CN101449118A - Refrigeration device - Google Patents
Refrigeration device Download PDFInfo
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- CN101449118A CN101449118A CNA200780018084XA CN200780018084A CN101449118A CN 101449118 A CN101449118 A CN 101449118A CN A200780018084X A CNA200780018084X A CN A200780018084XA CN 200780018084 A CN200780018084 A CN 200780018084A CN 101449118 A CN101449118 A CN 101449118A
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- heat absorption
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D29/00—Arrangement or mounting of control or safety devices
- F25D29/005—Mounting of control devices
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Other Air-Conditioning Systems (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The present invention provides a refrigeration device where a refrigeration expansion valve, a refrigeration heat exchanger, a compressor (11), and an outdoor heat exchanger are interconnected in sequence and that has a refrigerant circuit for performing a vapor compression refrigeration cycle. A suction pressure sensor (25) is attached to a suction tube (61) of the compressor (11) via heat absorption piping (90). The heat absorption piping (90) is connected to a discharge tube (64) of the compressor (11) via a heat transmission member (91).The length of the heat absorption piping (90) is set not less than a predetermined minimum length that is longer as the temperature of vapor in the refrigeration heat exchanger is lower.
Description
Technical field
[0001] the present invention is about refrigerating plant with the refrigerant loop of carrying out the steam compression type freeze cycle, particularly about the refrigerating plant of the installation constitution of the suction pressure inductor of the suction pressure of measuring compressing mechanism.
Background technology
[0002] up to now, comprise the refrigerant loop of carrying out freeze cycle, the refrigeration or the freezing refrigerating plant that carry out in the freezer have been well-known (for example patent documentation 1).
[0003] refrigerating plant of patent documentation 1, it is freezing with cooling heat exchanger, a rudimentary side compressor, a senior side compressor, outdoor heat converter and freezing expansion valve to be linked in sequence.In the refrigerant loop, by a rudimentary side compressor and a senior side compressor two stages of compression refrigerant, at outdoor heat converter heat release condensation liquefaction.The refrigerant that has liquefied is crossed the freezing cooling heat exchanger of using at above-mentioned freezing expansion valve expansion flow, absorbs heat the air in freezer, for example ,-30 ℃ of evaporations, will be cooled to-20 ℃ in the freezer.And the refrigerant after the evaporation is inhaled into a rudimentary side compressor again, repeats this circulation later on.
(patent documentation 1) patent disclosure 2004-353996 communique
(inventing problem to be solved)
[0004] yet, the refrigerating plant of above-mentioned patent documentation 1 is provided with to measuring the suction pressure inductor of compressor separately at a rudimentary side compressor and senior side compressor suction line separately.
[0005] concretely, as shown in Figure 5, connected tubule c on the suction line a of compressor, the end of this suction pipe c has formed from the teeth outwards to connecting the screw rod of pressure inductor b.On the other hand, pressure inductor b comprises that inner surface has formed the connecting portion d of nut, is screwed together in by the nut with this connecting portion d on the screw rod of tubule c and is connected in suction line a.
[0006] for this reason, in the above-mentioned refrigerating plant, the evaporating temperature of cooling heat exchanger is below zero centigrade, and this sub-zero refrigerant flows through the words of suction line a, enter moisture freezes in the gap between the screw thread of pressure inductor b and tubule c, the connecting portion d of just possible freezing this inductor b.
[0007], in the past, be to take the countermeasure that filling silica gel stops moisture to enter between the screw thread in this section at this.Yet because need the silica dehydrator time of long period, when having reduced the operating efficiency when installing, because produce the deviation of silica gel occupied state etc., this has just produced the problem that reliability reduces again.
[0008] also has, replace screwing togather of pressure inductor b and tubule c, can adopt the method for soldering.Yet, in this method, must reclaim refrigerant during exchange inductor b, this has just produced the problem that reduces the operating efficiency of maintenance again.
[0009] like this, former preventing freezes to destroy countermeasure, has inadequate problem aspect operation and the reliability.
Summary of the invention
[0010] the present invention, in view of above problem points is invented, it is in the refrigerating plant of the suction pressure inductor that comprises the suction pressure of measuring compressing mechanism that its purpose is levied, during for the installation that improves pressure inductor and the operation during exchange, improve the reliability of this pressure inductor simultaneously.
(for solving the method for problem)
[0011] first invention, in the refrigerant loop 10 that comprises the evaporimeter 16,17, compressing mechanism 11, condenser 13 and expansion mechanism 15a, the 15b that are linked in sequence, also be included as the refrigerating plant of the suction pressure inductor 25 of the suction pressure of measuring above-mentioned compressor structure 11, above-mentioned suction pressure inductor 25 is connected on the suction line 61 of above-mentioned compressor structure 11 with pipe arrangement 90 by the heat absorption that is higher than the temperature of suction line 61 for the temperature of connecting portion 25b that makes this suction pressure inductor 25.
[0012] in this first invention, in the above-mentioned suction line 61, because flow through the refrigerant of above-mentioned evaporimeter 16,17, so, the design temperature of evaporimeter 16,17 low (below 0 ℃), also mobile low temperature refrigerant below 0 ℃ in the suction line 61 of compressing mechanism 11.Therefore, in this first invention, by heat absorption pipe arrangement 90 setting pressure inductors 25, flow through the cold and hot connecting portion 25b that just is not easy to pass to suction pressure inductor 25 of the refrigerant of suction line 61, simultaneously, above-mentioned heat absorption by from heat absorptions such as surrounding airs, makes the temperature of the connecting portion 25b of above-mentioned pressure inductor 25 be higher than 0 ℃ with pipe arrangement 90, prevents freezing of connecting portion 25b.
[0013] second invention is in first invention, above-mentioned heat absorption pipe arrangement 90, and its length forms the temperature of the connecting portion 25b that makes above-mentioned suction pressure inductor 25, owing to environment temperature heats up than the high length of above-mentioned suction line 61 temperature.
[0014] in this second invention, absorb heat from surrounding air with pipe arrangement 90 by heat absorption, the connecting portion 25b from suction line 61 to above-mentioned suction pressure inductor 25 heats up slowly, makes the temperature of the connecting portion 25b of above-mentioned pressure inductor 25 be higher than 0 ℃.
[0015] the 3rd invention is in second invention, and above-mentioned heat absorption is with the minimum length of pipe arrangement 90, is set at the preseting length of the defined elongated along with the reduction of the evaporating temperature of above-mentioned evaporimeter 16,17.
[0016] in this 3rd invention, along with the reduction of the evaporating temperature of above-mentioned evaporimeter 16,17, the temperature that is flowing in the refrigerant of suction line 61 also reduces.Therefore, increase the minimum length of above-mentioned heat absorption by reduction with pipe arrangement 90 along with the evaporating temperature of above-mentioned evaporimeter 16,17, or, make the cold and hot connecting portion 25b that is not easy to pass to suction pressure inductor 25 of this refrigerant along with the temperature step-down of stream at the refrigerant of suction line 61.On the other hand, thus increasing above-mentioned heat absorption increases this heat absorption with the caloric receptivity of pipe arrangement 90 from heat absorptions such as surrounding airs with the area of pipe arrangement 90.
[0017] the 4th invention, in first～the 3rd any one invention, above-mentioned heat absorption is installed in by heat transfer component 91 on high pressure one side line 64 in above-mentioned refrigerant loop 10 with pipe arrangement 90.
[0018] in this 4th invention, the heat by high pressure one side line 64 conducts heat by heat transfer component 91, increases the caloric receptivity of above-mentioned heat absorption with pipe arrangement 90, makes the temperature of the connecting portion 25b of above-mentioned suction pressure inductor 25 be higher than 0 ℃.
[0019] still, high pressure one side line (64) in this 4th invention is to flow than the refrigerant of the refrigerant high pressure that flows through suction line 61 and compare the pipe arrangement of the refrigerant of 0 ℃ of high temperature.
[0020] the 5th invention is that above-mentioned high pressure one side line 64 is bleed pipes 64 of above-mentioned compressor structure 11 in the 4th invention.
[0021] above-mentioned heat absorption from the caloric receptivity of high pressure one side line 64 by heat transfer component 91 acceptance, is that the temperature of this high pressure one side line 64 is got over Gao Yueda with pipe arrangement 90.Therefore, in the 5th invention, be by above-mentioned heat absorption being connected with the bleed pipe 64 of the compressing mechanism 11 of high temperature by heat transfer component 91 with pipe arrangement 90, increasing the caloric receptivity of this heat absorption really with pipe arrangement 90.
-invention effect-
[0022] according to above-mentioned first invention because heat absorption is when, flowing through refrigerant cold and hot of suction line 61 with pipe arrangement 90 and just be not easy to pass to the connecting portion 25b of suction pressure inductor 25, above-mentioned heat absorption with pipe arrangement 90 by from heat absorptions such as surrounding airs.Its result, the design temperature of evaporimeter 16,17 low (below 0 ℃) is even if the situation of the low temperature refrigerant below 0 ℃ that flows in the suction line 61 also can make the temperature of connecting portion 25b of above-mentioned suction pressure inductor 25 higher than 0 ℃.Thus, just can prevent suction pressure inductor 25 connecting portion 25b freeze breakage, so improved the reliability of suction pressure inductor 25.
[0023] also has, do not need filling gel or soldering, also can carry out breakage and prevent, prevent that with former breakage measure from comparing, during the installation that improved suction pressure inductor 25 and the operation during exchange.
[0024] also has, according to above-mentioned second invention, because be with above-mentioned heat absorption pipe arrangement 90, form the temperature of the connecting portion 25b that makes above-mentioned suction pressure inductor 25, by the above-mentioned suction line 61 intensifications length higher than environment temperature, from the surrounding air heat absorption, this heat absorption usefulness pipe arrangement 90 slowly can the connecting portion 25b from suction line 61 to above-mentioned suction pressure inductor 25 heats up with pipe arrangement 90 for above-mentioned heat absorption.Its result makes the temperature of the connecting portion 25b of above-mentioned pressure inductor 25 be higher than 0 ℃.
[0025] also has, according to above-mentioned the 3rd invention, because be with the minimum length of above-mentioned heat absorption with pipe arrangement 90, be set at along with the reduction of the evaporating temperature of above-mentioned evaporimeter 16,17 and the preseting length of elongated defined, along with the reduction of the evaporating temperature of above-mentioned evaporimeter 16,17, can make the cold and hot connecting portion 25b that is not easy to pass to suction pressure inductor 25 of this refrigerant.Simultaneously, increase above-mentioned heat absorption and can increase this heat absorption with the caloric receptivity of pipe arrangement 90 from heat absorptions such as surrounding airs with the area of pipe arrangement 90.Thus, corresponding to the design temperature of evaporimeter 16,17, can make the temperature of the connecting portion 25b of above-mentioned suction pressure inductor 25 be higher than 0 ℃ really.
[0026] also have, according to above-mentioned the 4th invention, above-mentioned heat absorption can be passed through the heat that heat transfer component 91 absorbs high pressure one side line 64 in refrigerant loops 10 with pipe arrangement 90, just can increase the caloric receptivity of above-mentioned heat absorption with pipe arrangement 90.Thus, just can make the temperature of the connecting portion 25b of above-mentioned suction pressure inductor 25 be higher than 0 ℃.
[0027] also has, according to the 5th invention, above-mentioned heat absorption because the bleed pipe 64 of above-mentioned compressor structure 11 is a high temperature, can increase the caloric receptivity of above-mentioned heat absorption with pipe arrangement 90 with the heat of pipe arrangement 90 by the bleed pipe 64 of heat transfer component 91 absorption compressing mechanisms 11 really.Thus, just can make the temperature of the connecting portion 25b of above-mentioned suction pressure inductor 25 be higher than 0 ℃.
The simple declaration of accompanying drawing
[0028] Fig. 1 is the piping diagram in the refrigerant loop of the related refrigerating plant of expression embodiment.
Fig. 2 is the approximate three-dimensional map of the installation constitution of the related suction pressure inductor of expression embodiment.
Fig. 3 is the evaporating temperature of the related refrigeration heat exchanger of expression embodiment and the graph of a relation that heat absorption concerns with piping length.
Fig. 4 is the piping diagram of the loop direction of refrigerant in the cooling running of the related refrigerating plant of expression embodiment.
Fig. 5 is the summary pie graph of the installation constitution of the suction pressure inductor before the expression.
(symbol description)
[0029] 1 refrigerating plant
10 refrigerant loops
11 compressors (compressing mechanism)
13 outdoor heat converters (condenser)
25 suction pressure inductors
The 25a connecting portion
61 suction lines
64 bleed pipes (high pressure one side line)
90 heat absorption pipe arrangements
91 heat transfer components
The specific embodiment
[0030] below, describes embodiments of the present invention in detail based on accompanying drawing.
[0031] embodiments of the present invention as shown in Figure 1, are the refrigerating plants 1 of cooling cooling chamber, comprise outdoor unit 2, refrigerating unit 3 and controller 100.Above-mentioned outdoor unit 2, when being provided with without, above-mentioned refrigerating unit 3 is arranged in the cooling chamber.
[0032] in the above-mentioned refrigerating plant 1, is provided with outdoor loop 20 in the above-mentioned outdoor unit 2, is provided with freezer inner looping 30 in the above-mentioned refrigerating unit 3.In the refrigerating plant 1, when gas end one side in above-mentioned outdoor loop 20 and gas one side of above-mentioned freezer inner looping 30 are connected by gas communication pipe arrangement 22, the distolateral refrigerant loop 10 that connects and composes the steam compression type freeze cycle by liquid communication pipe arrangement 21 of the liquid of the distolateral and above-mentioned freezer inner looping 30 of the liquid in above-mentioned outdoor loop 20.
[0033]＜outdoor unit 〉
On the outdoor loop 20 of above-mentioned outdoor unit 2, be provided with compressor 11, outdoor heat converter 13, receiver 14, outdoor expansion valve 45, cool-heat-exchanger 50 and branch's expansion valve 46.Have again, on the outdoor loop 20, be provided with four-port conversion value 12, liquid draught excluder 53 and gas draught excluder 54.In this outdoor loop 20, liquid draught excluder 53 is connecting an end of aforesaid liquid contact pipe arrangement 21, is connecting an end of above-mentioned gas contact pipe arrangement 22 on the gas draught excluder 54.
[0034] above-mentioned compressor 11, are scroll compressors, and by anti-phase (inverter) control, running capacity constitutes variable.On suction one side of above-mentioned compressor 11, connecting an end of suction line 61, the other end of this suction line 61 is connected in four-port conversion value 12.On ejection one side of compressor 11, connecting an end of bleed pipe 64, the other end of this bleed pipe 64 is connecting four-port conversion value 12.
[0035] above-mentioned outdoor heat converter 13, intersection fin type fin comb heat exchanger carries out the heat exchange between refrigerant and the outdoor air, constitutes condenser.One end of outdoor heat converter 13 is connected in four-port conversion value 12.On the other hand, the other end of outdoor heat converter 13 is connected in receiver 14 by first liquid line 81.On this first liquid line 81, be provided with only permission from the non-return valve CV-1 of outdoor heat converter 13 to receiver 14 mobile refrigerants.The bottom of receiver 14 is connecting an end of second liquid line 82.
[0036] above-mentioned refrigerant heat exchanger 50 is heat-exchangerss of the plate type, carries out the heat exchange between refrigerant and the refrigerant, comprises the first stream 50a and the second stream 50b.The inlet side of the first stream 50a of above-mentioned refrigerant heat exchanger 50 is connecting the other end of aforesaid liquid pipe 82, and outlet one side of the first stream 50a is connecting the other end of the 3rd liquid line 83.The other end of aforesaid liquid pipe 83 is connected in an end of liquid communication pipe arrangement 21 by liquid draught excluder 53.On above-mentioned the 3rd liquid line 83, be provided with and only allow the non-return valve CV-2 to liquid draught excluder 53 mobile refrigerants from the first stream 50a.
[0037] on above-mentioned the 3rd liquid line 83, upper reaches one side of above-mentioned non-return valve CV-2 is connecting branch's liquid line 84, and the other end of this branch's liquid line 84 is connected in the inlet side of the second stream 50b of above-mentioned refrigerant heat exchanger 50.Also have, on the above-mentioned branch liquid line 84, be provided with branch's expansion valve 46.But this branch's expansion valve 46 is electric expansion valves of free adjustment aperture.
[0038] the second stream 50b of above-mentioned refrigerant heat exchanger 50 exports a side, is connecting an end of playpipe 85.The other end of this playpipe 85 is connected between the four-port conversion value 12 and compressor 11 of suction line 61.
[0039] in above-mentioned the 3rd liquid line 83, between non-return valve (CV-2) and the liquid draught excluder 53, connecting an end of the 4th liquid line 88.The other end of the 4th liquid line 81 is connected between the non-return valve CV-1 and receiver 14 of first liquid line 81.Also have, on the 4th liquid line 88, be provided with only permission from the non-return valve CV-3 of the 3rd liquid line 83 to receiver 14 mobile refrigerants.
[0040] on the above-mentioned branch liquid line 84, between above-mentioned the 3rd liquid line 83 and branch's expansion valve 46, an end that connects the 5th liquid line 89, the other end of the 5th liquid line 89 is arranged in first liquid line 81 between outdoor heat converter 13 other ends and the non-return valve (CV-1).Also have, on the 5th liquid line 89, be provided with outdoor expansion valve 45.
[0041] connected to have connected on bleed pipe 64, the second holes to have connected on outdoor heat converter 13, the four holes on suction line 61, the three holes on above-mentioned four-port conversion value 12, the first holes and connected gas draught excluder 54.And, above-mentioned four-port conversion value 12 constitutes first state (the solid line state shown in Fig. 1) that can switch first hole and the 3rd hole intercommunication, second hole and the 4th hole intercommunication mutually and second state (the dotted line state shown in Fig. 1) of first hole and the 4th hole intercommunication, second hole and the 3rd hole intercommunication.
[0042] on the above-mentioned outdoor loop 20, is provided with separator 70, oil return pipe 71.
[0043] above-mentioned separator 70 is arranged on the bleed pipe 64, is for separate the device of refrigerator oil from the gas of compressor 11 ejections.On the separator 70, connecting an end of first oil return pipe 71, the other end of this first oil return pipe 71 is connected between the connecting portion and compressor 11 of playpipe 85 of suction line 61.Also have, on the above-mentioned oil return pipe 71, be provided with to adjusting the capillary 72 of refrigerator oil flow.
[0044] on the above-mentioned outdoor loop 20, various inductors 19,23,24,25,51 and pressure switch 95a, 95b have been installed.Concretely, on the suction line 61 of compressor 11, between the connecting portion of the connecting portion of playpipe 85 and oil return pipe 71, be provided with inlet temperature inductor 24 and suction pressure inductor 25 in order.This suction pressure inductor 25 describes in detail in the back, as feature of the present invention, is to connect with pipe arrangement 90 by heat absorption on suction line 61.Also have, on ejection one side of compressor 11, be provided with ejection pressure inductor 23 and ejection temperature inductor 19.Also have, outlet one side of the first stream 50a of refrigerant heat exchanger 50 is provided with temperature inductor 51.
[0045] also has, on the above-mentioned outdoor unit 2, be provided with outer temperature inductor 13a and outdoor fan 13f.13f send outdoor air to outdoor heat converter 13 by this outdoor fan.
[0046]＜refrigerating unit 〉
On the freezer inner looping 30 of above-mentioned refrigerating unit 3, be provided with 16,17 and two draining base plate heating units of two refrigeration heat exchangers (drain pan heater) 26,27 respectively.
[0047] the above-mentioned heat exchanger 16,17 that respectively refrigerates all is an intersection fin type fin comb heat exchanger, carries out the heat exchange between the air in refrigerant and the cooling chamber, constitutes evaporimeter.Refrigerate an end of heat exchanger 16,17, be connected in by pipe arrangement and respectively refrigerate expansion valve 15a, 15b.On the other hand, on the above-mentioned other end that respectively refrigerates heat exchanger 16,17, connecting each the gas one pipe arrangement 22a of side branch, 22b respectively, the other end interflow of this gas one pipe arrangement 22a of side branch, 22b is connected in above-mentioned gas one side contact pipe arrangement 22.
[0048] above-mentioned expansion valve 15a, the 15b of respectively refrigerating is to constitute the electric expansion valve that can freely adjust aperture, constitutes expansion mechanism.On the above-mentioned refrigeration heat exchanger 16,17, be provided with the first refrigerant temperature inductor 16b, 17b respectively, each refrigerates on the other end of heat exchanger 16,17, is provided with the second refrigerant temperature inductor 18a, 18b respectively.The above-mentioned first refrigerant temperature inductor 16b, 17b are the inductors of measuring the evaporator refrigerant temperature of refrigeration heat exchanger 16,17.Above-mentioned refrigeration expansion valve 15a, 15b, constitute in the cooling running, exceed temperature (for example 5 ℃) the adjustment aperture of defined for the temperature that the second refrigerant temperature inductor 18a, 18b are measured than the evaporator refrigerant temperature of the first refrigerant temperature inductor 16b, 17b mensuration.
[0049] above-mentioned draining base plate heating unit 26,27 is arranged on the draining base plate, and the refrigerant of HTHP flows through this draining base plate of heating, prevents draining base plate extension frost or icing thus.On one end of above-mentioned each draining base plate heating unit 26,27, connect an end of each liquid one side branch pipe arrangement (21a, 21b) respectively, the other end interflow of this each the liquid one pipe arrangement 21a of side branch, 21b is connected in the other end of aforesaid liquid one side contact pipe arrangement 21.On the other hand, the other end of above-mentioned draining base plate heating unit 26,27 is connected in the end of above-mentioned refrigeration expansion valve 15a, 15b.
[0050] also has, on the above-mentioned refrigerating unit 3, be provided with temperature inductor 16a, 16b and cooling chamber internal fan 16f, 17f in the cooling chamber.Respectively refrigerate the air that heat exchanger 16,17 send in the cooling chamber by this cooling chamber internal fan 16f, 17f to above-mentioned.
[0051]＜controller 〉
Above-mentioned controller 100 is arranged on the conversion of the various valves in the above-mentioned refrigerant loop 10 or aperture adjustment etc., when control keeps the cooling running work of cooling chamber design temperature, also controls the defrosting running motion of cooling chamber.
[0052]＜installation constitution of suction pressure inductor 〉
Next, based on the installation constitution of the suction pressure inductor 25 of accompanying drawing 1～Fig. 3 more detailed description feature of the present invention.
When [0053] cooling of refrigerating plant 1 is turned round, flow through suction line 61 at refrigeration heat exchanger 16,17 vaporized refrigerants, so, the evaporator refrigerant temperature of refrigeration heat exchanger 16,17 is low, and the refrigerant temperature that flows through suction line 61 just worries that in the words below 0 ℃ the connecting portion 25b of suction pressure inductor 25 freezes breakage.At this, as feature of the present invention, above-mentioned suction pressure inductor 25, as shown in Figures 1 and 2, be connected on the suction line 61 of compressor 11 with pipe arrangement 90, have again by heat absorption, above-mentioned heat absorption is connected in the bleed pipe 64 of compressor 11 with pipe arrangement 90 by heat transfer component 91.
[0054] just, above-mentioned heat absorption is with pipe arrangement 90, is temperature for the connecting portion 25b that makes suction pressure inductor 25 temperature that is higher than suction line 61.
[0055] concretely, as shown in Figure 2, the centre of the suction line 61 of compressor 11 has connected the end of heat absorption with pipe arrangement 90.This heat absorption is with pipe arrangement 90, forms the 20cm length thinner than suction line 61, and four foldings are for small-sized.Also have, the above-mentioned heat absorption other end of pipe arrangement 90, peripheral part has formed not shown screw rod.Above-mentioned suction pressure inductor 25 by inductor 25a itself and connecting portion 25b, has formed not shown nut on the inner surface of connecting portion 25b.And above-mentioned suction pressure inductor 25, the nut thread by connecting portion 25b are screwed on the other end of heat absorption with pipe arrangement 90, being installed in heat absorption with on the pipe arrangement 90.Also have, above-mentioned heat absorption is connecting the hole tubule 90a of the L font that comprises correction hole 26 with the other end one side of pipe arrangement 90.
[0056] above-mentioned heat transfer component 91, as shown in Figure 2, forming section is the tabular of L font.And transverse direction one end of above-mentioned heat transfer component 91 is fixed on a dirty side of the separator 70 of bleed pipe 64, and on the other hand, the other end is fixed near the other end one side (the connecting portion 25b of suction pressure inductor 25) of heat absorption with pipe arrangement 90.Also have, lower end one side of above-mentioned heat transfer component 91 is fixed on the hole with on the tubule 90a.Still, this heat transfer component 91 has the function of the heat absorption supported with the support component of pipe arrangement 90.
[0057] next, based on Fig. 3 the experimental result of above-mentioned heat absorption with pipe arrangement 90 length is described.
[0058] Fig. 3 is that the connecting portion 25b of the evaporating temperature of expression refrigeration heat exchanger 16,17 and suction pressure inductor 25 becomes 10 ℃ heat absorption with the figure of the relation of the length of pipe arrangement 90.Among Fig. 3, conduits structure A, be will absorb heat without heat transfer component 91 to be connected to structure on the bleed pipe 64 of compressor 11 with pipe arrangement 90, conduits structure B is will absorb heat with heat transfer component 91 to be connected to structure on the bleed pipe 64 of compressor 11 with pipe arrangement 90 as present embodiment.
[0059] among the conduits structure A, the connecting portion 25b of suction pressure inductor 25 becomes the length of 10 ℃ heat absorption usefulness pipe arrangement 90, the evaporating temperature of refrigeration heat exchanger 16,17 is 20cm when being-10 ℃, be 48cm during for-20 ℃, be 57cm during for-40 ℃, so, learn that the reduction along with evaporating temperature is necessary lengthening.This be because, reduction along with the evaporating temperature that refrigerates heat exchanger 16,17, flow through the also step-down of temperature of the refrigerant of suction line 61, be necessary to make this part cold and hot connecting portion 25b that is not easy by suction pressure inductor 25, on the other hand, increasing above-mentioned heat absorption increases this heat absorption with the area of pipe arrangement 90 and also is necessary with the heat of pipe arrangement 90 from the surrounding air absorption.
[0060] on the other hand, among the conduits structure B, the connecting portion 25b of suction pressure inductor 25 becomes the length of 10 ℃ heat absorption usefulness pipe arrangement 90, the evaporating temperature of refrigeration heat exchanger 16,17 is 10cm when being-10 ℃, being 25cm during for-20 ℃, is 32cm during for-40 ℃, and A is the same with conduits structure, learn when reduction along with evaporating temperature is necessary to extend, compare with the situation of conduits structure A in the identical evaporating temperature and can shorten length.This is because above-mentioned heat absorption is by bleed pipe 64 heat absorptions of heat transfer component 91 from the compressor 11 of high temperature with pipe arrangement 90, compares with the situation of only absorbing heat from surrounding air, can increase the caloric receptivity of this heat absorption with pipe arrangement 90 really.
[0061] still, the temperature of the connecting portion 25b of suction pressure inductor 25, as long as in order not make this connecting portion 25b freeze to be higher than 0 ℃, still, in this experiment, research be length when reaching 10 ℃.This be because, can make the temperature of connecting portion 25b be higher than 0 ℃ length as long as set the length of absorbing heat with pipe arrangement 90, even if owing to the change of cooling load descends for the moment, also can making the temperature of connecting portion 25b return to really, the evaporating temperature of refrigeration heat exchanger 16,17 is higher than 0 ℃.Just like this, also considered the load change of refrigerating plant 1, set the minimum length of heat absorption as shown in Figure 3 with pipe arrangement 90.
[0062] and, in the present embodiment, as described later, the evaporating temperature of refrigeration heat exchanger 16,17 be-10 ℃, so saying among the conduits structure B absorbs heat is necessary to make more than the 10cm with pipe arrangement 90.Therefore, heat absorption is formed random length 20cm more than the 10cm with pipe arrangement 90.
[0063]-running work-
Next, based on Fig. 4 work in the cooling running of refrigerating plant 1 of present embodiment is described.
[0064] in the cooling of above-mentioned refrigerating plant 1 running, as shown in Figure 4, by the control of controller 100, the four-port conversion value 12 in outdoor loop 20 is set at first state, outdoor expansion valve 45 contract fullys.And, under this state, compressor 11 runnings, refrigeration expansion valve 15a, 15b and branch's expansion valve 46 are controlled to be suitable aperture, and refrigerant circulates along direction shown in the solid arrow of Fig. 4.Still, the design temperature with cooling chamber in this cooling running is set at for example 2 ℃.
[0065] from the refrigerant of above-mentioned compressor 11 ejections, is sent to outdoor heat converter 13 by four-port conversion value 12 from bleed pipe 64.In the outdoor heat converter 13, refrigerant is to outdoor air heat release condensation.At outdoor heat converter 13 chilled refrigerants, flow through first liquid line 81, flow to second liquid line 82 by receiver 14, flow through the first stream 50a of refrigerant heat exchanger 50.Flow through the liquid coolant of the first stream 50a, flow through the 3rd liquid line 83, its part shown in the dotted line as shown in Figure 4, flows through branch's liquid line 84 as branch's refrigerant, flows into the second stream 50b of above-mentioned refrigerant heat exchanger 50 in 46 decompressions of branch's expansion valve.Thus, flow through the refrigerant of the first stream 50a, carry out heat exchange with the branch's refrigerant that flows through the second stream 50b, for example be cooled to 15 ℃ after, flow through liquid communication pipe arrangement 21 from the 3rd liquid line (83) by liquid draught excluder 53, flow into freezer inner looping 30.Also have, branch's refrigerant evaporation of the second stream 50b sprays by the suction line 61 of playpipe 85 to compressor 11.
[0066] in the freezer inner looping 30,15 ℃ refrigerant is diverted to each liquid difference pipe arrangement 21a, 21b and flows through each draining base plate heating unit 26,27, prevent draining base plate 56,57 frost.
[0067] liquid coolant that flows out from draining base plate heating unit 26,27, puffing when refrigerating expansion valve 15a, 15b imports and respectively refrigerates heat exchanger 16,17 by each.This respectively refrigerates in the heat exchanger 16,17, and refrigerant is from the absorption of air heat of cooling chamber, in evaporating temperature evaporation for example-10 ℃.In the refrigerating unit 3, the air that has been cooled at refrigeration heat exchanger 16,17 offers in the cooling chamber, and the temperature of keeping in the cooling chamber is 2 ℃ of design temperatures.
[0068] flow through the above-mentioned refrigerant that respectively refrigerates heat exchanger 16,17, flow through each the gas one pipe arrangement 22a of side branch, 22b after, converge at gas one side contact pipe arrangement 22.Thereafter, the above-mentioned gas refrigerant flows through gas one side contact pipe arrangement 22 and flows through suction line 61 by four-port conversion value 12, is inhaled into compressor 11 compressions.
[0069] at this, in the suction line 61, the refrigerant of the pact-10 of above-mentioned refrigeration heat exchanger 16,17 evaporations ℃ flows, but, among the present invention, suction pressure inductor 25 is connected in suction line 61 by heat absorption with pipe arrangement 90, have again, heat absorption is connected by heat transfer component 91 with the bleed pipe 64 of pipe arrangement 90 and compressor 11, so the connecting portion 25b of suction pressure inductor 25 can not freeze breakage.Have again, as shown in Figure 3, as long as the evaporating temperature of refrigeration heat exchanger 16,17 is more than-23 ℃, the temperature of the connecting portion 25b of suction pressure inductor 25 really can be more than 10 ℃, even if cooling load change in the cooling running also can make the temperature of connecting portion 25b be higher than 0 ℃ really.
[0070] still, above-mentioned refrigerating plant 1 constitutes batch (-type) and stops above-mentioned cooling running, and running defrosts.Work in this defrosting running, not shown, but four-port conversion value 12 is set at second state, refrigeration expansion valve 15a, 15b are full-gear, branch's expansion valve 46 is a full-shut position, suitably controls outdoor expansion valve 45, and the contrary circulation of backward circulation was antifreeze when refrigerant was deceived the cooling operation.
[0071] concretely, the ejection gas coolant of compressor 11, respectively refrigerate heat exchanger 16,17 and each draining base plate heating unit 26,27 to flowing through, each refrigerates heat exchanger 16,17 or attached to the liquefaction of condensing of the white heat release on the draining base plate, flows through the 4th liquid line 88 in outdoor loop 20.Thereafter, refrigerant flows through liquid communication pipe arrangement 21 and imports outdoor loop 20, flows through the 4th liquid line 88, flows through the first stream 50a of receiver 14 and refrigerant heat exchanger 50.And, refrigerant, the outdoor expansion valve 45 when flowing through the 5th liquid line 89 expands and condenses at outdoor heat converter 13, sucks compressor 11.
[0072]-effect of embodiment-
Above-mentioned refrigerating plant 1, by heat absorption with pipe arrangement 90 make the refrigerant that flows through above-mentioned suction line 61 cold and hot when being not easy to pass to the connecting portion 25b of suction pressure inductor 25, above-mentioned heat absorption can be from surrounding air or bleed pipe 64 heat absorptions with pipe arrangement 90 from surrounding air or above-mentioned heat absorption with pipe arrangement 90.Its result ,-10 ℃ refrigerant of refrigeration heat exchanger 16,17 evaporations also flows through suction line 61, can make the connecting portion 25b of suction pressure inductor 25 be higher than 0 ℃.Thus, just can prevent suction pressure inductor 25 connecting portion 25b freeze breakage, improved the reliability of suction pressure inductor 25.Also have, do not need to carry out filling silica gel or soldering, just can carry out breakage and prevent, prevent that with former breakage countermeasure from comparing, during the installation that improved suction pressure inductor 25 and the operation in when exchange.
[0073] also have, above-mentioned heat absorption is to absorb the heat of the bleed pipe 64 in refrigerant loop 10 by heat transfer component 91 with pipe arrangement 90, so just can increase the caloric receptivity of above-mentioned heat absorption with pipe arrangement 90.Thus, can make the connecting portion 25b of suction pressure inductor 25 be higher than 0 ℃.
[0074] also have, above-mentioned heat absorption is the heats that absorb the bleed pipe 64 in refrigerant loop 10 by heat transfer component 91 with pipe arrangement 90, again because the bleed pipe 64 of above-mentioned compressor structure 11 is a high temperature, so can increase the caloric receptivity of above-mentioned heat absorption with pipe arrangement 90 really.Thus, can make the connecting portion 25b of suction pressure inductor 25 be higher than 0 ℃.
[0075] " other embodiment "
Above-mentioned embodiment can also constitute following mode.
[0076] refrigerating plant 1 of above-mentioned embodiment, having formed length is the heat absorption pipe arrangement 90 of 20cm, is connected in bleed pipe 64 by heat transfer component 91 again, but, heat transfer component 91 is not set, just heat absorption is set with pipe arrangement 90, carry out freezing preventing and also be fine by defined length.Just, as shown in Figure 3, even if be connected in pipe arrangement 90 among the conduits structure A of bleed pipe 64 will not absorbing heat, length setting with pipe arrangement 90 is that evaporating temperature is when being-10 ℃ more than the 20cm as long as will absorb heat, in the time of-30 ℃ more than the 48cm, the length of setting along with the evaporating temperature reduction is long more, just can make the connecting portion 25b of suction pressure inductor 25 arrive more than 10 ℃.Therefore, be longer than this more than length with the length of pipe arrangement 90, do not need heat absorption is connected in bleed pipe 64 with pipe arrangement 90, also can make connecting portion 25b be higher than 0 ℃ really and prevent to freeze breakage as long as set heat absorption.
[0077] just, above-mentioned heat absorption is with pipe arrangement 90, and the temperature that forms the connecting portion 25b of above-mentioned suction pressure inductor 25 is got final product by the heat up length of above-mentioned suction line 61 of environment temperature.And above-mentioned heat absorption is with the minimum length of pipe arrangement 90, as long as be set at along with the reduction of the evaporating temperature of above-mentioned evaporimeter 16,17 elongated.
[0078] also have, in this case, heat absorption pipe arrangement 90, can be arranged on any position, still, be arranged near the bleed pipe 64 position with pipe arrangement 90 as long as for example will absorb heat, the heat of the bleed pipe 64 of high temperature is by transfer of air, and increase that just can be bigger recepts the caloric.
[0079] also has, in the above-mentioned embodiment, the length of pipe arrangement 90 of heat absorption as shown in Figure 3, just individual example, heat absorption is with the length of pipe arrangement 90, and best is according to the suitable settings such as temperature of the bleed pipe 64 that the thermal conductivity of heat absorption with the temperature conditions around the pipe arrangement 90, heat transfer component 91, compressor 11 are set.Also have, the cooling load change of refrigerating plant 1 is little, and under the certain situation of the evaporating temperature of evaporimeter 16,17, the temperature that heat absorption can also be set the connecting portion 25b of suction pressure inductor 25 for the length of pipe arrangement 90 becomes for example 1 ℃ length.
[0080] refrigerating plant 1 of above-mentioned embodiment has carried out the freeze cycle of one-level compression refrigerant, and refrigerating plant has the freezing heat exchanger of using of freezing cooling chamber, also can be the device that carries out the freeze cycle of secondary compression refrigerant.In this case, the refrigerant temperature of suction line of compressor that flows through a rudimentary side is very low, so the pressure inductor of measuring this low temperature refrigerant pressure can be installed on suction line with pipe arrangement by heat absorption.Have again, this heat absorption with pipe arrangement can also be by heat transfer component and above-mentioned refrigerant loop high pressure one side line or the bleed pipe of the ejection refrigerant of mobile low pressure one side compressor be connected.
[0081] also has, for outdoor loop with senior side compressor, connect freezing with a heat exchanger and a rudimentary side compressor refrigerating circuit and have freezing refrigeration circuit and be connected in parallel with heat exchanger, the compressor of the compressor of high pressure one side and low pressure one side all sucks under the situation of the refrigerant below 0 ℃, can connect the suction pressure inductor of the suction line of each compressor by heat absorption with pipe arrangement.
[0082] also have, the refrigerating plant 1 of above-mentioned embodiment has been connected to heat absorption on the bleed pipe 64 of compressor with pipe arrangement 90, still, can also be connected in other high pressure one side line in refrigerant loop 10.Concrete, shown in first to the 3rd liquid line 81,82,83.
[0083] also have, the refrigerating plant 1 of above-mentioned embodiment, compressing mechanism 11 is made of a compressor 11, and still, compressing mechanism 11 can also be many compressors that are connected in parallel.
[0084] still, above embodiment is best example in essence, and the present invention is not intended to limit its suitable thing, or the scope of its purposes.
The possibility of utilizing on-the industry-
[0085] as discussed above, the present invention is for comprising the suction of measuring compressing mechanism The refrigerating plant that enters the suction pressure inductor of pressure is useful.
Claims (5)
1. refrigerating plant, when comprising the refrigerant loop (10) of the evaporimeter (16,17), compressing mechanism (11), condenser (13) and the expansion mechanism (15a, 15b) that are linked in sequence, also be included as the suction pressure inductor (25) of the suction pressure of measuring above-mentioned compressor structure (11), it is characterized in that:
Above-mentioned suction pressure inductor (25) is connected on the suction line (61) of above-mentioned compressor structure (11) with pipe arrangement (90) by the heat absorption that is higher than the temperature of suction line (61) for the temperature of connecting portion (25b) that makes this suction pressure inductor (25).
2. refrigerating plant according to claim 1 is characterized in that:
Above-mentioned heat absorption is with pipe arrangement (90), and its length forms the temperature of connecting portion (25b) of above-mentioned suction pressure inductor (25) owing to environment temperature heats up than the high length of temperature of above-mentioned suction line (61).
3. refrigerating plant according to claim 2 is characterized in that:
Above-mentioned heat absorption is with the minimum length of pipe arrangement (90), is set at the preseting length of the defined elongated along with the reduction of the evaporating temperature of above-mentioned evaporimeter (16,17).
4. refrigerating plant according to claim 1 is characterized in that:
Above-mentioned heat absorption is installed in by heat transfer component (91) on high pressure one side line (64) in above-mentioned refrigerant loop (10) with pipe arrangement (90).
5. refrigerating plant according to claim 4 is characterized in that:
Above-mentioned high pressure one side line (64) is the bleed pipe (64) of above-mentioned compressor structure (11).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006139040A JP4082434B2 (en) | 2006-05-18 | 2006-05-18 | Refrigeration equipment |
| JP139040/2006 | 2006-05-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101449118A true CN101449118A (en) | 2009-06-03 |
Family
ID=38723269
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200780018084XA Pending CN101449118A (en) | 2006-05-18 | 2007-05-17 | Refrigeration device |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20090188276A1 (en) |
| EP (1) | EP2019273A1 (en) |
| JP (1) | JP4082434B2 (en) |
| KR (1) | KR20090013222A (en) |
| CN (1) | CN101449118A (en) |
| AU (1) | AU2007252631A1 (en) |
| WO (1) | WO2007135957A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107109292A (en) * | 2015-01-19 | 2017-08-29 | 出光兴产株式会社 | Lubricating oil composition |
| CN111855735A (en) * | 2020-08-06 | 2020-10-30 | 兰州理工大学 | Efficient and accurate measuring device for salt expansion and frost heaving of salt solution |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5585189B2 (en) * | 2010-04-30 | 2014-09-10 | ダイキン工業株式会社 | Air conditioner |
| JP5821384B2 (en) * | 2011-08-08 | 2015-11-24 | ダイキン工業株式会社 | Sensor mounting structure |
| JP2014163548A (en) * | 2013-02-22 | 2014-09-08 | Fujitsu General Ltd | Air conditioning apparatus |
| CN103759477B (en) * | 2014-01-07 | 2016-06-29 | 广东美芝制冷设备有限公司 | Refrigerating circulatory device |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50148Y1 (en) * | 1970-08-12 | 1975-01-06 | ||
| JPS5116317Y1 (en) * | 1970-08-13 | 1976-04-28 | ||
| JPH0431689A (en) * | 1990-05-24 | 1992-02-03 | Hitachi Ltd | Scroll compressor and freezing cycle with scroll compressor |
| JPH09329517A (en) * | 1996-06-10 | 1997-12-22 | Fuji Koki:Kk | Pressure detecting device |
| JP2002048665A (en) * | 2000-07-31 | 2002-02-15 | Yamatake Corp | Steam jacket structure of pressure-measuring apparatus |
| JP2004301456A (en) * | 2003-03-31 | 2004-10-28 | Toyota Industries Corp | Refrigerating cycle apparatus and equipment for the same |
| JP2004353996A (en) | 2003-05-30 | 2004-12-16 | Daikin Ind Ltd | Refrigerating equipment |
-
2006
- 2006-05-18 JP JP2006139040A patent/JP4082434B2/en active Active
-
2007
- 2007-05-17 KR KR1020087029682A patent/KR20090013222A/en not_active Application Discontinuation
- 2007-05-17 EP EP07743586A patent/EP2019273A1/en not_active Withdrawn
- 2007-05-17 US US12/301,214 patent/US20090188276A1/en not_active Abandoned
- 2007-05-17 AU AU2007252631A patent/AU2007252631A1/en not_active Abandoned
- 2007-05-17 CN CNA200780018084XA patent/CN101449118A/en active Pending
- 2007-05-17 WO PCT/JP2007/060151 patent/WO2007135957A1/en active Application Filing
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107109292A (en) * | 2015-01-19 | 2017-08-29 | 出光兴产株式会社 | Lubricating oil composition |
| CN107109292B (en) * | 2015-01-19 | 2021-03-26 | 出光兴产株式会社 | Lubricating oil composition |
| CN111855735A (en) * | 2020-08-06 | 2020-10-30 | 兰州理工大学 | Efficient and accurate measuring device for salt expansion and frost heaving of salt solution |
Also Published As
| Publication number | Publication date |
|---|---|
| US20090188276A1 (en) | 2009-07-30 |
| JP4082434B2 (en) | 2008-04-30 |
| AU2007252631A1 (en) | 2007-11-29 |
| EP2019273A1 (en) | 2009-01-28 |
| JP2007309586A (en) | 2007-11-29 |
| KR20090013222A (en) | 2009-02-04 |
| WO2007135957A1 (en) | 2007-11-29 |
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