CN103671120A - Intermediate cooling medium flow passage and compressor comprising same - Google Patents

Intermediate cooling medium flow passage and compressor comprising same Download PDF

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Publication number
CN103671120A
CN103671120A CN201210359718.0A CN201210359718A CN103671120A CN 103671120 A CN103671120 A CN 103671120A CN 201210359718 A CN201210359718 A CN 201210359718A CN 103671120 A CN103671120 A CN 103671120A
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refrigerant
runner
flow channel
cylinder
area
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CN103671120B (en
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李健宝
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Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
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Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
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Abstract

The invention provides an intermediate cooling medium flow passage of a compressor. The intermediate cooling medium flow passage is a pipeline with a gradually-changing cross section as a whole, wherein the inner wall of the intermediate cooling medium flow passage is smooth. The invention further provides a two-stage rotary compressor comprising the intermediate cooling medium flow passage with the smooth inner wall. According to the intermediate cooling medium flow passage and the compressor, the inner wall of the intermediate cooling medium flow passage is smooth, so that the intermediate flow path of a cooling medium is relatively reduced, the pressure loss is reduced, and thus the energy consumption of a high-pressure cylinder is reduced; meanwhile, the occurrence of pressure pulsation at ladders is avoided, and the air suction of the high-pressure cylinder is stable, so that the air suction pressure of the high-pressure cylinder is increased, the energy consumption of the high-pressure cylinder is reduced, and the performance of the compressor is improved.

Description

Refrigerant intermediate flow channel and comprise the compressor of this refrigerant intermediate flow channel
Technical field
The present invention relates to a kind of compressor, relate in particular to a kind of 2 stage rotary compressor that comprises the refrigerant intermediate flow channel of variable cross section.
Background technique
Modern society constantly progress is because people constantly pursue better quality of the life.Along with the progress in epoch, many good products also produce thereupon, and compressor is exactly one and follows one of continuous progressive product of epoch.Along with constantly bringing forth new ideas of the mankind, compressor industry has more polynary development space.
Conventionally, compressor is that then the mechanical device of accepting power as motor, turbo machine etc. from power generation equipment compresses air, refrigeration agent or various gas.Compressor is the heart of refrigeration system, it sucks the refrigerant gas of low-temp low-pressure from sucking pipe, after driving piston to compress it by motor rotation, to outlet pipe, discharge the refrigerant gas of High Temperature High Pressure, for refrigeration cycle provides power, thus the refrigeration cycle of realization compression → condensation → expansion → evaporation (heat absorption).
2 stage rotary compressor arranges two rollers and two cylinders in upper and lower, and two cylinders communicate with each other, make a roller and the cylinder can the lower refrigeration agent of compression pressure, and another pair roller and cylinder can compress into the higher refrigeration agent of pressure of low pressure compression step.
But it is stair-stepping that the refrigerant intermediate flow channel of current 2 stage rotary compressor adopts, increased the middle flow process of refrigerant, the pressure loss is increased, it is large that high-pressure cylinder energy consumption becomes, and easily occur pressure pulsation at ladder place, affects the air-breathing stability of high-pressure cylinder.
Summary of the invention
In order to solve the problems of the technologies described above, the invention provides a kind of non-stair-stepping refrigerant intermediate flow channel and comprise the compressor of this refrigerant intermediate flow channel, it is simple in structure, easy to use.
Technological scheme of the present invention is as follows:
A refrigerant intermediate flow channel for compressor, described refrigerant intermediate flow channel integral body is a varying-arca channel gradually, the inwall of described refrigerant intermediate flow channel is level and smooth.
In an embodiment, the sectional shape of the both sides inwall of described refrigerant intermediate flow channel is oblique line therein.
In an embodiment, the sectional shape of the both sides inwall of described refrigerant intermediate flow channel is curve therein.
Therein in an embodiment, the area of the refrigerant entrance of described refrigerant intermediate flow channel is greater than the area of the refrigerant exit of described refrigerant intermediate flow channel, and the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 1.
In an embodiment, the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 0.8 therein.
In an embodiment, the center line of described refrigerant intermediate flow channel and the angle between substantially horizontal are 45 degree to 90 degree therein.
In an embodiment, center line and the angle between substantially horizontal of stating refrigerant intermediate flow channel are 90 degree therein.
Another object of the present invention is achieved through the following technical solutions:
A kind of two-stage rotary compressor, comprise dispenser component, lower cylinder, lower flange, lower cover plate, increase enthalpy pump housing sucking pipe, increase enthalpy housing sucking pipe, bent axle, lower roller, pump partition plate, upper cylinder, upper roller, upper flange component, motor stator, rotor, housing, cover assembly and relief opening, described lower cylinder is fixed on the top of described lower flange, described pump partition plate is arranged on the top of described lower cylinder, also comprise claim refrigerant intermediate flow channel as above, the refrigerant intermediate flow channel of described two stage compressor comprises the lower flange runner of lower flange, the lower cylinder runner of lower cylinder and the pump partition plate runner of pump partition plate.
In an embodiment, the outlet of the first flow of described lower flange runner is in contact with one another with the second runner entrance of described lower cylinder runner therein, and the 3rd runner entrance of the second runner exit of described lower cylinder runner and described pump partition plate runner is in contact with one another, the area of the first flow entrance of described lower flange runner is greater than the area of the first flow outlet of described lower flange runner, the area of the first flow outlet of described lower flange runner is greater than the area of the second runner entrance of described lower cylinder runner, the area of the second runner entrance of described lower cylinder runner is greater than the area of the second runner exit of described lower cylinder runner, the area of the second runner exit of described lower cylinder runner is greater than the area of the 3rd runner entrance of described pump partition plate runner, the area of the 3rd runner entrance of described pump partition plate runner is greater than the area of the 3rd runner exit of described pump partition plate runner.
The invention has the beneficial effects as follows:
Refrigerant intermediate flow channel inwall of the present invention is level and smooth, and the inwall of refrigerant intermediate flow channel is non-stepped; The middle flow process that has relatively reduced refrigerant, reduces the pressure loss, and then makes high-pressure cylinder Energy Intensity Reduction, avoided occurring pressure pulsation at ladder place simultaneously, made high-pressure cylinder air-breathing stable, improved high-pressure cylinder pressure of inspiration(Pi), reduce high-pressure cylinder energy consumption, improve compressor performance.
Accompanying drawing explanation
Below in conjunction with concrete drawings and the specific embodiments, the present invention is further elaborated.
Fig. 1 is that high-pressure cylinder pressure of inspiration(Pi) of the present invention is with the variation diagram of the refrigerant entrance of refrigerant intermediate flow channel and the Area Ratio of refrigerant exit;
Fig. 2 is that high-pressure cylinder power of the present invention is with the variation diagram of the refrigerant entrance of refrigerant intermediate flow channel and the Area Ratio of refrigerant exit;
Fig. 3 is the graph of a relation of angle of the center line of high-pressure cylinder pressure of inspiration(Pi) of the present invention and refrigerant intermediate flow channel;
Fig. 4 is an embodiment's of two stage compressor of the present invention overall schematic;
Fig. 5 is the schematic diagram of the refrigerant intermediate flow channel of two stage compressor of the present invention;
Fig. 6 is the part cooperation figure of compressor.
Description of reference numerals: 1-dispenser component, 2-lower cylinder, 3-lower flange, 4-lower cover plate, 5-increase enthalpy pump housing sucking pipe, 6-increases enthalpy housing sucking pipe, 7-bent axle, 8-lower roller, 9-pump partition plate, 10-upper cylinder, the upper roller of 11-, 12-upper flange component, 13-motor stator, 14-rotor, 15-housing, 16-cover assembly, 17-relief opening.
Embodiment
The invention provides a kind of novel, simple in structure refrigerant intermediate flow channel and compressor.More particularly, the present invention mainly improves refrigerant intermediate flow channel, and energy consumption of compressor is reduced.Below in detail preferred embodiment of the present invention will be described in detail.
A refrigerant intermediate flow channel for compressor, described refrigerant intermediate flow channel integral body is a varying-arca channel gradually, the inwall of described refrigerant intermediate flow channel is level and smooth.That is to say that refrigerant intermediate flow channel of the present invention is different from stair-stepping refrigerant intermediate flow channel of the prior art, the inwall of refrigerant intermediate flow channel of the present invention is level and smooth, there is not the stair-stepping abrupt change of cross-section, refrigerant intermediate flow channel integral body of the present invention is the pipeline of a cross section gradual change, and its internal diameter of the pipeline or area change gradually.Generally speaking, increase along with refrigerant flow path length, the pressure of compressed refrigerant can reduce gradually, the pressure loss increases along with the increase of refrigerant flow path, for two stage compressor, second level roller and cylinder, with regard to needing more mechanical energy refrigerant to be compressed to reach the requirement of refrigerant pressure, can increase unnecessary energy consumption thus.Adopt the refrigerant intermediate flow channel that this inwall is level and smooth, relatively reduced the middle flow process of refrigerant, the pressure loss is reduced, and then make high-pressure cylinder Energy Intensity Reduction, avoided occurring pressure pulsation at ladder place simultaneously, made high-pressure cylinder air-breathing stable, improved high-pressure cylinder pressure of inspiration(Pi), reduce high-pressure cylinder energy consumption, improve compressor performance.
Preferably, as a kind of embodiment, the sectional shape of the both sides inwall of described refrigerant intermediate flow channel is oblique line.In the present embodiment, the sectional shape of the both sides inwall of whole refrigerant intermediate flow channel is an oblique line, the slope of this oblique line is a definite value, the size of slope can specifically be determined according to the relative position of concrete refrigerant entrance and refrigerant exit, flow channel length etc., as long as the changes of section rate of the inwall of refrigerant intermediate flow channel is definite value.
Preferably, as a kind of embodiment, the sectional shape of the both sides inwall of described refrigerant intermediate flow channel is curve.In the present embodiment, the sectional shape of the both sides inwall of whole refrigerant intermediate flow channel is curve, also just says the non-definite value of changes of section rate.Described sectional shape is that curve is also just had a talk about from the sectional drawing of refrigerant intermediate flow channel, whole refrigerant intermediate flow channel be shaped as curve, be preferably parabola, can design more easily like this position of whole refrigerant intermediate flow channel.
Preferably, as a kind of embodiment, the area of the refrigerant entrance of described refrigerant intermediate flow channel is greater than the area of the refrigerant exit of described refrigerant intermediate flow channel, and the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 1.Referring to Fig. 1 and Fig. 2, Fig. 1 is that high-pressure cylinder pressure of inspiration(Pi) is with the variation schematic diagram of the refrigerant entrance of refrigerant intermediate flow channel and the Area Ratio of refrigerant exit; Fig. 2 is that high-pressure cylinder power is with the variation schematic diagram of the refrigerant entrance of refrigerant intermediate flow channel and the Area Ratio of refrigerant exit.As seen in Figure 1, when adopting stair-stepping refrigerant intermediate flow channel, high-pressure cylinder pressure of inspiration(Pi) is a straight line, and adopt while reducing shape intermediate flow channel, along with the increase of the Area Ratio of refrigerant exit and refrigerant entrance, high-pressure cylinder pressure of inspiration(Pi) is a parabola, when the Area Ratio of refrigerant exit and refrigerant entrance is 0.4 to 1, the pressure of inspiration(Pi) when pressure of inspiration(Pi) of high-pressure cylinder is greater than stair-stepping refrigerant intermediate flow channel, Energy Intensity Reduction that like this can high-pressure cylinder.As seen in Figure 2, when adopting stair-stepping refrigerant intermediate flow channel, high-pressure cylinder power is a straight line, and adopt while reducing shape intermediate flow channel, along with the increase of the Area Ratio of refrigerant exit and refrigerant entrance, high-pressure cylinder power is a parabola, when the Area Ratio of refrigerant exit and refrigerant entrance is 0.4 to 1, the power when power of high-pressure cylinder is less than stair-stepping refrigerant intermediate flow channel, the energy consumption of high-pressure cylinder is lower like this.Preferably, the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 0.8; Within the scope of this, the pressure of inspiration(Pi) of high-pressure cylinder is maximum, and power is minimum.
Preferably, as a kind of embodiment, the center line of described refrigerant intermediate flow channel and the angle between substantially horizontal are 45 degree to 90 degree.Refrigerant intermediate flow channel can design according to actual needs, generally refrigerant intermediate flow channel is designed to symmetrical shape, and so conveniently design and refrigerant flows.Fig. 3 is the graph of a relation of angle of the center line of high-pressure cylinder pressure of inspiration(Pi) and refrigerant intermediate flow channel.By Fig. 3 analysis, can draw, along with the center line of refrigerant intermediate flow channel and the increase of substantially horizontal angle, high-pressure cylinder pressure of inspiration(Pi) increases.
Preferably, as a kind of embodiment, the center line of described refrigerant intermediate flow channel and the angle between substantially horizontal are 90 degree.Referring to Fig. 3, when the center line of refrigerant intermediate flow channel and the angle between substantially horizontal are 90 while spending, high-pressure cylinder pressure of inspiration(Pi) is maximum.
As a kind of mode of execution, referring to Fig. 4 to Fig. 6, non-stepped refrigerant intermediate flow channel is applied to two-stage rotary compressor, this two-stage rotary compressor comprises dispenser component 1, lower cylinder 2, lower flange 3, lower cover plate 4, increase enthalpy pump housing sucking pipe 5, increase enthalpy housing sucking pipe 6, bent axle 7, lower roller 8, pump partition plate 9, upper cylinder 10, upper roller 11, upper flange component 12, motor stator 13, rotor 14, housing 15, cover assembly 16 and relief opening 17, described lower cylinder 2 is fixed on the top of described lower flange 3, described pump partition plate 9 is arranged on the top of described lower cylinder 2, also comprise refrigerant intermediate flow channel as above, the refrigerant intermediate flow channel of described two stage compressor comprises the lower flange runner of lower flange, the lower cylinder runner of lower cylinder and the pump partition plate runner of pump partition plate.Referring to Fig. 4 and Fig. 6, the present embodiment provides a kind of two-stage rotary compressor, and this compressor is offered and increased enthalpy mouth on lower cylinder, and has increased increasing enthalpy seal ring, increasing enthalpy pump housing sucking pipe, increasing enthalpy housing sucking pipe.The dispenser component 1 of described compressor is connected with lower cylinder 2 by sucking pipe, described lower cylinder is low-pressure cylinder namely, lower cover plate 4 is fixed by screws in the below of lower flange 3, increase the side that enthalpy housing sucking pipe 6 is welded on housing 15, increasing enthalpy pump housing sucking pipe 5 is compressed and is arranged on the increasing enthalpy mouth inwall of lower cylinder 2 by the increasing enthalpy seal ring with its interference fit, increasing enthalpy bend pipe is connected increasing enthalpy housing sucking pipe 6 and increasing enthalpy pump housing sucking pipe 5 by welding, upper cylinder 10 is also connected with pump partition plate 9 with upper flange component 12 is fixing by screw simultaneously, upper flange component 12 is welded on housing 15, bent axle 7 is through lower flange 3, lower cylinder 2, lower cover plate 4, pump partition plate 9, upper cylinder 10, upper flange component 12, lower roller 8 is enclosed within on the lower eccentric part of bent axle 7, upper roller 11 is enclosed within on the upper eccentric part of bent axle 7, outlet pipe 17 is welded on cover assembly 16, cover assembly 16 is welded on housing 15.
The refrigerant process of circulation of described 2 stage rotary compressor is summarized as follows: at motor (rotor 14, motor stator 13) under dragging, compressor operation, the refrigerant of returning from system enters into lower cylinder 2(low-pressure cylinder by dispenser component 1) compressed and be discharged to lower flange 3, another part refrigerant comes to enter increasing enthalpy bend pipe from another loop of system, enter again and increase enthalpy pump housing sucking pipe 5, by the increasing enthalpy mouth on lower cylinder 2, flow in lower flange 3, mix with the refrigerant of coming in after lower cylinder 2 compressors, the mixing refrigerant fluid of pressing in formation, this fluid is flowed through after pump partition plate 9 by the lower cylinder runner on lower cylinder 2 again, by upper cylinder 10, sucked and be compressed into high pressure refrigerant fluid, by upper flange component 12, be expelled to by housing 15, in the space that cover assembly 16 surrounds, and be discharged to system (vaporizer or condenser) from outlet pipe 17, complete a Two-stage Compression of compressor and increase the working procedure of enthalpy.
Referring to Fig. 5, refrigerant intermediate flow channel in the present embodiment is pressed the circulation passage that mixes refrigerant fluid, and the refrigerant intermediate flow channel in the present embodiment comprises the lower flange runner 31 of lower flange 3,2 lower cylinder runners 21 of lower cylinder and the pump partition plate runner 91 of pump partition plate 9.Mixed middle pressure refrigerant fluid successively by the lower flange runner 31 of lower flange 3,2 lower cylinder runners 21 of lower cylinder and the pump partition plate runner 91 of pump partition plate 9 enter upper cylinder 10, this refrigerant intermediate flow channel integral body is a varying-arca channel gradually, the inwall of described refrigerant intermediate flow channel is level and smooth, for non-stepped.That is to say the ladder that there will not be the abrupt change of cross-section between lower flange runner, lower cylinder runner and pump partition plate runner, the inwall of whole refrigerant intermediate flow channel is all level and smooth.Adopt the refrigerant intermediate flow channel that this inwall is level and smooth, relatively reduced the middle flow process of refrigerant, the pressure loss is reduced, and then make high-pressure cylinder Energy Intensity Reduction, avoided occurring pressure pulsation at ladder place simultaneously, made high-pressure cylinder air-breathing stable, improved high-pressure cylinder pressure of inspiration(Pi), reduce high-pressure cylinder energy consumption, improve compressor performance.
Preferably, as a kind of embodiment, first flow outlet and the second runner entrance of described lower cylinder runner 21 of described lower flange runner 31 are in contact with one another, and the 3rd runner entrance of the second runner exit of described lower cylinder runner 21 and described pump partition plate runner 91 is in contact with one another, the area of the first flow entrance of described lower flange runner 31 is greater than the area of the first flow outlet of described lower flange runner 31, the area of the first flow outlet of described lower flange runner 31 is greater than the area of the second runner entrance of described lower cylinder runner 21, the area of the second runner entrance of described lower cylinder runner 21 is greater than the area of the second runner exit of described lower cylinder runner 21, the area of the second runner exit of described lower cylinder runner 21 is greater than the area of the 3rd runner entrance of described pump partition plate runner 91, the area of the 3rd runner entrance of described pump partition plate runner 91 is greater than the area of the 3rd runner exit of described pump partition plate runner.Generally speaking, the area of the runner entrance of the refrigerant intermediate flow channel in the present embodiment (being the first flow entrance of lower flange runner) is greater than the area of the runner exit (being the 3rd runner exit of pump partition plate runner) of refrigerant intermediate flow channel, and convergent during whole refrigerant intermediate flow channel, there is not stair-stepping inwall, do not have the abrupt change of cross-section.
Preferably, as a kind of embodiment, the sectional shape of the both sides inwall of the described refrigerant intermediate flow channel of the compressor in the present embodiment is oblique line.The slope of this oblique line is a definite value, and the size of slope can specifically be determined according to the relative position of concrete refrigerant entrance and refrigerant exit, flow channel length etc., as long as the changes of section rate of the inwall of refrigerant intermediate flow channel is definite value.
Preferably, as a kind of embodiment, the sectional shape of the both sides inwall of the described refrigerant intermediate flow channel of the compressor in the present embodiment is curve.Also just say the non-definite value of changes of section rate.Described sectional shape be curve namely from the sectional drawing of refrigerant intermediate flow channel, whole refrigerant intermediate flow channel be shaped as curve, be preferably parabola, can design more easily like this position of whole refrigerant intermediate flow channel.
Preferably, as a kind of embodiment, the area of the refrigerant entrance of the described refrigerant intermediate flow channel of the compressor in the present embodiment is greater than the area of the refrigerant exit of described refrigerant intermediate flow channel, and the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 1.Referring to Fig. 1 and Fig. 2, Fig. 1 is that high-pressure cylinder pressure of inspiration(Pi) is with the variation schematic diagram of the refrigerant entrance of refrigerant intermediate flow channel and the Area Ratio of refrigerant exit; Fig. 2 is that high-pressure cylinder power is with the variation schematic diagram of the refrigerant entrance of refrigerant intermediate flow channel and the Area Ratio of refrigerant exit.As seen in Figure 1, when adopting stair-stepping refrigerant intermediate flow channel, high-pressure cylinder pressure of inspiration(Pi) is a straight line, and adopt while reducing shape intermediate flow channel, along with the increase of the Area Ratio of refrigerant exit and refrigerant entrance, high-pressure cylinder pressure of inspiration(Pi) is a parabola, when the Area Ratio of refrigerant exit and refrigerant entrance is 0.4 to 1, the pressure of inspiration(Pi) when pressure of inspiration(Pi) of high-pressure cylinder is greater than stair-stepping refrigerant intermediate flow channel, Energy Intensity Reduction that like this can high-pressure cylinder.As seen in Figure 2, when adopting stair-stepping refrigerant intermediate flow channel, high-pressure cylinder power is a straight line, and adopt while reducing shape intermediate flow channel, along with the increase of the Area Ratio of refrigerant exit and refrigerant entrance, high-pressure cylinder power is a parabola, when the Area Ratio of refrigerant exit and refrigerant entrance is 0.4 to 1, the power when power of high-pressure cylinder is less than stair-stepping refrigerant intermediate flow channel, the energy consumption of high-pressure cylinder is lower like this.Preferably, the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 0.8; Within the scope of this, the pressure of inspiration(Pi) of high-pressure cylinder is maximum, and power is minimum.
Preferably, as a kind of embodiment, the center line of the described refrigerant intermediate flow channel of the compressor in the present embodiment and the angle between substantially horizontal are 45 degree to 90 degree.Refrigerant intermediate flow channel can design according to actual needs, generally refrigerant intermediate flow channel is designed to symmetrical shape, and so conveniently design and refrigerant flows.Fig. 3 is the graph of a relation of angle of the center line of high-pressure cylinder pressure of inspiration(Pi) and refrigerant intermediate flow channel.By Fig. 3 analysis, can draw, along with the center line of refrigerant intermediate flow channel and the increase of substantially horizontal angle, high-pressure cylinder pressure of inspiration(Pi) increases.Preferably, as a kind of embodiment, the center line of described refrigerant intermediate flow channel and the angle between substantially horizontal are 90 degree.Referring to Fig. 3, when the center line of refrigerant intermediate flow channel and the angle between substantially horizontal are 90 while spending, high-pressure cylinder pressure of inspiration(Pi) is maximum.
Finally, it should be noted that, in this patent document, the relational terms such as first, second grade is only for an entity or operation are separated with another entity or control panel, and not necessarily requires or imply and between these entities or operation, have any relation or sequentially.And, in this patent document, term " comprises ", " comprising " or its any other variant, it is intended to contain but not exclusive inclusion, thereby make to comprise process, method, article or the equipment of a series of key elements, not only comprise these key elements, but also comprise and clearly not listing and other key elements that those skilled in the art can know, or be also included as the known requisite key element of these processes, method, article or equipment.
The above embodiment has only expressed several mode of execution of the present invention, and it describes comparatively concrete and detailed, but can not therefore be interpreted as the restriction to the scope of the claims of the present invention.It should be pointed out that for the person of ordinary skill of the art, without departing from the inventive concept of the premise, can also make some distortion and improvement, these all belong to protection scope of the present invention.Therefore, the protection domain of patent of the present invention should be as the criterion with claims.

Claims (9)

1. a refrigerant intermediate flow channel for compressor, is characterized in that: described refrigerant intermediate flow channel integral body is a varying-arca channel gradually, and the inwall of described refrigerant intermediate flow channel is level and smooth.
2. refrigerant intermediate flow channel according to claim 1, is characterized in that: the sectional shape of the both sides inwall of described refrigerant intermediate flow channel is oblique line.
3. refrigerant intermediate flow channel according to claim 1, is characterized in that: the sectional shape of the both sides inwall of described refrigerant intermediate flow channel is curve.
4. according to the refrigerant intermediate flow channel described in claim 2 or 3, it is characterized in that: the area of the refrigerant entrance of described refrigerant intermediate flow channel is greater than the area of the refrigerant exit of described refrigerant intermediate flow channel, and the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 1.
5. refrigerant intermediate flow channel according to claim 4, is characterized in that: the Area Ratio of the refrigerant entrance of the refrigerant exit of described refrigerant intermediate flow channel and described refrigerant intermediate flow channel is 0.4 to 0.8.
6. according to the refrigerant intermediate flow channel described in claim 2 or 3, it is characterized in that: the center line of described refrigerant intermediate flow channel and the angle between substantially horizontal are 45 degree to 90 degree.
7. refrigerant intermediate flow channel according to claim 6, is characterized in that: the center line of described refrigerant intermediate flow channel and the angle between substantially horizontal are 90 degree.
8. a two-stage rotary compressor, comprise dispenser component, lower cylinder, lower flange, lower cover plate, increase enthalpy pump housing sucking pipe, increase enthalpy housing sucking pipe, bent axle, lower roller, pump partition plate, upper cylinder, upper roller, upper flange component, motor stator, rotor, housing, cover assembly and relief opening, described lower cylinder is fixed on the top of described lower flange, described pump partition plate is arranged on the top of described lower cylinder, it is characterized in that: also comprise the refrigerant intermediate flow channel described in claim 1 ~ 6 any one, the refrigerant intermediate flow channel of described two stage compressor comprises the lower flange runner of lower flange, the lower cylinder runner of lower cylinder and the pump partition plate runner of pump partition plate.
9. compressor according to claim 8, it is characterized in that: first flow outlet and the second runner entrance of described lower cylinder runner of described lower flange runner are in contact with one another, and the 3rd runner entrance of the second runner exit of described lower cylinder runner and described pump partition plate runner is in contact with one another, the area of the first flow entrance of described lower flange runner is greater than the area of the first flow outlet of described lower flange runner, the area of the first flow outlet of described lower flange runner is greater than the area of the second runner entrance of described lower cylinder runner, the area of the second runner entrance of described lower cylinder runner is greater than the area of the second runner exit of described lower cylinder runner, the area of the second runner exit of described lower cylinder runner is greater than the area of the 3rd runner entrance of described pump partition plate runner, the area of the 3rd runner entrance of described pump partition plate runner is greater than the area of the 3rd runner exit of described pump partition plate runner.
CN201210359718.0A 2012-09-25 2012-09-25 Coolant intermediate flow channel and include the compressor of this coolant intermediate flow channel Active CN103671120B (en)

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Publication number Priority date Publication date Assignee Title
CN105864041A (en) * 2016-05-24 2016-08-17 珠海格力节能环保制冷技术研究中心有限公司 Compressor and air conditioner with same
CN105864041B (en) * 2016-05-24 2017-11-21 珠海格力节能环保制冷技术研究中心有限公司 Compressor and there is its air conditioner

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