greater than design than (DE/DC), can be by to flow divider 11 with give the operation of the aperture of pressure-reducing valve 12, adjust to desirable high side pressure, under the situation that operational efficiency and ability are reduced, provide the freezing cycle device that can move.

Below, as flow divider 11 and the concrete method of operating of giving pressure-reducing valve 12, the control to the 1st operator 21 carries out is illustrated according to flow chart shown in Figure 2.

In the control of present embodiment, utilize the dependency relation of high side pressure and discharge temperature, on measuring, needn't carry out high side pressure by the sensor of needs costliness and detect and utilize the discharge temperature that to measure more cheaply to flow divider flow divider 11 and give pressure-reducing valve 12 and control.

That is, when the operation of freezing cycle device, read in detected value (discharge temperature Td) (step 100) from discharge temperature detecting unit 20.Compare (step 110) with being stored in target discharge temperature (target Td) among ROM etc. and the discharge temperature of in step 100, reading in advance.

When discharge temperature is lower than the target discharge temperature,, at first, judge whether flow divider 11 is full cut-off (step 120) because high side pressure has the tendency lower than optimum pressure.At flow divider 11 is under the situation of full cut-off, gives pressure-reducing valve 12 (step 130) to the closing direction operation, makes the refrigerant decompression that flows into expansion mechanism 3, and refrigerant density is reduced, and high side pressure and discharge temperature are risen.In addition, be under the situation of not full cut-off at flow divider 11, to closing direction operation flow divider 11 (step 140), inflow is reduced the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, high side pressure and discharge temperature are risen.

Otherwise, when discharge temperature is higher than the target discharge temperature,, at first, judges and give whether pressure-reducing valve 12 is standard-sized sheet (step 150) because high side pressure has the tendency higher than optimum pressure.Giving pressure-reducing valve 12 under the situation of standard-sized sheet,, inflow is being increased the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, high side pressure and discharge temperature are reduced to opening direction operation flow divider 11 (step 160).In addition, be under the situation of not standard-sized sheet giving pressure-reducing valve 12, give pressure-reducing valve 12 (step 170) to opening the direction operation, do not reduce pressure by making the refrigerant that flows into expansion mechanism 3, do not reduce by making refrigerant density, high side pressure and discharge temperature are reduced.

After above step, turn back to step 100, later on by repeating from step 100 until step 170, as shown in Figure 3, to flow divider 11 with give pressure-reducing valve 12 and jointly control.

As mentioned above, in the control method of the freezing cycle device of embodiment 1, because density is than certain restriction, be difficult to keep in the freezing cycle device of decompressor of optimal high side pressure in use, no matter the density under the running status of reality prefer during than (DE/DC) less than or greater than design design volumetric ratio (VC/VE) time, by based on discharge temperature operation flow divider 11 and give the aperture of pressure-reducing valve 12, can adjust to desired high side pressure, can under the situation of operational efficiency that does not make freezing cycle device and ability reduction, move.

In addition, flow divider 11, give pressure-reducing valve 12 judgement for standard-sized sheet or full cut-off, do not need physically that valve becomes standard-sized sheet or full cut-off, consider reliability of valve or the like, can judge yet by becoming near the maximum opening or the minimum aperture of predetermined standard-sized sheet or full cut-off.

In addition, the refrigerant that illustrates in the present embodiment is carbon dioxide (CO ₂), but other refrigerant, such as, R410A etc. also can obtain same effect.

[embodiment 2]

Freezing cycle device to embodiments of the invention 2 is illustrated below.The structure of the freezing cycle device of the freezing cycle device of present embodiment and embodiment 1 is roughly the same, gives prosign and omits its explanation for same functional part.Fig. 4 is the structure chart that the freezing cycle device of embodiments of the invention 2 is shown.In addition, Fig. 5 is the flow chart of control method that the freezing cycle device of embodiments of the invention 2 is shown.

In the freezing cycle device of present embodiment, and the freezing cycle device difference of embodiment 1 is that its formation has the evaporating temperature detecting unit 30 of detection from the inlet of evaporimeter 5 to the temperature (evaporating temperature of evaporimeter) between outlet, detect compressing mechanism 1 inlet temperature (inlet temperature of compressing mechanism 1) inlet temperature detecting unit 31 and calculate the degree of superheat (inlet temperature and evaporating temperature poor) from evaporating temperature detecting unit 30 and inlet temperature detecting unit 31 detected values, go forward side by side the 2nd operator 32 of line operate of the aperture of calculating flow divider 11 and giving pressure-reducing valve 12 replaces discharge temperature detecting unit 20 and the 1st operator 21 of embodiment 1.

According to flow chart shown in Figure 5 the control that the 2nd operator 32 carries out is illustrated below.In the control of present embodiment, utilize the dependency relation of the high side pressure and the degree of superheat, on measuring, needn't carry out the detection of high side pressure and utilize the degree of superheat that the evaporating temperature that can measure more cheaply and inlet temperature calculate to flow divider flow divider 11 and give pressure-reducing valve 12 and control by the sensor of needs costliness.

That is, when the operation of freezing cycle device, read in detected value (evaporating temperature Te) (step 200) from evaporating temperature detecting unit 30.And, read in detected value (inlet temperature Ts) (step 210) from inlet temperature detecting unit 31.Calculate the degree of superheat (SH) (step 220) from these detected values that read in, compare (step 230) being stored in the target degree of superheat (target SH) among the ROM etc. and the degree of superheat that in step 200, calculates in advance as the difference of inlet temperature and evaporating temperature.

When the degree of superheat is lower than the target degree of superheat,, at first, judge whether flow divider 11 is full cut-off (step 240) because high side pressure has the tendency lower than optimum pressure.At flow divider 11 is the occasion of full cut-off, gives pressure-reducing valve 12 (step 250) to the closing direction operation, makes the refrigerant decompression that flows into expansion mechanism 3, and refrigerant density is reduced, and high side pressure and discharge temperature are risen.In addition, be the occasion of full cut-off not at flow divider 11, to closing direction operation flow divider 11 (step 260), inflow is reduced the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, the high side pressure and the degree of superheat are risen.

Otherwise, when the degree of superheat is higher than the target degree of superheat,, at first, judges and give whether pressure-reducing valve 12 is standard-sized sheet (step 270) because high side pressure has the tendency higher than optimum pressure.Be the occasion of standard-sized sheet giving pressure-reducing valve 12,, inflow increased the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, the high side pressure and the degree of superheat are reduced to opening direction operation flow divider 11 (step 280).

In addition, be the occasion of standard-sized sheet not giving pressure-reducing valve 12, give pressure-reducing valve 12 (step 290), do not reduce pressure, refrigerant density is not reduced, high side pressure and discharge temperature are reduced by making the refrigerant that flows into expansion mechanism 3 to opening the direction operation.

After above step, turn back to step 200, later on by repeating from step 200 until step 290, to flow divider 11 with give pressure-reducing valve 12 and jointly control.

As mentioned above, in the freezing cycle device and control method thereof of embodiment 2, because density is than certain restriction, be difficult to keep in the freezing cycle device of decompressor of optimal high side pressure in use, no matter under the situation of the design volumetric ratio (VC/VE) that prefers during less than or greater than design than (DE/DC) of the density under the running status of reality, by according to degree of superheat operation flow divider 11 and give the aperture of pressure-reducing valve 12, can adjust to desired high side pressure, can under the situation of operational efficiency that does not make freezing cycle device and ability reduction, move.

[embodiment 3]

Freezing cycle device to embodiments of the invention 3 is illustrated below.The structure of the freezing cycle device of the freezing cycle device of present embodiment and embodiment 1 is roughly the same, gives prosign and omits its explanation for same functional part.Fig. 6 is the structure chart that the freezing cycle device of embodiments of the invention 3 is shown.Fig. 7 is the flow chart of control method that the freezing cycle device of embodiments of the invention 3 is shown.

In the freezing cycle device of present embodiment, be that with the freezing cycle device difference of embodiment 1 it constitutes and does not have the giving pressure-reducing valve 12 of embodiment 1 and have the 3rd operator of the rotating speed of the drive source 8 that drives flow divider 11 and compressing mechanism 1 being operated based on discharge temperature detecting unit 20 detected values 40.

According to flow chart shown in Figure 7 the control that the 3rd operator 40 carries out is illustrated below.The same with embodiment 1, control according to discharge temperature.

That is, when the operation of freezing cycle device, read in detected value (discharge temperature) (step 300) from discharge temperature detecting unit 20.Compare (step 310) with being stored in target discharge temperature among ROM etc. and the discharge temperature of in step 300, reading in advance.

When discharge temperature is lower than the target discharge temperature,, at first, judge whether flow divider 11 is full cut-off (step 320) because high side pressure has the tendency lower than optimum pressure.At flow divider 11 is the occasion of full cut-off, increases the rotating speed (step 330) of drive source 8.When driving the rotating speed increasing, the internal circulating load of the refrigerant of discharging from compressing mechanism 1 increases, because the heat exchanger effectiveness in radiator 2, the evaporimeter 5 descends, when the outlet temperature at radiator 2 rises, makes the refrigerant density that flows into expansion mechanism 3 to reduce, the outlet temperature of evaporimeter 5 reduces, increase because suck the refrigerant density of compressing mechanism 1, so density reduces than (DE/DC).Therefore, can obtain the effect equal, high side pressure and discharge temperature are risen with give pressure-reducing valve 12 to closing direction operation.

In addition, be the occasion of full cut-off not at flow divider 11, judge whether to drive rotating speed less than predetermined reference value (step 340).When driving rotating speed,, think that driving rotating speed reduces because in step 380 described later less than predetermined reference value, by until the scope of a reference value in, strengthen and drive rotating speed (step 350), reduce density, high side pressure and discharge temperature are risen than (DE/DC).In addition, be the occasion of a reference value driving rotating speed, to closing direction operation flow divider 11 (step 360), inflow is reduced the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, high side pressure and discharge temperature are risen.

Otherwise, when discharge temperature is higher than the target discharge temperature,, at first, judge whether flow divider 11 is standard-sized sheet (step 370) because high side pressure has the tendency higher than optimum pressure.At flow divider 11 is the occasion of standard-sized sheet, reduces the rotating speed (step 380) of drive source 8.When the driving rotating speed reduces, the internal circulating load of the refrigerant of discharging from compressing mechanism 1 reduces, because the heat exchanger effectiveness in radiator 2, the evaporimeter 5 improves, when the outlet temperature at radiator 2 descends, makes the refrigerant density that flows into expansion mechanism 3 to rise, the outlet temperature of evaporimeter 5 rises, reduce because suck the refrigerant density of compressing mechanism 1, so density increases than (DE/DC).Therefore, can obtain and give the equal effect of pressure-reducing valve 12, high side pressure and discharge temperature are reduced to opening direction operation.

In addition, be the occasion of standard-sized sheet not at flow divider 11, judge whether to drive rotating speed greater than predetermined reference value (step 390).When driving rotating speed,, think that driving rotating speed increases because in step 330 greater than predetermined reference value, by until the scope of a reference value in, reduce to drive rotating speed (step 400), increase density, high side pressure and discharge temperature are reduced than (DE/DC).In addition, be the occasion of a reference value driving rotating speed, to opening operation flow divider 11 (step 410) on the direction, inflow is increased the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, high side pressure and discharge temperature are reduced.

After above step, turn back to step 300, later on by repeating from step 300 until step 410, as shown in Figure 8, the driving rotating speed of flow divider 11 and drive source 8 is jointly controlled.

As mentioned above, in the freezing cycle device and control method thereof of embodiment 3, because density is than certain restriction, be difficult to keep in the freezing cycle device of decompressor of optimal high side pressure in use, no matter under the situation of the design volumetric ratio (VC/VE) that prefers during less than or greater than design than (DE/DC) of the density under the running status of reality, by based on the aperture of discharge temperature operation flow divider 11 and the driving rotating speed of drive source 8, can adjust to desired high side pressure.

In addition, as shown in Figure 8, even be the occasion of standard-sized sheet, owing to operate by driving rotating speed to drive source 8 in the aperture of flow divider 11, can adjust to desired high side pressure, can under the situation of operational efficiency that does not make freezing cycle device and ability reduction, move.

In addition, in the present embodiment, the same with embodiment 1 is that the example of controlling based on discharge temperature is illustrated, but also can equally with embodiment 2 control based on the degree of superheat.In addition, also the aperture operation of giving pressure-reducing valve 12 of embodiment 1,2 can be implemented with the driving rotating speed operative combination of the drive source 8 of present embodiment.In addition, be the judgement of standard-sized sheet or full cut-off at flow divider 11, do not need physically that valve becomes standard-sized sheet or full cut-off, consider reliability of valve or the like, also can judge by becoming near the maximum opening or the minimum aperture of predetermined standard-sized sheet or full cut-off.In addition, the refrigerant that illustrates in the present embodiment is carbon dioxide (CO ₂), but other refrigerant, such as, R410A etc. also can obtain same effect.

[embodiment 4]

Freezing cycle device to embodiments of the invention 4 is illustrated below.The structure of the freezing cycle device of the freezing cycle device of present embodiment and embodiment 1 is roughly the same, gives prosign and omits its explanation for same functional part.Fig. 9 is the structure chart that the freezing cycle device of embodiments of the invention 4 is shown.Figure 10 is the flow chart of control method that the freezing cycle device of embodiments of the invention 4 is shown.

In the freezing cycle device of present embodiment, be that with the freezing cycle device difference of embodiment 1 it constitutes and does not have the giving pressure-reducing valve 12 of embodiment 1 and have the 4th operator of the rotating speed of the drive source (not shown) that drives flow divider 11 and drive fan 4 being operated based on discharge temperature detecting unit 20 detected values 50.

According to flow chart shown in Figure 10 the control that the 4th operator 50 carries out is illustrated below.In the control of present embodiment, the same with embodiment 1, control based on discharge temperature.

That is, when the operation of freezing cycle device, read in detected value (discharge temperature) (step 400) from discharge temperature detecting unit 20.Compare (step 410) with being stored in target discharge temperature among ROM etc. and the discharge temperature of in step 400, reading in advance.

When discharge temperature is lower than the target discharge temperature,, at first, judge whether flow divider 11 is full cut-off (step 420) because high side pressure has the tendency lower than optimum pressure.At flow divider 11 is the occasion of full cut-off, increases the rotating speed (step 430) of fan 4.Because because when rotation speed of the fan strengthened, evaporating pressure (pressure of evaporimeter 5 inlet～compressing mechanisms 1 inlet) rose, the refrigerant density of the outlet of evaporimeter 5 rises, density reduces than (DE/DC).Therefore, can obtain the effect equal, high side pressure and discharge temperature are risen with give pressure-reducing valve 12 to closing direction operation.

In addition, be the occasion of full cut-off not at flow divider 11, judge that whether rotation speed of the fan is less than predetermined reference value (step 440).During less than predetermined reference value,, think that rotation speed of the fan reduces at rotation speed of the fan because in step 480 described later, by until the scope of a reference value in, strengthen rotation speed of the fan (step 450), reduce density, high side pressure and discharge temperature are risen than (DE/DC).In addition, be the occasion of a reference value at rotation speed of the fan, to closing direction operation flow divider 11 (step 460), inflow is reduced the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, high side pressure and discharge temperature are risen.

Otherwise, when discharge temperature is higher than the target discharge temperature,, at first, judge whether flow divider 11 is standard-sized sheet (step 470) because high side pressure has the tendency higher than optimum pressure.At flow divider 11 is the occasion of standard-sized sheet, reduces the driving rotating speed (step 480) of fan 4.Because because when rotation speed of the fan reduced, evaporating pressure reduced, the refrigerant density of the outlet of evaporimeter 5 reduces, density increases than (DE/DC).Therefore, can obtain with to opening the equal effect of direction operation flow divider 11, high side pressure and discharge temperature are reduced.

In addition, be the occasion of standard-sized sheet not at flow divider 11, judge that whether rotation speed of the fan is greater than predetermined reference value (step 490).When driving rotating speed,, think that rotation speed of the fan increases because in step 430 greater than predetermined reference value, by until the scope of a reference value in, reduce rotation speed of the fan (step 500), increase density, high side pressure and discharge temperature are reduced than (DE/DC).In addition, be the occasion of a reference value driving rotating speed, to opening direction operation flow divider 11 (step 510), inflow is increased the coolant quantity of the shunting stream 10 of expansion mechanism 3 shuntings, high side pressure and discharge temperature are reduced.

After above step, turn back to step 400, later on by repeating from step 400 until step 510, as shown in Figure 11, the rotating speed of flow divider 11 and fan 4 is jointly controlled.

As mentioned above, in the freezing cycle device and control method thereof of embodiment 4, because density is than certain restriction, be difficult to keep in the freezing cycle device of decompressor of optimal high side pressure in use, no matter under the situation of the design volumetric ratio (VC/VE) that prefers during less than or greater than design than (DE/DC) of the density under the running status of reality, by based on the aperture of degree of superheat operation flow divider 11 and the rotating speed of fan 4, can adjust to desired high side pressure.

In addition, as shown in figure 11, even be the occasion of standard-sized sheet, because by the rotating speed of fan 4 is operated in the aperture of flow divider 11, can adjust to desired high side pressure, can under the situation of operational efficiency that does not make freezing cycle device and ability reduction, move.

In addition, in the present embodiment, the same with embodiment 1 is that the example of controlling based on discharge temperature is described, but also can equally with embodiment 2 control based on the degree of superheat.In addition, also the rotating speed operative combination of the fan 4 of the driving rotating speed operation of the compressing mechanism 11 of the aperture operation of giving pressure-reducing valve 12 of embodiment 1,2, embodiment 3 and present embodiment can be implemented.In addition, be the judgement of standard-sized sheet or full cut-off at flow divider 11, do not need physically that valve becomes standard-sized sheet or full cut-off, consider reliability of valve or the like, also can judge by becoming near the maximum opening or the minimum aperture of predetermined standard-sized sheet or full cut-off.In addition, the refrigerant that illustrates in the present embodiment is carbon dioxide (CO ₂), but other refrigerant, such as, R410A etc. also can obtain same effect.

[embodiment 5]

Freezing cycle device to embodiments of the invention 5 is illustrated below.In addition, because the structure of the freezing cycle device of present embodiment and control method thereof are identical with embodiment 1, omit the same structure and the explanation of action.

The structure of the freezing cycle device of present embodiment be characterised in that with the volume of cylinder of compressing mechanism 1 as VC, with the volume of cylinder of expansion mechanism 3 as VE, with the outlet refrigerant density of evaporimeter 5 as DC, with the outlet refrigerant density of radiator 2 during as DE, design volumetric ratio (VC/VE) in design and the density that becomes than (DE/DC) in the density under the actual motion state under the maximum condition roughly more consistent than the value of (DE/DC).In addition, in specific words, be to design and make and become density under the condition of maximum than the roughly consistent this point of value of (DE/DC) with the outlet refrigerant density (DE) of radiator 2.

In addition, in the freezing cycle device that uses as hot water machine, design volumetric ratio (VC/VE), with in the scope of application of hot water machine, the density when moving under the condition that environment temperature (outer temperature degree) water temperature (going into coolant-temperature gage) minimum and inflow radiator 2 is minimum and hot water temperature's (hot water effluent's temperature) that flow out from radiator 2 is the highest of evaporimeter 5 is roughly more consistent than (DE/DC) to be the feature of project organization.

In addition, in specific words, in the freezing cycle device that uses as hot water machine, the value of design volumetric ratio (VC/VE) is features of project organization more than or equal to 10.

But, in the freezing cycle device of present embodiment, as illustrated in embodiment 1, when the density under the actual motion state than (DE/DC) during less than the design volumetric ratio (VC/VE) of when design decision, by to open direction operation flow divider 11 or in density than (DE/DC) during greater than design volumetric ratio (VC/VE), by giving pressure-reducing valve 12 to opening the direction operation, make density more consistent with design volumetric ratio (VC/VE) than (DE/DC), can adjust to desired high side pressure.Yet, increase or utilize and give pressure-reducing valve 12 when the pressure differential of pre-expansion is increased at the coolant quantity that flows through shunting stream 10, owing to should reduce by recuperable power, the raising rate of operational efficiency (COP) is descended.So it is very important how the design volumetric ratio being designed to optimum value.

Therefore, utilize accompanying drawing 12 and 13 optimal design volumetric ratios to be described in detail below for the occasion that the freezing cycle device of present embodiment is used as hot water machine.

Figure 12 illustrates the density ratio of embodiments of the invention 5 and the correlation diagram of COP ratio, and Figure 13 illustrates the density ratio of embodiments of the invention 5 and the correlation diagram of refrigerant density.

In Figure 12, outer temperature degree is to set according to the high order of temperature: period in summer, interim, period in winter and low temperature period.Going into coolant-temperature gage is the minimum temperature that prefers according to each outer temperature degree condition, and hot water effluent's temperature is the normal temperature that prefers according to each outer temperature degree condition.In addition, the COP ratio is outside each under temperature degree condition, is 100 with the COP of the freezing cycle device that do not use decompressor.Below, with period in summer condition be that example describes.

In period in summer condition, the density under the actual motion state is about 7 than (DE/DC).With occasion, under period in summer condition, must make coolant distribution arrive shunting stream 10 greater than the freezing cycle device of the design volumetric ratio (VC/VE) of this value design.Otherwise, with occasion, under period in summer condition, must make the refrigerant utilization give pressure-reducing valve 12 and expand in advance less than the freezing cycle device of the design volumetric ratio (VC/VE) of this value design.Yet, known in shunting, expand under any one situation in advance, with the situation of having carried out optimal design in period in summer under the condition, promptly be designed to about 7 situation and compare will designing volumetric ratio (VC/VE), COP particularly, sharply descends at the pre-occasion COP ratio that expands significantly than reducing.

On the other hand, under period condition and the low temperature condition in period, the density under the actual motion state is respectively about 10 and about 12 than (DE/DC) in the winter time.In the occasion of the freezing cycle device that designs with design volumetric ratio (VC/VE), under period condition and the low temperature condition in period, must make coolant distribution arrive shunting stream 10 in the winter time greater than these values.Otherwise the occasion at the freezing cycle device that designs with the design volumetric ratio (VC/VE) less than these values under period condition and the low temperature condition in period, must make the refrigerant utilization give pressure-reducing valve 12 and expand in advance in the winter time.Yet, known in shunting, expand under any one situation in advance, with the situation of having carried out optimal design under each condition of condition and the low temperature condition in period of period in the winter time, promptly be designed to about 10 and about 12 situation and compare will designing volumetric ratio (VC/VE), COP is than reducing, particularly, sharply descend significantly at the pre-occasion COP ratio that expands.

In other words, because because of different service conditions such as seasons, optimal design volumetric ratio difference is utilized in an axle 9 direct-connected freezing cycle devices at compressing mechanism 1 and expansion mechanism 3, design volumetric ratio (VC/VE) can only determine a value when design.Therefore, such as, design be that best design volumetric ratio (VC/VE) is under about 7 the situation under the condition in period in summer, the COP ratio is about 112 under period in summer condition, but the COP ratio is about 101～103 in season under other condition.

Relative therewith, design be that best design volumetric ratio (VC/VE) is that the COP ratio is about 110 under low temperature condition in period under about 12 the situation under the low temperature condition in period, and the COP ratio is about 107～108 in season under other condition.Perhaps, design under the condition in period in the winter time for best design volumetric ratio (VC/VE) under about 10 the situation, low temperature COP in period ratio short between the comparable period is about 103, but is 110 under the condition in period in the winter time, is about 108 in other seasons under the condition.

Like this, will design volumetric ratio (VC/VE) is designed in the winter time under period condition and the low temperature condition in period the difference in season of COP raising rate to be reduced, even service condition differences such as season also can often be kept high operational efficiency when best.

In other words, in the freezing cycle device of embodiment 5, as can be seen from Figure 12, the occasion that is conceived to expand is in advance compared with the occasion of shunting, the little this point of raising rate of COP, be designed to roughly more consistent than the value of (DE/DC) than the value of (DE/DC) by designing volumetric ratio (VC/VE) for the density under the maximum condition (occasion at Figure 12 is a low temperature condition in period) in the density under the actual motion state, even make the service condition difference also not give expansion as much as possible, can often keep the operation of the freezing cycle device of high operational efficiency.

In addition, outlet refrigerant density (DC) from evaporimeter shown in Figure 13 5, or the dependency relation of the outlet refrigerant density (DE) of radiator 2 and density ratio, density is than (DE/DC) as can be known, compare with the variation of the outlet refrigerant density (DC) of evaporimeter 5, more be subjected to the influence of variation of the outlet refrigerant density (DE) of radiator 2, and then, with the roughly proportional relation of outlet refrigerant density (DE) of radiator 2.

So, be designed to density under the actual motion state by design volumetric ratio (VC/VE) and be maximum condition than the value of (DE/DC) with the freezing cycle device of present embodiment, promptly the density that becomes under the maximum condition with the outlet refrigerant density (DE) of radiator 2 is roughly more consistent than the value of (DE/DC), just can often keep the operation of the freezing cycle device of high operational efficiency.

In addition, as having illustrated among Figure 12, because in the freezing cycle device that uses as hot water machine, in its scope of application, environment temperature (outer temperature degree) at evaporimeter 5 is minimum, and the water temperature of inflow radiator 2 (going into coolant-temperature gage) is minimum, and the situation of moving under the highest condition of hot water temperature's (hot water effluent's temperature) of flowing out from radiator 2 (the low temperature condition in period of the occasion of Figure 12) is more suitable than the situation that (DE/DC) moves under the condition that becomes maximum with the actual motion state density down of freezing cycle device, so, just can often keep the operation of the freezing cycle device of high operational efficiency by being designed to design volumetric ratio (VC/VE) roughly consistent than (DE/DC) in the density under this running status.

In addition, density under the running status of the reality of freezing cycle device becomes maximum condition than (DE/DC), when freezing cycle device is hot water machine, with minimum in the environment temperature of evaporimeter 5, and the water temperature of inflow radiator 2 is minimum, and the condition that the hot water temperature of flowing out from radiator 2 is the highest is suitable, when being applied to comprise general freezing cycle device such as air conditioner described later, the temperature that can be replaced into the fluid of heating refrigerant in evaporimeter 5 is minimum, and the temperature of incoming fluid of inflow radiator 2 that is used for cooling off refrigerant in radiator 2 is minimum, and from the highest condition of temperature of the fluid that the radiator 2 of heating flows out by this refrigerant cooling.

In addition, in employed freezing cycle device as hot water machine, by design make design volumetric ratio (VC/VE) become value more than or equal to 10 (with the occasion of Figure 12 period in winter condition and the corresponding value of low temperature condition in period), just can often keep the operation of the freezing cycle device of high operational efficiency.

[embodiment 6]

Below, be not utilize embodiment 1 hot water machine example but utilize the example of air conditioner to come the freezing cycle device of embodiments of the invention 6 is illustrated.Figure 14 is the structure chart that the freezing cycle device of embodiments of the invention 6 is shown.In addition, because the structure of the freezing cycle device of present embodiment and embodiment 1 are roughly the same, use prosign for same functional part.So, omit for the explanation of same structure and action thereof.In addition, because the control method of freezing cycle device is identical with embodiment 1, it illustrates omission.

The freezing cycle device of present embodiment is made of off-premises station C and indoor set D.So, off-premises station C by compressing mechanism the 1, the 1st cross valve 60, carry out outdoor heat converter the 62, the 2nd cross valve 63 of heat exchange and expansion mechanism 3 etc. with air and constitute by outdoor fan 61 air-supply, in addition, indoor set D, indoor heat converter 65 grades of carrying out heat exchange with the air of being blown by indoor fan 64 constitute.

So, in the freezing cycle device of present embodiment, when making the 1st cross valve the 60, the 2nd cross valve 63 switch to solid line direction among the figure, by making outdoor heat converter 62 as radiator, make indoor heat converter 65 as evaporimeter, just can make the indoor cold-room that becomes that indoor set D is set.In addition, when making the 1st cross valve the 60, the 2nd cross valve 63 switch to dotted line direction among the figure, by making indoor heat converter 65 as radiator, make outdoor heat converter 62 as evaporimeter, just can make indoor set D is set indoor become greenhouse and carry out the action of air conditioning.

In addition, the structure of present embodiment be characterised in that with the volume of cylinder of compressing mechanism 1 as VC, with the volume of cylinder of expansion mechanism 3 as VE, with the outlet refrigerant density of any one heat exchanger when the evaporimeter in outdoor heat converter 62 or the indoor heat converter 65 as DC (the inflow refrigerant density of compressing mechanism 1), with the outlet refrigerant density of any one heat exchanger when the radiator in outdoor heat converter 62 or the indoor heat converter 65 during as DE (the inflow medium density of expansion mechanism 3), make design volumetric ratio (VC/VE) in design and the density that becomes than (DE/DC) in the density under the actual motion state under the maximum condition roughly more consistent than the value of (DE/DC).In addition, in specific words, be to design make with outdoor heat converter 62 or indoor heat converter 65 in the outlet refrigerant density (DE) of any one heat exchanger during as radiator become density under the condition of maximum than the roughly consistent this point of value of (DE/DC).

In addition, in the freezing cycle device that uses as air conditioner, design volumetric ratio (VC/VE), with in the scope of application of air conditioner, minimum to the air themperature of blowing as the outdoor heat converter 62 or any one heat exchanger in the indoor heat converter 65 of evaporimeter, and minimum to the air themperature of blowing as the outdoor heat converter 62 or any one heat exchanger in the indoor heat converter 65 of radiator, and the density under the highest condition of the air themperature that blows out as the heat exchanger of radiator during operation is roughly more consistent than (DE/DC) to be the feature of project organization.

In addition, in specific words, in the freezing cycle device that uses as air conditioner, the value of design volumetric ratio (VC/VE) is features of project organization more than or equal to 8.

Utilize accompanying drawing 15 and 16 to be described in detail as the optimal design volumetric ratio that air conditioner uses below for freezing cycle device with present embodiment.

Figure 15 illustrates the density ratio of embodiments of the invention 6 and the correlation diagram of COP ratio, and Figure 16 illustrates the density ratio of embodiments of the invention 6 and the correlation diagram of refrigerant density.

In Figure 15, outer temperature degree is to set according to the high order of temperature: period in summer cold-room, interim cold-room, interim greenhouse and period in winter greenhouse.Indoor temperature (to the air themperature of indoor heat converter 65 air-supply), indoor blowing temperature (air themperature that blows out from indoor heat converter 65) are respectively the normal temperatures according to temperature degree condition enactment outside each.In addition, the COP ratio is outside each under temperature degree condition, is 100 with the COP of the freezing cycle device that do not use decompressor.Below, with period in summer the cold-room condition be that example describes.

In period in summer cold-room condition, the density under the actual motion state is about 4 than (DE/DC).With occasion, under period in summer cold-room condition, must make coolant distribution arrive shunting stream 10 greater than the freezing cycle device of the design volumetric ratio (VC/VE) of this value design.Otherwise, with occasion, under period in summer cold-room condition, must make the refrigerant utilization give pressure-reducing valve 12 and expand in advance less than the freezing cycle device of the design volumetric ratio (VC/VE) of this value design.Yet, known in shunting, expand under any one situation in advance, with the situation of having carried out optimal design in period in summer under the cold-room condition, promptly be designed to about 4 situation and compare will designing volumetric ratio (VC/VE), COP particularly, sharply descends at the pre-occasion COP ratio that expands significantly than reducing.

On the other hand, under interim greenhouse condition and period in winter greenhouse condition, the density under the actual motion state is respectively about 8～9 than (DE/DC).With occasion, under interim greenhouse condition and period in winter greenhouse condition, must make coolant distribution arrive shunting stream 10 greater than the freezing cycle device of the design volumetric ratio (VC/VE) of these values design.Otherwise, with occasion, under interim greenhouse condition and period in winter greenhouse condition, must make the refrigerant utilization give pressure-reducing valve 12 and expand in advance less than the freezing cycle device of the design volumetric ratio (VC/VE) of these values design.Yet, known in shunting, expand under any one situation in advance, with interim greenhouse condition and period in winter the greenhouse condition each condition under carried out the situation of optimal design, promptly be designed to about 8～9 situation and compare will designing volumetric ratio (VC/VE), COP is than reducing, particularly, sharply descend significantly at the pre-occasion COP ratio that expands.

In other words, because because of different service conditions such as seasons, optimal design volumetric ratio difference is utilized in an axle 9 direct-connected freezing cycle devices at compressing mechanism 1 and expansion mechanism 3, design volumetric ratio (VC/VE) can only determine a value when design.Therefore, such as, design be that best design volumetric ratio (VC/VE) is under about 4 the situation under the cold-room condition in period in summer, the COP ratio is about 130 under period in summer cold-room condition, but under interim greenhouse condition and period in winter greenhouse condition, the COP ratio is about 102～104.

Relative therewith, design is that optimum design volumetric ratio (VC/VE) is about 8～9 occasion under the greenhouse condition in interim greenhouse condition and period in winter, COP ratio under interim greenhouse condition and period in winter greenhouse condition is about 111, but under period in summer cold-room condition and interim cold-room condition, the COP ratio is about 113～114.

Like this, will design volumetric ratio (VC/VE) is designed under interim greenhouse condition and period in winter greenhouse condition the difference in season of COP raising rate to be reduced, even service condition differences such as season also can often be kept high operational efficiency when best.

In other words, in the freezing cycle device of embodiment 6, as can be seen from Figure 15, the occasion that is conceived to expand is in advance compared with the occasion of shunting, the little this point of raising rate of COP, be designed to roughly more consistent than the value of (DE/DC) than the value of (DE/DC) by designing volumetric ratio (VC/VE) for the density under the maximum condition (occasion at Figure 15 is a greenhouse condition in period in winter) in the density under the actual motion state, even make the service condition difference also not give expansion as much as possible, can often keep the operation of the freezing cycle device of high operational efficiency.

In addition, from the outlet refrigerant density (DC) of any one with outdoor heat converter 62 or the indoor heat converter 65 shown in Figure 16 during as evaporimeter, or with in outdoor heat converter 62 or the indoor heat converter 65 any one when the radiator outlet refrigerant density (DE) and density than the dependency relation of (DE/DC), density is than (DE/DC) as can be known, compare with the variation of the outlet refrigerant density (DC) of evaporimeter, more be subjected to the influence of variation of the outlet refrigerant density (DE) of radiator 2, and then, with the roughly proportional relation of outlet refrigerant density (DE) of radiator 2.

So, in the freezing cycle device of present embodiment, be maximum condition by its design volumetric ratio (VC/VE) being designed to than the value of (DE/DC) with density under the actual motion state, promptly the density that becomes under the maximum condition with the outlet refrigerant density (DE) of radiator is roughly more consistent than the value of (DE/DC), just can often keep the operation of the freezing cycle device of high operational efficiency.

In addition, as having illustrated among Figure 15, because in the freezing cycle device that uses as air conditioner, in its scope of application, minimum to the air themperature of blowing as the outdoor heat converter 62 or any one heat exchanger in the indoor heat converter 65 of evaporimeter, and minimum to the air themperature of blowing as the outdoor heat converter 62 or any one heat exchanger in the indoor heat converter 65 of radiator, and situation about under the highest condition of the air themperature that blows out as the heat exchanger of radiator, moving, with more suitable than the situation (the greenhouse condition in period in winter of the occasion of Figure 15) that (DE/DC) moves under for maximum condition in the density under the running status of reality, so, just can often keep the operation of the freezing cycle device of high operational efficiency by being designed to design volumetric ratio (VC/VE) roughly consistent than (DE/DC) in the density under this running status.

In addition, in the freezing cycle device that uses as air conditioner, by design make design volumetric ratio (VC/VE) become value more than or equal to 8 (with the occasion of Figure 15 period in winter the greenhouse condition and the corresponding value of interim greenhouse condition), just can often keep the operation of the freezing cycle device of high operational efficiency.

[embodiment 7]

Freezing cycle device to embodiments of the invention 7 is illustrated below.Figure 17 is the structure chart that the freezing cycle device of embodiments of the invention 7 is shown.In addition, because the structure of the freezing cycle device of present embodiment and embodiment 1 are roughly the same, use prosign and omit its explanation for same functional part.In addition, because the control method of freezing cycle device is also identical with embodiment 1, its explanation is omitted.In addition, about the freezing cycle device of present embodiment, be to be that example describes with the hot water machine.

The freezing cycle device of present embodiment is made of refrigerant circulation circuit A and hot water supply closed circuit B.Refrigerant circulation circuit A have motor etc. drive source 71, carry out evaporimeter 5 of heat exchange or the like by drive source 71 compressor driven structures 72, the auxiliary compressor structure 73 that will recompress, radiator 2, expansion mechanism 74 and with outer gas by fan air-supply from the refrigerant that compressing mechanism 72 is discharged.In addition, hot water supply closed circuit B is the same with the structure of embodiment 1, has feed pump 6, radiator 2 and hot water supply jar 7 or the like.In addition, auxiliary compressor structure 73 be by axle 75 be connected with the expansion mechanism 74 that pressure can be transformed to power, by the power-actuated structure of the recovery of expansion mechanism 74.

Below, with the volume of cylinder of auxiliary compressor structure 73 as VCs, with the volume of cylinder of expansion mechanism 74 as VE, with the outlet refrigerant density of compressing mechanism 72 as DCs (the inflow medium density of auxiliary compressor structure 73), the action during to the operation of the freezing cycle device that constitutes as mentioned above describes as DE (the inflow medium density of expansion mechanism 3) with the outlet refrigerant density of radiator 2.At first, than (DE/DCs), the roughly equal occasion of the design volumetric ratio (VC/s/VE) that prefers during with design is illustrated to the density under the running status of reality.

Compressing mechanism 72 is compressed to pressure (intermediate pressure) above critical pressure with refrigerant always.This refrigerant that is compressed is compressed to high side pressure by auxiliary compressor structure 73 again.So, become the refrigerant of high-temperature high-pressure state, when flowing through radiator 2, water-cooled is cooled off.Thereafter, refrigerant is become by expansion mechanism 74 decompression and is the gas-liquid two-phase state.The pressure of refrigerant can be transformed to power in expansion mechanism 74, and this transmission of power is to axle 75.By being delivered to this power drive auxiliary compressor structure 73 of 75.Refrigerant through expansion mechanism 74 decompressions flow into evaporimeter 5, and in this evaporimeter 5, refrigerant becomes gas-liquid two-phase or gaseous state by the air cooling., become the refrigerant of gas-liquid two-phase or gaseous state, be drawn into compressing mechanism 72 once more thereafter.

Below to being illustrated in the situation more different with the design volumetric ratio (VCs/VE) that when designing, prefers of the density under the actual motion state than (DE/DCs).At first, to being illustrated greater than the action of the situation of the design volumetric ratio (VCs/VE) that when designing, prefers than (DE/DCs) in the density under the actual motion state.

In this case, because density is than certain restriction, for the refrigerant density (DE) of the outlet (inlet of expansion mechanism 74) that makes radiator 2 diminishes, freeze cycle is carried out balance under the state that high side pressure is reduced.But, being lower than under the desired pressure status at high side pressure, discharge temperature reduces and the heating efficiency of freezing cycle device is reduced, and the efficient of freezing cycle device is reduced.Therefore, if flow divider 11 is not a full-shut position,, make the refrigerant of original inflow shunting stream 10 flow into expansion mechanism 74 to closing direction operation flow divider 11.Perhaps,, give pressure-reducing valve 12, make the refrigerant decompression that flows into expansion mechanism 74, refrigerant density is reduced to the closing direction operation if flow divider 11 is full-shut positions.By these actions, high side pressure is risen, because can adjust to desirable pressure, so can carry out high efficiency operation.

Otherwise the action of the occasion of the design volumetric ratio (VCs/VE) that the density under the actual motion state time is preferred less than design than (DE/DCs) is illustrated.

In this case, because density is than certain restriction, for the refrigerant density (DE) of the outlet (inlet of expansion mechanism 74) that makes radiator 2 becomes big, freeze cycle is carried out balance under the state that high side pressure is risen.But under the state that high side pressure rises than desired pressure, the operational efficiency of freezing cycle device reduces.Therefore, not full-gear if give pressure-reducing valve 12, give pressure-reducing valve 12 to opening direction operation, the refrigerant that flows into expansion mechanism 74 is not reduced pressure and refrigerant density is risen.Perhaps, are full-gears if give pressure-reducing valve 12, to opening direction operation flow divider 11, make the part of the refrigerant that flows into expansion mechanism 74 flow into shunting stream 10.By these actions, high side pressure is reduced, because can adjust to desirable pressure, so can carry out high efficiency operation.

As mentioned above, in the freezing cycle device of embodiment 7, because density is than certain restriction, be difficult to keep in the freezing cycle device of decompressor of optimal high side pressure in use, no matter under the situation of the design volumetric ratio (VCs/VE) that prefers during less than or greater than design than (DE/DCs) of the density under the running status of reality, can be by to flow divider 11 with give the operation of the aperture of pressure-reducing valve 12, adjust to desirable high side pressure, under the situation that operational efficiency and ability are reduced, provide the freezing cycle device that can move.

In addition, the discharge temperature of the freeze cycle of present embodiment is the outlet temperature of auxiliary compressor structure 73, and the degree of superheat of freeze cycle is evaporating temperature poor of the inlet temperature of compressing mechanism 72 and evaporimeter 5.

[embodiment 8]

Freezing cycle device to embodiments of the invention 8 is illustrated below.Because the structure of the freezing cycle device of present embodiment and control method thereof are identical with embodiment 7, omit explanation for same structure and action etc.

The structure of present embodiment be characterised in that with the volume of cylinder of auxiliary compressor structure 73 as VCs, with the volume of cylinder of expansion mechanism 74 as VE, with the outlet refrigerant density of compressing mechanism 72 as DCs, with the outlet refrigerant density of radiator 2 during as DE, make design volumetric ratio (VCs/VE) in design and the density that becomes than (DE/DCs) in the density under the actual motion state under the maximum condition roughly more consistent than the value of (DE/DCs).In addition, in specific words, be to design and make and become density under the condition of maximum than the roughly consistent this point of value of (DE/DCs) with the outlet refrigerant density (DE) of radiator 2.

In addition, in the freezing cycle device that uses as hot water machine, design volumetric ratio (VCs/VE), with in the scope of application of hot water machine, the density when moving under the condition that environment temperature (outer temperature degree) water temperature (going into coolant-temperature gage) minimum and inflow radiator 2 is minimum and hot water temperature's (hot water effluent's temperature) that flow out from radiator 2 is the highest of evaporimeter 5 is roughly more consistent than (DE/DCs) to be the feature of project organization.

In addition, in specific words, in the freezing cycle device that uses as hot water machine, the value of design volumetric ratio (VCs/VE) is features of project organization more than or equal to 3.5.

But, in the freezing cycle device of present embodiment, as illustrated in embodiment 1, when the density under the actual motion state than (DE/DCs) during less than the design volumetric ratio (VCs/VE) of when design decision, by to open direction operation flow divider 11 or in density than (DE/DCs) during greater than design volumetric ratio (VCs/VE), by giving pressure-reducing valve 12 to opening the direction operation, make density more consistent with design volumetric ratio (VCs/VE) than (DE/DCs), can adjust to desired high side pressure.Yet, increase or utilize and give pressure-reducing valve 12 when the pressure differential of pre-expansion is increased at the coolant quantity that flows through shunting stream 10, owing to should reduce by recuperable power, the raising rate of operational efficiency (COP) is descended.So it is very important how the design volumetric ratio being designed to optimum value.

Therefore, utilize accompanying drawing 18 and 19 optimal design volumetric ratios to be described in detail below for the occasion that the freezing cycle device of present embodiment is used as hot water machine.

Figure 18 illustrates the density ratio of embodiments of the invention 8 and the correlation diagram of COP ratio, and Figure 19 illustrates the density ratio of embodiments of the invention 8 and the correlation diagram of refrigerant density.

In Figure 18, outer temperature degree is to set according to the high order of temperature: period in summer, interim, period in winter and low temperature period.Going into coolant-temperature gage is the minimum temperature that prefers according to each outer temperature degree condition, and hot water effluent's temperature is the normal temperature that prefers according to each outer temperature degree condition.In addition, the COP ratio is outside each under temperature degree condition, is 100 with the COP of the freezing cycle device that do not use decompressor.Below, with period in summer condition be that example describes.

In period in summer condition, the density under the actual motion state is about 4.1 than (DE/DCs).With occasion, under period in summer condition, must make coolant distribution arrive shunting stream 10 greater than the freezing cycle device of the design volumetric ratio (VCs/VE) of this value design.Otherwise, with occasion, under period in summer condition, must make the refrigerant utilization give pressure-reducing valve 12 and expand in advance less than the freezing cycle device of the design volumetric ratio (VCs/VE) of this value design.Yet, known in shunting, expand under any one situation in advance, with when having carried out optimal design under the condition period in summer, promptly be designed to about 4.1 occasion and compare will designing volumetric ratio (VCs/VE), COP particularly, sharply descends at the pre-occasion COP ratio that expands significantly than reducing.

On the other hand, under period condition and the low temperature condition in period, the density under the actual motion state is respectively about 4.3 and about 4.5 than (DE/DCs) in the winter time.In the occasion of the freezing cycle device that designs with design volumetric ratio (VCs/VE), under period condition and the low temperature condition in period, must make coolant distribution arrive shunting stream 10 in the winter time greater than these values.Otherwise the occasion at the freezing cycle device that designs with the design volumetric ratio (VCs/VE) less than these values under period condition and the low temperature condition in period, must make the refrigerant utilization give pressure-reducing valve 12 and expand in advance in the winter time.Yet, known in shunting, expand under any one situation in advance, situation with optimal design under each condition of condition and the low temperature condition in period of period in the winter time, promptly set and to be about about 4.3 and about 4.5 occasion and to compare will designing volumetric ratio (VCs/VE), COP is than reducing, particularly, sharply descend significantly at the pre-occasion COP ratio that expands.

In other words, because because of different service conditions such as seasons, optimal design volumetric ratio difference is utilized in an axle 75 direct-connected freezing cycle devices at auxiliary compressor structure 73 and expansion mechanism 74, and design volumetric ratio (VCs/VE) can only determine a value when design.Therefore, such as, be designed under period in summer condition for best design volumetric ratio (VCs/VE) under about 4.1 the situation, the COP ratio is about 112 under period in summer condition, but the COP ratio is about 105 in season under other condition.

Relative therewith, design be that best design volumetric ratio (VCs/VE) is that the COP ratio is about 110 under low temperature condition in period under about 4.5 the situation under the low temperature condition in period, and the COP ratio is about 110～111 in season under other condition.Perhaps, design under the condition in period in the winter time for the situation of best design volumetric ratio (VCs/VE) too.

Like this, will design volumetric ratio (VCs/VE) is designed in the winter time under period condition and the low temperature condition in period the difference in season of COP raising rate to be reduced, even service condition differences such as season also can often be kept high operational efficiency when best.

In other words, in the freezing cycle device of embodiment 8, as can be seen from Figure 18, the occasion that is conceived to expand is in advance compared with the occasion of shunting, the little this point of raising rate of COP, be designed to roughly more consistent than the value of (DE/DCs) than the value of (DE/DCs) by designing volumetric ratio (VCs/VE) for the density under the maximum condition (occasion at Figure 18 is a low temperature condition in period) in the density under the actual motion state, even make the service condition difference also not give expansion possibly, can often keep the operation of the freezing cycle device of high operational efficiency.

In addition, outlet refrigerant density (DCs) from compressing mechanism shown in Figure 19 71, or the outlet refrigerant density (DE) of radiator 2 and density are than the dependency relation of (DE/DCs), density is compared with the variation of the outlet refrigerant density (DCs) of compressing mechanism 71 than (DE/DCs) as can be known, more be subjected to the influence of variation of the outlet refrigerant density of radiator 2, and then, with the roughly proportional relation of outlet refrigerant density (DE) of radiator 2.

So, be designed to density under the actual motion state by design volumetric ratio (VCs/VE) and be maximum condition than the value of (DE/DCs) with the freezing cycle device of present embodiment, promptly the density that becomes under the maximum condition with the outlet refrigerant density (DE) of radiator 2 is roughly more consistent than the value of (DE/DCs), just can often keep the operation of the freezing cycle device of high operational efficiency.

In addition, as having illustrated among Figure 18, because in the freezing cycle device that uses as hot water machine, in its scope of application, environment temperature (outer temperature degree) at evaporimeter 5 is minimum, and the water temperature of inflow radiator 2 (going into coolant-temperature gage) is minimum, and the situation of moving under the highest condition of hot water temperature's (hot water effluent's temperature) of flowing out from radiator 2 (the low temperature condition in period of the occasion of Figure 18) is more suitable than the situation that (DE/DC) moves under the condition that becomes maximum with the actual motion state density down of freezing cycle device, so, just can often keep the operation of the freezing cycle device of high operational efficiency by being designed to design volumetric ratio (VCs/VE) roughly consistent than (DE/DCs) in the density under this running status.

In addition, have in the employed freezing cycle device of hot water machine of auxiliary compressor structure 73 in conduct, make design volumetric ratio (VCs/VE) become value more than or equal to 4 (with the condition in period in summer of the occasion of Figure 18, interim condition, period in winter condition and the whole basically corresponding values of low temperature condition in period) by design, just can often keep the operation of the freezing cycle device of high operational efficiency.

In addition,, as shown in figure 18, compare, owing to, just can often keep the operation of the freezing cycle device of high operational efficiency because of the variation of the volumetric ratio of different occasion such as the service condition in season etc. diminishes with Figure 12 of embodiment 5 according to the formation of present embodiment.

In other words, in freezing cycle device with auxiliary compressor structure 73, for the variation that makes the volumetric ratio under the running status of reality little, even the design volumetric ratio that prefers during with design is different, by an aperture operation to flow divider 11, also can adjust becomes desired high side pressure, can move under the situation of operational efficiency that does not make freezing cycle device and capacity reduction.That is, also can not give pressure-reducing valve 12 and only constitute with flow divider 11, and, even under situation about only constituting with flow divider 11, the bigger value of the preferred design volumetric ratio of setting when adopting than design.

Freezing cycle device of the present invention and control method thereof are applicable to hot water supply apparatus (water heater), domestic air conditioner, commercial air conditioner, car air-conditioner machine (air conditioner for automobile machine) etc.So, can in the very wide range of operation of amplitude, obtain high power recovery effect, the freezing cycle device with the good efficiencies operation can be provided.Particularly, it is big to become in the freezing cycle device of supercriticality effect in the high-pressure side of the freeze cycle of using carbon dioxide.

Claims

1. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that comprising:

Make the shunting stream of above-mentioned expansion mechanism shunting;

The flow divider that on above-mentioned shunting stream, is provided with;

The pre-pressure-reducing valve that the refrigerant that flows into above-mentioned expansion mechanism is reduced pressure; And

Control the operator of above-mentioned flow divider and above-mentioned pre-pressure-reducing valve based on discharge temperature or the degree of superheat.

2. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that comprising:

Make the shunting stream of above-mentioned expansion mechanism shunting;

The flow divider that on above-mentioned shunting stream, is provided with; And

Control the operator of the rotating speed of above-mentioned flow divider and above-mentioned drive source based on discharge temperature or the degree of superheat.

3. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that the refrigerant that flows out from above-mentioned expansion mechanism is heated is characterized in that comprising:

Make the shunting stream of above-mentioned expansion mechanism shunting;

The flow divider that on above-mentioned shunting stream, is provided with;

Fan to above-mentioned evaporimeter air-supply; And

Control the operator of the rotating speed of above-mentioned flow divider and said fans based on discharge temperature or the degree of superheat.

4. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that:

The volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is roughly consistent with value maximum among the ratio of each outlet refrigerant density of above-mentioned radiator and above-mentioned evaporimeter under the running status of freezing cycle device.

5. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that:

The volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is roughly consistent for ratio of each outlet refrigerant density of above-mentioned radiator under the running status of maximum freezing cycle device and above-mentioned evaporimeter with refrigerant density in the outlet of above-mentioned radiator.

6. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that:

The volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is with minimum in the environment temperature of above-mentioned evaporimeter and to flow into ratio of each outlet refrigerant density of above-mentioned radiator under the running status of the minimum and freezing cycle device that hot water temperature that flow out from above-mentioned radiator is the highest of the water temperature of above-mentioned radiator and above-mentioned evaporimeter roughly consistent.

7. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out from the refrigerant that the above-mentioned compressor structure is discharged, use carbon dioxide to use, it is characterized in that as refrigerant and as hot water machine:

The volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is more than or equal to 10.

8. freezing cycle device, have when compressing mechanism, expansion mechanism and drive source connected by axle, radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out is characterized in that:

The volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is roughly consistent with ratio of each outlet refrigerant density of above-mentioned radiator under the running status of and to the air themperature of above-mentioned radiator air-supply minimum and freezing cycle device that air themperature that from above-mentioned radiator blow out the highest minimum to the air themperature of above-mentioned evaporimeter air-supply and above-mentioned evaporimeter.

9. freezing cycle device, it is characterized in that have compressing mechanism, expansion mechanism and drive source connected by axle in, radiator that will be cooled off and the evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out from the refrigerant that the above-mentioned compressor structure is discharged, use carbon dioxide to use, it is characterized in that as refrigerant and as air conditioner:

The volumetric ratio that makes above-mentioned compressor structure and above-mentioned expansion mechanism is more than or equal to 8.

10. the control method of a freezing cycle device, have compressing mechanism, expansion mechanism and drive source connected by an axle in, the radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged; The evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out; Make the shunting stream of above-mentioned expansion mechanism shunting; The flow divider that on above-mentioned shunting stream, is provided with; And in the freezing cycle device of the pre-pressure-reducing valve that the refrigerant that flows into above-mentioned expansion mechanism is reduced pressure, it is characterized in that:

Control above-mentioned flow divider and above-mentioned pre-pressure-reducing valve based on the discharge temperature or the degree of superheat.

11. the control method of a freezing cycle device, have compressing mechanism, expansion mechanism and drive source connected by axle in, the radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged; The evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out; Make the shunting stream of above-mentioned expansion mechanism shunting; In the freezing cycle device of the flow divider that on above-mentioned shunting stream, is provided with, it is characterized in that:

Control the rotating speed of above-mentioned flow divider and above-mentioned drive source based on discharge temperature or the degree of superheat.

12. the control method of a freezing cycle device, have compressing mechanism, expansion mechanism and drive source connected by axle in, the radiator that will be cooled off from the refrigerant that the above-mentioned compressor structure is discharged; The evaporimeter that will heat from the refrigerant that above-mentioned expansion mechanism flows out; Make the shunting stream of above-mentioned expansion mechanism shunting; The flow divider that on above-mentioned shunting stream, is provided with; And in the freezing cycle device of the fan that above-mentioned evaporimeter is blown, it is characterized in that:

Control the rotating speed of above-mentioned flow divider and said fans based on discharge temperature or the degree of superheat.

13. a freezing cycle device has when the auxiliary compressor structure is connected by an axle with expansion mechanism the compressing mechanism of compression refrigerant; The auxiliary compressor structure that will recompress from the refrigerant that the above-mentioned compressor structure is discharged; Cooling is characterized in that comprising from the radiator and the evaporimeter of heating from the refrigerant of above-mentioned expansion mechanism outflow of the refrigerant of above-mentioned auxiliary compressor structure discharge:

Make the shunting stream of above-mentioned expansion mechanism shunting;

The flow divider that on above-mentioned shunting stream, is provided with.

14. freezing cycle device as claimed in claim 13 is characterized in that also comprising:

The pre-pressure-reducing valve that the refrigerant that flows into above-mentioned expansion mechanism is reduced pressure.

15. freezing cycle device as claimed in claim 14 is characterized in that also comprising:

The operator of controlling above-mentioned flow divider and above-mentioned pre-pressure-reducing valve based on the discharge temperature or the degree of superheat of this freezing cycle device.

16. freezing cycle device as claimed in claim 13 is characterized in that:

The volumetric ratio that makes above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is roughly consistent with value maximum among the ratio of each outlet refrigerant density of above-mentioned radiator under the running status of freezing cycle device and above-mentioned compressor structure.

17. freezing cycle device as claimed in claim 13 is characterized in that:

The volumetric ratio that makes above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is roughly consistent for ratio of each outlet refrigerant density of above-mentioned radiator under the running status of maximum freezing cycle device and above-mentioned compressor structure with refrigerant density in the outlet of above-mentioned radiator.

18. freezing cycle device as claimed in claim 13 is characterized in that:

The volumetric ratio that makes above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is with minimum in the environment temperature of above-mentioned evaporimeter and to flow into ratio of each outlet refrigerant density of above-mentioned radiator under the running status of the minimum and freezing cycle device that hot water temperature that flow out from above-mentioned radiator is the highest of the water temperature of above-mentioned radiator and above-mentioned evaporimeter roughly consistent.

19. freezing cycle device as claimed in claim 13 is characterized in that:

In the freezing cycle device that uses as hot water machine that uses carbon dioxide as refrigerant, the volumetric ratio of setting above-mentioned auxiliary compressor structure and above-mentioned expansion mechanism is more than or equal to 4.