CN205174914U - Cooling systems - Google Patents
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- CN205174914U CN205174914U CN201520945007.0U CN201520945007U CN205174914U CN 205174914 U CN205174914 U CN 205174914U CN 201520945007 U CN201520945007 U CN 201520945007U CN 205174914 U CN205174914 U CN 205174914U
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Abstract
The utility model discloses a cooling systems, include: compressor, switching -over subassembly, outdoor heat exchanger subassembly, indoor heat exchanger and cooling path, the compressor includes gas vent, return -air mouth, first cylinder, second cylinder and median septum, in the first cylinder and/or be equipped with cooling chamber way in the median septum, the export that said in the cooling chamber and the induction port intercommunication of second cylinder. Has first valve port to fourth valve port to the subassembly. Cooling path's both ends are continuous with the import of cooling off the chamber way with the second end of outdoor heat exchanger subassembly respectively, and the last series connection of cooling path has the 2nd throttling element. According to the utility model discloses cooling systems can improve the compression efficiency of first cylinder, can reduce compressor discharge temp and compression work when system cold die formula, improves the compressor -running environment, in the extension compressor life -span, improves system reliability. Need not to set up other coolant simultaneously for compressor and cooling systems's simple structure.
Description
Technical field
The utility model relates to refrigerating field, especially relates to a kind of refrigeration system.
Background technology
In correlation technique, the general mode of water-cooled that adopts cools cylinder, need arrange extra part in the cylinder, add cost, and make the complex structure of cylinder.Cool the technical scheme of cylinder in prior art, focus mostly in internal combustion engine, air compressor and large-scale open compressor.
Utility model content
The utility model is intended to solve one of technical problem in correlation technique at least to a certain extent.For this reason, the utility model proposes a kind of refrigeration system, refrigerant can enter in cooling channel and cool the first cylinder, makes the structure of compressor and refrigeration system simple, can improve compressor operating environment when refrigeration mode.
According to the refrigeration system of the utility model embodiment, comprise: compressor, described compressor comprises exhaust outlet, gas returning port, the first cylinder, the second cylinder and median septum, described median septum is located between described first cylinder and described second cylinder, be provided with cooling channel in described first cylinder and/or in described median septum, the outlet of described cooling channel is communicated with the air entry of described second cylinder; Commutation assembly, described commutation assembly has the first valve port to the 4th valve port, described first valve port is communicated with one of them in the 3rd valve port with the second valve port, described 4th valve port and described second valve port are communicated with another in described 3rd valve port, described first valve port is communicated with described exhaust outlet, and described 4th valve port is communicated with described gas returning port; Outdoor heat exchanger assembly and indoor heat exchanger, the first end of described outdoor heat exchanger assembly is connected with described second valve port, the first end of described indoor heat exchanger is connected with described 3rd valve port, is in series with first throttle element between the second end of described outdoor heat exchanger assembly and the second end of described indoor heat exchanger; Refrigerant passage, the two ends of described refrigerant passage are connected with the import of described cooling channel with the second end of described outdoor heat exchanger assembly respectively, described refrigerant passage are in series with second section fluid element.
According to the refrigeration system of the utility model embodiment, refrigerant can enter in cooling channel and cool the first cylinder, thus the compression efficiency of the first cylinder can be improved, compressor exhaust temperature and work done during compression can be reduced when refrigeration mode, improve compressor operating environment, extend the compressor life-span, improve system reliability.Simultaneously by adopting low-temp low-pressure refrigerant to cool the first cylinder, without the need to arranging other cooling medium, make the structure of compressor and refrigeration system simple.
In embodiments more of the present utility model, described outdoor heat exchanger assembly comprises an outdoor heat exchanger.
In other embodiments of the present utility model, described second cylinder has additional discharge port; Described outdoor heat exchanger assembly comprises the first outdoor heat exchanger and the second outdoor heat exchanger, the two ends of described first outdoor heat exchanger are connected with described first throttle element with described second valve port respectively, the first end of described second outdoor heat exchanger is connected with described additional discharge port, and described refrigerant passage is connected with the second end of described second outdoor heat exchanger.
Alternatively, described second outdoor heat exchanger is positioned at the below of described first outdoor heat exchanger.
In embodiments more of the present utility model, described compressor is positive displacement compressor, and described second cylinder has running status and halted state.
Particularly, the vane slot of described second cylinder is communicated with to make described second cylinder run or stop with one of them in described gas returning port with described exhaust outlet.
In embodiments more of the present utility model, described first throttle element is electric expansion valve.
In embodiments more of the present utility model, described commutation assembly is cross valve.
In embodiments more of the present utility model, the volume of described first cylinder is greater than the volume of described second cylinder.
Preferably, the volumetric ratio of described second cylinder and described first cylinder is M, M < 2:8.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the refrigeration system according to some embodiments of the utility model;
Fig. 2 is the schematic diagram of the refrigeration system according to other embodiments of the utility model;
Fig. 3 is the schematic diagram according to the utility model refrigeration system of some embodiments again;
Fig. 4 is the schematic diagram of the major cycle of refrigeration system according to the utility model embodiment.
Reference numeral:
Refrigeration system 100,
Compressor 1, exhaust outlet a, gas returning port b, the first cylinder 11, second cylinder 12, median septum 13, additional discharge port c,
Commutation assembly 2, first valve port d, the second valve port e, the 3rd valve port f, the 4th valve port g,
Outdoor heat exchanger assembly 3, first outdoor heat exchanger 30, second outdoor heat exchanger 31,
Indoor heat exchanger 4,
First throttle element 5,
Second section fluid element 6,
Refrigerant passage 7,
Triple valve 8, first port h, the second port n, the 3rd port m.
Detailed description of the invention
Be described below in detail embodiment of the present utility model, the example of described embodiment is shown in the drawings.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the utility model, and can not be interpreted as restriction of the present utility model.
In description of the present utility model, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", " counterclockwise ", " 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 utility model and simplified characterization for convenience of description, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as restriction of the present utility model.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristic.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise at least one this feature.In description of the present utility model, the implication of " multiple " is at least two, such as two, three etc., unless otherwise expressly limited specifically.
In the utility model, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection or each other can communication; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements, unless otherwise clear and definite restriction.For the ordinary skill in the art, the concrete meaning of above-mentioned term in the utility model can be understood as the case may be.
Be described in detail the refrigeration system 100 according to the utility model embodiment below with reference to Fig. 1-Fig. 4, this refrigeration system 100 has heating mode, refrigeration mode and defrosting mode.
As shown in Figure 1-Figure 3, according to the refrigeration system 100 of the utility model embodiment, comprising: compressor 1, commutation assembly 2, outdoor heat exchanger assembly 3, indoor heat exchanger 4 and refrigerant passage 7.Wherein, compressor 1 comprises exhaust outlet a, gas returning port b, the first cylinder 11, second cylinder 12 and median septum 13, and median septum 13 is located between the first cylinder 11 and the second cylinder 12.Particularly, compressor 1 can be constant volume compressor or positive displacement compressor.Be understandable that, compressor 1 also comprises other elements such as motor, bent axle, and the contraction principle of compressor 1 pair of refrigerant has been prior art, is just not described in detail here.
Be provided with cooling channel (scheming not shown) in first cylinder 11 and/or in median septum 13, the outlet of cooling channel is communicated with the air entry of the second cylinder 12.That is, can be provided with cooling channel in the first cylinder 11, also can be provided with cooling channel in median septum 13, or be equipped with cooling channel in the first cylinder 11 with in median septum 13, and cooling channel is used for cooling the first cylinder 11.
When being provided with cooling channel in the first cylinder 11, can be provided with cavity to limit cooling channel in the first cylinder 11, also can be embedded with pipeline to limit cooling channel in the first cylinder 11, wherein the shape, size etc. of cooling channel can limit according to actual conditions, as long as make the structural strength of the first cylinder 11 to meet the demands.
When being provided with cooling channel in median septum 13, can be provided with cavity in median septum 13 to limit cooling channel, also can be embedded with pipeline to limit cooling channel in median septum 13, wherein the shape, size etc. of cooling channel can limit according to actual conditions, as long as make the structural strength of median septum 13 to meet the demands.
Commutation assembly 2 has the first valve port d to the 4th valve port g, first valve port d is communicated with one of them in the 3rd valve port f with the second valve port e, 4th valve port g and the second valve port e are communicated with another in the 3rd valve port f, first valve port d is communicated with exhaust outlet a, 4th valve port g is communicated with gas returning port b, the first end of outdoor heat exchanger assembly 3 is connected with the second valve port e, and the first end of indoor heat exchanger 4 is connected with the 3rd valve port f.When refrigeration system 100 is refrigeration mode, the first valve port d is communicated with the second valve port e and the 3rd valve port f is communicated with the 4th valve port g, and when refrigeration system 100 is heating mode, the first valve port d is communicated with the 3rd valve port f and the second valve port e is communicated with the 4th valve port g.
Preferably, commutation assembly 2 be cross valve, it is appreciated of course that the assembly 2 that commutates can also be formed as other structures, can realize commutating as long as have the first valve port d to the 4th valve port g.
Be in series with first throttle element 5 between second end of outdoor heat exchanger assembly 3 and the second end of indoor heat exchanger 4, wherein first throttle element 5 plays the effect of reducing pressure by regulating flow.Alternatively, first throttle element 5 is electric expansion valve, it is appreciated of course that first throttle element 5 can also be the structures such as the combination of capillary or capillary and electric expansion valve.
The two ends of refrigerant passage 7 are connected with the import of cooling channel with the second end of outdoor heat exchanger assembly 3 respectively, and refrigerant passage 7 is in series with second section fluid element 6, wherein second section fluid element 6 can play the effect of reducing pressure by regulating flow.Alternatively, second section fluid element 6 is electric expansion valve, it is appreciated of course that second section fluid element 6 can also be the structures such as the combination of capillary and electric expansion valve.
Compressor 1, outdoor heat exchanger assembly 3, refrigerant passage 7, cooling channel limit auxiliary circulation.Particularly, refrigerant flow in refrigerant passage 7, refrigerant is formed as the refrigerant of low-temp low-pressure after the reducing pressure by regulating flow of second section fluid element 6, then the refrigerant of low-temp low-pressure flow in cooling channel from the import of cooling channel, when being provided with cooling channel in the first cylinder 11, the refrigerant in cooling channel can directly cool the first cylinder 11; When being provided with cooling channel in median septum 13, refrigerant cooling median septum 13 in cooling channel and then cooling the first cylinder 11, thus the partial heat of the first cylinder 11 is absorbed, the Compressed Gas process of the first cylinder 11 becomes approximate constant temperature process from polytropic process, reduces work done during compression, improves the compression efficiency of the first cylinder 11, improve compressor 1 efficiency, compressor 1 running environment can be improved when refrigeration mode, reduce compressor 1 delivery temperature and work done during compression, extend the life-span of compressor 1.
According to the refrigeration system 100 of the utility model embodiment, by being provided with auxiliary circulation, refrigerant can enter in cooling channel and cool the first cylinder 11, thus the compression efficiency of the first cylinder 11 can be improved, compressor 1 delivery temperature and work done during compression can be reduced when refrigeration mode, improve compressor 1 running environment, extend compressor 1 life-span, improve system reliability.Simultaneously by adopting low-temp low-pressure refrigerant to cool the first cylinder 11, without the need to arranging other cooling medium, make the structure of compressor 1 and refrigeration system 100 simple.
In embodiments more of the present utility model, the volume of the first cylinder 11 is greater than the volume of the second cylinder 12.Further, the volumetric ratio of the second cylinder 12 and the first cylinder 11 is M, M < 2:8.In concrete example of the present utility model, compressor 1 is positive displacement compressor, second cylinder 12 has running status and halted state, the volumetric ratio of the second cylinder 12 and the first cylinder 11 is M, M < 2:8, thus the kind of refrigeration cycle amount of refrigeration system 100 can be ensured and heat internal circulating load.
Be described in detail according to the refrigeration system 100 of the utility model three specific embodiments below with reference to Fig. 1-Fig. 4, be understandable that, following each specific embodiment is exemplary description.
Embodiment 1:
As shown in Figure 1, according to the refrigeration system 100 of the utility model embodiment, comprising: compressor 1, commutation assembly 2, outdoor heat exchanger assembly 3, indoor heat exchanger 4, refrigerant passage 7, first throttle element 5, second section fluid element 6 and triple valve 8.Commutation assembly 2 is cross valve.
Compressor 1 is positive displacement compressor, and compressor 1 comprises in exhaust outlet a, gas returning port b, the first cylinder 11, second cylinder 12 and median septum 13, first cylinder 11 and is provided with cooling channel, and the outlet of cooling channel is connected with the air entry of the second cylinder 12.Second cylinder 12 has running status and halted state.Second cylinder 12 has additional discharge port c.The piston of eccentric rotary and the slide plate of reciprocating movement is provided with in second cylinder 12.
Triple valve 8 comprises the first port h to the 3rd port m, first port h is communicated with one of them in the 3rd port m with the second port n, first port h is communicated with the slide plate chamber of the second cylinder 12, and the second port n is communicated with exhaust outlet a, and the 3rd port m is communicated with gas returning port b.When the first port h is communicated with the second port n, the slide plate chamber of the second cylinder 12 is hyperbaric environment, thus the tip of slide plate can be contacted with the periphery wall of piston all the time, and the second cylinder 12 can be in compressive state and running status.When the first port h is communicated with the 3rd port m, the slide plate chamber of the second cylinder 12 is environment under low pressure, thus the periphery wall of the tip of slide plate and piston is separated from, and piston is in idling conditions, and therefore the second cylinder 12 is in stopping compressive state.In brief, the vane slot of the second cylinder 12 is communicated with to make the second cylinder 12 run or stop with one of them in gas returning port b with exhaust outlet a, and by controlling the switching of triple valve 8, the second cylinder 12 can switch between halted state and running status.It is appreciated of course that the utility model is not limited thereto, other modes can also be adopted to switch the second cylinder 12.
Cross valve 2 comprises the first valve port d to the 4th valve port g, first valve port d is communicated with one of them in the 3rd valve port f with the second valve port e, 4th valve port g and the second valve port e are communicated with another in the 3rd valve port f, and the first valve port d is connected with exhaust outlet a, and the 4th valve port g is connected with gas returning port b.
Outdoor heat exchanger assembly 3 comprises the first outdoor heat exchanger 30 and the second outdoor heat exchanger 31, the two ends of the first outdoor heat exchanger 30 are connected with the second valve port e with first throttle element 5 respectively, the first end of the second outdoor heat exchanger 31 is connected with additional discharge port c, and the two ends of refrigerant passage 7 are connected with the import of cooling channel with the second end of the second outdoor heat exchanger 31 respectively.
The first end of indoor heat exchanger 4 is connected with the 3rd valve port f, and the second end of indoor heat exchanger 4 is connected with first throttle element 5.Second section fluid element 6 is connected on refrigerant passage 7.Compressor 1, second outdoor heat exchanger 31, refrigerant passage 7, cooling channel limit auxiliary circulation, in the present embodiment, opening or closing of auxiliary circulation can be determined by the running status of the second cylinder 12, when the second cylinder 12 is in running status, auxiliary circulation is in open mode, when the second cylinder 12 is in halted state, auxiliary circulation is in closed condition.
When refrigeration system 100 is in refrigeration mode and the second cylinder 12 is in running status, the first valve port d of cross valve 2 and the second valve port e conducting and the 4th valve port g and the 3rd valve port f conducting, the first port h of triple valve 8 and the second port n conducting.Refrigeration system 100 has major cycle and auxiliary circulation.
As shown in Figure 4, the refrigerant of major cycle flows to as follows: the refrigerant of discharging from the exhaust outlet a of compressor 1 is through the first valve port d of cross valve 2, second valve port e enters into the first outdoor heat exchanger 30, discharge from the second end of the first outdoor heat exchanger 30 after refrigerant carries out heat exchange with outdoor environment in the first outdoor heat exchanger 30, then refrigerant is drained in indoor heat exchanger 4 after the reducing pressure by regulating flow of first throttle element 5, refrigerant carries out heat exchange to freeze to indoor environment with indoor environment in indoor heat exchanger 4, the refrigerant that heat exchanger 4 is discharged indoor is expelled back into compressor 1 through the 3rd valve port f of cross valve 2 and the 4th valve port g, repetition like this is to freeze.
The refrigerant of auxiliary circulation flows to as follows: the refrigerant of discharging from the additional discharge port c of the second cylinder 12 is drained into the second outdoor heat exchanger 31, refrigerant carries out heat exchange with outdoor environment in the second outdoor heat exchanger 31, the refrigerant of discharging from the second outdoor heat exchanger 31 is drained in refrigerant passage 7, refrigerant in refrigerant passage 7 is drained in cooling channel after the reducing pressure by regulating flow of second section fluid element 6, refrigerant in cooling channel cools the first cylinder 11, refrigerant is drained in the second cylinder 12 from the outlet of cooling channel and compresses afterwards, refrigerant after the second cylinder 12 compresses can be discharged from additional discharge port c.It is appreciated of course that a part for the refrigerant after the second cylinder 12 compresses also can discharge compressor 1 from exhaust outlet a.
When refrigeration system 100 is in heating mode and the second cylinder 12 is in running status, the first valve port d of cross valve 2 and the 3rd valve port f conducting and the second valve port e and the 4th valve port g conducting, the first port h of triple valve 8 and the second port n conducting.Refrigeration system 100 has major cycle and auxiliary circulation.
The refrigerant of major cycle flows to as follows: be drained into indoor heat exchanger 4 from the refrigerant of compressor 1 discharge through the first valve port d of cross valve 2 and the 3rd valve port f, refrigerant in indoor heat exchanger 4 and indoor environment carry out heat exchange to heat indoor environment, the refrigerant that heat exchanger 4 is discharged indoor is drained in the first outdoor heat exchanger 30 after the reducing pressure by regulating flow of first throttle element 5, refrigerant in first outdoor heat exchanger 30 and outdoor environment carry out heat exchange, the refrigerant of discharging from the first outdoor heat exchanger 30 is expelled back into compressor 1 through the second valve port e of cross valve 2 and the 4th valve port g, repetition like this heats to complete.
The refrigerant of auxiliary circulation flows to as follows: the refrigerant of discharging from the additional discharge port c of the second cylinder 12 is drained into the second outdoor heat exchanger 31, refrigerant carries out heat exchange with outdoor environment in the second outdoor heat exchanger 31, the refrigerant of discharging from the second outdoor heat exchanger 31 is drained in refrigerant passage 7, refrigerant in refrigerant passage 7 is drained in cooling channel after the reducing pressure by regulating flow of second section fluid element 6, refrigerant in cooling channel cools the first cylinder 11, refrigerant is drained in the second cylinder 12 from the outlet of cooling channel and compresses afterwards, refrigerant after the second cylinder 12 compresses can be discharged from additional discharge port c.It is appreciated of course that a part for the refrigerant after the second cylinder 12 compresses also can discharge compressor 1 from exhaust outlet a.
To sum up analyze known, no matter refrigeration system 100 is in refrigerating state or heats state, and when auxiliary partially unrolling, the refrigerant in auxiliary circulation flows to identical.During refrigeration, auxiliary circulation cools the first cylinder 11, improves the compression process of the first cylinder 11, reduces work done during compression and the delivery temperature of the first cylinder 11, extends compressor 1 service life, is specially adapted to T3 high-temperature refrigeration operating mode compressor.When heating, auxiliary circulation is constant, and the temperature of the second outdoor heat exchanger 31 is higher than the temperature of the first outdoor heat exchanger 30, and by heat transfer transferring heat, delay the frosting velocity of outdoor heat exchanger assembly 3, prolongation system heats the time.When refrigeration system 100 defrosts, can also defrost be accelerated, and during owing to heating, auxiliary circulation is constant, thus can accomplishes not shut down heating and defrosting.
It is appreciated of course that, when refrigeration system 100 is in refrigerating state or heats state, second cylinder 12 also can be in halted state and make auxiliary circulation be in closed condition, such as when the load of refrigeration system 100 is high or outdoor heat exchanger assembly 3 frost-free time, second cylinder 12 is out of service with unloading, reduces power output.
As shown in Figure 1, second outdoor heat exchanger 31 is positioned at the below of the first outdoor heat exchanger 30, when heating or defrost, because hot-air has the trend upwards flowed, therefore by the second outdoor heat exchanger 31 being located at the below of the first outdoor heat exchanger 30, can heat transfer effect be accelerated, delay the frosting velocity of outdoor heat exchanger assembly 3 further, heat the time to extend system further.When refrigeration system 100 defrosts, defrost can also be accelerated.
It is appreciated of course that the arrangement of the first outdoor heat exchanger 30 and the second outdoor heat exchanger 31 is not limited thereto, the first outdoor heat exchanger 30 and the second outdoor heat exchanger 31 can also be that left and right is arranged.Two parts of the first outdoor heat exchanger 30 and the second outdoor heat exchanger 31 can be two heat exchange elements also can a be heat exchange element.
Embodiment 2:
As shown in Figure 2, refrigeration system in the present embodiment 100 is with the difference of the refrigeration system 100 in embodiment 1: compressor 1 can not transfiguration, namely compressor 1 is constant volume compressor, when compressor 1 runs, second cylinder 12 is in running status always, second cylinder 12 can not unload, opening or closing of auxiliary circulation can be determined by the duty of second section fluid element 6, when second section fluid element 6 is in open mode, auxiliary circulation is in open mode, when second section fluid element 6 is in closed condition, auxiliary circulation is in closed condition.When auxiliary circulation is in closed condition, can be discharged from exhaust outlet a by the refrigerant after the second cylinder 12 compresses.It is appreciated of course that auxiliary circulation can also be in open mode always.
What needs were described is, the refrigeration system 100 of the present embodiment be in refrigeration mode and auxiliary partially unrolling time, refrigeration system 100 be in heating mode and auxiliary partially unrolling time, the major cycle of refrigeration system 100 and the refrigerant of auxiliary circulation flow to and flow to identical with the refrigerant of the refrigeration system 100 in embodiment 1, just repeat no more here.
As shown in Figure 2, second outdoor heat exchanger 31 is positioned at the below of the first outdoor heat exchanger 30, when heating or defrost, because hot-air has the trend upwards flowed, therefore by the second outdoor heat exchanger 31 being located at the below of the first outdoor heat exchanger 30, can heat transfer effect be accelerated, delay the frosting velocity of outdoor heat exchanger assembly 3 further, heat the time to extend system further.When refrigeration system 100 defrosts, defrost can also be accelerated.
It is appreciated of course that the arrangement of the first outdoor heat exchanger 30 and the second outdoor heat exchanger 31 is not limited thereto, the first outdoor heat exchanger 30 and the second outdoor heat exchanger 31 can also be that left and right is arranged.Two parts of the first outdoor heat exchanger 30 and the second outdoor heat exchanger 31 can be two heat exchange elements also can a be heat exchange element.
Embodiment 3:
As shown in Figure 3, refrigeration system 100 in the present embodiment is with the distinctive points of the refrigeration system 100 in embodiment 1: outdoor heat exchanger assembly 3 is an outdoor heat exchanger, cooling channel is located in median septum 13, second cylinder 12 does not possess additional discharge port c, the first end of outdoor heat exchanger 3 is connected with the second valve port e, and the second end of outdoor heat exchanger 3 is connected with second section fluid element 6 with first throttle element 5 respectively.Compressor 1, outdoor heat exchanger 3, refrigerant passage 7, cooling channel limit auxiliary circulation, and opening or closing of auxiliary circulation can be determined by the running status of second section fluid element 6.
When refrigeration system 100 is in refrigeration mode and second section fluid element 6 is opened, the refrigerant of discharging from the exhaust outlet a of compressor 1 is drained into outdoor heat exchanger 3 through the first valve port d of cross valve 2 and the second valve port e, refrigerant carries out heat exchange with outdoor environment in outdoor heat exchanger 3, and the refrigerant that heat exchanger 3 is discharged outdoor is divided into following two-way:
Part refrigerant enters into indoor heat exchanger 4 after the reducing pressure by regulating flow of first throttle element 5, refrigerant carries out heat exchange to freeze to indoor environment with indoor environment in indoor heat exchanger 4, and the refrigerant that heat exchanger 4 is discharged indoor is expelled back in compressor 1 through the 3rd valve port f of cross valve 2 and the 4th valve port g.
Another part refrigerant enters in refrigerant passage 7, refrigerant in refrigerant passage 7 enters in cooling channel after the reducing pressure by regulating flow of second section fluid element 6, refrigerant in cooling channel cools the first cylinder 11, enter in the second cylinder 12 from the refrigerant of cooling channel discharge and compress, be understandable that, the air entry of the second cylinder 12 can also be communicated with the gas vent of gas returning port b or the first cylinder 11.Namely the source of suction of the second cylinder 12 is from two places.
When refrigeration system 100 is in heating mode and second section fluid element 6 is closed, the refrigerant of discharging from the exhaust outlet a of compressor 1 is drained into indoor heat exchanger 4 through the first valve port d of cross valve 2 and the 3rd valve port f, refrigerant in indoor heat exchanger 4 and indoor environment carry out heat exchange to heat indoor environment, the refrigerant that heat exchanger 4 is discharged indoor is drained in outdoor heat exchanger 3 after the reducing pressure by regulating flow of first throttle element 5, refrigerant in outdoor heat exchanger 3 and outdoor environment carry out heat exchange, the refrigerant that heat exchanger 3 is discharged outdoor is expelled back in compressor 1 through the second valve port e and the 4th valve port g.
That is, when refrigeration system 100 is in heating mode and second section fluid element 6 is closed, do not have refrigerant to enter in cooling channel, the second 12, cylinder absorbs the refrigerant of the gas vent from gas returning port b or the first cylinder 11.
It is appreciated of course that when refrigeration system 100 is in heating mode, second section fluid element 6 also can be in open mode, now a part of refrigerant can be drained in cooling channel after the reducing pressure by regulating flow of second section fluid element 6.
It will also be appreciated that, when second section fluid element 6 is in closed condition, no matter refrigeration system 100 is in refrigeration mode or heating mode, second cylinder 12 can open or close according to the load request of system, such as when the load request of system is lower, the second cylinder 12 can be in run-stopping status.
What it will be appreciated by those skilled in the art that is, three above-mentioned specific embodiments are exemplary description, be not to concrete restriction of the present utility model, those skilled in the art is after having read above-mentioned specific embodiment, can improve above-described embodiment as the case may be, such as the compressor 1 in embodiment 3 is replaced to constant volume compressor, or the cooling channel in embodiment 1, embodiment 2 can be located in median septum 13.
In the utility model, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.
In the description of this description, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " 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 utility model or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this description or example and different embodiment or example can carry out combining and combining by those skilled in the art.
Although illustrate and described embodiment of the present utility model above, be understandable that, above-described embodiment is exemplary, can not be interpreted as restriction of the present utility model, those of ordinary skill in the art can change above-described embodiment, revises, replace and modification in scope of the present utility model.
Claims (10)
1. a refrigeration system, is characterized in that, comprising:
Compressor, described compressor comprises exhaust outlet, gas returning port, the first cylinder, the second cylinder and median septum, described median septum is located between described first cylinder and described second cylinder, be provided with cooling channel in described first cylinder and/or in described median septum, the outlet of described cooling channel is communicated with the air entry of described second cylinder;
Commutation assembly, described commutation assembly has the first valve port to the 4th valve port, described first valve port is communicated with one of them in the 3rd valve port with the second valve port, described 4th valve port and described second valve port are communicated with another in described 3rd valve port, described first valve port is communicated with described exhaust outlet, and described 4th valve port is communicated with described gas returning port;
Outdoor heat exchanger assembly and indoor heat exchanger, the first end of described outdoor heat exchanger assembly is connected with described second valve port, the first end of described indoor heat exchanger is connected with described 3rd valve port, is in series with first throttle element between the second end of described outdoor heat exchanger assembly and the second end of described indoor heat exchanger;
Refrigerant passage, the two ends of described refrigerant passage are connected with the import of described cooling channel with the second end of described outdoor heat exchanger assembly respectively, described refrigerant passage are in series with second section fluid element.
2. refrigeration system according to claim 1, is characterized in that, described outdoor heat exchanger assembly comprises an outdoor heat exchanger.
3. refrigeration system according to claim 1, is characterized in that, described second cylinder has additional discharge port;
Described outdoor heat exchanger assembly comprises the first outdoor heat exchanger and the second outdoor heat exchanger, the two ends of described first outdoor heat exchanger are connected with described first throttle element with described second valve port respectively, the first end of described second outdoor heat exchanger is connected with described additional discharge port, and described refrigerant passage is connected with the second end of described second outdoor heat exchanger.
4. refrigeration system according to claim 3, is characterized in that, described second outdoor heat exchanger is positioned at the below of described first outdoor heat exchanger.
5. refrigeration system according to claim 1, is characterized in that, described compressor is positive displacement compressor, and described second cylinder has running status and halted state.
6. refrigeration system according to claim 5, is characterized in that, the vane slot of described second cylinder is communicated with to make described second cylinder run or stop with one of them in described gas returning port with described exhaust outlet.
7. refrigeration system according to claim 1, is characterized in that, described first throttle element is electric expansion valve.
8. refrigeration system according to claim 1, is characterized in that, described commutation assembly is cross valve.
9. the refrigeration system according to any one of claim 1-8, is characterized in that, the volume of described first cylinder is greater than the volume of described second cylinder.
10. refrigeration system according to claim 9, is characterized in that, the volumetric ratio of described second cylinder and described first cylinder is M, M < 2:8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520945007.0U CN205174914U (en) | 2015-11-23 | 2015-11-23 | Cooling systems |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520945007.0U CN205174914U (en) | 2015-11-23 | 2015-11-23 | Cooling systems |
Publications (1)
| Publication Number | Publication Date |
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| CN205174914U true CN205174914U (en) | 2016-04-20 |
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| CN201520945007.0U Active CN205174914U (en) | 2015-11-23 | 2015-11-23 | Cooling systems |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106052217A (en) * | 2016-07-28 | 2016-10-26 | 广东美芝制冷设备有限公司 | Refrigeration device |
| CN106247667A (en) * | 2016-08-26 | 2016-12-21 | 广东美芝制冷设备有限公司 | Refrigeration system and control method thereof |
| CN110107500A (en) * | 2019-05-31 | 2019-08-09 | 宁波奥克斯电气股份有限公司 | A kind of double-cylinder variable-capacity compressor system, transfiguration increasing enthalpy system and control method |
| CN111622920A (en) * | 2019-02-28 | 2020-09-04 | 青岛海尔智能技术研发有限公司 | Refrigeration equipment, double-cylinder linear compressor and design method thereof |
-
2015
- 2015-11-23 CN CN201520945007.0U patent/CN205174914U/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106052217A (en) * | 2016-07-28 | 2016-10-26 | 广东美芝制冷设备有限公司 | Refrigeration device |
| CN106247667A (en) * | 2016-08-26 | 2016-12-21 | 广东美芝制冷设备有限公司 | Refrigeration system and control method thereof |
| CN106247667B (en) * | 2016-08-26 | 2018-09-11 | 广东美芝制冷设备有限公司 | refrigeration system and its control method |
| CN111622920A (en) * | 2019-02-28 | 2020-09-04 | 青岛海尔智能技术研发有限公司 | Refrigeration equipment, double-cylinder linear compressor and design method thereof |
| CN110107500A (en) * | 2019-05-31 | 2019-08-09 | 宁波奥克斯电气股份有限公司 | A kind of double-cylinder variable-capacity compressor system, transfiguration increasing enthalpy system and control method |
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