CN104879942A - Refrigerating and heating circulating system - Google Patents
Refrigerating and heating circulating system Download PDFInfo
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- CN104879942A CN104879942A CN201510244299.XA CN201510244299A CN104879942A CN 104879942 A CN104879942 A CN 104879942A CN 201510244299 A CN201510244299 A CN 201510244299A CN 104879942 A CN104879942 A CN 104879942A
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
- F25B31/00—Compressor 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
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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
- F25B41/30—Expansion means; Dispositions thereof
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The invention discloses a refrigerating and heating circulating system. The system comprises a liquid storing device, a compressor, a condenser, an evaporator, a flash evaporator, a first throttling device and a second throttling device; when the refrigerating and heating circulating system runs at a small load condition, a first air absorbing opening is used for charging a high pressure refrigerant into an air injection cavity; an air absorbing cavity of one of two cylinders is communicated with a first exhaust opening to guide the high pressure refrigerant into the air absorbing cavity; when the refrigerating and heating circulating system stably runs in a large-load and ultralow-temperature heating condition, the first air absorbing opening is used for charging a medium pressure refrigerant into the air injection cavity; the air absorbing cavity of one of the two cylinders is communicated with the first exhaust opening to guide the medium pressure refrigerant into the air absorbing cavity; when the refrigerating and heating circulating system runs in other large-load conditions out of the ultralow-temperature heating condition, the air absorbing cavity of one of the two cylinders is communicated with an air outlet. The system can effectively quickly refrigerate and heat.
Description
Technical field
The present invention relates to heating-cooling equipment manufacturing technology field, especially relate to a kind of cooling and warming circulatory system.
Background technology
Point out in correlation technique, due to the difference of external environment condition change, user's request etc., the burden requirement of air-conditioning system is also different, and under the condition of bad environments, user's General Requirements air-conditioning system can realize fast-refrigerating and heat.The load difference of air-conditioning system is large, also has very large difference to the requirement of air-conditioning system and performance.
When air-conditioning system load is large, as ultralow temperature heats, because the specific volume of refrigerant is large, the compressor air suction mass flow of air-conditioning system reduces, significantly reduce except causing compressor heating capacity, meanwhile, because mass flow reduces, oil return difficulty, the heat that refrigerant is taken away reduces, easily cause the compressing mechanism wearing and tearing of compressor and motor reliability to decline, and system energy efficiency is low, under such conditions, adopt the jet compression of twin-stage, effectively can increase gas mass flow, improve system heating capacity and efficiency, and improve compressing mechanism lubrication.
But, when operating mode refrigerating operatons such as centre refrigeration, pressure ratio is little, single stage compress efficiency improves, if also adopt Two-stage Compression, because it has two cylinders to work simultaneously, friction power loss can be caused to increase to be increased soon than cold, also may cause the situation of refrigerant overcompression simultaneously, cause the efficiency of Two-stage Compression to reduce.
In small load condition condition, as easily occurred under middle cryogenic conditions, refrigerating capacity is superfluous, thus causes energy waste, simultaneously in high load working condition condition, as ultralow temperature heats down, easily occur the phenomenon of heating capacity deficiency, and efficiency is very low.And, user require system can realize fast-refrigerating heat time, cold medium flux cannot be increased fast.
Summary of the invention
The present invention is intended at least to solve one of technical problem existed in prior art.For this reason, one object of the present invention is to propose a kind of cooling and warming circulatory system, can meet actual requirement better.
According to the cooling and warming circulatory system of the embodiment of the present invention, comprising: reservoir, described reservoir has air inlet and gas outlet, compressor, described compressor comprises the housing with row's refrigerant mouth and the compressing mechanism be located in described housing, described compressing mechanism comprises cylinder assembly, and be located at the base bearing at axial two ends and the supplementary bearing of described cylinder assembly, described cylinder assembly comprises two cylinders, and the dividing plate be located between described two cylinders, each described cylinder has compression chamber, described compression chamber comprises suction muffler and discharge chamber, described compressing mechanism is formed with the jet chamber with the first air entry and first row gas port, described first air entry is used for passing into middle pressure refrigerant or high pressure refrigerant in described jet chamber, the described suction muffler of one of them in described two cylinders is communicated with described gas outlet and described discharge chamber is communicated with described jet chamber, another described suction muffler in described two cylinders is communicated with described gas outlet or described first row gas port, condenser and evaporimeter, described condenser is communicated with described row's refrigerant mouth with one end of one of them in described evaporimeter, and described condenser is communicated with described air inlet with another the one end in described evaporimeter, flash vessel, described flash vessel is located between the other end of described condenser and the other end of described evaporimeter, and first throttle device and the second throttling arrangement, described first throttle device is located between described condenser and described flash vessel, and described second throttling arrangement is located between described evaporimeter and described flash vessel, when the cooling and warming circulatory system is run under small load condition, described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described high pressure refrigerant with described first row gas port, when the cooling and warming circulatory system is at large load and under ultralow temperature heating condition during stable operation, described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port, when running under other high load working condition except heating except ultralow temperature of the cooling and warming circulatory system, another the described suction muffler in described two cylinders is communicated with described gas outlet.
According to the cooling and warming circulatory system of the embodiment of the present invention, the cooling and warming circulatory system can adapt to the change of Wide Range condition, remains on the Effec-tive Function under each working condition, and can effectively realize fast-refrigerating, heats.
Further, described first air entry is further used for passing into low pressure refrigerant in described jet chamber, when the cooling and warming circulatory system is run under small load condition, described first air entry passes into described low pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described gas outlet; When the cooling and warming circulatory system is at large load and when running under ultralow temperature heating condition, described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port; When running under other high load working condition except heating except ultralow temperature of the cooling and warming circulatory system, another the described suction muffler in described two cylinders is communicated with described gas outlet.
Alternatively, when the cooling and warming circulatory system starts, described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described gas outlet; Afterwards, the different choice according to load: described first air entry passes into low pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described first row gas port; Or described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port; Or running status during maintenance startup.
Further, described first air entry place is provided with the middle pressure breather pipe and low pressure breather pipe that are arranged in parallel, the free end of described middle pressure breather pipe is connected with flash vessel, the free end of described low pressure breather pipe is connected with described air inlet, on-off control valve is provided with between described flash vessel and described second throttling arrangement, when cooling and warming circulatory system Defrost operation, described on-off control valve is in closed condition, described middle pressure breather pipe is communicated with described low pressure breather pipe presses refrigerant to be delivered to described air inlet in being come by described flash vessel, another described suction muffler described in described two cylinders is communicated with described gas outlet.
Alternatively, when the cooling and warming circulatory system starts, described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described gas outlet; Afterwards, different choice according to load: described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described high pressure refrigerant with described first row gas port; Or described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port; Or running status during maintenance startup.
Further, on-off control valve is provided with between described flash vessel and described second throttling arrangement, when cooling and warming circulatory system Defrost operation, described on-off control valve is in closed condition, described first air entry passes into middle pressure refrigerant in described jet chamber, described middle pressure refrigerant is the refrigerant of coming from described flash vessel, and another the described suction muffler described in described two cylinders is communicated with to be imported in described suction muffler by described middle pressure refrigerant with described first row gas port.
Further, when the described cooling and warming circulatory system is out of service, described first air entry passes into described high pressure refrigerant in described jet chamber.
Additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present invention.
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present invention and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 is the schematic diagram of the cooling and warming circulatory system according to the embodiment of the present invention;
Fig. 2 is the schematic diagram of the compressor assembly shown in Fig. 1;
Fig. 3 is another schematic diagram of the cooling and warming circulatory system shown in Fig. 1, is wherein provided with on-off control valve between flash vessel and the second throttling arrangement;
Fig. 4 is the schematic diagram of the cooling and warming circulatory system in accordance with another embodiment of the present invention;
Fig. 5 is the schematic diagram of the compressor assembly shown in Fig. 4;
Fig. 6 is another schematic diagram of the cooling and warming circulatory system shown in Fig. 4, is wherein provided with on-off control valve between flash vessel and the second throttling arrangement;
Fig. 7 is the schematic diagram of the compressing mechanism according to the embodiment of the present invention;
Fig. 8 is the schematic diagram of compressing mechanism in accordance with another embodiment of the present invention;
Fig. 9 is the schematic diagram of the compressing mechanism according to another embodiment of the present invention.
Reference numeral:
100: the cooling and warming circulatory system;
1: compressor assembly; 11: compressor; 111: housing; 112: motor;
1111: row's refrigerant mouth; 113: base bearing; 114: supplementary bearing;
1141: jet chamber; 1142: the first air entries; 1143: first row gas port;
115: upper cylinder; 1151: compression chamber; 1152: piston; 116: lower cylinder; 117: dividing plate;
118: cover plate; 1181: the first magnetic elements; 119: slide plate;
12: reservoir; 121: air inlet; 122: gas outlet;
21: condenser; 22: evaporimeter; 3: flash vessel;
41: first throttle device; 42: the second throttling arrangements;
51: control valve; 52: control device; 6: on-off control valve;
7: four-way control valve; Control valve port at 71: the first; Control valve port at 72: the second;
73: the three control valve port; 74: the four control valve port;
81: the first control valve assemblies; 811: high pressure breather pipe; 812: middle pressure breather pipe; 813: low pressure breather pipe;
91: the second flexible members; 92: the second magnetic elements.
Detailed description of the invention
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Being exemplary below by the embodiment be described with reference to the drawings, only for explaining the present invention, and can not limitation of the present invention being interpreted as.
In describing the invention, it will be appreciated that, term " " center ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end ", " interior ", " outward ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.
In addition, term " first ", " second ", " the 3rd ", " the 4th " etc. only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristic.Thus, one or more these features can be expressed or impliedly be comprised to the feature being limited with " first ", " second ", " the 3rd ", " the 4th " etc.In describing the invention, except as otherwise noted, the implication of " multiple " is two or more.
In describing the invention, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or connect integratedly; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, concrete condition above-mentioned term concrete meaning in the present invention can be understood.
Below with reference to Fig. 1-Fig. 9, the cooling and warming circulatory system 100 according to the embodiment of the present invention is described.Wherein, the cooling and warming circulatory system 100 can be applied in air-conditioner or heat pump water-heating machine.
As shown in Fig. 1, Fig. 3, Fig. 4 and Fig. 6, according to the cooling and warming circulatory system 100 of the embodiment of the present invention, comprise compressor 11, reservoir 12, condenser 21, evaporimeter 22, flash vessel 3, first throttle device 41 and the second throttling arrangement 42.
Compressor 11 and reservoir 12 form compressor assembly 1 jointly, reservoir 12 is located at outside compressor 11, reservoir 12 is formed with air inlet 121 and gas outlet 122, such as, with reference to Fig. 1 composition graphs 2, air inlet 121 is formed in the top of reservoir 12, and gas outlet 122 is formed in the bottom of reservoir 12, gaseous coolant after being separated for carrying out gas-liquid separation to the refrigerant entering into reservoir 12 inside from air inlet 121, and is fed in compressor 11 from gas outlet 122 by reservoir 12.Alternatively, compressor 11 is rotary compressor.
Wherein, compressor 11 can be vertical compressor.In description below the application, be described for vertical compressor for compressor 11.Certainly, those skilled in the art are appreciated that compressor 11 can also be horizontal compressor (scheming not shown).Here, it should be noted that, " vertical compressor " can be understood as the compressor 11 (as shown in Figure 2) of central axis upright in the installed surface of compressor 11 of the cylinder of the compressing mechanism of compressor 11.Correspondingly, the central axis that " horizontal compressor " can be understood as cylinder is roughly parallel to the compressor 11 of the installed surface of compressor 11.
Compressor 11 comprises housing 111, motor 112 and compressing mechanism, and as shown in Figure 2, housing 111 is vertically arranged, now the central axis of housing 111 vertically extends.Housing 111 is preferably formed to rotary structure, to facilitate processing and manufacturing.Motor 112 and compressing mechanism are all located in housing 111, and motor 112 and compressing mechanism are arranged in the vertical direction, and motor 112 is positioned at the top of compressing mechanism, and motor 112 is connected to compress the refrigerant entered in it with compressing mechanism.Housing 111 is formed with row's refrigerant mouth 1111, for example, referring to Fig. 1 and composition graphs 2, row's refrigerant mouth 1111 is formed in the top of housing 111, to be discharged outside compressor 11 by the refrigerant after compression.
Specifically, compressing mechanism comprises base bearing 113, cylinder assembly and supplementary bearing 114, base bearing 113 and supplementary bearing 114 are located at the axial two ends of cylinder assembly respectively, when compressor 11 is vertical compressor, such as in the figure 2 example, base bearing 113 and supplementary bearing 114 are located at the top and bottom of cylinder assembly respectively.
When compressor 11 is duplex cylinder compressor, with reference to Fig. 2, cylinder assembly comprises two cylinders (i.e. upper cylinder 115 and lower cylinder 116), dividing plate 117, two slide plates 119 and two pistons 1152, upper cylinder 115 and lower cylinder 116 are arranged in the vertical direction, dividing plate 117 is located between these two cylinders, each cylinder is formed with compression chamber 1151 and vane slot, two pistons 1152 are located in two compression chambers 1151 respectively and inwall along corresponding compression chamber 1151 can roll, vane slot is communicated with compression chamber 1151 and radial direction along cylinder extends, two slide plates 119 are located in corresponding vane slot respectively, and the inner of each slide plate 119 is only supported so that compression chamber 1151 is divided into suction muffler and discharge chamber with the periphery wall of corresponding piston 1152 respectively, suction muffler is for sucking refrigerant to be compressed, discharge chamber is used for the refrigerant after by compression and discharges.Wherein, direction " interior " can be understood as towards the direction of cylinder axis, and its rightabout is defined as " outward ", namely away from the direction of cylinder axis.
When compressor more than compressor 11 is three cylinders or three cylinders, cylinder assembly is included in the cylinder of more than three or three that axially arrange, and is provided with dividing plate 117 between two adjacent cylinders.Be appreciated that other configuration example of the compressor of more than three cylinders or three cylinders is as substantially identical with duplex cylinder compressor in piston 1152, slide plate 119 etc., do not repeat them here.It should be noted that, in the description below the application, be described for duplex cylinder compressor for compressor 11, and above-mentioned two cylinders are called upper cylinder 115 and lower cylinder 116, to facilitate description.The suction muffler of one of them (lower cylinder 116 such as, in Fig. 2) in two cylinders is communicated with the gas outlet 122 of reservoir 12.
Compressing mechanism is formed there is the first air entry 1142 and first row gas port 1143 jet chamber 1141, first air entry 1142 for passing into middle pressure refrigerant or high pressure refrigerant in jet chamber 1141, the pressure of middle pressure refrigerant is less than the pressure of high pressure refrigerant.In two cylinders one of them (such as, lower cylinder 116 in Fig. 2) suction muffler to be communicated with the gas outlet 122 of reservoir 12 and the discharge chamber of one of them in two cylinders is communicated with jet chamber 1141, thus the refrigerant in the discharge chamber of this cylinder after compression can enter in jet chamber 1141, the suction muffler of another (upper cylinder 115 such as, in Fig. 2) in two cylinders is communicated with the gas outlet 122 of reservoir 12 or the first row gas port 1143 in jet chamber 1141.
Condenser 21 is communicated with row's refrigerant mouth 1111 with one end of one of them in evaporimeter 22, and condenser 21 is communicated with air inlet 121 with another the one end in evaporimeter 22.Here following two kinds of situations are comprised: the first, one end of condenser 21 (such as, left end in Fig. 1) be communicated with row's refrigerant mouth 1111, one end of evaporimeter 22 (such as, left end in Fig. 1) be communicated with the air inlet 121 of reservoir 12, now the cooling and warming circulatory system 100 is refrigeration mode; The second, one end of evaporimeter 22 is communicated with row's refrigerant mouth 1111, and one end of condenser 21 is communicated with the air inlet 121 of reservoir 12, and now the cooling and warming circulatory system 100 is heating mode.
Wherein, condenser 21 and evaporimeter 22 and the mode of communicating between row's refrigerant mouth 1111 and the air inlet 121 of reservoir 12 can be realized by four-way control valve 7.Specifically, four-way control valve 7 comprises the first control valve port 71, second and controls valve port 72, the 3rd control valve port 73 and the 4th control valve port 74, first controls valve port 71 is connected with above-mentioned one end of condenser 21, second controls valve port 72 is connected with row's refrigerant mouth 1111,3rd controls valve port 73 is connected with air inlet 121, and the 4th controls valve port 74 is connected with above-mentioned one end of evaporimeter 22.When the cooling and warming circulatory system 100 is run in cooling mode, the first control valve port 71 and second controlling four-way control valve 7 controls valve port 72 conducting, and the 3rd controls valve port 73 and the 4th controls valve port 74 conducting; When the cooling and warming circulatory system 100 is run in a heating mode, the first control valve port 71 and the 3rd controlling four-way control valve 7 controls valve port 73 conducting, and second controls valve port 72 and the 4th controls valve port 74 conducting.
Flash vessel 3 is located between the other end (such as, the right-hand member in Fig. 1) of condenser 21 and the other end (such as, the right-hand member in Fig. 1) of evaporimeter 22, and flash vessel 3 is for carrying out shwoot and gas-liquid separation to the refrigerant entered in it.
First throttle device 41 is located between condenser 21 and flash vessel 3, second throttling arrangement 42 is located between evaporimeter 22 and flash vessel 3, such as, when the cooling and warming circulatory system 100 is run in cooling mode, first throttle device 41 can expand by the cooled refrigerant of condenser 21, and the refrigerant after flash vessel 3 shwoot can expand by the second throttling arrangement 42 further.Wherein, first throttle device 41 and the second throttling arrangement 42 can be capillary, electric expansion valve, heating power expansion valve etc., but are not limited thereto.
Thus, when the cooling and warming circulatory system 100 is run under middle refrigeration mode, with reference to Fig. 1 composition graphs 2, high pressure refrigerant enters in another the suction muffler above-mentioned of two cylinders by jet chamber 1141, due to the pressure of inspiration(Pi) of the suction muffler of this cylinder and the pressure at expulsion of discharge chamber consistent, therefore this cylinder unloading, one of them work above-mentioned only in two cylinders, realizes single cylinder single stage compress.Wherein, high pressure refrigerant can for being drained into the refrigerant of housing 111 inside by the discharge chamber of cylinder.
Under this middle refrigeration mode, first of four-way control valve 7 controls valve port 71 and second and controls valve port 72 conducting, 3rd controls valve port 73 and the 4th controls valve port 74 conducting, refrigerant after compressor 11 compresses flows to condenser 21 by four-way control valve 7, evaporimeter 22 is entered after flowing through first throttle device 41, flash vessel 3 and the second throttling arrangement 42 more successively, after evaporimeter 22 absorbs heat, flow into reservoir 12, then turn back to compressor 11.Now because the cooling and warming circulatory system 100 load is little, carry out single cylinder single stage compress, reduce unnecessary overcompression loss and friction loss, and, compressor 11 can be allowed to run under the frequency that motor 112 efficiency is higher, and reduce leakage loss, thus the efficiency of the cooling and warming circulatory system 100 under improve this operating mode.
When the cooling and warming circulatory system 100 is run in a heating mode, the refrigerant that one of them discharge chamber above-mentioned in two cylinders is discharged and middle pressure refrigerant enter in another the suction muffler above-mentioned of two cylinders by jet chamber 1141, pressure at expulsion in the discharge chamber of this another cylinder above-mentioned is that (this pressure is relative pressure to middle pressure, namely between the size of this pressure pressure of refrigerant of discharging between the gas outlet 122 of reservoir 12 and housing 111 internal pressure), another cylinder above-mentioned carries out second-compressed after sucking above-mentioned two kinds of refrigerants, it is inner that refrigerant after compression is discharged to housing 111, realize two stages of compression.Wherein, middle pressure refrigerant can for press refrigerant from the cooling and warming circulatory system 100.
Under this heating mode, first of four-way control valve 7 controls valve port 71 and the 3rd and controls valve port 73 conducting, second controls valve port 72 and the 4th controls valve port 74 conducting, refrigerant after compressor 11 compresses flows to evaporimeter 22 through four-way control valve 7, to be expand into after middle pressure refrigerant through the second throttling arrangement 42 by evaporimeter 22 refrigerant out and flow into flash vessel 3, gas-liquid two-phase state is flashed into and gas-liquid separation at flash vessel 3, refrigerant after gas-liquid separation is divided into two-way: the liquid refrigerants of main road enters condenser 21 after first throttle device 41 throttling expansion, gaseous coolant is become carry out heat exchange in condenser 21 after, flow into again in one of them cylinder above-mentioned of compressor 11 and compress, the gaseous coolant of bypass from flash vessel 3 out, enter compressor 11 by middle pressure breather pipe 812, mix with the refrigerant after one of them cylinder compression above-mentioned, mixed refrigerant enters another cylinder above-mentioned, discharge after this another cylinder compression, thus complete two stages of compression.
When the cooling and warming circulatory system 100 is applied to heat pump water-heating machine, evaporimeter 22 carries out heat exchange with the water tank of the cooling and warming circulatory system 100, and the cooling and warming circulatory system 100 circulates consistent with above-mentioned.Thus, when heating, pressure reduction pressure ratio is larger, particularly under low-temperature heating and heat pump working condition, adopt two stages of compression, not only effectively can improve the heating capacity of the cooling and warming circulatory system 100, and reduce the pressure ratio of every grade of compression, reduce leakage and clearance impact, effective recovery section work done during compression, improves the efficiency under this working condition.
When the cooling and warming circulatory system 100 is run under overload refrigeration mode, two kinds of methods of operation can be selected: the first, Two-stage Compression mode; The second, twin-tub single stage compress mode.
Under Two-stage Compression mode, the refrigerant that one of them discharge chamber above-mentioned in two cylinders is discharged and middle pressure refrigerant enter in another the suction muffler above-mentioned of two cylinders by jet chamber 1141, pressure at expulsion in the discharge chamber of this another cylinder above-mentioned is that (this pressure is relative pressure to middle pressure, namely between the size of this pressure pressure of refrigerant of discharging between the gas outlet 122 of reservoir 12 and housing 111 internal pressure), another cylinder above-mentioned carries out second-compressed after sucking above-mentioned two kinds of refrigerants, it is inner that refrigerant after compression is discharged to housing 111, realize Two-stage Compression.
Under twin-tub single stage compress mode, low pressure refrigerant enters in another the suction muffler above-mentioned of two cylinders by jet chamber 1141, the refrigerant of discharging from the gas outlet 122 of reservoir 12 is sucked in one of them suction muffler above-mentioned in two cylinders, pressure of inspiration(Pi) due to the suction muffler of two cylinders is all low pressure, pressure at expulsion is all high pressure, namely discharge after low pressure refrigerant is all directly compressed to high pressure by two cylinders in respective compression travel, realize twin-tub compression.
Under this overload refrigeration mode, first of four-way control valve 7 controls valve port 71 and second and controls valve port 72 conducting, 3rd controls valve port 73 and the 4th controls valve port 74 conducting, refrigerant after compressor 11 compresses flows to condenser 21 through four-way control valve 7, evaporimeter 22 is entered after flowing through first throttle device 41, flash vessel 3 and the second throttling arrangement 42 more successively, after evaporimeter 22 absorbs heat, flow into reservoir 12, then turn back to compressor 11.Now because the cooling and warming circulatory system 100 load is large, evaporating temperature is also higher simultaneously, namely mainly refrigeration requirement is large, two cylinders are adopted to carry out single stage compress, greatly can improve the refrigerant circulation of the cooling and warming circulatory system 100, thus the refrigerating capacity increased fast under this operating mode, and under overload refrigeration mode, the efficiency of the cooling and warming circulatory system 100 is high.Be appreciated that and select which kind of pattern can carry out different selections according to the difference of operating mode, territory of use.
When the cooling and warming circulatory system 100 is run under small load condition, first air entry 1142 passes into high pressure refrigerant in jet chamber 1141, and another the suction muffler above-mentioned in two cylinders is communicated with to import in above-mentioned suction muffler by the high pressure refrigerant in jet chamber 1141 with the first row gas port 1143 in jet chamber 1141; When the cooling and warming circulatory system is at large load and when especially needing under ultralow temperature heating condition to keep cooling and warming circulatory system efficient stable to run, first air entry 1142 passes into middle pressure refrigerant in jet chamber 1141, and another the suction muffler above-mentioned in two cylinders is communicated with to press refrigerant to import in above-mentioned suction muffler in jet chamber 1141 with the first row gas port 1143 in jet chamber 1141; When the cooling and warming circulatory system heat except ultralow temperature especially need to keep the cooling and warming circulatory system efficient except other high load working condition under run time, another the suction muffler above-mentioned in two cylinders is communicated with the gas outlet 122 of reservoir 12.
Here, it should be noted that, " high load working condition " be appreciated that comprise high-temperature refrigeration, superhigh temperature refrigeration, low-temperature heating, ultralow temperature heats this four kinds of operating modes, other operating mode except these four kinds of operating modes is " small load condition ", such as, in the middle of refrigeration etc.
Thus, according to the cooling and warming circulatory system 100 of the embodiment of the present invention, the cooling and warming circulatory system 100 can adapt to the change of Wide Range condition, remains on the Effec-tive Function under each working condition, and can effectively realize fast-refrigerating, heats.
According to a specific embodiment of the present invention, as shown in Figure 2, compressing mechanism also comprises: cover plate 118, cover plate 118 is located at the side away from cylinder assembly of one of them in base bearing 113 and supplementary bearing 114, limits above-mentioned jet chamber 1141 in base bearing 113 and supplementary bearing 114 between above-mentioned one of them and cover plate 118.
Such as, with reference to Fig. 2 and Fig. 9, cover plate 118 is located at the bottom of supplementary bearing 114, and cover plate 118 extends in the horizontal direction, jet chamber 1141 is limited jointly by supplementary bearing 114 and cover plate 118, and the first air entry 1142 and first row gas port 1143 are formed on jet chamber 1141 with being spaced apart from each other.Or cover plate 118 can also be located at the top of base bearing 113, now jet chamber 1141 is limited (scheming not shown) jointly by base bearing 113 and this cover plate 118.
Certainly, the present invention is not limited thereto, dividing plate 117 can also comprise between two sub-dividing plates, 117, two sub-dividing plates 117 and limits above-mentioned jet chamber 1141 (scheming not shown).Specifically, such as, two sub-dividing plates 117 can be arranged in the vertical direction, sub-dividing plate 117 bottom-open of top, the sub-dividing plate 117 of below extends in the horizontal direction and is located at the bottom of the sub-dividing plate 117 of top, and now jet chamber 1141 is limited jointly by these two sub-dividing plates 117.Wherein, the first air entry 1142 and first row gas port 1143 can be formed in one of them in two sub-dividing plates 117, and such as, the first air entry 1142 and first row gas port 1143 are all formed on the sub-dividing plate 117 of top.Or the first air entry 1142 can also be formed in one of them in two cylinders, such as, the first air entry 1142 is formed on lower cylinder 116, and the first air entry 1142 is communicated with inside, jet chamber 1141.
Certainly, the top that can also be the sub-dividing plate 117 of below is unlimited, the sub-dividing plate 117 of top extends in the horizontal direction and is located at the top of the sub-dividing plate 117 of below, and wherein, the first air entry 1142 and first row gas port 1143 can all be formed on the sub-dividing plate 117 of below.
The cooling and warming circulatory system also comprises control valve 51, specifically, as shown in Figure 2, control valve 51 comprises the first valve port, the second valve port and the 3rd valve port, first valve port is communicated with the gas outlet 122 of reservoir 12, second valve port is communicated with another the suction muffler above-mentioned in two cylinders, and the 3rd valve port is communicated with first row gas port 1143.When the second valve port and the first valve port conducting, reservoir 12 passes into low pressure refrigerant by gas outlet 122 in another the suction muffler above-mentioned in two cylinders, and when the second valve port and the 3rd valve port conducting, first row gas port 1143 passes into and enter in jet chamber 1141 refrigerant of pressing in one of them the discharge chamber above-mentioned of refrigerant or high pressure refrigerant and two cylinders by the first air entry 1142 in another the suction muffler above-mentioned in two cylinders.Alternatively, control valve 51 is triple valve or cross valve.
When the cooling and warming circulatory system 100 is run under middle refrigeration mode, in jet chamber 1141, high pressure refrigerant is passed into by the first air entry 1142, such as, with reference to Fig. 1 composition graphs 2, the suction muffler of upper cylinder 115 is communicated with the first row gas port 1143 in jet chamber 1141, now the second valve port of control valve 51 such as triple valve and the 3rd valve port conducting, thus high pressure refrigerant can enter in upper cylinder 115, due to the pressure of inspiration(Pi) of the suction muffler of this upper cylinder 115 and the pressure at expulsion of discharge chamber consistent, therefore upper cylinder 115 unloads, only lower cylinder 116 works, realize single cylinder single stage compress.Thus, the cooling and warming circulatory system 100 is simple, and cost is lower.
Wherein, high pressure refrigerant can for being drained into the refrigerant of housing 111 inside by the discharge chamber of cylinder, now the first air entry 1142 is communicated with housing 111 inside, such as, first air entry 1142 place can arrange high pressure breather pipe 811 to pass into high pressure refrigerant in jet chamber 1141, now one end of high pressure breather pipe 811 (such as, upper end in Fig. 2) can directly be communicated with housing 111 inside, certainly, one end of high pressure breather pipe 811 (such as, upper end in Fig. 1) can also be communicated with the row's refrigerant mouth 1111 for the refrigerant after discharging housing 111 internal compression at housing 111 top.Or high pressure breather pipe 811 can also independently be arranged, to pass into high pressure refrigerant (scheming not shown) in jet chamber 1141.
When the cooling and warming circulatory system 100 is run in a heating mode, in jet chamber 1141, middle pressure refrigerant is passed into by the first air entry 1142, such as, with reference to Fig. 1 composition graphs 2, the suction muffler of upper cylinder 115 is communicated with the first row gas port 1143 in jet chamber 1141, now the second valve port of control valve 51 such as triple valve and the 3rd valve port conducting, pressure at expulsion in the discharge chamber of lower cylinder 116 is that (this pressure is relative pressure to middle pressure, namely between the size of this pressure pressure of refrigerant of discharging between the gas outlet 122 of reservoir 12 and housing 111 internal pressure), thus the discharge chamber that the refrigerant in jet chamber 1141 is lower cylinder 116 refrigerant and the middle pressure refrigerant of discharging mix refrigerant, upper cylinder 115 carries out second-compressed after sucking this mixing refrigerant, it is inner that refrigerant after compression is discharged to housing 111, realize two stages of compression.
Wherein, as shown in Figure 1, middle pressure refrigerant can be from pressing refrigerant in the cooling and warming circulatory system 100, specifically, first air entry 1142 place can arrange middle pressure breather pipe 812 to pass into middle pressure refrigerant in jet chamber 1141, one end (upper end such as, in Fig. 1) of middle pressure breather pipe 812 is connected with flash vessel 3.Certainly, middle pressure breather pipe 812 can also independently be arranged, to pass into middle pressure refrigerant (scheming not shown) in jet chamber 1141.
When the cooling and warming circulatory system 100 is run under overload refrigeration mode, wherein, under Two-stage Compression mode, in jet chamber 1141, middle pressure refrigerant is passed into by the first air entry 1142, such as, with reference to Fig. 1 composition graphs 2, the suction muffler of upper cylinder 115 is communicated with the first row gas port 1143 in jet chamber 1141, pressure at expulsion in the discharge chamber of lower cylinder 116 is that (this pressure is relative pressure to middle pressure, namely between the size of this pressure pressure of refrigerant of discharging between the gas outlet 122 of reservoir 12 and housing 111 internal pressure), thus the refrigerant in jet chamber 1141 be the refrigerant of discharging through the discharge chamber of upper cylinder 115 with middle pressure refrigerant mix refrigerant, upper cylinder 115 carries out second-compressed after sucking this mixing refrigerant, it is inner that refrigerant after compression is discharged to housing 111, realize Two-stage Compression.
Under twin-tub single stage compress mode, low pressure refrigerant enters in another the suction muffler above-mentioned of two cylinders by jet chamber 1141, the refrigerant of discharging from the gas outlet 122 of reservoir 12 is sucked in one of them suction muffler above-mentioned in two cylinders, pressure of inspiration(Pi) due to the suction muffler of two cylinders is all low pressure, pressure at expulsion is all high pressure, namely discharge after low pressure refrigerant is all directly compressed to high pressure by two cylinders in respective compression travel, realize twin-tub compression.
Wherein, the first air entry 1142 place is provided with the first control valve assembly 81 for controlling to pass into middle pressure refrigerant or high pressure refrigerant in jet chamber 1141.Such as, as shown in Figure 1-Figure 3, first control valve assembly 81 comprises two magnetic valves be arranged in parallel, and each magnetic valve is located on middle pressure breather pipe 812 and high pressure breather pipe 811 respectively, to press conducting and the disconnection of breather pipe 812 and high pressure breather pipe 811 in controlling respectively.Certainly, first control valve assembly 81 can also comprise the magnetic valve and triple valve (scheming not shown) that are arranged in series, triple valve is located at the side away from the first air entry 1142 of magnetic valve, specifically, a valve port of triple valve is connected with magnetic valve, two other valve port of triple valve is connected with flash vessel 3 with row's refrigerant mouth 1111 of housing 111 respectively.
Alternatively, when the cooling and warming circulatory system 100 starts, first air entry 1142 passes into high pressure refrigerant in jet chamber 1141, and another the suction muffler above-mentioned in two cylinders is communicated with the gas outlet 122 of reservoir 2, such as, by the first control valve assembly 81, high pressure refrigerant can be imported in jet chamber 1141, and by the first valve port of triple valve and the second valve port conducting, low pressure be imported in upper cylinder 115 and lower cylinder 116 as air-breathing.Afterwards, after have passed through the arbitrary time, the different choice according to load:
First air entry 1142 passes into high pressure refrigerant in jet chamber 1141, and another the suction muffler above-mentioned in two cylinders is communicated with to import in suction muffler by high pressure refrigerant with the first row gas port 1143 in jet chamber 1141; Or
First air entry 1142 passes into middle pressure refrigerant in jet chamber 1141, and another the suction muffler above-mentioned in two cylinders is communicated with to import in suction muffler by middle pressure refrigerant with the first row gas port 1143 in jet chamber 1141; Or
Keep running status when starting.Here " difference of load " can be understood as small load condition above-mentioned or high load working condition.
According to a further embodiment of the invention, as shown in Figure 3 and Figure 6, the cooling and warming circulatory system 100 comprises further: on-off control valve 6, and on-off control valve 6 is located between flash vessel 3 and the second throttling arrangement 42 to control conducting and the partition of flash vessel 3 and the second throttling arrangement 42.
When the cooling and warming circulatory system 100 is run under small load condition, the first air entry 1142 passes into low pressure refrigerant in jet chamber 1141, and another the suction muffler above-mentioned in two cylinders is communicated with the gas outlet 122 of reservoir 12; When the cooling and warming circulatory system 100 is at large load and when running under ultralow temperature heating condition, first air entry 1142 passes into middle pressure refrigerant in jet chamber 1141, and another the suction muffler in two cylinders is communicated with to import in suction muffler by middle pressure refrigerant with the first row gas port 1143 in jet chamber 1141; When running under other high load working condition except heating except ultralow temperature of the cooling and warming circulatory system 100, another the suction muffler in two cylinders is communicated with the gas outlet 122 of reservoir 12.
When the cooling and warming circulatory system 100 Defrost operation, on-off control valve 6 is in closed condition, first air entry 1142 passes into middle pressure refrigerant in jet chamber 1141, middle pressure refrigerant is the refrigerant of coming from flash vessel 3, and another the suction muffler above-mentioned in two cylinders is communicated with to be imported in above-mentioned suction muffler by middle pressure refrigerant with the first row gas port 1143 in jet chamber 1141.Such as, can pass in jet chamber 1141 by the first control valve assembly 81 by middle pressure refrigerant, now, pressure refrigerant comprises the refrigerant of coming from flash vessel 3, and middle pressure refrigerant is entered in the suction muffler of upper cylinder 115 by control valve 51 such as triple valve.
In this circulation, refrigerant after compressor 11 compresses flows to condenser 21 through four-way control valve 7, expanded through first throttle device 41 by condenser 21 cold-producing medium out, refrigerant after expansion flows into flash vessel 3, enters compressor 11 from flash vessel 3 refrigerant out by middle pressure breather pipe 812.Now, upper cylinder 115 air-breathing presses refrigerant in passing into from middle pressure breather pipe 812, forms single cylinder and runs, when the cooling and warming circulatory system 100 is applied to air-conditioner, the indoor set of air-conditioner flows without refrigerant circulation, avoids the indoor set cycle heat exchange when defrosting and makes indoor temperature decline too fast.
According to a further embodiment of the invention, the first air entry 1142 is further used for passing into low pressure refrigerant in jet chamber 1141, and the pressure of low pressure refrigerant is less than the pressure of middle pressure refrigerant.Wherein, the first air entry 1142 place can arrange low pressure breather pipe 813 to pass into low pressure refrigerant in jet chamber 1141, and one end (upper end such as, in Fig. 4) of low pressure breather pipe 813 is communicated with the air inlet 121 of reservoir 12.
When the cooling and warming circulatory system 100 is run under middle refrigeration mode, with reference to Fig. 4 composition graphs 5, in jet chamber 1141, low pressure refrigerant is passed into by the first air entry 1142, the suction muffler of upper cylinder 115 is communicated with by control valve 51 such as triple valve with the first row gas port 1143 in jet chamber 1141, the pressure of inspiration(Pi) of the suction muffler of lower cylinder 116 and the pressure at expulsion of discharge chamber are low pressure, lower cylinder 116 unloads, and only upper cylinder 115 runs, and forms single cylinder pattern.Thus, windage loss is less.Now the circulation of the cooling and warming circulatory system 100 is with above-mentioned not pass into the circulation of the cooling and warming circulatory system 100 of low pressure refrigerant by the first air entry 1142 in jet chamber 1141 the same, does not repeat them here.
In addition, when the cooling and warming circulatory system 100 is run under heating mode, overload refrigeration mode, the mode of operation of compressor 11 and the circulation pattern of the cooling and warming circulatory system 100, with above-mentioned not pass into the circulation of the cooling and warming circulatory system 100 of low pressure refrigerant by the first air entry 1142 in jet chamber 1141 the same, do not repeat them here.
First air entry 1142 place is provided with the first control valve assembly 81 for controlling to pass into low pressure refrigerant, middle pressure refrigerant or high pressure refrigerant in jet chamber 1141.Specifically, such as, as Figure 4-Figure 6, first control valve assembly 81 comprises three magnetic valves be arranged in parallel, each magnetic valve is located on low pressure breather pipe 813, middle pressure breather pipe 812 and high pressure breather pipe 811 respectively, to control conducting and the disconnection of low pressure breather pipe 813, middle pressure breather pipe 812 and high pressure breather pipe 811 respectively.
Certainly, first control valve assembly 81 can also comprise two triple valves (scheming not shown) be arranged in series, one of them in two triple valves is located at another the side away from the first air entry 1142 in two triple valves, now a valve port of another triple valve above-mentioned is connected with one of them triple valve above-mentioned, two other valve port of another triple valve above-mentioned is connected with row's refrigerant mouth 1111 of housing 111 with the air inlet 121 of reservoir 12 respectively, and a valve port of one of them triple valve above-mentioned can be connected with flash vessel 3.
When the cooling and warming circulatory system starts, first air entry 1142 passes into high pressure refrigerant in jet chamber 1141, and another the suction muffler in two cylinders is communicated with the gas outlet 122 of reservoir 12, such as, high pressure refrigerant can be imported in jet chamber 1141 by the first control valve assembly 81, and by the first valve port of triple valve and the second valve port conducting, low pressure is imported in upper cylinder 115 and lower cylinder 116 as air-breathing.Afterwards, after have passed through the arbitrary time, the different choice according to load:
First air entry 1142 passes into low pressure refrigerant in jet chamber 1141, and another the suction muffler in two cylinders is communicated with the first row gas port 1143 in jet chamber 1141; Or
First air entry 1142 passes into middle pressure refrigerant in jet chamber 1141, and another the suction muffler in two cylinders is communicated with to import in suction muffler by middle pressure refrigerant with the first row gas port 1143 in jet chamber 1141; Or
Keep running status when starting.
When system just starts, compressor 11 adopts twin-tub operational mode (substantially identical with overload cooling operation mode, certainly, according to the difference of freezing and heat, the flow direction of refrigerant is different).Due to when starting, particularly under severe conditions (such as, overload refrigeration or when heating), such as, when the cooling and warming circulatory system 100 is applied to air-conditioner, user's General Requirements drops to (or being raised to) design temperature temperature fast, adopt twin-tub mode operation, greatly can increase the refrigerant circulation of the cooling and warming circulatory system 100 when starting, setting up pressure reduction fast, thus realize fast-refrigerating and heat, improve comfortableness.
Thus, by adopting compressor 11 as shown in Figure 2 and Figure 5, the complexity of part can be reduced.
First air entry 1142 place is provided with the middle pressure breather pipe 812 and low pressure breather pipe 813 that are arranged in parallel, the free end of middle pressure breather pipe 812 (such as, upper end in Fig. 6) be connected with flash vessel 3, the free end (upper end such as, in Fig. 6) of low pressure breather pipe 813 is connected with the air inlet 121 of reservoir 12.
As shown in Figure 6, when the cooling and warming circulatory system 100 Defrost operation, on-off control valve 6 is in closed condition, middle pressure breather pipe 812 is communicated with low pressure breather pipe 813 and is communicated with the gas outlet 122 of reservoir 12 with another the suction muffler above-mentioned of pressing refrigerant to be delivered in air inlet 121, two cylinders of reservoir 12 in being come by flash vessel 3.Such as, press breather pipe 812 to be communicated with low pressure breather pipe 813 in can being controlled by the first control valve assembly 81, and the refrigerant of being come by flash vessel 3 import in the suction muffler of upper cylinder 115 and lower cylinder 116 as air-breathing.Thus, when Defrost operation, by being communicated with low pressure breather pipe 813 by middle pressure breather pipe 812, can effectively avoid lower cylinder 116 may occur the situation of intake negative-pressure when Defrost operation.And when defrosting, because high-low pressure pressure reduction is little, pressure ratio is little, effectively can avoid adopting two stages of compression and the situation that causes overcompression, cause power consumption to rise.
With reference to Fig. 7 and Fig. 8, two cylinders have two the slide plate chambeies being located at vane slot rear portion, that is, the rear portion of the vane slot of each cylinder is a slide plate chamber, vane slot comprises slide plate chamber, slide plate chamber is positioned at the rear side of slide plate 119, and at least one wherein in two slide plate chambeies is communicated with housing 111 inside.Here, it should be noted that, direction " afterwards " can be understood as the direction away from cylinder axis, and its rightabout is defined as " elder generation ", namely towards the direction of cylinder axis.Thus, the pressure reduction between the tip of slide plate 119 and rear end can be utilized to control slide plate 119 action.
Alternatively, be provided with the second flexible member 91 such as spring at least one in two slide plate chambeies, slide plate 119 is located in corresponding vane slot movably by the second flexible member 91.Such as, as shown in Figure 7, spring is one, and this spring is located in the slide plate chamber of lower cylinder 116, in other words, in the slide plate chamber of upper cylinder 115, spring is not set, so not only spring can be saved, reduce production cost, and, when upper cylinder 115 air-breathing pressure at expulsion identical (i.e. single cylinder operational mode), owing to there is no spring action, slide plate 119 would not prop up piston 1152, thus avoids the friction between slide plate 119 tip and piston 1152, reduces abrasion and power.
Further, compressing mechanism be provided be suitable in absorption two cylinders one of them in the second magnetic element 92 of slide plate 119.Such as, with reference to Fig. 7, the upper surface of dividing plate 117 is formed with the holding tank being suitable for accommodation second magnetic element 92, holding tank is positioned at the below of the slide plate 119 of upper cylinder 115, and thus, this slide plate 119 can more stably remain in vane slot, motion can not be produced because of air pressure inside fluctuation, cause slide plate 119 to produce with piston 1152 or cylinder to collide, cause damage parts, thus improve the reliability of compressor 11.Certainly, the second magnetic element 92 can also be located at the side of the contiguous cylinder of base bearing 113, as shown in Figure 7.Alternatively, the second magnetic element 92 is magnet.
Alternatively, another the swept volume above-mentioned in two cylinders is less than one of them the swept volume above-mentioned in two cylinders.Thus, the efficiency that compressor 11 runs under the jet operational mode of twin-stage can be improved.Wherein, the definition of " swept volume " is thought known by those skilled in the art, no longer describes in detail at this.
Further, when the cooling and warming circulatory system 100 is out of service, the first air entry 1142 passes into high pressure refrigerant in jet chamber 1141.
According to the compressor 11 of the cooling and warming circulatory system 100 of the embodiment of the present invention, can select to run under single cylinder operational mode, twin-tub operational mode, the jet operational mode of twin-stage, thus avoid the situation occurring overcompression when Smaller load, and when large load, cold or the heat demand of the cooling and warming circulatory system 100 can be met, improve the cooling and warming circulatory system 100 and the performance of compressor 11 under various environment temperature thereof, improve the efficiency of the cooling and warming circulatory system 100, and different refrigeration requirement can be provided, meet comfortableness requirement.
According to the cooling and warming circulatory system 100 of the embodiment of the present invention other form and operation be all known to those skilled in the art, be not described in detail here.
In the description of this description, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although illustrate and describe embodiments of the invention, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present invention and aim, scope of the present invention is by claim and equivalents thereof.
Claims (7)
1. a cooling and warming circulatory system, is characterized in that, comprising:
Reservoir, described reservoir has air inlet and gas outlet;
Compressor, described compressor comprises the housing with row's refrigerant mouth and the compressing mechanism be located in described housing, described compressing mechanism comprises cylinder assembly, and be located at the base bearing at axial two ends and the supplementary bearing of described cylinder assembly, described cylinder assembly comprises two cylinders, and the dividing plate be located between described two cylinders, each described cylinder has compression chamber, described compression chamber comprises suction muffler and discharge chamber, described compressing mechanism is formed with the jet chamber with the first air entry and first row gas port, described first air entry is used for passing into middle pressure refrigerant or high pressure refrigerant in described jet chamber, the described suction muffler of one of them in described two cylinders is communicated with described gas outlet and described discharge chamber is communicated with described jet chamber, another described suction muffler in described two cylinders is communicated with described gas outlet or described first row gas port,
Condenser and evaporimeter, described condenser is communicated with described row's refrigerant mouth with one end of one of them in described evaporimeter, and described condenser is communicated with described air inlet with another the one end in described evaporimeter;
Flash vessel, described flash vessel is located between the other end of described condenser and the other end of described evaporimeter; And
First throttle device and the second throttling arrangement, described first throttle device is located between described condenser and described flash vessel, and described second throttling arrangement is located between described evaporimeter and described flash vessel;
When the cooling and warming circulatory system is run under small load condition, described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described high pressure refrigerant with described first row gas port; When the cooling and warming circulatory system is at large load and under ultralow temperature heating condition during stable operation, described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port; When running under other high load working condition except heating except ultralow temperature of the cooling and warming circulatory system, another the described suction muffler in described two cylinders is communicated with described gas outlet.
2. the cooling and warming circulatory system according to claim 1, is characterized in that, described first air entry is further used for passing into low pressure refrigerant in described jet chamber,
When the cooling and warming circulatory system is run under small load condition, described first air entry passes into described low pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described gas outlet; When the cooling and warming circulatory system is at large load and when running under ultralow temperature heating condition, described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port; When running under other high load working condition except heating except ultralow temperature of the cooling and warming circulatory system, another the described suction muffler in described two cylinders is communicated with described gas outlet.
3. the cooling and warming circulatory system according to claim 2, it is characterized in that, when the cooling and warming circulatory system starts, described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described gas outlet; Afterwards, according to the different choice of load:
Described first air entry passes into low pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described first row gas port; Or
Described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port; Or
Keep running status when starting.
4. the cooling and warming circulatory system according to Claims 2 or 3, it is characterized in that, described first air entry place is provided with the middle pressure breather pipe and low pressure breather pipe that are arranged in parallel, the free end of described middle pressure breather pipe is connected with flash vessel, the free end of described low pressure breather pipe is connected with described air inlet, on-off control valve is provided with between described flash vessel and described second throttling arrangement
When cooling and warming circulatory system Defrost operation, described on-off control valve is in closed condition, described middle pressure breather pipe is communicated with described low pressure breather pipe presses refrigerant to be delivered to described air inlet in being come by described flash vessel, and another the described suction muffler described in described two cylinders is communicated with described gas outlet.
5. the cooling and warming circulatory system according to claim 1, it is characterized in that, when the cooling and warming circulatory system starts, described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with described gas outlet; Afterwards, according to the different choice of load:
Described first air entry passes into high pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described high pressure refrigerant with described first row gas port; Or
Described first air entry passes into middle pressure refrigerant in described jet chamber, and another the described suction muffler described in described two cylinders is communicated with to import in described suction muffler by described middle pressure refrigerant with described first row gas port; Or
Keep running status when starting.
6. the cooling and warming circulatory system according to claim 1, is characterized in that, is provided with on-off control valve between described flash vessel and described second throttling arrangement,
When cooling and warming circulatory system Defrost operation, described on-off control valve is in closed condition, described first air entry passes into middle pressure refrigerant in described jet chamber, described middle pressure refrigerant is the refrigerant of coming from described flash vessel, and another the described suction muffler described in described two cylinders is communicated with to be imported in described suction muffler by described middle pressure refrigerant with described first row gas port.
7. the cooling and warming circulatory system according to claim 1, is characterized in that, when the described cooling and warming circulatory system is out of service, described first air entry passes into described high pressure refrigerant in described jet chamber.
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105423666A (en) * | 2015-11-27 | 2016-03-23 | 珠海格力电器股份有限公司 | Control method and control device for variable-capacity compressor system |
| CN105650925A (en) * | 2016-01-14 | 2016-06-08 | 安徽美芝精密制造有限公司 | Refrigerating system and control method thereof |
| CN106871386A (en) * | 2017-04-13 | 2017-06-20 | 青岛海尔空调器有限总公司 | A kind of air-conditioner and control method |
| CN107152811A (en) * | 2017-06-30 | 2017-09-12 | 美的集团武汉制冷设备有限公司 | The control method of air-conditioning system and air-conditioning system |
| CN107869854A (en) * | 2016-09-26 | 2018-04-03 | 广东美芝制冷设备有限公司 | refrigeration system and its control method |
| CN108679890A (en) * | 2018-07-23 | 2018-10-19 | 珠海格力电器股份有限公司 | Heat pump circulation system for composite defrosting and operation method |
| CN108692485A (en) * | 2018-07-09 | 2018-10-23 | 中国科学院广州能源研究所 | The ultralow-temperature air energy heat pump unit of quickly defrosting |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05149634A (en) * | 1991-06-20 | 1993-06-15 | Mitsubishi Electric Corp | Air-conditioning device |
| CN102588285A (en) * | 2011-01-18 | 2012-07-18 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner including same |
| CN103557624A (en) * | 2013-10-11 | 2014-02-05 | 广东美芝制冷设备有限公司 | Refrigeration cycling device |
| CN203604204U (en) * | 2013-12-12 | 2014-05-21 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotating compressor assembly and air conditioner with same |
| CN103821716A (en) * | 2014-03-03 | 2014-05-28 | 广东美芝制冷设备有限公司 | Two-stage rotary compressor and refrigeration circulating device with same |
| CN204025050U (en) * | 2014-06-09 | 2014-12-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner |
| CN204630142U (en) * | 2015-05-13 | 2015-09-09 | 广东美芝制冷设备有限公司 | The cooling and warming circulatory system |
-
2015
- 2015-05-13 CN CN201510244299.XA patent/CN104879942B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05149634A (en) * | 1991-06-20 | 1993-06-15 | Mitsubishi Electric Corp | Air-conditioning device |
| CN102588285A (en) * | 2011-01-18 | 2012-07-18 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner including same |
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