CN202560563U - Compressor, air conditioner system comprising same and heat pump water heater system - Google Patents
Compressor, air conditioner system comprising same and heat pump water heater system Download PDFInfo
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- CN202560563U CN202560563U CN 201220150545 CN201220150545U CN202560563U CN 202560563 U CN202560563 U CN 202560563U CN 201220150545 CN201220150545 CN 201220150545 CN 201220150545 U CN201220150545 U CN 201220150545U CN 202560563 U CN202560563 U CN 202560563U
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Abstract
The utility model provides a compressor, an air conditioner system comprising the compressor and a heat pump water heater system. The compressor provided by the utility model comprises a low-pressure compression component, a medium-pressure chamber, a low-pressure chamber air discharge passageway, an enthalpy-increasing component, a high-pressure compression component, a medium-pressure gas passageway and a high-pressure chamber gas discharge passageway, wherein the medium-pressure gas passageway comprises a low-pressure chamber passageway side passageway section and a high-pressure chamber suction passageway-side passageway section, and the ratio of the minimum cross section of the low-pressure chamber air discharge passageway side passageway section to the minimum cross section of the high-pressure chamber suction passageway-side passageway section is from 1.4 to 4. According to the compressor provided by the utility model, the pressure impulse and the flow speed impulse of refrigerant are relatively small, the first-stage air discharge plumpness and the second-stage air discharge plumpness can be improved, and the air supply quantity can be improved, therefore, the efficiency and the energy efficiency of the compressor can be improved, and the energy consumption can be reduced.
Description
Technical field
The utility model relates to air-conditioning and art of heat pumps, more specifically, relates to a kind of compressor, has the air-conditioning system and the heat pump water heater system of this compressor.
Background technique
In the existing technology; Have two-spool two-stage and increase the enthalpy compressor after carrying out tonifying Qi and increasing enthalpy, the different phase refrigerant pressure in the medium pressure gas runner is different with flow velocity, and the sectional area of its medium pressure gas runner is identical; This causes the gas between air-breathing of the exhaust of low pressure compression assembly and the partial high pressure compressed assembly of the first order bigger; Influenced compressor suction with the plumpness of exhaust, thereby reduced compressor efficiency and compressor efficiency, increased energy consumption.
The model utility content
The utility model purpose is to provide a kind of can improve compressor efficiency and efficiency, the compressor that cuts down the consumption of energy, the air-conditioning system with this compressor and heat pump water heater system.
The utility model provides a kind of compressor, comprising: the low pressure compression assembly, have low pressure chamber, and the low pressure compression assembly sucks and pressurized gas forms first body of calming the anger; The middle chamber of pressing; The low pressure chamber grate flow channel is pressed first body of calming the anger in the chamber from the low pressure compression assembly enters; Increase the enthalpy assembly, in middle pressure chamber, carry second body of calming the anger, second body and first body of calming the anger of calming the anger mixes formation and is mixed with the body of calming the anger in middle pressure chamber; The high pressure compressed assembly comprises hyperbaric chamber, the high pressure compressed assembly sucks and compressed mixed is calmed the anger body forms the 3rd body of calming the anger; The medium pressure gas runner will be mixed with the body of calming the anger and therefrom press the chamber to be delivered to the high pressure compressed assembly; The hyperbaric chamber grate flow channel is discharged the 3rd body of calming the anger from the high pressure compressed assembly; The medium pressure gas runner comprises low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of hyperbaric chamber section, and wherein, the smallest cross-section area of the smallest cross-section area of low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of hyperbaric chamber section is than between 1.4 to 4.
Further; The medium pressure gas runner also comprises the intermediate flow channel section; The intermediate flow channel section is positioned between low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of the hyperbaric chamber section, and wherein, the smallest cross-section area of low pressure chamber grate flow channel side runner section compares H with the smallest cross-section area of intermediate flow channel section
2Between 1.2 to 2, and the smallest cross-section area of the smallest cross-section area of intermediate flow channel section and the air-breathing runner side runner of hyperbaric chamber section compares H
3Between 1.2 to 2.
Further, low pressure chamber grate flow channel area and hyperbaric chamber grate flow channel area ratio are 1.2.
Further, the smallest cross-section area H of medium pressure gas runner
InSmallest cross-section area H with the low pressure chamber grate flow channel
LowRatio H
1Greater than 1.2.
Further, the volume V of hyperbaric chamber
HighVolume V with low pressure chamber
LowRatio R
1Between 0.8 to 0.9.
Further, compressor comprises bent axle, and bent axle has first eccentric part and second eccentric part; The low pressure compression assembly comprises low pressure (LP) cylinder and in low pressure (LP) cylinder, is arranged at the low pressure roller on first eccentric part, forms low pressure chamber between low pressure (LP) cylinder and the low pressure roller; The high pressure compressed assembly comprises high-pressure cylinder and in high-pressure cylinder, is arranged at the high pressure roller on second eccentric part, forms hyperbaric chamber between high-pressure cylinder and the high pressure roller.
Further, first eccentric part is identical with the offset of second eccentric part; The height of high-pressure cylinder is less than the height of low pressure (LP) cylinder.
Further, the offset of first eccentric part is less than the offset of second eccentric part; The height of high-pressure cylinder is identical with the height of low pressure (LP) cylinder.
Further, the ratio range of the cylinder height of low pressure (LP) cylinder and cylinder bore diameter is between 0.4 to 0.55; The cylinder height of high-pressure cylinder and cylinder bore diameter ratio range in 0.4 to 0.55 between; The ratio range of the offset of first eccentric part and the cylinder bore diameter of low pressure (LP) cylinder is in 0.1～0.2; The ratio range of the offset of second eccentric part and the cylinder bore diameter of high-pressure cylinder is in 0.1～0.2.
Further, the volume V in middle pressure chamber
InVolume V with low pressure chamber
LowRatio R
2Greater than 1.
Further, compressor also comprises: lower flange, be arranged at low pressure compression assembly below, and the downside of lower flange comprises the lower flange cavity; Lower cover plate, the below and the lid that are arranged at lower flange are located on the lower flange cavity, press the chamber in forming with lower flange is common.
Further, compressor also comprises: middle cylinder, be arranged between low pressure compression assembly and the high pressure compressed assembly, and middle cylinder comprises the middle cylinder cavity towards a side of high pressure compressed assembly; Pump housing dividing plate is arranged between high pressure compressed assembly and the middle cylinder and is covered on the middle cylinder cavity, presses the chamber in forming with middle cylinder is common.
Further, compressor also comprises: frame set, hold low pressure compression assembly and high pressure compressed assembly; Middle housing is arranged at the frame set outside, presses the chamber during the inner space of middle housing forms.
The utility model also provides a kind of air-conditioning system, comprises aforesaid compressor.
The utility model also provides a kind of heat pump water heater system, comprises aforesaid compressor.Compressor according to the utility model; Owing to reasonably be provided with the medium pressure gas runner, than having set preferable scope, the pressure pulsation of refrigerant and stream velocity fluctuation are all less relatively to the smallest cross-section area of the smallest cross-section area of low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of hyperbaric chamber section; Can improve the air-breathing plumpness in the first order exhaust and the second level; Improve air compensation, thereby improve compressor efficiency and efficiency, cut down the consumption of energy.
Description of drawings
The accompanying drawing that constitutes the application's a part is used to provide the further understanding to the utility model, and illustrative examples of the utility model and explanation thereof are used to explain the utility model, do not constitute the improper qualification to the utility model.In the accompanying drawings:
Fig. 1 is the compressor arrangement schematic representation according to the utility model first embodiment;
Fig. 2 is the sectional structure schematic representation according to the upper flange of the utility model first embodiment's compressor;
Fig. 3 is the left TV structure schematic representation of Fig. 2;
Fig. 4 is the sectional structure schematic representation according to the high-pressure cylinder of the utility model first embodiment's compressor;
Fig. 5 is the right TV structure schematic representation of Fig. 4;
Fig. 6 is the left TV structure schematic representation of Fig. 4;
Fig. 7 is the sectional structure schematic representation according to the pump housing dividing plate of the utility model first embodiment's compressor;
Fig. 8 is the left TV structure schematic representation of Fig. 7;
Fig. 9 is the sectional structure schematic representation according to the low pressure (LP) cylinder of the utility model first embodiment's compressor;
Figure 10 is the right TV structure schematic representation of Fig. 9;
Figure 11 is the left TV structure schematic representation of Fig. 9;
Figure 12 is the sectional structure schematic representation according to the lower flange of the utility model first embodiment's compressor;
Figure 13 is the right TV structure schematic representation of Figure 12;
Figure 14 is the left TV structure schematic representation of Figure 12;
Figure 15 is according to the low pressure of first embodiment's compressor of the utility model and the decomposition texture schematic representation of high pressure compressed assembly;
Figure 16 be maximal phase according to first embodiment's compressor of the utility model to air compensation with H
2Change schematic representation;
Figure 17 is that Energy Efficiency Ratio according to first embodiment's compressor of the utility model is with area ratio H
2Change schematic representation;
Figure 18 be maximal phase according to first embodiment's compressor of the utility model to air compensation with ratio H
1Change schematic representation;
Figure 19 is that Energy Efficiency Ratio according to first embodiment's compressor of the utility model is with ratio H
1Change schematic representation;
Figure 20 be maximal phase according to first embodiment's compressor of the utility model to air compensation with ratio R
1Change schematic representation;
Figure 21 is that Energy Efficiency Ratio according to first embodiment's compressor of the utility model is with ratio R
1Change schematic representation;
Figure 22 be maximal phase according to first embodiment's compressor of the utility model to air compensation with ratio R
2Change schematic representation;
Figure 23 is that Energy Efficiency Ratio according to first embodiment's compressor of the utility model is with ratio R
2Change schematic representation;
Figure 24 is the compressor arrangement schematic representation according to the utility model second embodiment; And
Figure 25 is the compressor arrangement schematic representation according to the utility model the 3rd embodiment.
Embodiment
Below with reference to accompanying drawing and combine embodiment to specify the utility model.Need to prove that under the situation of not conflicting, embodiment and the characteristic among the embodiment among the application can make up each other.
First embodiment
Fig. 1 to Figure 15 shows the utility model first embodiment's compressor, and this compressor is that the two-stage of middle pressure chamber in the low pressure chamber bottom increases the enthalpy compressor.
First embodiment's compressor mainly comprises frame set, motor, low pressure compression assembly, increases enthalpy assembly, lower flange 3, high pressure compressed assembly, pump housing dividing plate 11, upper flange 14 and liquor separator 1 or the like.
Frame set comprises upper shell 18a, middle casing 17 and lower shell body 18b.Motor is arranged at frame set inside, mainly is made up of stator 15 and rotor 16.The low pressure compression assembly mainly comprises low pressure (LP) cylinder 2 and the low pressure roller 10 that is arranged in the low pressure (LP) cylinder 2.The below of lower flange 3 is provided with cavity, and lower cover plate 4 is pressed the chamber in covering and surrounding on the cavity that is located at lower flange 3.The high pressure compressed assembly mainly comprises high-pressure cylinder 12 and the high pressure roller 13 that is arranged in the high-pressure cylinder 12.Increasing the enthalpy assembly mainly comprises and increases enthalpy seal ring 5, increases enthalpy pump housing sucking pipe 6, increases enthalpy housing sucking pipe 7 and increase enthalpy bend pipe 8 etc.
The process of circulation of refrigerant in first embodiment's compressor is summarized as follows:
Under the dragging of motor, the running of the low pressure compression assembly of compressor and high pressure compressed assembly, the low pressure refrigerant that refluxes from system enters into low pressure (LP) cylinder 2 compressions through liquor separator 1 and forms first and press refrigerant.After low pressure compression assembly compression first in press during refrigerant low pressure (LP) cylinder relief opening 21 and Figure 13 through low pressure (LP) cylinder 2 be discharged to lower flange 3 and the lower cover plate 4 common middle pressure chambeies that form to the lower flange relief opening 31 on the lower flange 3 shown in Figure 14.Simultaneously; Press middle hydraulic circuit entering the increase enthalpy bend pipe 8 of refrigerant in second through system; Get into again and increase enthalpy pump housing sucking pipe 6; The enthalpy mouth 23 that increases through on the low pressure (LP) cylinder shown in Figure 10 to 11 2 flow into middle the pressure in the chamber; With first in press refrigerant to mix to form and press refrigerant in mixing, press refrigerant more successively through behind the second medium pressure gas runner 22 on the first medium pressure gas runner 32 on the lower flange 3, the low pressure (LP) cylinder 2, the 3rd medium pressure gas runner 111 on the pump housing dividing plate 11, in the high-pressure cylinder suction port 121 suction high-pressure cylinders 12 through high-pressure cylinder 12 in the mixing; Be compressed into the high pressure refrigerant by the high pressure compressed assembly; The high-pressure cylinder relief opening 122 of high pressure refrigerant through last high-pressure cylinder 12 enters in the upper space that is surrounded by upper flange 14, middle casing 17 and upper shell 18a with upper flange relief opening 141 on the upper flange 14, and enters the vaporizer or the condenser of system from outlet pipe 19, accomplishes a twin-stage compression of compressor and increases the working procedure of enthalpy.Each direction of arrow among Fig. 1 has been represented the flow process of refrigerant in compressor.
Can know that according to above description the low pressure chamber grate flow channel is made up of low pressure (LP) cylinder relief opening on the low pressure (LP) cylinder 2 21 and lower flange relief opening 31.
The medium pressure gas runner is divided into three runner sections, is respectively the high-pressure cylinder suction port 121 of cutting sth. askew on the high-pressure cylinder 12 that is positioned at of the 3rd medium pressure gas runner 111 on the second medium pressure gas runner 22 and the pump housing dividing plate 11 on the low pressure (LP) cylinder 2 that is positioned at the first medium pressure gas runner 32 on the lower flange 3, intermediate flow channel section of low pressure chamber grate flow channel side runner section, the air-breathing runner side runner of hyperbaric chamber section.
The hyperbaric chamber grate flow channel then is made up of the runner between high-pressure cylinder relief opening 122 to the upper flange relief opening 141 on the high-pressure cylinder 12.Preferably, low pressure chamber grate flow channel area and hyperbaric chamber grate flow channel area ratio are 1.2.
In first embodiment of the utility model, the scope of the cross-section area ratio of three different runner sections through setting the medium pressure gas runner reduces refrigerant pressure and stream velocity fluctuation, thus improve compressor efficiency, reduce power consumption.
Particularly, the smallest cross-sectional ratio of three of the medium pressure gas runner runner sections is set to: the smallest cross-section area of low pressure chamber grate flow channel side runner section compares H with the smallest cross-section area of intermediate flow channel section
2Between 1.2 to 2, and the smallest cross-section area of the smallest cross-section area of intermediate flow channel section and the air-breathing runner side runner of hyperbaric chamber section compares H
3Between 1.2 to 2.And the smallest cross-section area of the smallest cross-section area of low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of hyperbaric chamber section is comparatively more suitable between 1.4 to 4 than H.
Referring to maximal phase among Figure 16 to air compensation with H
2Change curve, work as H
21.2 between 2 the time, maximal phase is bigger to air compensation.Referring to Energy Efficiency Ratio among Figure 17 with H
2Change curve, work as H
21.2 between 2 the time, Energy Efficiency Ratio is bigger.Maximal phase to air compensation and Energy Efficiency Ratio with H
3Change curve respectively with Figure 16 and Figure 17 in H
2Change curve similar, also be H
3Best between 1.2 to 2, not shown at this.This moment, the pressure pulsation and the stream velocity fluctuation of refrigerant were all less relatively, can improve the air-breathing plumpness in the first order exhaust and the second level, improved relative complement tolerance, thereby improved the compressor efficiency, cut down the consumption of energy.
In addition, in first embodiment preferably, the smallest cross-section area H of medium pressure gas runner
InWith low pressure chamber grate flow channel smallest cross-section area H
LowRatio H
1Greater than 1.2.Referring to maximal phase among Figure 18 to air compensation with ratio H
1Change curve, maximal phase compares H to air compensation with cross-section area
1Increase and increase, work as H
1Greater than 1.2 o'clock, maximal phase to air compensation with H
1Increase and improve more remarkable.Referring to Energy Efficiency Ratio among Figure 19 with ratio H
1Change curve, Energy Efficiency Ratio with
H1Increase increase afterwards earlier and reduce, work as H
1Greater than 1.2 o'clock, Energy Efficiency Ratio was near maximum.
In first embodiment more preferably, the hyperbaric chamber volume V
HighVolume V with low pressure chamber
LowRatio R 1 between 0.8 to 0.9.Referring to maximal phase shown in Figure 20 to air compensation with ratio R
1Change curve, along with ratio R
1The increase maximal phase air compensation is increased gradually, work as ratio R
10.8 between 0.9 the time, the amplitude that maximal phase increases air compensation begins to strengthen.Referring to Energy Efficiency Ratio shown in Figure 21 with ratio R
1Change curve, along with R
1Increase, Energy Efficiency Ratio increases afterwards earlier and lowers, and works as ratio R
10.8 between 0.9 the time, Energy Efficiency Ratio is near maximum.
In order to reach ratio R
1Scope between 0.8 to 0.9, can adopt different modes to realize.For example, can adopt following mode respectively:
When the offset of eccentric part and following eccentric part is identical on the bent axle 9 in inserting high-pressure cylinder 12 and low pressure (LP) cylinder 2, can realize volume ratio R through the height that makes high-pressure cylinder 12 less than the height of low pressure (LP) cylinder 2 through the height ratio of adjusting high-pressure cylinder 12 and low pressure (LP) cylinder 2
1Value between 0.8 to 0.9.
High when identical at the cylinder of high-pressure cylinder 12 and low pressure (LP) cylinder 2; Can insert the ratio of offset of last eccentric part and the following eccentric part of the bent axle 9 in high-pressure cylinder 12 and the low pressure (LP) cylinder 2 through adjustment, realize volume ratio R through the little upward offset of eccentric part of offset that makes down eccentric part
1Value between 0.8 to 0.9.
At high-pressure cylinder 12 and low pressure (LP) cylinder 2 cylinder height and cylinder bore diameter ratio range separately all between 0.4 to 0.55; And the ratio range of the offset of eccentric part and following eccentric part and corresponding cylinder bore diameter is under the prerequisite between 0.1 to 0.2 on the bent axle; Then can be through internal diameter and the height of adjusting high-pressure cylinder 12 and low pressure (LP) cylinder 2 simultaneously, and the offset of regulating the upper and lower eccentric part of bent axle 9 is realized volume ratio R
1Value between 0.8 to 0.9.
In first embodiment further preferably, the volume V in middle pressure chamber
InVolume V with low pressure chamber
LowRatio R
2Greater than 1.Tonifying Qi this moment fluid pulsation is less, and maximal phase is all bigger to air compensation and Energy Efficiency Ratio.Maximal phase shown in figure 22 is to the change curve of air compensation with R2, maximal phase to air compensation with R
2Increase and increase, work as R
2Equal 1 o'clock maximal phase air compensation is reached higher value, work as R
2Bigger greater than 1 o'clock its maximal phase to air compensation.Energy Efficiency Ratio shown in figure 23 is with volume ratio R
2Change curve, Energy Efficiency Ratio is with volume ratio R
2Increase and increase, work as R
2Greater than 1 o'clock, Energy Efficiency Ratio was near maximum.
Below two other embodiment's of the utility model structure is described, no longer specify for structure identical or close or parameter value scope etc. with first embodiment's compressor.
Second embodiment
Shown in figure 24; Second embodiment's compressor is that the two-stage of middle pressure chamber between low pressure compression assembly and high pressure compressed assembly increases the enthalpy compressor, and it mainly comprises liquor separator 201, low pressure (LP) cylinder 202, middle cylinder 203, increases enthalpy pipe 204, pump housing dividing plate 205, high-pressure cylinder 206, upper flange 207 and lower flange 208 or the like.Second embodiment's compressor is because middle pressure chamber is arranged on low pressure chamber top, and the middle pressure refrigerant of compressor complete machine directly travels up to the high pressure compressed assembly.
Among second embodiment; Liquor separator 201 is connected with low pressure (LP) cylinder 202 through sucking pipe; On lower flange 208, on low pressure (LP) cylinder 202, the upside of middle cylinder 203 comprises cavity to middle cylinder 203 to low pressure (LP) cylinder 202 through screw by screw; Pump housing dividing plate 205 covers in the cavity top formation that is located at middle cylinder 203 presses the chamber, increases enthalpy pipe 204 and is connected with middle cylinder 203 interior middle pressure chambeies.On middle cylinder 203, high-pressure cylinder 206 is fixing through screw and upper flange 207, links to each other with pump housing dividing plate 205 simultaneously through screw for pump housing dividing plate 205, and upper flange 207 is welded on the frame set.
The low pressure (LP) cylinder intakeport that the low pressure refrigerant gas that refluxes from air-conditioning system flows on the low pressure (LP) cylinder 202 through liquor separator 201; Press refrigerant in first by forming after the compression of low pressure compression assembly; Press refrigerant to flow into middle cylinder 203 and the pump housing dividing plate 205 common middle pressure chambeies that form in first through low pressure (LP) cylinder relief opening on the low pressure (LP) cylinder 202 and the middle cylinder relief opening on the middle cylinder 203; Being used for tonifying Qi increases second of enthalpy and presses refrigerant to flow through to increase enthalpy pipe 204 backs and also flow in the middle cylinder 203 through the middle cylinder intakeport on the middle cylinder 203; With flow in press the chamber first in press refrigerant to mix the back to form in the mixing and press refrigerant; Press refrigerant to flow into the high-pressure cylinder intakeport of high-pressure cylinder 206 through the pump housing dividing plate medium pressure gas runner on the pump housing dividing plate 205 in the mixing; The upper flange relief opening of the high pressure refrigerant that forms through high pressure compressed assembly compression back through high-pressure cylinder relief opening on the high-pressure cylinder 206 and upper flange 207 enters in the upper cavity that frame set and upper flange 207 surround; Flow into air-conditioning system through compressor exhaust pipe at last, flow back to compressor after the evaporation through air-conditioning system again, thereby accomplish once circulation.
Can know that according to above description the low pressure chamber grate flow channel is made up of low pressure (LP) cylinder relief opening on the low pressure (LP) cylinder 202 and the middle cylinder relief opening on the middle cylinder 203 in a second embodiment.
In a second embodiment, the medium pressure gas runner is divided into two runner sections, is respectively: pump housing dividing plate medium pressure gas runner on the pump housing dividing plate 205 of low pressure chamber grate flow channel side and the air-breathing flow passage side of hyperbaric chamber be positioned at the high-pressure cylinder suction port on the high-pressure cylinder 206.
The hyperbaric chamber grate flow channel then is made up of the upper flange relief opening of high-pressure cylinder relief opening on the high-pressure cylinder 206 and upper flange assembly 207.
Second embodiment's who more than describes compressor is compared with first embodiment, does not have the intermediate flow channel section.Through experimental verification, among second embodiment, the smallest cross-section area of the smallest cross-section area of low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of hyperbaric chamber section is also comparatively more suitable between 1.4 to 4 than H.Other each Parameter H
1, R
1, R
2And the span and the effect of low pressure chamber grate flow channel area and hyperbaric chamber grate flow channel area ratio etc. are close with first embodiment's compressor, the volume ratio R of first embodiment's compressor
1Each implementation etc. likewise be applicable to and therefore no longer be repeated in this description above second embodiment's compressor.
The 3rd embodiment
Shown in figure 25, the 3rd embodiment's compressor presses the two-stage of chamber external structure to increase the enthalpy compressor through increasing external airtight middle housing in forming.The 3rd embodiment's compressor mainly comprises motor, low pressure compression assembly, middle housing 304, high pressure compressed assembly, frame set, liquor separator 301 or the like.
The low pressure (LP) cylinder intakeport that the low pressure refrigerant that refluxes from air-conditioning system flows on the low pressure (LP) cylinder 302 through liquor separator 301; Forms by low pressure compression assembly compression back and to press refrigerant in first, press refrigerant through the middle pressure chamber of the low pressure (LP) cylinder relief opening on the low pressure (LP) cylinder 302 in first with downtake pipe entering middle housing 304 inside.Being used for tonifying Qi increases second of enthalpy and presses refrigerant to flow through to increase enthalpy pipe 305 backs to get into the inner middle pressure chambeies of middle housings 304; In middle pressure chamber, pressing in first refrigerant to mix the back forms in the mixing and presses refrigerant; Press refrigerant to flow into the high-pressure cylinder intakeport of high-pressure cylinder 307 through second exhaust pipe in the mixing; The high pressure refrigerant that forms through high pressure compressed assembly compression back enters in the upper space that frame set 309 and upper flange assembly 308 surround through the high-pressure cylinder relief opening on the high-pressure cylinder 307 and the upper flange relief opening on the upper flange 308; Flow into air-conditioning system through compressor exhaust pipe at last, flow back to compressor after the evaporation through air-conditioning system again, accomplish once circulation.
Can know according to above description, be the low pressure (LP) cylinder relief opening on the low pressure (LP) cylinder 302 at the 3rd embodiment's mesolow chamber grate flow channel.
In the 3rd embodiment; The medium pressure gas runner is divided into three runner sections, is respectively: the downtake pipe of low pressure chamber grate flow channel side runner section, the second exhaust pipe of intermediate flow channel section and the air-breathing runner side runner of high pressure section be positioned at the hyperbaric chamber suction port of cutting sth. askew on the high-pressure cylinder 307.
The hyperbaric chamber grate flow channel then is made up of the upper flange relief opening of high-pressure cylinder relief opening on the high-pressure cylinder 307 and upper flange assembly 308.
More than the 3rd embodiment's each Parameter H, the H of compressor
1, H
2, H
3, R
1, R
2And the span of low pressure chamber grate flow channel area and hyperbaric chamber grate flow channel area ratio etc. is same close with first embodiment's compressor with effect, the volume ratio R of first embodiment's compressor
1Each implementation also be applicable to above the 3rd embodiment's compressor, therefore no longer be repeated in this description.
From above description, can find out; The utility model the above embodiments have realized following technique effect: owing to reasonably be provided with the medium pressure gas runner; Smallest cross-section area to low pressure chamber grate flow channel side runner section has been set preferable scope with the smallest cross-section area of the air-breathing runner side runner of hyperbaric chamber section than H; The pressure pulsation of refrigerant and stream velocity fluctuation are all less relatively, can improve the air-breathing plumpness in the first order exhaust and the second level, improve air compensation; Thereby improve the compressor efficiency, cut down the consumption of energy.
The preferred embodiment that the above is merely the utility model is not limited to the utility model, and for a person skilled in the art, the utility model can have various changes and variation.All within the spirit and principle of the utility model, any modification of being done, be equal to replacement, improvement etc., all should be included within the protection domain of the utility model.
Claims (15)
1. compressor comprises:
The low pressure compression assembly has low pressure chamber, and said low pressure compression assembly sucks and pressurized gas forms first body of calming the anger;
The middle chamber of pressing;
The low pressure chamber grate flow channel enters said first body of calming the anger and presses in the chamber said from said low pressure compression assembly;
Increase the enthalpy assembly, in said, press and carry second body of calming the anger in the chamber, said second body and said first body of calming the anger of calming the anger is pressed in said and is mixed formation in the chamber and be mixed with the body of calming the anger;
The high pressure compressed assembly comprises hyperbaric chamber, and said high pressure compressed assembly sucks and compresses the said body of calming the anger that is mixed with and forms the 3rd body of calming the anger;
The medium pressure gas runner presses the chamber to be delivered to said high pressure compressed assembly from said the said body of calming the anger that is mixed with;
The hyperbaric chamber grate flow channel is discharged the said the 3rd body of calming the anger from said high pressure compressed assembly;
It is characterized in that; Said medium pressure gas runner comprises low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of hyperbaric chamber section; Wherein, the smallest cross-section area of the smallest cross-section area of said low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of said hyperbaric chamber section is than between 1.4 to 4.
2. compressor according to claim 1; It is characterized in that; Said medium pressure gas runner also comprises the intermediate flow channel section; Said intermediate flow channel section is positioned between said low pressure chamber grate flow channel side runner section and the air-breathing runner side runner of the said hyperbaric chamber section, and wherein, the smallest cross-section area of said low pressure chamber grate flow channel side runner section compares H with the smallest cross-section area of said intermediate flow channel section
2Between 1.2 to 2, and the smallest cross-section area of the smallest cross-section area of said intermediate flow channel section and the air-breathing runner side runner of said hyperbaric chamber section compares H
3Between 1.2 to 2.
3. compressor according to claim 1 and 2 is characterized in that, said low pressure chamber grate flow channel area and said hyperbaric chamber grate flow channel area ratio are 1.2.
4. compressor according to claim 1 and 2 is characterized in that, the smallest cross-section area H of said medium pressure gas runner
InSmallest cross-section area H with said low pressure chamber grate flow channel
LowRatio H
1Greater than 1.2.
5. compressor according to claim 1 and 2 is characterized in that, the volume V of said hyperbaric chamber
HighVolume V with said low pressure chamber
LowRatio R
1Between 0.8 to 0.9.
6. compressor according to claim 5 is characterized in that,
Said compressor comprises bent axle (9), and said bent axle (9) has first eccentric part and second eccentric part;
Said low pressure compression assembly comprises low pressure (LP) cylinder (2) and in said low pressure (LP) cylinder (2), is arranged at the low pressure roller (10) on said first eccentric part, forms said low pressure chamber between said low pressure (LP) cylinder (2) and the said low pressure roller (10);
Said high pressure compressed assembly comprises high-pressure cylinder (12) and in said high-pressure cylinder (12), is arranged at the high pressure roller (13) on said second eccentric part, forms said hyperbaric chamber between said high-pressure cylinder (12) and the said high pressure roller (13).
7. compressor according to claim 6 is characterized in that,
Said first eccentric part is identical with the offset of said second eccentric part;
The height of said high-pressure cylinder (12) is less than the height of said low pressure (LP) cylinder (2).
8. compressor according to claim 6 is characterized in that,
The offset of said first eccentric part is less than the offset of said second eccentric part;
The height of said high-pressure cylinder (12) is identical with the height of said low pressure (LP) cylinder (2).
9. compressor according to claim 6 is characterized in that,
The cylinder height of said low pressure (LP) cylinder (2) and the ratio range of cylinder bore diameter are between 0.4 to 0.55;
The cylinder height of said high-pressure cylinder (12) and cylinder bore diameter ratio range in 0.4 to 0.55 between;
The ratio range of the cylinder bore diameter of the offset of said first eccentric part and said low pressure (LP) cylinder (2) is in 0.1～0.2;
The ratio range of the cylinder bore diameter of the offset of said second eccentric part and said high-pressure cylinder (12) is in 0.1～0.2.
10. compressor according to claim 1 and 2 is characterized in that, said middle volume V of pressing the chamber
InVolume V with said low pressure chamber
LowRatio R
2Greater than 1.
11. compressor according to claim 1 and 2 is characterized in that, said compressor also comprises:
Lower flange (3) is arranged at said low pressure compression assembly below, and the downside of said lower flange (3) comprises the lower flange cavity;
Lower cover plate (4), the below and the lid that are arranged at said lower flange (3) are located on the said lower flange cavity, form the said middle chamber of pressing jointly with said lower flange (3).
12. compressor according to claim 1 is characterized in that, said compressor also comprises:
Middle cylinder (203) is arranged between said low pressure compression assembly and the said high pressure compressed assembly, and said middle cylinder (203) comprises the middle cylinder cavity towards a side of said high pressure compressed assembly;
Pump housing dividing plate (204) is arranged between said high pressure compressed assembly and the said middle cylinder (203) and is covered on the said middle cylinder cavity, forms jointly with said middle cylinder (203) and presses the chamber in said.
13. compressor according to claim 1 and 2 is characterized in that, said compressor also comprises:
Frame set (309) holds said low pressure compression assembly and said high pressure compressed assembly;
Middle housing (304) is arranged at said frame set (309) outside, and the inner space of said middle housing (304) forms the said middle chamber of pressing.
14. an air-conditioning system comprises compressor, it is characterized in that, said compressor is according to each described compressor in the claim 1 to 13.
15. a heat pump water heater system comprises compressor, it is characterized in that, said compressor is according to each described compressor in the claim 1 to 13.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220150545 CN202560563U (en) | 2012-04-10 | 2012-04-10 | Compressor, air conditioner system comprising same and heat pump water heater system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220150545 CN202560563U (en) | 2012-04-10 | 2012-04-10 | Compressor, air conditioner system comprising same and heat pump water heater system |
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| Publication Number | Publication Date |
|---|---|
| CN202560563U true CN202560563U (en) | 2012-11-28 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220150545 Withdrawn - After Issue CN202560563U (en) | 2012-04-10 | 2012-04-10 | Compressor, air conditioner system comprising same and heat pump water heater system |
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| Country | Link |
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| CN (1) | CN202560563U (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013152599A1 (en) * | 2012-04-10 | 2013-10-17 | 国家节能环保制冷设备工程技术研究中心 | Compressor, air conditioner system comprising the compressor and heat pump water heater system |
| CN103940138A (en) * | 2014-04-01 | 2014-07-23 | 广东美的暖通设备有限公司 | Air-cooled heat pump unit |
| CN103967788A (en) * | 2013-02-05 | 2014-08-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compression assembly, compressor, air conditioner and heat pump water heater |
| CN104963862A (en) * | 2015-07-09 | 2015-10-07 | 广东美芝制冷设备有限公司 | Compressor and air conditioning system with same |
| CN105443385A (en) * | 2014-05-27 | 2016-03-30 | 珠海格力节能环保制冷技术研究中心有限公司 | Two-stage enthalpy-increase compressor and air conditioner |
-
2012
- 2012-04-10 CN CN 201220150545 patent/CN202560563U/en not_active Withdrawn - After Issue
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013152599A1 (en) * | 2012-04-10 | 2013-10-17 | 国家节能环保制冷设备工程技术研究中心 | Compressor, air conditioner system comprising the compressor and heat pump water heater system |
| CN103362807A (en) * | 2012-04-10 | 2013-10-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, air conditioning system with same and heat-pump water heater system |
| CN103362807B (en) * | 2012-04-10 | 2016-06-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, the air conditioning system with this compressor and heat pump water heater system |
| US10041482B2 (en) | 2012-04-10 | 2018-08-07 | National Engineering Research Center Of Green Refrigeration Equipment | Compressor, air conditioner system comprising the compressor and heat pump water heater system |
| CN103967788A (en) * | 2013-02-05 | 2014-08-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compression assembly, compressor, air conditioner and heat pump water heater |
| CN103940138A (en) * | 2014-04-01 | 2014-07-23 | 广东美的暖通设备有限公司 | Air-cooled heat pump unit |
| CN103940138B (en) * | 2014-04-01 | 2016-08-17 | 广东美的暖通设备有限公司 | Air-Cooled Heat Pump Unit |
| CN105443385A (en) * | 2014-05-27 | 2016-03-30 | 珠海格力节能环保制冷技术研究中心有限公司 | Two-stage enthalpy-increase compressor and air conditioner |
| CN104963862A (en) * | 2015-07-09 | 2015-10-07 | 广东美芝制冷设备有限公司 | Compressor and air conditioning system with same |
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Granted publication date: 20121128 Effective date of abandoning: 20160608 |
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| C25 | Abandonment of patent right or utility model to avoid double patenting |