CN101548066A

CN101548066A - Freezing apparatus, and expander

Info

Publication number: CN101548066A
Application number: CNA2007800448285A
Authority: CN
Inventors: 鉾谷克己; 冈本昌和; 熊仓英二; 冈本哲也
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2006-12-08
Filing date: 2007-12-07
Publication date: 2009-09-30
Anticipated expiration: 2027-12-07
Also published as: EP2090746A1; JP4946840B2; EP2090746B1; EP2090746A4; WO2008072575A1; JP2008163938A; ES2721233T3; CN101548066B

Abstract

Provided is a freezing apparatus, which is constituted to make the inlet quantity of a coolant of an expansion mechanism variable while recovering the energy of a high-pressure coolant as a power to the maximum by the expansion mechanism. The expansion mechanism (50) is equipped with two rotary mechanism units (70 and 80) having displacements made different from each other. These rotary mechanism units are connected in series, and the rotary mechanism unit of the smaller displacement has two inlet ports (55 and 56) formed in its cylinder (71). Inlet pipes (24 and 27), as connected to the inlet ports (55 and 56), are equipped with a front throttle valve (60) and a switch valve (61). A bypass pipe (65) for bypassing the expansion mechanism (50) is equipped with a bypass valve (66). These valves (60, 61 and 66) are controlled to attain a balance between the coolant circulation rate of the expansion mechanism (50) and the coolant circulation rate of a compression mechanism (40).

Description

Refrigerating plant and decompressor

Technical field

The present invention relates to a kind of refrigerating plant that comprises expansion mechanism, particularly relates to a kind of displacement type expander structure that is produced power by the expansion of fluid.

Background technique

Up to now, disclose, in the refrigerant circuit that carries out freeze cycle, known to compressing mechanism is provided with the refrigerating plant of promising expansion mechanism from refrigerant-recovery power oneself is as patent documentation 1,2.The power that is reclaimed from high-pressure refrigerant by this expansion mechanism is passed to the compressing mechanism of binding by live axle, is used in and drives this compressing mechanism.

Because refrigerant circuit is a loop, the unit time by compressing mechanism circulating mass of refrigerant (being equivalent to mass flow rate, as follows) and the circulating mass of refrigerant by expansion mechanism must be consistent often.Yet,, when under departing from the condition of this design method, turning round, will produce too much or very few situation between the circulating load of compressing mechanism and the circulating load of expansion mechanism if design according to certain design method point (for example specified heating).Specifically, for example, if with the consistent condition design of the circulating load of described compressing mechanism when specified the heating and expansion mechanism, then when the high specified refrigeration of the suction pressure of compressing mechanism, the inlet capacity of best expansion mechanism is big during than specified heating, so just produced the overexpansion of lack of refrigerant.

Therefore, in the described

patent documentation

1,2, by injecting high-pressure refrigerant when the expansion stroke of expansion mechanism or the path of this expansion mechanism of bypass being set and regulating bypass volume of the cooling medium, the compressing mechanism side of balanced system refrigerant circuit and the refrigerant flow of expansion mechanism side by control valve.

Patent documentation 1: Japanese publication communique spy opens the 2004-150748 communique

Patent documentation 2: Japanese publication communique spy opens the 2001-116371 communique

-invent technical problem to be solved-

Yet, as mentioned above, in expansion stroke, expansion mechanism is injected high-pressure refrigerant or makes the refrigerant bypass expansion mechanism, though balance the circulating mass of refrigerant of compressing mechanism and expansion mechanism, but, originally being that the energy that can reclaim the high-pressure refrigerant of power to greatest extent but can only reclaim a part by expansion mechanism, is not desirable formation from the viewpoint of reuse efficiency.

Summary of the invention

The present invention, each point and inventing in view of the above, its purpose is: the energy that obtains reclaiming high-pressure refrigerant to greatest extent in decompressor constitutes the refrigerating plant of the intake of the refrigeration agent that can change this expansion mechanism simultaneously as power.

-be the technical solution problem method-

In order to reach described purpose, in refrigerating plant involved in the present invention 1, described expansion mechanism 50,100,200 is provided with at the main inlet hole 55,103,201 that is interconnected with described fluid chamber 72,82,230 at the very start of induction stroke and the auxiliary inlet hole 56,104,113,114,203,204,205 that is interconnected with fluid chamber 72,82,230 again after being interconnected with this main inlet hole 55,103,201.

Specifically, the invention of first aspect, be to have first parts 71,81,102,112,210 and second parts 75,85,116,124,220 of doing relative eccentric motion to comprise, the refrigerating plant that makes the fluid expansion in the fluid chamber 72,82,230 that is formed between these two parts and be converted into the expansion mechanism 50,100,200 of power is an object.

And, in described expansion mechanism 50,100,200, be provided with in induction stroke and make main inlet hole 55,103,201 that described fluid chamber 72,82,230 and inlet passage 24 be interconnected and the auxiliary inlet hole 56,104,113,114,203,204,205 that after being interconnected, described fluid chamber 72,82,230 and inlet passage 27 is interconnected at the very start with this main inlet hole 55,103,201.

According to this formation, in the induction stroke of described expansion mechanism 50,100,200, can in fluid chamber 72,82,230, import fluid in order from a plurality of inlet holes 55,56,103,104,113,114,201,203,204,205, also just can be adjusted in the volume of fluid circulated in this fluid chamber 72,82,230.

Therefore, even if variation has taken place in operating condition, also can the described expansion mechanism 50,100,200 of balance and compressing mechanism 40 between circular flow, and, because all fluids can be imported fluid chamber 72,82,230 in induction stroke, so can in described expansion mechanism 50,100,200, carry out effective power recovery.

In described formation, separated described fluid chamber 72,82,230 in the described expansion mechanism 50,100,200 and made and in this fluid chamber 72,82,230, can carry out induction stroke and discharge stroke (invention of second aspect) independently at least.As multistage or rotary expansion mechanism, so long as independently carry out the formation of induction stroke and discharge stroke, the high-pressure liquid that just can prevent to import in induction stroke in the fluid chamber does not have to expand in expansion mechanism 50,100,200 and directly flow out outside.Therefore, so long as the above such formation just can be expanded fluid in described expansion mechanism 50,100,200 fully.

Also having, preferably be set to described auxiliary inlet hole 56,104,113,114,203,204,205 with respect to described fluid chamber 72,82,230, is the form (invention of the third aspect) from its below towards described fluid chamber 72,82,230 openings.Like this, by described auxiliary inlet hole 56,104,113,114,203,204,205 being set to the form from its below towards its opening with respect to described fluid chamber 72,82,230, not when this auxiliary inlet hole 56,104,113,114,203,204,205 imports fluids, be communicated in the inlet passage 27 of this auxiliary inlet hole 56,104,113,114,203,204,205 just storage and stay refrigerator oil in the expansion mechanism 50,100.Like this, just can prevent that this inlet passage 27 from becoming storage and staying the dead angle that stockpiles fluid (dead volume) in the described fluid chamber 72,82,230, also just can in this fluid chamber 72,82,230, fluid be expanded effectively.

Have again, the inlet passage 27 that is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205 is provided with switch valve 61, is provided with the check valve 95 (invention of fourth aspect) that only allows fluid to flow to auxiliary inlet hole 56,104,113,114,203,204,205 from this switch valve 61 in described switch valve 61 downstream sides.

By such check valve 95 that is provided with, because can more positively prevent the fluid in the incoming fluid chamber 72,82,230 in inlet passage 27, just can reduce the invalid volume in the expansion mechanism 50,100,200 really, in this expansion mechanism 50,100,200, fluid is more effectively expanded.

Also have, preferably comprise bypass circulation 65, and bypass flow regulator 66 (invention aspect the 5th) is set on this bypass circulation 65 described expansion mechanism 50,100,200 bypass.Like this, by bypass circulation 65 and bypass flow regulator 66 are set, just may carry out fine adjustment to the volume of fluid circulated of described expansion mechanism 50,100,200, simultaneously when just starting back and defrosting running etc., even if compare with common running under the situation that volume of fluid circulated increases considerably, the pressure that also can absorb these increase part repression of swelling mechanism 50,100,200 suction sides rises.

And, in the formation that comprises above-described bypass flow regulator 66, comprise based on being imported into hydrodynamic pressure in the described expansion mechanism 50,100,200 and control the bypass flow controller 94 (invention of the 6th aspect) of described bypass flow regulator 66.Thus, can regulate the feasible pressure of described expansion mechanism 50,100,200 that imports of bypass amount of this expansion mechanism 50,100,200 near desired value.

Also have, preferably the inlet passage 24 that is interconnected with described main inlet hole 55,103,201 is provided with flow control valve 60 (invention of the 7th aspect).Like this, can regulate the volume of fluid circulated that imports fluid chamber 72,82,230 from main inlet hole 55,103,201 by flow control valve 60, so can make the fluid of optimal circulating load flow into expansion mechanism 50,100,200 corresponding to the volume of fluid circulated of compressing mechanism 40.

Particularly, described flow control valve 60 is arranged on the downstream side (invention of eight aspect) of the branch location of the inlet passage 27 that is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205.By like this, do not change from the circulating load of the fluid of auxiliary inlet hole importing, only adjusting just becomes possibility from the circulating load of the fluid of described main inlet hole 55,103,201 importings.

Also have, comprise based on being imported into hydrodynamic pressure in the described expansion mechanism 50,100,200 and control the flow dontroller 92 (invention of the 9th aspect) of described flow control valve 60.Thus, can regulate the volume of fluid circulated of this expansion mechanism 50,100,200 and make described 50,100,200 the pressure of importing near equaling desired value.

Also have, comprise based on the switch valve control device 93 (invention aspect the tenth) that is imported into the switch valve 61 of hydrodynamic pressure control setting on the inlet passage 27 that is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205 in the described expansion mechanism 50,100,200.By with these switch valve control device 93 control switch valves 61, just can control the flow that imports fluid chamber 72,82,230.That is to say, by controlling described switch valve 61 based on the hydrodynamic pressure that imports described expansion mechanism 50,100,200, just can reach the most suitable pressure to expansion mechanism 50,100,200, just the flow control of suitable circulating load just can expand fluid in this expansion mechanism 50,100,200 effectively.

Specifically, be provided with a plurality of described auxiliary inlet holes 56,104,113,114,203,204,205, with each auxiliary inlet hole 56,104,113,114,203,204,205 inlet passages that are interconnected 27 are provided with switch valve 61, under the big situation of described pressure ratio desired value, described switch valve control device 93 carries out the control of opening of described switch valve 61 in order, makes described auxiliary inlet hole 56,104,113,114,203,204,205 make described fluid chamber 72 in order, 82,230 with inlet passage 27 be interconnected (the tenth on the one hand invention).

Thus, under the hydrodynamic pressure that imports described expansion mechanism 50,100,200 situation bigger than desired value, that is to say be necessary under the situation of this expansion mechanism 50,100,200 increase circulating loads, just can increase the circulating load that imports fluid chamber 72,82,230 interimly by opening described switch valve 61 in order.Therefore, even if necessary circulating load has big variation in described fluid chamber 72,82,230, the closing control by described switch valve 61 is importing fluid in this fluid chamber 72,82,230 promptly just.

On the other hand, under the little situation of described pressure ratio desired value, described switch valve control device 93 is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205 from last, carries out the closing control (invention of the 12 aspect) of described switch valve 61 in order.

Thus, under the hydrodynamic pressure that imports described expansion mechanism 50,100,200 situation littler than desired value, the circulating load that is to say this expansion mechanism 50,100,200 is many, under the situation that is necessary to reduce, just can reduce the circulating load that imports fluid chamber 72,82,230 by closing described switch valve 61 in order interimly.Therefore, even if necessary circulating load has big variation in described fluid chamber 72,82,230, opening control and just can promptly reduce and flow to the interior fluid flow of this fluid chamber 72,82,230 by described switch valve 61.

Also have, comprise in addition be arranged on in the bypass circulation 65 of described expansion mechanism 50,100 bypass in order to control bypass flow regulator 66 bypass flow controller 94, the described bypass flow regulator 66 of described bypass flow controller 94 controls, make described pressure reach desired value, reach under the situation of aperture of defined the opening and closing (invention of the 13 aspect) of the described switch valve control device 93 described switch valves of control (61) at described bypass flow regulator 66.At this, under the state of opening switch valve 61, the aperture of defined, mean be can not be again than opening big abundant big aperture more than this, and under the state of off switch valve 61, the aperture of defined then means the state that aperture is almost nil.

By doing like this, the volume of fluid circulated that just can fine adjustment imports the fluid chamber 72,82,230 of expansion mechanism 50,100,200 by the bypass flow regulator on the bypass circulation 65 66, under situation about can't regulate, can control the circulating load that described switch valve 61 increases and decreases described fluid chamber 72,82,230 rapidly and positively simultaneously by switch by this bypass flow regulator 66.Thus, just can be rapidly and positively regulate the circulating load that fluid flow that flow make to flow into described fluid chamber 72,82,230 is best suited for.

Have again, also comprise the flow dontroller 92 that is used for the flow control valve 60 of control setting on the inlet passage 24 that is interconnected with described main inlet hole 55,103,201, even if described bypass flow regulator 66 and switch valve 61 are in when described pressure still is lower than the situation of desired value under the full closing state, described flow dontroller 92 is controlled described flow control valve 60, is carried out the Flow-rate adjustment (invention of the 14 aspect) of described expansion mechanism 50,100,200 by described flow control valve 60.

That is to say, under the situation of the volume of fluid circulated that reduces described expansion mechanism 50,100,200, reduce the volume of fluid circulated that imports from auxiliary inlet hole 56,104,113,114,203,204,205 by closing described bypass flow regulator 66 and switch valve 61, only import fluid to fluid chamber 72,82,230 from main inlet hole 55,103,201, even if the circulating load of fluid still is under the too much situation, to regulate by flow control valve 60 more like this.Thus, can be really and promptly reduce the fluid import volume that flows to described fluid chamber 72,82,230.

Also have, described expansion mechanism 50,100, have a plurality of rotary mechanism part 70,80,101,111,121 that are connected in series by work discharge capacity order from small to large, described main inlet hole 55,103 and auxiliary inlet hole 56,104,113,114 are arranged on than in the portion of previous stage sideway swivel mechanism 70,101,111 of final step rotary mechanism part 80,121 (invention of the 15 aspect).Like this, by multi-stage rotary expansion mechanism 50,100, just can prevent that high-pressure liquid from passing from the suction side to the ejection side, expands fluid effectively in this expansion mechanism 50,100.

Particularly, described expansion mechanism 50 has two

rotary mechanism part

70,80 of series connection, is provided with described main inlet hole 55 and auxiliary inlet hole 56 (invention aspect the 16) in the little previous stage rotary mechanism part 70 of work discharge capacity.

By such 2 stage rotary expansion mechanism, just can prevent passing of fluid really by simple constituting, reduced manufacture cost.

Also have, as mentioned above, in the formation of a plurality of rotary mechanism part 70,80,101,111,121 series connection, described auxiliary inlet hole 56,104,113,114 is arranged on based on desirable work discharge capacity and adds in the angular orientation of trying to achieve from geometry on the angular orientation of correction value of defined (invention aspect the 17).

Thus, from auxiliary inlet hole 56,104,113,114 when fluid chamber 72,230 flows into refrigeration agents, consider because the influx that the pressure loss reduces, this part influx, just can increase influx by enlarging the angular orientation of setting this auxiliary inlet hole 56,104,113,114, make the refrigeration agent of necessary influx flow into described fluid chamber 72,230.Therefore, can make necessary volume of the cooling medium flow into expansion mechanism 50,100 really.

Particularly in above-described formation, necessary work discharge capacity (invention of the tenth eight aspect) when the work discharge capacity of described hope is cooling operation.

By doing like this, with heat the pressure that running compares low voltage side and uprise, even if in expansion mechanism 50,100, need in the cooling operation of more refrigerant flow, the pressure loss when the consideration refrigeration agent incoming fluid chamber 72,230 can flow into necessary refrigerant flow in this fluid chamber 72,230.Therefore, the lack of refrigerant of described expansion mechanism 50,100 in the time of just can preventing cooling operation and produce overexpansion.

Also have, described expansion mechanism 200, have to constitute and be included in a pair of scroll element 210,220 that is formed with Vorticose tooth on the end plate, be meshing with each other by the tooth 211,221 that makes this two scroll element 210,220 and constitute the vortex mechanism of at least one pair of fluid chamber 231,232, on the position that in the induction stroke of described vortex mechanism, is interconnected, be provided with described main inlet hole 201 and auxiliary inlet hole 203,204,205 (invention of the 19 aspect) with described fluid chamber 231,232.

By using such scroll expansion machine structure, need not lean on the such use multistage of rotary expansion mechanism just can prevent passing of high-pressure liquid.

Also have, in above formation, the refrigeration agent that preferably uses carbon dioxide to make carries out overcritical freeze cycle (invention of the 20 aspect) as described fluid.Thus, can constitute the refrigerant circuit that is fit to environment.

The invention of the 20 one side, be to have first parts 71,81,102,112,210 and second parts 75,85,116,124,220 of doing relative eccentric motion, fluid in the fluid chamber 72,82,230 that is formed between these two parts expanded and the decompressor that is converted into the expansion mechanism 50,100,200 of power is an object to comprise.

And, in described expansion mechanism 50,100,200, be provided with induction stroke make main inlet hole 55,103,201 that described fluid chamber 72,82,230 and inlet passage 24 be interconnected at the very start and after being interconnected with this main inlet hole 55,103,201 again with the auxiliary inlet hole 56,104,113,114,203,204,205 that described fluid chamber 72,82,230 and inlet passage 27 are interconnected.Thus, just can constitute the decompressor that can access with the invention same function of first aspect.

The effect of-invention-

In the refrigerating plant involved in the present invention, on expansion mechanism 50,100,200, be provided with the main inlet hole 55,103,201 that is interconnected with fluid chamber 72,82,230 at the very start in induction stroke and be interconnected with auxiliary inlet hole 56,104,113,114,203,204,205 more thereafter because be, so just can control flows to the fluid flow of described fluid chamber 72,82,230, even if big variation takes place operating condition, also can make the volume of fluid circulated of described expansion mechanism 50,100,200 keep the most suitable.Therefore, just can in described expansion mechanism 50,100,200, fluid be expanded effectively, also just can carry out effective power recovery.

Also have, invention according to second aspect, in described expansion mechanism 50,100,200, at least induction stroke and discharge stroke are separate carrying out, just pass expansion mechanism even if the importing high-pressure liquid also can expand, can in expansion mechanism 50,100,200, make refrigeration agent obtain really expanding.

Also have, invention according to the third aspect, by with described auxiliary inlet hole 56,104,113,114,203,204,205 form with respect to fluid chamber 72,82,230 from the below towards this

fluid chamber

72,82, the form of 230 openings, not from this auxiliary inlet hole 56,104,113,114,203,204,205 import under the situation of fluid, will be at this auxiliary inlet hole 56,104,113,114,203,204,205 interior reservoir is stayed refrigerator oil, thereby can prevent this auxiliary inlet hole 56 really, 104,113,114,203,204,205 become storage

stays fluid chamber

72,82, the dead angle (dead volume) of the fluid in 230.Thus, just can in described expansion mechanism 50,100,200, fluid more effectively be expanded.Particularly as the invention of fourth aspect, as long as switch valve 61 downstream sides on the inlet passage 27 that is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205 are provided with check valve 95, just can prevent really that this auxiliary inlet hole 56,104,113,114,203,204,205 from becoming the dead angle that stockpiles fluid (dead volume) in the fluid chamber 72,82,230, also just can expand fluid effectively in described expansion mechanism 50,100,200.

Also have, invention according to the 5th aspect, because make the bypass circulation 65 of described expansion mechanism 50,100,200 bypass be provided with bypass flow regulator 66, so the fine adjustment of the volume of fluid circulated of described expansion mechanism 50,100,200 and the Flow-rate adjustment compared with common running the time under the extremely many situations of fluid flow all become possibility.Particularly, invention according to the 6th aspect, by carry out described bypass flow regulator 66 controls based on the hydrodynamic pressure that is imported into described expansion mechanism 50,100,200, just can regulate circulating load and make the pressure of this expansion mechanism 50,100,200 become possibility near desired value.

Also have, invention according to the 7th aspect, because the inlet passage 24 that is interconnected with described main inlet hole 55,103,201 is provided with flow control valve 60, so the fluid flow that just can regulate in the fluid chamber 72,82,230 that imports described expansion mechanism 50,100,200 makes it become optimal flow, also just can reclaim power effectively in this expansion mechanism 50,100,200.

Also have, invention according to eight aspect, because be the downstream side that described flow control valve 60 is arranged on the branch location of the inlet passage 27 that is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205, so can only regulate separately from the flow of the fluid of main inlet hole 55,103,201 importings, so just can control the volume of fluid circulated of described expansion mechanism 50,100,200 more meticulously.

The described the 7th and the invention of eight aspect in, particularly as the invention of the 9th aspect, pressure based on the fluid that is imported into described expansion mechanism 50,100,200 carries out described flow control valve 60 controls, think the pressure that makes this expansion mechanism 50,100,200 near desired value, just can directly regulate the flow of the fluid that imports from main inlet hole 55,103,201.

Also have, invention according to the tenth aspect, because be provided with the switch valve control device 93 that is arranged on the control of the switch valve 61 on the inlet passage 27 that is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205 based on the hydrodynamic pressure that is imported into described expansion mechanism 50,100,200, by carrying out the switch control of described switch valve 61, just can increase and decrease this circulating load and make the volume of fluid circulated of expansion mechanism 50,100,200 become optimal circulating load, just can in this expansion mechanism 50,100,200, carry out power recovery effectively.

Also have, invention according to the tenth one side, because under the big situation of described pressure ratio desired value, described switch valve control device 93 carries out the control of opening of described switch valve 61 in order, make described auxiliary inlet hole 56,104,113,114,203,204,205 in order described fluid chamber 72,82,230 and inlet passage 27 are interconnected, thus just can be rapidly and the flow that positively increases fluid make expansion mechanism 50,100,200 necessary flows be met.

Also have, invention according to the 12 aspect, constitute under the little situation of described pressure ratio desired value because be, described switch valve control device 93 is according to carrying out the closing control of described switch valve 61 from the last order that is interconnected with described auxiliary inlet hole 56,104,113,114,203,204,205, thus just can be rapidly and the flow that positively reduces fluid make expansion mechanism 50,100,200 necessary flows be met.

Also have, invention according to the 13 aspect, at first, constitute to make described pressure reach the control that desired value is carried out described bypass flow regulator 66 because be, and reach the switch control of carrying out described switch valve 61 under the situation of aperture of defined at described bypass flow regulator 66, so the volume of fluid circulated of can be rapidly and successfully regulating described expansion mechanism 50,100,200 also just can be carried out effective power recovery.

Also have, invention according to the 14 aspect, constitute when the volume of fluid circulated that reduces described expansion mechanism 50,100,200 because be, even if closed described switch valve 61 and bypass flow regulator 66 circulating loads and still be under the too much situation, can also carry out Flow-rate adjustment by flow control valve 60, so just can be rapidly and successfully, wide scope ground reduces the volume of fluid circulated of described expansion mechanism 50,100,200, also just can carry out more effective power recovery.

Also have,,,, in described expansion mechanism 50,100, fluid is expanded effectively so just can prevent that the high-pressure liquid that imports from passing because be the described expansion mechanism 50,100 that constitutes multi-stage rotary according to the invention of the 15 aspect.Particularly the invention of the 16 aspect is such, by constituting the 2 stage rotary expansion mechanism, when preventing that really high-pressure liquid from passing expansion mechanism, has also simplified structure, has reduced cost.

Also have, invention according to the 17 aspect, constitute described auxiliary inlet hole 56 because be, 104,113,114 are arranged on based on desirable work discharge capacity and add from the angular orientation that geometry is tried to achieve on the angular orientation of correction value of defined, so considered from this auxiliary inlet hole 56,104,113,114 flow to fluid chamber 72, the minimizing of the refrigeration agent influx that the pressure loss when the refrigeration agent in 230 causes, really can be in this fluid chamber 72, flow through necessary refrigerant flow in 230, just can prevent at expansion mechanism 50, overexpansion in 100.Particularly according to the invention of the tenth eight aspect because described desirable work discharge capacity essential work discharge capacity when being cooling operation, so just can prevent cooling operation really the time in the overexpansion of expansion mechanism 50,100.

Also have,,, just can not prevent passing of high-pressure liquid really, obtain effective expansion mechanism 200 so do not need to be provided with multistage because described expansion mechanism 200 is eddy typees according to the invention of the 19 aspect.

Also have, according to the invention of the 20 aspect, because be to use refrigeration agent that carbon dioxide makes to carry out overcritical freeze cycle, so just can obtain being suitable for the refrigerating plant of environment as described fluid.

Have again, invention according to the 20 one side, by described main inlet hole 55,103,201 and auxiliary inlet hole 56,104,113,114,203,204,205 are arranged on the decompressor, just can obtain decompressor with the invention effect same of described first aspect.

Description of drawings

Fig. 1 is the summary pie graph of the refrigerant circuit of the related air attemperation apparatus of first mode of execution.

Fig. 2 is the longitudinal section of compression-expansion unit.

Fig. 3 is the amplification view in the longitudinal section of expression expansion mechanism.

Fig. 4 is the amplification view in the cross section at main position in the expression expansion mechanism.

Fig. 5 is that the angle of rotation of bent axle is every the main position of the state of each rotary mechanism part of 90 ° sectional view in the expansion mechanism of expression first mode of execution.

Fig. 6 is the plotted curve of the relation of expression refrigeration agent inlet capacity of expansion mechanism and pressure.

Fig. 7 is the figure that relatively injects situation and the Fig. 6 of being equivalent to of the present invention.

Fig. 8 is the figure that the summary of the control gear of each valve of expression control constitutes.

Fig. 9 is the flow chart of the control flow of each valve of expression.

Figure 10 is the figure of an example of each valve control of expression.

Figure 11 is the real figure of relation that schematically illustrates the circulating mass of refrigerant of all valve openings of each valve and expansion mechanism.

Figure 12 is that a plurality of inhalation interfaces of expression are the plotted curve of an example of the relation of refrigeration agent inlet capacity under the situation of open mode and pressure.

Figure 13 is the related figure that is equivalent to Fig. 3 of first variation of first mode of execution.

Figure 14 is the related figure that is equivalent to Fig. 4 of second variation of first mode of execution.

Figure 15 is in the expansion mechanism of expression second mode of execution, and the angle of rotation of moving vortex is every the sectional elevation of 60 ° state.

Figure 16 is the plotted curve of an example of the relation of expression angular orientation of second inhalation interface and refrigerant flow.

Figure 17 is that expression has changed the angular orientation of second inhalation interface under the situation of heat exchanger performance and the figure that calculates the result.

-symbol description-

1 air attemperation apparatus (refrigerating plant)

10 refrigerant circuits

20 compression-expansion units

24 first ingress pipes (suction path)

27 second ingress pipes (suction path)

40 compressing mechanisms

50 expansion mechanisms

55 first inhalation interfaces (main inlet hole)

56 second inhalation interfaces (auxiliary inlet hole)

59 expansion chambers

60 pre-throttle valve (flow control valve)

61 switch valves

65 bypass tubes (bypass circulation)

66 bypass valve (bypass flow regulator)

70 first rotary mechanism part

71 first cylinders (first parts)

First fluid chambers (fluid chamber) 72

75 first pistons (second parts)

80 second rotary mechanism part

81 first cylinders (first parts)

82 second fluid chamber (fluid chamber)

85 second pistons (second parts)

90 pressure detectors

92 pre-throttle flow rate control devices (flow dontroller)

93 switch control devices (switch valve control device)

94 bypass valve flow control portions (bypass flow controller)

95 check valves

100 expansion mechanisms

101 first rotary mechanism part

102 first cylinders (first parts)

103 first inhalation interfaces (main inlet hole)

104 second inhalation interfaces (auxiliary inlet hole)

111 second rotary mechanism part

112 second cylinders (first parts)

113 the 3rd inhalation interfaces (auxiliary inlet hole)

114 the 4th inhalation interfaces (auxiliary inlet hole)

116 second pistons (second parts)

121 the 3rd rotary mechanism part

122 the 3rd cylinders (first parts)

124 the 3rd pistons (second parts)

200 vortex mechanisms (expansion mechanism)

201 inhalation interfaces (main suction port)

203 second inhalation interfaces (auxiliary inlet hole)

204 the 3rd inhalation interfaces (auxiliary inlet hole)

205 the 4th inhalation interfaces (auxiliary inlet hole)

210 moving vortexs (first parts, scroll element)

211 moving teeth (tooth (lap))

220 quiet vortexs (second parts, scroll element)

221 quiet teeth (tooth)

230 fluid chamber

A chambers (fluid chamber) 231

B chambers (fluid chamber) 232

Embodiment

Below, based on the description of drawings embodiments of the present invention.In addition, below preferred embodiment explanation, from only being an example in essence, the present invention has no intention to limit its suitable thing or its purposes.

(first mode of execution)

The integral body formation of-air conditioner-

Among Fig. 1, represented as the related refrigerant circuit 10 of first embodiment of the invention as the air attemperation apparatus 1 of refrigerating plant.This air attemperation apparatus 1 comprises outdoor unit 2 and indoor set 3.In the outdoor unit 2, the bridge type return portion 13 that is provided with compression-expansion unit 20, outdoor heat converter 14, four-way change-over valve 12 and constitutes by

check valve

11,11,11,11.On the other hand, in the indoor set 3, be provided with indoor heat converter 15.In addition, not special diagram in described each

heat exchanger

14,15, all is provided with fan separately, under this kind configuration state this each

heat exchanger

14,15 is blown outdoor air and indoor air.

Described outdoor unit 2 and indoor set 3 are interconnected by a pair of

contact pipe arrangement

16,17, constitute the described refrigerant circuit 10 as loop that has been communicated with described compression-expansion unit 20 and

heat exchanger

14,15 etc. thus.In this embodiment, filled carbon dioxide as refrigeration agent in this refrigerant circuit 10.

Described compression-expansion unit 20 comprises the housing 21 that forms lengthwise seal container cylindraceous.In this housing 21, be provided with compressing mechanism 40, expansion mechanism 50 and motor 26.Just, in housing 21, be provided with compressing mechanism 40, motor 26 and expansion mechanism 50 from top to bottom.The detailed content of this compression-expansion unit 20 still, as feature of the present invention, in described expansion mechanism 50, is provided with the

inhalation interface

55,56 of a plurality of inlet holes in the back narration, makes the intake of refrigeration agent become variable.In addition, in above-mentioned Fig. 1, exemplified the expansion mechanism that is provided with two expansion mechanism 50 inhalation interfaces.

At this, in the described refrigerant circuit 10, the suction side of the compressing mechanism 40 of described compression-expansion unit 20 is provided with liquid-storage container 18.Also have, the suction side of expansion mechanism 50, corresponding described a plurality of inhalation interfaces 55,56 are provided with pre-throttle valve 60 and switch valve 61.Specifically, be to be respectively arranged with the switch valve 61 that the inlet passage of pre-throttle valve 60 on the inlet passage that the induction stroke-beginning of described expansion mechanism 50 just is interconnected with first inhalation interface 55 of fluid chamber 72 and second and second inhalation interface 56 is interconnected.In addition, described pre-throttle valve 60 corresponding to flow control valve of the present invention, described first inhalation interface 55 is corresponding to main inlet hole of the present invention, described second inhalation interface 56 is corresponding to auxiliary inlet hole of the present invention.

Also have, in the described refrigerant circuit 10, be provided with the bypass tube 65 that constitutes suction side that makes described expansion mechanism 50 and the bypass circulation that sprays the side bypass.On this bypass tube 65, be provided with bypass valve 66 as bypass flow regulator of the present invention.By regulate the refrigerant flow of bypass tube 65 with this bypass valve 66, just can regulate the refrigerant flow that flows into expansion mechanism 50.

Described

heat exchanger

14,15 all is made of intersection fin type pipe type heat exchanger.And in described outdoor heat converter 14, circuit refrigeration agent and outdoor air carry out heat exchange in refrigerant circuit 10, and in described indoor heat converter 15, the refrigeration agent and the indoor air that are circulated in the refrigerant circuit 10 carry out heat exchange.

Described four-way change-over valve 12 comprises four valve ports.First valve port of this four-way change-over valve 12 and the ejection side of compressing mechanism 40 are interconnected, one end of second valve port and indoor heat converter 15 is interconnected, the other end of the 3rd valve port and outdoor heat converter 14 is interconnected, and the suction side of the 4th valve port and compressing mechanism 40 is interconnected.

And, described four-way change-over valve 12 constitutes switching: the state (state shown in the solid line among Fig. 1) and first valve port that first valve port and second valve port are interconnected and the 3rd valve port and the 4th valve port are interconnected and the state (state shown in the dotted line among Fig. 1) that the 3rd valve port is interconnected and second valve port and the 4th valve port are interconnected.

Described bridge type return portion 13, be to be combined into the bridge-type shape by four

check valves

11,11,11,11, action by described four-way change-over valve 12, become backward situation even if constitute the flow direction of the refrigeration agent in the described refrigerant circuit 10, also always press certain orientation supply system cryogen for described expansion mechanism 50.By doing like this, compare with the situation that a four-way change-over valve is set beyond the above four-way change-over valve 12 more in addition, no longer need to carry out the control of this four-way change-over valve, formation becomes simple.In addition, being to have constituted bridge type return portion 13 by

check valve

11,11,11,11 in this mode of execution, but being not limited to this, can also be that a four-way change-over valve is set again.

The formation of-compression-expansion unit-

As shown in Figure 2, compression-expansion unit 20 comprises the housing 21 of the columnar seal container of lengthwise.In the inside of this housing 21, be provided with compressing mechanism 40, motor 26 and expansion mechanism 50 from bottom to top in order.Also have, in the described housing 21, be provided with suction pipe 22, spraying pipe 23, become the ingress pipe 24,27 and the delivery line 25 of the part of inlet passage of the present invention in the mode of the body portion that connects it.This suction pipe 22 is interconnected with compressing mechanism 40, and ingress pipe 24,27 and delivery line 25 are interconnected with expansion mechanism 50.Described spraying pipe 23, be set to the distolateral opening of one in described housing 21 motor 26 and the space between the expansion mechanism 50.In addition, first ingress pipe 24 is interconnected with described first inhalation interface 55 in the described ingress pipe 24,27, described second ingress pipe 27 and second inhalation interface 56 be interconnected.That is to say, on outer section of the housing 21 of described first ingress pipe 24, than with the position of described second ingress pipe 27 branches more by the downstream side, be provided with described pre-throttle valve 60, simultaneously, on outer section of the housing 21 of second ingress pipe 27, than with the position of described first ingress pipe 24 branches more by the downstream side, be provided with described switch valve 61.Like this, by described pre-throttle valve 60 being arranged on the branch location downstream side with second ingress pipe 27, just can only regulate, promptly import the flow of the refrigeration agent of expansion mechanism 50, just become possibility so the trace of refrigeration agent is regulated from first inhalation interface 55 from first ingress pipe 24.

Described compressing mechanism 40 constitutes oscillating-piston type rotary compressor.This compressing mechanism 40 comprises 41,42 and two

pistons

47,47 of two cylinders.In the described compressing mechanism 40, overlapping from bottom to top top (rear head), back 44, first cylinder 41, intermediate clapboard (middle plate) 46, second cylinder 42 and preceding top (the front head) 45 of being provided with.

Also have, in described compressing mechanism 40, be provided with first bent axle 31, link with described motor 26 and drive.This first bent axle 31 is set to from the state at top 44, perforation back, bottom, first cylinder 41, intermediate clapboard 46, second cylinder 42 and preceding top 45.

Say that at length the bottom of described first bent axle 31 has formed two compressed side

eccentric parts

32,33 in axially-aligned.These compressed side

eccentric parts

32,33, their axle center is eccentric in the axle center of first bent axle 31.First compressed side eccentric part 32 of downside and the second compressed side eccentric part 33 of upside differ 180 ° on eccentric direction.And the described first compressed side eccentric part 32 is in first cylinder 41, and the described second compressed side eccentric part 33 is in second cylinder 42.

Described first and second compressed side

eccentric part

32,33,

cylindric piston

47,47 in outer separately embedding.These

pistons

47,47 are installed in described first and second cylinder 41,42 inside one to one, thus, have formed

pressing chamber

43,43 respectively between the inner peripheral surface of the outer circumferential face of this

piston

47,47 and cylinder 41,42.In addition, not special diagram, on the side of piston 47, projection is provided with the planar blade that extends to outer direction radially, and this blade pass is crossed the swing lining and is supported on the described cylinder 41,42.

In addition, described first bent axle 31, end face is provided with embedding hole 34 thereon.This embedding hole 34 is holes of the hexagonal section of extending downwards along the axle center of described first bent axle 31, and is chimeric mutually with the mosaic process 38 that is formed on second bent axle, 35 lower ends described later.

On described first and second cylinder 41,42, be provided with an inhalation interface 48 separately.Each inhalation interface 48 is radially connecting cylinder 41,42, the one distolateral inner peripheral surfaces that are opened on cylinder 41,42 to be communicated with described pressing chamber 43, and simultaneously, another distolateral and suction pipe 22 are interconnected.

On described preceding top 44 and the top 45, back, respectively be provided with an ejection interface.Be arranged on the ejection interface on the preceding top 44, the inner space of pressing chamber 43 and housing 21 in second cylinder 42 is interconnected.On the other hand, be arranged on the ejection interface of back on the top 45, the inner space of pressing chamber 43 and housing 21 in first cylinder 41 is interconnected.Also have, each sprays interface, and their terminal is provided with the ejection valve that is formed by leaf valve, carries out switch by these ejection valves.Thus, from the gas refrigerant of described compressing mechanism 40, send from compression-expansion unit 20 through spraying pipe 23 to the ejection of the inner space of housing 21.In addition, in above-mentioned Fig. 2, omitted the diagram of ejection interface and ejection valve.

Described compressing mechanism 40 is fixed on the housing 21 by the mounting plate 49 of ring-type.Specifically, mounting plate 49, its outer circumferential side the preceding top 44 of compressing mechanism 40 by being fixedly welded on housing 21 inner faces with not shown bolton on this mounting plate 49.

Described motor 26 is arranged on the middle body of the length direction in the housing 21.This motor 26 is made of stator 27 and rotor 28.Stator 27, its outer circumferential side is fixed on the inner peripheral surface of described housing 21.Rotor 28 is arranged on the inboard of stator 27, is connected by the top of described first bent axle 31.

As Fig. 4 and shown in Figure 5, described expansion mechanism 50, just so-called oscillating-piston type rotary expander on this expansion mechanism 50, is provided with two and forms the

cylinder

71,81 of the first right parts and the

piston

75,85 of second parts.Also have, this expansion mechanism 50 comprises preceding top 51, intermediate clapboard 53 and top 52, back.In this expansion mechanism 50, each

cylinder

71,81, preceding top 51, intermediate clapboard 53 and top, back 52 constitute quiet parts, and each

piston

75,85 constitutes dynamic component.

In the described expansion mechanism 50, from bottom to top in order: preceding top 51, first cylinder 71, intermediate clapboard 53, second cylinder 81, top 52, back become overlap condition.Under this state, first cylinder 71, its lower end surface is by 51 sealings of preceding top, and its upper-end surface is by intermediate clapboard 53 sealings.On the other hand, second cylinder 81, its lower end surface is by intermediate clapboard 53 sealings, and its upper-end surface is by 52 sealings of top, back.

Described each

cylinder

71,81 roughly forms annular thick plate-like.The internal diameter of second cylinder 81 is bigger than the internal diameter of first cylinder 71.Also have, the thickness of second cylinder 81 (highly) is thicker than the thickness (highly) of first cylinder 71.

In this expansion mechanism 50, be provided with second bent axle 35 with the state that connects described preceding top 51, first cylinder 71, intermediate clapboard 53, second cylinder 81 and top 52, back.On this second bent axle 35, its lower end surface upper process is provided with mosaic process 38.This mosaic process 38 is the hexagon prisms that extend downwards from the lower end surface of second bent axle 35.The section configuration of mosaic process 38 is corresponding to the hexagonal configuration of the embedding hole 34 of described first bent axle 31.First bent axle 31 and second bent axle 35 engage by the embedding hole 34 that first bent axle 31 is inserted in the mosaic process 38 of second bent axle 35, constitute an axle 30.

The top of described second bent axle 35, corresponding described

cylinder

71,81 has formed two expansion side eccentric parts 36,37.These two expansion side

eccentric parts

36,37, their axle center is eccentric in second bent axle 35.The second expansion side eccentric part 37 of downside first expansion side eccentric part 36 and upside, the direction that is eccentric in the axle center of second bent axle 35 is consistent.But the offset of the described second expansion side eccentric part 37 is greater than the offset of the first expansion side eccentric part 36.The described first expansion side eccentric part 36 is arranged in first cylinder 71, and the described second expansion side eccentric part 37 is arranged in second cylinder 81.

On described first and second expansion side

eccentric part

36,37, separately outer embedding

piston

75,85 cylindraceous.And the first piston 75 that is embedded in outward on the described first expansion side eccentric part 36 is positioned at described first cylinder 71, and second piston 85 that is embedded in outward on the described second expansion side eccentric part 37 is positioned at described second cylinder 81.

As above-mentioned shown in Figure 4, described first piston 75, its outer circumferential face is in sliding contact on the inner peripheral surface of first cylinder 71, its lower end surface sliding contact on preceding top 51, its upper-end surface sliding contact on intermediate clapboard 53.Thus, in first cylinder 71, formed first fluid chamber 72 between the outer circumferential face of its inner peripheral surface and first piston 75.

On the other hand, described second piston 85, its outer circumferential face sliding contact on the inner peripheral surface of second cylinder 81, it the lower end surface sliding contact on the intermediate clapboard 53, it the upper-end surface the back top 52 on sliding contact.Thus, in second cylinder 81, formed second fluid chamber 82 between the outer circumferential face of its inner peripheral surface and second piston 85.

On described first and

second piston

75,85, be wholely set a

slice blade

76,86 separately.These

blades

76,86, form from the outer circumferential face of

piston

75,85 to radial outside extend tabular.

In the described

cylinder

71,81, be provided with one separately and form right lining 77,87.Each lining 77,87 is that inner side surface forms the plane and outer side surface forms the small pieces of arc surface.Described paired lining 77,87 is arranged to sandwich the state of

blade

76,86, make lining 77,87 separately inner side surface slide on the

blade

76,86, outer side surface slides on cylinder 71,81.Thus, the

blade

76,86 integrally formed with

piston

75,85 is supported on the

cylinder

71,81 by described lining 77,87, can rotate freely and freely advance and retreat with respect to

cylinder

71,81.

First fluid chamber 72 in described first cylinder 71 is separated by described first blade 76, becomes first low pressure chamber 74 of the low voltage side on high-tension side first hyperbaric chamber 73 in first blade, 76 left sides among Fig. 4 and its right side.Equally, second fluid chamber 82 of described second cylinder, 81 inner peripheral surfaces is separated by described second blade 86, becomes second low pressure chamber 84 of the low voltage side on high-tension side second hyperbaric chamber 83 in second blade, 86 left sides among Fig. 4 and its right side.

Described first cylinder 71 and second cylinder 81 are configured on circumferencial direction separately the position consistency with lining 77,87.In other words, second cylinder 81 is 0 ° with respect to the arrangement angles of first cylinder 71.Also have, as mentioned above, the first expansion eccentric part 36 and the second expansion eccentric part 37 are eccentric in same direction with respect to the axle center of second bent axle 35.Therefore, first blade 76 becomes when falling back on the outermost state of first cylinder 71, and second blade 86 also becomes the outermost state that falls back on second cylinder 81.

On the described intermediate clapboard 53, be provided with the access 54 that connects from the thickness direction of this intermediate clapboard 53.One end of the access 54 at the place, first blade, 76 right sides among Fig. 4, opening is on the face of first cylinder, 71 sides of described intermediate clapboard 53.On the other hand, the other end of the access 54 at place, second blade, 86 left sides, opening is on the face of second cylinder, 81 sides of described intermediate clapboard 53.That is to say that this access 54 is configured such that the form that first low pressure chamber 74 and second hyperbaric chamber 83 are interconnected.Like this, first low pressure chamber 74 and second hyperbaric chamber 83 are interconnected, form an expansion chamber 59 by access 54.

Formed outflow interface 57 on described second cylinder 81.This flows out interface 57, and opening is on the inner peripheral surface of second cylinder 81, and the place, right side slightly at the lining 87 of Fig. 4 is interconnected with second low pressure chamber 84.As above-mentioned Fig. 1, Fig. 2 and Fig. 4, this outflow interface 57 is interconnected with delivery line 25.

And,, on described preceding top 51, formed in the first fluid chamber 72 of described first cylinder 71, importing first and

second inhalation interface

55,56 of refrigeration agent as one of characteristic of the present invention.These inhalation interfaces 55,56, also as shown in Figure 3, in the past the outer circumferential face at top 51 extends to radially interior side direction, form its terminal part upward curved openings on the upper surface at this preceding top 51.That is to say, in Fig. 4, if see first fluid chamber 72 from the top, be set to: described first inhalation interface 55, extend diametrically, opening is at the position in left side slightly of lining 77, described second inhalation interface 56, also extend diametrically, opening with the defined angle (for example 160 degree) of the almost opposite side position of described first inhalation interface 55.Being described in detail of angular orientation about this second inhalation interface 56 sees below.

At this, described first inhalation interface 55 is interconnected with first ingress pipe 24 that is provided with pre-throttle valve 60, and described second inhalation interface 56 is interconnected with second ingress pipe 27 that is provided with switch valve 61.

Like this, refrigeration agent is imported a plurality of inhalation interfaces 55,56 in the described first fluid chamber 72, just can easily regulate the flow that imports the refrigeration agent in this fluid chamber 72 by being provided with.That is to say, in the circulating load (mass flow rate of having only described first inhalation interface, 55 refrigeration agents, below identical) under the not enough situation, also can just can guarantee expansion mechanism 50 necessary circulating mass of refrigerant by importing refrigeration agents from described second inhalation interface 56.

Also have, as mentioned above, by

inhalation interface

55,56 is communicated in first fluid chamber 72 from the below, for example, closing described switch valve 61 under the situation of second inhalation interface, 56 importing refrigeration agents, refrigerator oil described fluid chamber 72 in is stayed in storage in this second inhalation interface 56, filling this part space, just can prevent inflow refrigeration agent in this second inhalation interface 56 for this reason.That is to say,, just can prevent that described second inhalation interface 56 from becoming dead angle (dead volume), just can expand refrigeration agent effectively in described expansion mechanism 50 by described such formation.

At this, in the described expansion mechanism 50 of such as mentioned above formation, constitute first rotary mechanism part 70 by preceding top 51 and intermediate clapboard 53, first piston 75 and first blade 76 at first cylinder 71, first lining 77, sealing first cylinder 71 two ends.Also have, by second cylinder 81, second lining 87, sealing second cylinder 81 two ends intermediate clapboard 53 and top 52, back, second piston 85 and second blade 86 constitute second rotary mechanism part 80.

That is to say that described expansion mechanism 50 is the 2 stage rotary decompressors that comprise first rotary mechanism part 70 and second rotary mechanism part 80.For this reason, as the single-stage rotary expander, inhalation interface and outflow interface are not interconnected by fluid chamber, just can prevent from directly to pass the outflow interface from the high-pressure refrigerant that this inhalation interface imports.Particularly present embodiment is such, be provided with under the situation of a plurality of inhalation interfaces, inhalation interface and outflow interface are just connected mutually in the single-stage rotary expander, and just can make induction stroke and discharge stroke separate by the multi-stage rotary decompressor that constitutes more than the two-stage, also just can prevent the expansion mechanism that passes of high-pressure refrigerant really, high-pressure refrigerant is expanded fully.

In addition, described expansion mechanism 50, the same with described compressing mechanism 40, the mounting plate 58 by ring-type is fixed on the housing 21.Specifically, mounting plate 58 is fixed on housing 21 internal surfaces by welding its outer circumferential side, and the preceding top 51 of expansion mechanism 50 is by not shown being bolted on this mounting plate 58.

The angular orientation of-the second inhalation interface-

Below, describe the determining method of the angular orientation be arranged on second inhalation interface 56 on the described expansion mechanism 50 (position of

blade

76,86 is the angle under 0 ° the situation) in detail.

As mentioned above, by beyond first inhalation interface 55, second inhalation interface 56 being set again, just can in first fluid chamber 72, multithread go into this part refrigeration agent.And because the difference of position of the angle of this second inhalation interface 56 is set, the volume of the

fluid chamber

72,82 that is interconnected with this second inhalation interface 56 can be different, also just can try to achieve work discharge capacity when the suction refrigeration agent with geometry from this volume-variation.Specifically, shown in the heavy line of Figure 16, can be for the angular orientation of described second inhalation interface 56 from calculating the influx of the refrigeration agent that flows into expansion mechanism 50 geometrically.

Yet,, do not lose because consider the suction pressure of second inhalation interface 56, so actual refrigeration agent influx is lacked than the refrigeration agent intake of being tried to achieve by geometry from the refrigeration agent influx that geometry is tried to achieve.That is to say that as above-mentioned shown in Figure 16, the measured value of refrigeration agent influx (black triangle) is owing to from the pressure loss of second inhalation interface 56 when first fluid chamber 72 flows into refrigeration agent, just lack than the desirable refrigeration agent influx of being tried to achieve by geometry.In addition, again as from Figure 16 learnt, the bigger angular orientation of volume-variation in the

fluid chamber

72,82 that is communicated with described second inhalation interface 56 is provided with under the situation of this second inhalation interface 56, because the influence of losing in the suction pressure of second inhalation interface 56 becomes big, so actual refrigeration agent influx (black triangle) reduces significantly than the refrigeration agent influx (heavy line) of being tried to achieve by geometry.

For this reason, in the present embodiment, the refrigeration agent influx that the pressure loss when considering that above such because refrigeration agent sucks reduces, the angular orientation corresponding to the refrigeration agent influx that geometry is calculated adds correction value, on the angular orientation corresponding to the refrigeration agent influx of reality second inhalation interface 56 is set.

At this, in the present embodiment, because the expansion ratio of described expansion mechanism 50, be set at when the specified running that heats to optimum, so, detailed content as described later, during the specified running of refrigeration, the height during specified running that the pressure ratio of low voltage side heats.Consequently, be necessary to increase the influx of high-pressure refrigerant.For this reason, the position that is necessary to set this second inhalation interface 56 when the specified running of refrigeration from described second inhalation interface 56 so that supply with necessary refrigeration agent influx.

Figure 17 has represented the calculated example of the angular orientation of described second inhalation interface 56.In Figure 17, change (increase or the reduce) outdoor heat converter 14 of air attemperation apparatus 1 or performance of indoor heat converter 15 based on measured value, obtain the angular orientation of described second inhalation interface 56 of necessary refrigerant flow in the time of can guaranteeing heating specified running and freezing specified running under the various situations respectively.At this, the high pressure shown in above-mentioned Figure 17 is that ejection pressure, the low pressure from compressing mechanism 40 is the suction pressure of this compressing mechanism 40.Also have, gas cooler exit temperature equates with the inlet temperature of expansion mechanism 50 substantially.

As shown in Figure 17 above-mentioned, in this calculated example, the expansion ratio when heating specified running becomes 2.7～3.0, and the work discharge capacity of necessity is its 1.3～1.6 times (claim this ratio be work discharge capacity than) when freezing specified running.And, during from the specified running of this refrigeration necessary work discharge capacity than and expansion ratio in the angular orientation of described second inhalation interface 56 of trying to achieve geometrically, be based on that the heavy line of above-mentioned Figure 16 calculates.

In addition, the angular orientation of described second inhalation interface 56 of necessary work discharge capacity then can access the value shown in above-mentioned Figure 17 right-hand member when going to ask into the specified running of acquisition refrigeration as if the measured value approximate curve (fine line) that uses above-mentioned Figure 16.

Therefore,, add about 50 °～65 ° correction value in the angular orientation of second inhalation interface 56 of trying to achieve from geometry as above-mentioned shown in Figure 17, thus, just can be in the hope of can obtain freezing specified running the time angular orientation of necessary work discharge capacity.In addition, can also be on the angular orientation of described second inhalation interface 56 of trying to achieve geometrically, to add about 60 ° correction value.Even if this situation is compared with the situation of not carrying out angle modification, can obtain the flow of the refrigerant flow of more approaching necessity.

At this, as above-mentioned shown in Figure 16, even if different condition (situations that refrigerant flow is different), the angular orientation of second inhalation interface 56 of trying to achieve for geometry and the relation (shown in the thick dashed line) of refrigerant flow, as previously discussed, consider the pressure loss when second inhalation interface 56 sucks, the angular orientation (shown in the fine dotted line) of second inhalation interface 56 of trying to achieve by Modified geometrical is with measured value (triangle in vain) basically identical.Therefore, by aforesaid method for correcting, can be in the hope of the angular orientation of sufficient high-precision described second inhalation interface 56.In addition, the situation of present embodiment, the position of described second inhalation interface 56, as as indicated in, preferably set refrigerant flow and change more than 10%, greater than 120 ° angular orientation from above-mentioned Figure 16, as shown in Figure 17, preferably set 150 °～200 ° scope.

-running action-

The action of described air conditioner 1 is described.At this, when the cooling operation of air conditioner 1 is described and the action when heating running, the action of subsequent explanation expansion mechanism 50.

＜cooling operation 〉

During cooling operation, four-way change-over valve 12 switches to state shown in dotted lines in Figure 1.If to motor 26 energisings of compression-expansion unit 20, then the direction along dotted arrow makes refrigerant cycle and carries out steam compressed freeze cycle in refrigerant circuit 10 under this state.

The refrigeration agent that in compressing mechanism 40, has been compressed, by spraying pipe 23 from 20 ejections of compression-expansion unit.Under this state, its critical pressure of the pressure ratio of refrigeration agent is also high.This ejection refrigeration agent is sent in the outdoor heat converter 14 to the outdoor air heat release.

In described outdoor heat converter 14, put hot high-pressure refrigerant, flowed into expansion mechanism 50 by ingress pipe 24,27.In this expansion mechanism 50, high-pressure refrigerant expands, and reclaims power from these high-pressure refrigerants.Low pressure refrigerant after the expansion is sent to indoor heat converter 15 by outlet pipe 25.

In indoor heat converter 15, the refrigeration agent of inflow evaporates from the indoor air heat absorption, and indoor air is cooled.Low-pressure refrigerant gas from indoor heat converter 15 flows out is inhaled into compressing mechanism 40 by suction pipe 22.Compressing mechanism 40 sprays after compressing the refrigeration agent that sucks once more.

＜heat running 〉

Heat when running, four-way change-over valve 12 switches to the state shown in the solid line of Fig. 1.If to motor 26 energisings of compression-expansion unit 20, then the direction along solid arrow makes refrigerant cycle and carries out steam compressed freeze cycle in refrigerant circuit 10 under this state.

The refrigeration agent that in compressing mechanism 40, has been compressed, by spraying pipe 23 from 20 ejections of compression-expansion unit.Under this state, its critical pressure of the pressure ratio of refrigeration agent is also high.This ejection refrigeration agent is sent to indoor heat converter 15.In indoor heat converter 15, the refrigeration agent of inflow heats indoor air to the indoor air heat release.

In indoor heat converter 15, put hot refrigeration agent, flowed into expansion mechanism 50 through ingress pipe 24,27.In expansion mechanism 50, high-pressure refrigerant expands, and reclaims power from these high-pressure refrigerants.Low pressure refrigerant after the expansion is sent to outdoor heat converter 14 through delivery line 25, evaporates from the outdoor air heat absorption.Low-pressure refrigerant gas from outdoor heat converter 14 flows out is inhaled into compressing mechanism 40 through suction pipe 22.Compressing mechanism 40 sprays after compressing the refrigeration agent that sucks once more.

The action of＜expansion mechanism 〉

The action of expansion mechanism 50 is described with reference to Fig. 5.

At first, the process that flows into the high-pressure refrigerant of supercritical state to first hyperbaric chamber 73 of first rotary mechanism part 70 is described.From angle of rotation is that 0 ° state rotates second bent axle 35 slightly, and the contact position of the first piston 75 and first cylinder 71 is by the opening portion of first inhalation interface 55, and high-pressure refrigerant begins to flow into first hyperbaric chamber 73 from this first inhalation interface 55.Thereafter, progressively increasing along with the angle of rotation of second bent axle 35 is 60 °, 180 °, 270 °, and high-pressure refrigerant flows into first hyperbaric chamber 73.High-pressure refrigerant flows into the process in first hyperbaric chamber 73 from this first inhalation interface 55, till the angle of rotation that lasts till second bent axle 35 reaches about 360 ° (first inhalation interface 55 be closed till).

When this, so long as described switch valve 61 is an open mode, the angle of rotation of described second bent axle 35 becomes defined angle (being for example 160 ° in the present embodiment), the contact position of the first piston 75 and first cylinder 71 is by the opening portion of second inhalation interface 56, and high-pressure refrigerant also begins to flow into first hyperbaric chamber 73 from this second inhalation interface 56.From of the inflow of this second inhalation interface 56 to the high-pressure refrigerant in first hyperbaric chamber 73, last till that this second inhalation interface 56 is closed till.

Therefore, the angle of rotation of described second inhalation interface 56 is above 360 °, reach the angle (in the present embodiment being 520 °) till described second inhalation interface 56 is closed, in described first hyperbaric chamber 73, flow into high-pressure refrigerant from described first and

second inhalation interface

55,56, constitute to compare with the prior art that described first inhalation interface 55 only is set and to prolong induction stroke, also just can import more high-pressure refrigerant.

Next, the inflation process of refrigeration agent in the expansion mechanism 50 is described.As above-mentioned shown in Figure 5, from the angle of rotation of second bent axle 35 is that the state of 0 ° (360 °) rotates slightly, first hyperbaric chamber 73 of first cylinder 71 and second hyperbaric chamber 83 of second cylinder 81 are interconnected by access 54, and refrigeration agent begins to flow to second hyperbaric chamber 83 from described first low pressure chamber 74.As described, high-pressure refrigerant flow into from described second inhalation interface 56 first hyperbaric chamber 73 during, refrigeration agent does not expand substantially in this first hyperbaric chamber 73 and second hyperbaric chamber 83, but described second inhalation interface 56 is closed back (angle of swing reach about 520 ° after), progressively increasing along with the angle of rotation of second bent axle 35 is 540 °, 630 °, described first hyperbaric chamber 73, the volume in second hyperbaric chamber 83 progressively increased when just the volume of first low pressure chamber 74 progressively reduced, its as a result the volume of expansion chamber 59 progressively increase.The volume of this expansion chamber 59 increases, the angle of rotation that lasts till second bent axle 35 near and will reach till 720 °.And the refrigeration agent in the process that the volume of expansion chamber 59 increases in the expansion chamber 59 expands, and expansion driven second bent axle 35 by this refrigeration agent rotates.Like this, the refrigeration agent in first low pressure chamber 74 flows to second hyperbaric chamber 83 through expansion limit, access 54 limit.

Next, the process that flows out refrigeration agent from second low pressure chamber 84 of second rotary mechanism part 80 is described.If the refrigeration agents in described second low pressure chamber 84 expand, then this second hyperbaric chamber 83 is 720 ° constantly to be communicated with outflow interface 57 since the angle of rotation of second bent axle 35, becomes second low pressure chamber 84.That is to say, flow out refrigeration agent to flowing out interface 57 since second low pressure chamber 84.Thereafter, it is 810 °, 900 °, 990 ° that the angle of rotation of second bent axle 35 progressively increases, till this angle of rotation arrives 1080 ° during in, the low pressure refrigerant that flows out after expanding from second low pressure chamber 84.

The inlet capacity of the expansion chamber 59 of described expansion mechanism 50 changes and the relation table of variation in pressure is shown among Fig. 6.Among this Fig. 6, dotted line is represented only to import high-pressure refrigerant from first inhalation interface 55, the curve of the situation of overexpansion does not take place, fine line is represented only to import high-pressure refrigerant from first inhalation interface 55, the curve of the situation of overexpansion takes place, and heavy line represents to import from second inhalation interface 56 curve of the situation of high-pressure refrigerant.

For example, do not take place under the situation of overexpansion (situation of dotted line among above-mentioned Fig. 6) at expansion mechanism 50, the high-pressure refrigerant of supercritical state from an a to flowing into first hyperbaric chamber 73 b.Thereafter, first hyperbaric chamber 73 is communicated with access 54 and switches to first low pressure chamber 74.In the expansion chamber 59 of first low pressure chamber 74 and second hyperbaric chamber, 83 formations, inner high-pressure refrigerant sharply is declined to become saturation state from a b to pressure the c.Become the refrigeration agent of saturation state, evaporation is a part and expanding wherein, and pressure descends lentamente till put d.And second hyperbaric chamber 83 and is flowed out interface 57 and is communicated with and switches to second low pressure chamber 84.Refrigeration agent in this second low pressure chamber 84 is sent outflow interface 35 in the time period till some e.At this moment, the density ratio that sucks refrigeration agent and discharging refrigerant is consistent with the design expansion ratio, and carries out the running of power recovery excellent in efficiency.

On the other hand, because cooling operation and heat the switching of running or the variation of outside air temperature etc., high-pressure and low pressure can the off-design values.That is to say, among Fig. 6, design expansion mechanism 50 in case air conditioner 1 heat pressure and inlet capacity are changed when specified and situation under, if switch to cooling operation, the low-pressure lateral pressure that then freezes when specified rises to the fine line grade, and has produced the overexpansion region D.

To this, such as mentioned above, by also importing high-pressure refrigerants, among above-mentioned Fig. 6 from second inhalation interface 56, the scope generation inlet capacity that adds the heavy line zone C on the B zone changes and variation in pressure, and this part variation just can be carried out more power recovery.

Described formation is compared with the situation (Fig. 7) of carrying out gunite in the expansion stroke of prior art, can more effectively carry out power recovery.That is to say, as shown in Figure 7, in the formation of spraying, can only carry out it, and carry out power recovery as the part of the zone C of the effect of spraying in the area B that reclaims power by the high-pressure refrigerant that imports from first inhalation interface 55.To this, also shown in the dot and dash line of Fig. 7, in described formation, can carry out more power recovery.

Yet, because described refrigerant circuit 10 is loops, just be necessary to make the refrigerant flow of described expansion mechanism 50 consistent with the refrigerant flow of compressing mechanism 40, so, in the air conditioner 1 involved in the present invention, just merely do not increase the circulating mass of refrigerant of expansion mechanism 50 like that as mentioned above, but constitute the circulating load of suitably regulating refrigeration agent.

Below, describe control in detail for each

valve

60,61,66 of the refrigerant flow control of carrying out described expansion mechanism 50.

The control of＜valve 〉

With reference to Fig. 8 to Figure 12 explanation by the pre-throttle valve 60 that is arranged at first ingress pipe 24, be arranged at the switch valve 61 of second ingress pipe 27 and be arranged at the switch control of bypass flow regulator 66 of bypass circulation 65 or the refrigerant flow that described expansion mechanism 50 is controlled in flow control.

In the related air conditioner 1 of present embodiment, as shown in Figure 8, be provided with the pressure detector 90 of the pressure that detects the high-pressure refrigerant that imports expansion mechanism 50.This pressure detector 90, for example the pressure transducer (omitting diagram) by the ejection side pressure that detects compressing mechanism 40 constitutes.Force value by these pressure detector 90 detected high-pressure refrigerants sends controller 91 to.

At this, described controller 91 comprises: for the pre-throttle flow rate control device 92 of the flow control of carrying out described pre-throttle valve 60, for the switch control device 93 of the switch control of carrying out described switch valve 61 be the bypass valve flow control portion 94 of the flow control of carrying out described bypass valve 65, described controller 91 constitutes based on described pressure detector 90 detected force value and carries out the control of each

valve

60,61,66 by described each control device 92,93,94.

In addition, make described pre-throttle flow rate control device 92 corresponding to flow dontroller of the present invention, described switch valve control portion 93 corresponding to switch valve control device of the present invention, described bypass valve flow control portion 94 corresponding to bypass flow controller 94 of the present invention.

Below, based on the concrete control of each

valve

60,61,66 of flowchart text of Fig. 9.In addition, switch valve 61 is a closed condition during A-stage.

At first, if the flow process of above-mentioned Fig. 9 begins, then in step S1, detect the pressure of the high-pressure refrigerant that imports expansion mechanism 50 by described pressure detector 90.This force value and predefined desired value are compared (step S2), if than this desired value big (situation of "Yes"), the circulating mass of refrigerant that flows to expansion mechanism 50 by described bypass valve 66 fine adjustment earlier makes force value near desired value.The aperture of described bypass valve 66 reaches the value (situation of step 4 "Yes") of defined, by making described switch valve 61 become the circulating mass of refrigerant that open mode increases described expansion mechanism 50, be adjusted to the circulating mass of refrigerant (step S5) identical with described compressing mechanism 40.In addition, even if make described switch valve 61 become the situation of open mode in this wise, also carry out the fine adjustment of circulating load by described bypass valve 66.Among the described step S4, under the little situation of the value of the opening ratio defined of described bypass valve 66, return described step S2, reach till the desired value or the aperture of this bypass valve 66 is driven big this bypass valve 66 till reaching the value of defined to force value.

At this, described desired value, set COP and become maximum force value, the defined value of described bypass valve 66 apertures, be equivalent to aperture given to this invention, mean and this bypass valve 66 can't be opened big aperture more than this aperture, also can't regulate flow to this more than the aperture even if open in other words greatly.

Whether little than desired value on the other hand, described force value is (situation of the "No" of described step S2) under the situation below the desired value, enters step S6, carry out the judgement of described force value.If be judged as this force value unlike under the little situation of desired value (situation of the "No" of step S6),,, begin this flow process again so return beginning because force value equals desired value.

Among the described step S6, when being judged as the force value situation littler than desired value (situation of "Yes"), close described bypass valve 66 in following step S7, the circulating mass of refrigerant that fine adjustment flows to described expansion mechanism 50 makes force value reach desired value.Even if described like this force value still than (situation of the "Yes" of step S8) under the little situation of desired value, is closed described switch valve 61 in following step S9, reduce the circulating mass of refrigerant that flows to described expansion mechanism 50.At this moment, because the circulating mass of refrigerant of compressing mechanism 40 is few, so in order to cooperate it to be necessary to reduce the circulating mass of refrigerant of expansion mechanism 50.When this, flow to the fine adjustment of the circulating mass of refrigerant of this expansion mechanism 50 by described bypass valve 66.

Even if make switch valve 61 become the described force value of closed condition still than desired value under the little situation (situation of the "Yes" of step S10) at described step S9, with described bypass valve 66 contract fullys or contract fully (defined aperture) (step S11) almost, even if like this if, close the adjusting (step S13) that described pre-throttle valve 60 carries out circulating mass of refrigerant still than (situation of the "Yes" of step S12) under the little situation of desired value., return beginning, begin this flow process again thereafter.

On the other hand, among described step S8, step S10, the step S12,, equal reference value, return beginning, begin this flow process again in order to make this force value when judging under the described force value situation little (situation of "No") unlike desired value.

One example of the valve control in the above-mentioned flow chart shown in Figure 9 is illustrated among Figure 10; The schematic that concerns of the aperture of the circulating mass of refrigerant of described expansion mechanism 50 and described each

valve

60,61,66 is shown among Figure 11; Opening the refrigeration agent inlet capacity under the switch valve situation and the relation table of pressure is shown among Figure 12.In addition, above-mentioned Figure 10 to Figure 12, it is the example of situation that is provided with the inhalation interface of a plurality of described expansion mechanisms 50, in this case, need to increase the quantity of switch valve corresponding to this, so among above-mentioned Fig. 9, if append make other switch valves become out state or close state step.

As above-mentioned shown in Figure 10, under the situation of the force value of high-pressure refrigerant greater than desired value, described pre-throttle valve 60 is a full-gear, along with step STP advances (increase of STP numerical value), if the difference of described force value and desired value is little, then the fine adjustment that imports the high-pressure refrigerant flow of expansion mechanism 50 by described bypass valve 66 makes this force value near equaling desired value, and the aperture of working as this bypass valve 66 reaches under the above situation of defined aperture (being 80% in the example of figure), makes described switch valve 61 become out state.In addition, in the example of above-mentioned Figure 10, be provided with the inhalation interface of three described expansion mechanisms 50, the switch valve of second inhalation interface is second suction valve, and the switch valve of the 3rd inhalation interface is the 3rd suction valve.

On the contrary, if force value diminishes, gradually diminish with the difference of desired value, then the direction that reduces to step STP advances, the limit is by described bypass valve 66 control flow rate, and the limit makes described switch valve 61 become the state of closing, even if like this force value still is under the little situation, make described bypass valve 66 become full-shut position, carry out the adjusting of circulating mass of refrigerant by described pre-throttle valve 60.

That is to say, as above-mentioned shown in Figure 11, under the situation of the circulating mass of refrigerant that increases described expansion mechanism 50, open by controlling a plurality of switch valves in turn, can increase circulating mass of refrigerant stagely, simultaneously till opening to switch valve during, by by bypass valve 66 adjusting circulating mass of refrigerant, just can successfully increase circulating mass of refrigerant.Like this, as shown in figure 12, become open mode, can increase the inlet capacity of refrigeration agent by controlling a plurality of switch valves in turn.

On the other hand, reduce the situation of the circulating mass of refrigerant of described expansion mechanism 50, control by the off switch valve can reduce circulating mass of refrigerant by the stage shape, arrive simultaneously till the off switch valve during, by regulating circulating mass of refrigerant, just can successfully reduce circulating mass of refrigerant by bypass valve 66.Have again, become full-shut position, also can carry out the adjusting of circulating mass of refrigerant by described pre-throttle valve 60 even if close described switch valve bypass valve 66.

Therefore,, just can increase and decrease circulating mass of refrigerant rapidly and successfully, just can keep balance with the circulating mass of refrigerant of compressing mechanism 40 in wide scope to described expansion mechanism 50 by carrying out the control of such as mentioned above circulating mass of refrigerant.

The effect of-the first mode of execution-

As previously discussed, in the present embodiment, on expansion mechanism 50, be provided with first and second inhalation interface 55, in the time of 56, also by on first ingress pipe 24 that is communicated with first inhalation interface 55, pre-throttle valve 60 being set, on second ingress pipe 27 that is communicated with second inhalation interface 56, switch valve 61 is set, the increase and decrease of corresponding compressing mechanism 40 circulating mass of refrigerant increases and decreases the high-pressure refrigerant that imports described expansion mechanism 50 rapidly and positively and becomes possibility, just can make the circulating mass of refrigerant of the high-pressure refrigerant that imports this expansion mechanism 50 and the circulating mass of refrigerant of compressing mechanism 40 reach balance, carry out effectively power recovery simultaneously from this high-pressure refrigerant energy.

Also have,, in this

inhalation interface

55,56, will store up the refrigerator oil that stays in the fluid chamber 72, just can prevent that also the storage of refrigeration agent from staying by with the downside of described

inhalation interface

55,56 openings in first fluid chamber 72.That is to say,, just can prevent that this

inhalation interface

55,56 from becoming dead angle (dead volume), also just can expand refrigeration agent effectively in expansion mechanism 50 by described

inhalation interface

55,56 is set to from the open lower side of fluid chamber 72.

Also have, by the bypass tube 65 of the described expansion mechanism 50 of bypass is set, on this bypass tube 65, bypass valve 66 is set, just can relax owing to the control of the switch of described switch valve 61 makes the rapid increase and decrease of circulating mass of refrigerant, the circulating mass of refrigerant that should close described compressing mechanism 40 successfully changes the circulating mass of refrigerant of described expansion mechanism 50.

Have again, because described expansion mechanism 50 is the 2 stage rotary decompressors that comprise first rotary mechanism part 70 and second rotary mechanism part 80, so inhalation interface is to be interconnected by fluid chamber with flowing out interface unlike the single-stage rotary expander, just can prevents from not to be inflated and just pass the outflow interface from the high-pressure refrigerant of this inhalation interface importing.Therefore, in the described expansion mechanism 50, high-pressure refrigerant is expanded fully.

Also have, by described second inhalation interface 56 being arranged on to for guaranteeing that in refrigeration angular orientation that necessary work discharge capacity is tried to achieve from geometry carries out on the angular orientation that the correction of defined obtains during specified running, replenish in fluid chamber 72, to flow into when the refrigeration agent and just can make the refrigerant flow that flows through necessity in this fluid chamber 72, also just can prevent from when cooling operation, to flow to the deficiency of refrigerant flow of expansion mechanism 50 and the overexpansion that causes because the flow that the pressure loss causes reduces from this second inhalation interface 56.

First variation of-the first mode of execution-

As shown in figure 13, this first variation, it is different with described first mode of execution that check valve 95 this point are set in second inhalation interface 56 of expansion mechanism 50.

Specifically, only allow to flow to the refrigeration agent of first fluid chamber 72 in described second inhalation interface 56, be provided with check valve 95 in order not make its contrary direction flow system cryogen.Thus,, do not import the state of high-pressure refrigerant, can prevent refrigeration agent adverse current really from described fluid chamber 72 from described second inhalation interface 56 even if switch valve 61 becomes closed condition.That is to say, can reduce the dead angle (dead volume) of described second inhalation interface 56 really, also just can in described expansion mechanism 50, refrigeration agent be expanded effectively.

Second variation of-the first mode of execution-

As shown in figure 14, this second variation, expansion mechanism is that three grades of rotary expander this point that formed by three rotary mechanism part are different with described mode of execution.

Specifically, described expansion mechanism 100 comprises and essentially identical first rotary mechanism part 101 of first mode of execution and second rotary mechanism part 111, also comprises the 3rd rotary mechanism part 121 at their upside.

These rotary mechanism part 101,111,121, basic is identical formation with described first mode of execution, omit its detailed description, but, on first cylinder 102 of described first rotary mechanism part 101, be provided with first inhalation interface 103 and second inhalation interface 104, on second cylinder 112 of described second rotary mechanism part 111, be provided with the 3rd inhalation interface 113 and the 4th inhalation interface 114, flow out interface 123 and be arranged on the 3rd cylinder 122 of the 3rd rotary mechanism part 121.

Also have, be provided with access 115 between described second cylinder 112 and the 3rd cylinder 122.Specifically, described access 115, in Figure 14, from the right side of the lining 118 of outward extending second blade 117 of outer circumferential face that is arranged on cylindric second piston 116 in described second cylinder 112, extend to the left side of the lining 126 of the 3rd blade 125 that support extends radially outward from the 3rd pistons 124 that are arranged in described the 3rd cylinder 122.

Thus, because the fluid chamber of described second cylinder 112 is communicated with the fluid chamber of the 3rd cylinder 122, do not resemble just that refrigeration agent expands when second cylinder 112 moves from first cylinder 102 described first mode of execution, when in second cylinder 112, in the 3rd cylinder 122, moving, expanding yet.

In the expansion mechanism 100 that constitutes like this, by such as mentioned above a plurality of inhalation interfaces 103,104,113,114 are set, even if three grades of rotary expanders, also can be as described first mode of execution, the circulating mass of refrigerant that this expansion mechanism 100 is regulated on effective power recovery limit is carried out on the limit.

(second mode of execution)

Next, describe second mode of execution of the present invention in detail based on accompanying drawing.As shown in figure 15, this second mode of execution, expansion mechanism 50 are that this point that is made of two

rotary mechanism part

70,80 is different with described first mode of execution, usefulness vortex mechanism 200 formation expansion mechanisms.Formation beyond this expansion mechanism because identical with described first mode of execution, is omitted diagram and explanation.

Specifically, described vortex mechanism 200 comprises quiet vortex 220 that is fixed in housing (not shown) and the moving vortex 210 that is supported in described housing by bearing (not shown).

Described quiet vortex 220 constitutes scroll element, comprises flat quiet end plate (not shown) and erects the quiet tooth 221 of scroll that is arranged on this quiet end plate.On the other hand, described moving vortex 210 constitutes scroll element, comprises flat moved end plate (not shown) and erects the moving tooth 211 of the scroll that is arranged on this moved end plate.And the quiet tooth 221 of quiet vortex 220 and the moving tooth 211 of moving vortex 210 are meshing with each other, and between forms a plurality of fluid chamber 230.

On the described quiet vortex 220, when having formed inhalation interface 201 and having flowed out interface 202, two second inhalation interfaces 203,203, the 3rd inhalation interface 204,204 and the 4th inhalation interface 205,205 have also respectively been formed.Described inhalation interface 201, opening is near quiet tooth 221 beginning scrollwork side ends.On the other hand, described outflow interface 202, opening is near quiet vortex 220 end scrollwork side ends.Described second to the 4th inhalation interface 203,204,205 as described later, is arranged at the position that quiet tooth 221 beginning scrollwork side spaces can be communicated with in order in induction stroke.

In described a plurality of fluid chamber 230, the folded space of outer side surface of the inner side surface of quiet tooth 221 and moving tooth 211 constitutes the A chamber 231 as first fluid chamber 230.Also have, the folded space of inner side surface of the outer side surface of quiet tooth 221 and moving tooth 211 constitutes the B chamber 232 as second fluid chamber 230.

Described second to the 4th inhalation interface 203,204,205, when moving vortex 210 revolves round the sun with respect to quiet vortex 220, order according to second inhalation interface 203,203, the 3rd inhalation interface 204,204 and the 4th inhalation interface 205,205 begins to be communicated in fluid chamber 230, be separated into two Room to the next fluid chamber 230 that forms of beginning till (moving vortex 210 revolves round the sun till 540 ° with respect to quiet vortex 220) be communicated with this fluid chamber 230.

Also have, be communicated in the ingress pipe of described second to the 4th inhalation interface 203,204,205, be provided with not shown switch valve respectively, the same with described first mode of execution, constitute corresponding to high pressure (ejection of compressor is pressed) and carry out switch control.In addition, this mode of execution also is: be provided with pre-throttle valve on the ingress pipe that is communicated in described inhalation interface 201, be provided with bypass valve on the bypass tube of bypass expansion mechanism, the control of these each valves is the same with described first mode of execution.

-running action-

Next, the expansion action of described vortex mechanism 200 is described.In addition, in the following description, be the on high-tension side pressure ratio desired value height of explanation, the expansion action under the situation that described second to the 4th inhalation interface 203,204,205 is an open mode.

At first, import high-pressure refrigerant from inhalation interface 201, inflow is clipped near the quiet tooth 221 beginning scrollworks and a near fluid chamber 230 of moving tooth 211 beginning scrollworks.That is to say that high-pressure refrigerant imports fluid chamber 130 from inhalation interface 201.

At this, among above-mentioned Figure 15, moving tooth 211 when contact with moving tooth 211 inner side surfaces with quiet tooth 221 beginning scrollwork side ends, to begin scrollwork side ends and quiet tooth 221 inner side surface state of contact be 0 ° of benchmark.

Described moving vortex 210 revolves round the sun, progressively enlarge along with its revolution angle increases described fluid chamber 230 from 60 ° to 360 °, these fluid chamber's 230 second inhalation interfaces 203,203, the 3rd inhalation interface 204,204 and the 4th inhalation interface 205,205 are connected in order.At this moment, the revolution angle of described moving vortex 210 surpasses 180 °, and described fluid chamber 230 is separated into two spaces gradually, and the revolution angle reaches 360 °, and described fluid chamber 230 is separated into described A chamber 231 and B chamber 232.

Next, the revolution angle of moving vortex 210 through 420 °, 480 ° till arriving 540 °, in A chamber 231 and the B chamber 232, be communicated with second to the 4th inhalation interface 203,204,205, import high-pressure refrigerant.That is to say that the scope that this revolution angle reaches till 540 ° is equivalent to induction stroke.

Thereafter, the revolution angle of moving vortex 210 surpasses 540 °, and described second to the 4th inhalation interface 203,204,205 is for 232 the one-tenths closed conditions in A chamber 231 and B chamber, and this A chamber 231 and B chamber 232 volumes enlarge, in this A chamber 231 and B chamber 232 inner refrigerants begin expansion.

Expansion stroke in the described A chamber 231, till the revolution angle that lasts till described moving vortex 210 arrived 1020 °, this moving vortex 210 continued rotation, and this A chamber 231 is communicated with outflow interface 202, refrigeration agent in this A chamber 231 flows out to the outside from flowing out interface 202, the beginning discharge stroke.

On the other hand, the expansion stroke in the described B chamber 232 is till the revolution angle that lasts till described moving vortex 210 arrives 840 °, should continue rotation by moving vortex 210, this B chamber 232 is communicated with outflow interface 202, and the refrigeration agents in this B chamber 232 flow out to the outside from flowing out interface 202, the beginning discharge stroke.

In addition, in the described mode of execution, be provided with four inhalation interfaces, but be not limited to this, the same with first mode of execution, can be provided with two, also can be provided with more than three or five.

The effect of-the second mode of execution-

As mentioned above, according to this mode of execution, even if in the expansion mechanism that constitutes by vortex mechanism 200, the same with described first mode of execution, by a plurality of inflow interfaces 201,203,204,205 are set, when reclaiming power effectively, can also increase the circulating mass of refrigerant of this expansion mechanism.That is to say, even if for example on high-tension side force value is bigger than desired value, be necessary to increase the situation of the circulating mass of refrigerant of expansion mechanism, by importing high-pressure refrigerant from described inflow interface 203,204,205, just can guarantee necessary circulating mass of refrigerant, the circulating mass of refrigerant that just can the described expansion mechanism of balance and the circulating mass of refrigerant of compressing mechanism.

(other mode of executions)

Among the present invention, described mode of execution can also be following formation.

In described first mode of execution, being each

rotary mechanism part

70,80 of the expansion mechanism 50 that is made of oscillating-piston type rotary type fluid machine, but being not limited to this, can also be to constitute each

rotary mechanism part

70,80 by rolling piston type rotary type fluid machine.In this case, in each

rotary mechanism part

70,80,

blade

76,86 and

piston

75,85 form respectively.Also have, in each

rotary mechanism part

70,80, omitted lining 77,87.And

blade

76,86, its tip press under the state of outer circumferential face of

piston

75,85, along with the action of

piston

75,85 in the to-and-fro motion that makes progress of the radius of

cylinder

71,81.

Also have, in described first mode of execution, be provided with two

inhalation interfaces

55,56 on the expansion mechanism 50, but be not limited to this, inhalation interface can also be provided with more than three.Have again, in described second mode of execution, on vortex mechanism 200, be provided with four inhalation interfaces 201,203,204,205, but be not limited to this, both two or three can also be set, also can be provided with more than five.

Also have, in described first mode of execution, be communicated on the inlet passage of first inhalation interface 55 of expansion mechanism 50, be provided with described pre-throttle valve 60 in downstream side, position with the inlet passage branch that is communicated in second inhalation interface 56, but be not limited to this, can also be arranged on the upstream side of this branch location.In this case, by the whole flow of first and

second inhalation interface

55,56 of described pre-throttle valve adjustment.

Practicality on the-industry-

Just as described above, the present invention is for comprising the expansion mechanism that is produced power by fluid expansion Refrigerating plant be useful.

Claims

1. refrigerating plant, comprise expansion mechanism (50,100,200), in this expansion mechanism (50,100,200), have first parts (71,81,102,112,210) and second parts (75,85,116,124,220) of doing relative eccentric motion, fluid in the fluid chamber (72,82,230) that is formed between these two parts expanded and be converted into power, it is characterized in that:

On described expansion mechanism (50,100,200), be provided with induction stroke make at the very start main inlet hole (55,103,201) that described fluid chamber (72,82,230) and inlet passage (24) be interconnected and with the auxiliary inlet hole (56,104,113,114,203,204,205) that described fluid chamber (72,82,230) and inlet passage (27) is interconnected after this main inlet hole (55,103,201) is communicated with.

2. refrigerating plant according to claim 1 is characterized in that:

Separated described fluid chamber (72,82,230) in the described expansion mechanism (50,100,200), so that in this fluid chamber (72,82,230), can carry out induction stroke and discharge stroke independently at least.

3. refrigerating plant according to claim 1 is characterized in that:

Described auxiliary inlet hole (56,104,113,114,203,204,205), with respect to described fluid chamber (72,82,230), from the below towards described fluid chamber (72,82,230) opening.

4. refrigerating plant according to claim 1 is characterized in that:

The inlet passage (27) that is communicated in described auxiliary inlet hole (56,104,113,114,203,204,205) is provided with switch valve (61),

Downstream side in described switch valve (61) is provided with the check valve (95) that only allows fluid to flow to auxiliary inlet hole (56,104,113,114,203,204,205) from this switch valve (61).

5. refrigerating plant according to claim 1 is characterized in that:

Comprise bypass circulation (65), this bypass circulation (65) is described expansion mechanism (50,100,200) bypass,

Bypass circulation (65) is provided with bypass flow regulator (66).

6. refrigerating plant according to claim 5 is characterized in that:

Comprise bypass flow controller (94), this bypass flow controller (94) is based on the described bypass flow regulator of pressure control (66) that is imported into the fluid in the described expansion mechanism (50,100,200).

7. refrigerating plant according to claim 1 is characterized in that:

The inlet passage (24) that is interconnected with described main inlet hole (55,103,201) is provided with flow control valve (60).

8. refrigerating plant according to claim 7 is characterized in that:

Described flow control valve (60) is arranged on the downstream side of the branch location of the inlet passage (27) that is interconnected with described auxiliary inlet hole (56,104,113,114,203,204,205).

9. refrigerating plant according to claim 7 is characterized in that:

Comprise flow dontroller (92), this flow dontroller (92) is based on the described flow control valve of pressure control (60) that is imported into the fluid in the described expansion mechanism (50,100,200).

10. refrigerating plant according to claim 1 is characterized in that:

Comprise switch valve control device (93), this switch valve control device (93) is arranged on the switch valve (61) on the inlet passage (27) that is communicated in described auxiliary inlet hole (56,104,113,114,203,204,205) based on the pressure control that is imported into the fluid in the described expansion mechanism (50,100,200).

11. refrigerating plant according to claim 10 is characterized in that:

Be provided with a plurality of described auxiliary inlet holes (56,104,113,114,203,204,205), the inlet passage (27) that is interconnected with each auxiliary inlet hole (56,104,113,114,203,204,205) is provided with switch valve (61),

Under the big situation of described pressure ratio desired value, described switch valve control device (93) carries out the control that described switch valve (61) is opened in order, and is communicated with described fluid chamber (72,82,230) and inlet passage (27) in order by described auxiliary inlet hole (56,104,113,114,203,204,205).

12. refrigerating plant according to claim 10 is characterized in that:

Under the little situation of described pressure ratio desired value, described switch valve control device (93) carries out closing control to described switch valve (61) in order, makes to go up the last described auxiliary inlet hole (56,104,113,114,203,204,205) that is communicated with in described fluid chamber (72,82,230).

13., it is characterized in that according to claim 11 or 12 described refrigerating plants:

Also comprise bypass flow controller (94),

This bypass flow controller (94) is used for control setting at the bypass flow regulator (66) with the bypass circulation (65) of described expansion mechanism (50,100,200) bypass,

Described bypass flow controller (94) is controlled described bypass flow regulator (66), so that described pressure reaches desired value,

Reach at described bypass flow regulator (66) under the situation of aperture of defined, described switch valve control device (93) is controlled the opening and closing of described switch valve (61).

14. refrigerating plant according to claim 13 is characterized in that:

Also comprise flow dontroller (92),

This flow dontroller (92) is used for the flow control valve (60) of control setting on the inlet passage (24) that is communicated in described main inlet hole (55,103,201),

Even if make described bypass flow regulator (66) and switch valve (61) be in all that described pressure still is lower than under the situation of desired value under the full closing state, described flow dontroller (92) is controlled described flow control valve (60), is regulated the flow of described expansion mechanism (50,100,200) by this flow rate regulating valve (60).

15. refrigerating plant according to claim 1 is characterized in that:

Described expansion mechanism (50,100) has a plurality of rotary mechanism part (70,80,101,111,121) that the work discharge capacity is connected from small to large and is communicated with,

Described main inlet hole (55,103) and auxiliary inlet hole (56,104,113,114) are arranged in the portion of previous stage sideway swivel mechanism (70,101,111) than final step rotary mechanism part (80,121).

16. refrigerating plant according to claim 15 is characterized in that:

Described expansion mechanism (50) has two rotary mechanism part (70,80) of series connection,

The little previous stage rotary mechanism part (70) of work discharge capacity is provided with described main inlet hole (55) and auxiliary inlet hole (56).

17. refrigerating plant according to claim 15 is characterized in that:

Described auxiliary inlet hole (56,104,113,114) is arranged on based on desirable discharge capacity and is added on the angular orientation of being tried to achieve after the correction value of defined by the geometry angular orientation.

18. refrigerating plant according to claim 17 is characterized in that:

Described desirable work discharge capacity is the work discharge capacity of necessity when carrying out cooling operation.

19. refrigerating plant according to claim 1 is characterized in that:

Described expansion mechanism (200), has vortex mechanism, this vortex mechanism is included in a pair of scroll element (210,220) that is formed with Vorticose tooth on the end plate, this vortex mechanism is meshing with each other by the tooth (211,221) that makes this two scroll element (210,220) and constitutes at least one pair of fluid chamber (231,232)

The position that is interconnected with described fluid chamber (231,232) in the induction stroke of described vortex mechanism is provided with described main inlet hole (201) and auxiliary inlet hole (203,204,205).

20. refrigerating plant according to claim 1 is characterized in that:

Constitute the refrigeration agent made from carbon dioxide and carry out overcritical freeze cycle as described fluid.

21. decompressor, comprise expansion mechanism (50,100,200), in this expansion mechanism (50,100,200), have first parts (71,81,102,112,210) and second parts (75,85,116,124,220) of doing relative eccentric motion, fluid in the fluid chamber (72,82,230) that is formed between these two parts expanded and change into power, it is characterized in that:

On described expansion mechanism (50,100,200), be provided with the auxiliary inlet hole (56,104,113,114,203,204,205) that after induction stroke makes the main inlet hole (55,103,201) that described fluid chamber (72,82,230) and inlet passage (24) be interconnected at the very start and this main inlet hole (55,103,201) is communicated with, described fluid chamber (72,82,230) and inlet passage (27) is interconnected.