CN202789525U - Twin-stage enthalpy increasing compressor - Google Patents
Twin-stage enthalpy increasing compressor Download PDFInfo
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- CN202789525U CN202789525U CN 201220494645 CN201220494645U CN202789525U CN 202789525 U CN202789525 U CN 202789525U CN 201220494645 CN201220494645 CN 201220494645 CN 201220494645 U CN201220494645 U CN 201220494645U CN 202789525 U CN202789525 U CN 202789525U
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Abstract
The utility model provides a twin-stage enthalpy increasing compressor. The twin-stage enthalpy increasing compressor comprises an upper flange and a lower flange. The upper flange is provided with an upper exhaust port and an upper valve slice used for closing the upper exhaust port in an air suction process. The lower flange is provided with a lower exhaust port and a lower valve slice used for closing the lower exhaust port in the air suction process. The diameter of the head of the upper valve slice is d1, and the diameter of the head of the lower valve slice is d2. Beta is equal to the d1 divided by the d2. Beta is larger than or equal to 0.87, and is smaller than or equal to 1. Due to the fact that the size of the valve slice and the size of the exhaust port are proportionally arranged, exhaust resistance of a compressor is reduced with the same quantity of flow of freezing medium, and technical effect of increased energy efficiency is achieved.
Description
Technical field
The utility model relates to compressor field, especially, relates to a kind of Dual-level enthalpy adding compressor.
Background technique
Along with improving constantly of people's living standard, the Consumer is more and more higher to the requirement of air-conditioning system.The rolling rotor-type Dual-level enthalpy adding compressor operates steadily, low-temperature heating and the high-temperature refrigeration ability is strong, efficiency is high, thereby more and more is widely used in air-conditioning and the heat pump hot-water system.
The rolling rotor-type Dual-level enthalpy adding compressor is mainly by frame set, cover assembly, the closed chamber that lower cover forms, hot jacket is at the motor stator component of frame set inside, drag the bent axle of compressor rotation, the motor rotor component of hot jacket on bent axle, support upper flange (or upper bearing (metal)) and the lower flange (or lower bearing) of bent axle, the common low pressure stage compression chamber that forms of low pressure stage cylinder and low pressure stage roller and low pressure stage slide plate, the common high pressure stage compression chamber that forms of high pressure stage cylinder and high pressure stage roller and high pressure stage slide plate, with high pressure stage compression chamber and the separated central diaphragm of low pressure stage compression chamber, press the middle pressure part in chamber in the formation, go deep into the gas-liquid separator that the low pressure stage cylinder is communicated with the low pressure stage compression chamber, what centering pressed that the chamber carries out tonifying Qi increases the enthalpy construction package.
Existing compound compressor, upper flange is provided with the upper relief opening for the high pressure stage cylinder exhaust, is coated with exhaust valve plate on the upper relief opening; Be provided with the lower relief opening for the low pressure stage cylinder exhaust on the lower flange (or lower cylinder, or central diaphragm), be coated with lower exhaust valve plate on the lower relief opening.Because lower diameter of outlet is larger, generally according to lower relief opening design valve block; This valve block is with respect to upper relief opening, and the windage area is excessive, and under the identical operating mode, the exhaust resistance loss is larger; On the other hand, by F=Δ PS, because upper exhaust port area is little, upper relief opening inside and outside differential pressure Δ P must highlyer could realize exhaust, causes upper cylinder overcompression amount Δ P to raise, and compressor horsepower increases, and efficiency reduces.Exhaust valve plate and lower exhaust valve plate basic structure are measure-alike on the existing Dual-level enthalpy adding compressor, cause the high pressure stage exhaust resistance larger, thereby so that the efficiency of compressor integral body are lower.
The model utility content
The utility model purpose is to provide a kind of Dual-level enthalpy adding compressor, to solve the large technical problem of exhaust resistance.
For achieving the above object, the utility model provides a kind of Dual-level enthalpy adding compressor, comprises upper flange, is provided with relief opening on the upper flange and is used for the upper valve block of the upper relief opening of sealing when air-breathing; Lower flange is provided with lower relief opening and is used for the lower valve of the lower relief opening of sealing when air-breathing on the lower flange, upper valve block head diameter is d1, and the lower valve head diameter is d2, β=d1/d2,0.87≤β≤1.
Further, upper valve block length is a1, and lower valve length is a2, α=a1/a2,0.7≤α≤1.
Further, upper valve block waist width is b1, and lower valve waist width is b2, γ=b1/b2,0.52≤γ≤1.
Further, upper valve block length is a1, and the upper cylinder internal diameter is c1, δ 1=a1/c1, and 0.55≤δ 1≤0.73.
Further, lower valve length is a2, and the lower cylinder internal diameter is c2, δ 2=a2/c2, and 0.6≤δ 2≤0.8.
Further, upper valve block length is a1, upper diameter of outlet e1, and ε 1=a1/e1,3.4≤ε 1≤4.4.
Further, lower valve length is a2, lower diameter of outlet e2, and ε 2=a2/e2,3.4≤ε 2≤4.4.
Further, upper valve block head diameter is d1, upper diameter of outlet e1, and ζ 1=d1/e1,1.4≤ζ 1≤1.8.
Further, the lower valve head diameter is d2, lower diameter of outlet e2, and ζ 2=d2/e2,1.3≤ζ 2≤1.5.
The utlity model has following beneficial effect:
By the proportional setting of the size of valve block and relief opening, in the identical situation of refrigerant flow, reduced the compressor air-discharging resistance, improve the technique effect of efficiency.
Except purpose described above, feature and advantage, the utility model also has other purpose, feature and advantage.The below is described in further detail the utility model with reference to figure.
Description of drawings
The accompanying drawing that consists of the application's a part is used to provide further understanding of the present utility model, and illustrative examples of the present utility model and explanation thereof are used for explaining the utility model, do not consist of improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the valve block scheme of installation according to Dual-level enthalpy adding compressor of the present utility model;
Fig. 2 is the valve block schematic representation according to Dual-level enthalpy adding compressor of the present utility model;
Fig. 3 is according to the exhaust resistance loss of Dual-level enthalpy adding compressor of the present utility model and the change curve schematic representation of ratio beta;
Fig. 4 is according to the exhaust resistance loss of Dual-level enthalpy adding compressor of the present utility model and the change curve schematic representation of ratio cc; And
Fig. 5 is according to the exhaust resistance loss of Dual-level enthalpy adding compressor of the present utility model and the change curve schematic representation of ratio γ.
Embodiment
Below in conjunction with accompanying drawing embodiment of the present utility model is elaborated, but the multitude of different ways that the utility model can be defined by the claims and cover is implemented.
Referring to Fig. 1 to Fig. 3, according to Dual-level enthalpy adding compressor of the present utility model, comprise upper flange, be provided with relief opening on the upper flange and be used for the upper valve block of the upper relief opening of sealing when air-breathing; Lower flange is provided with lower relief opening and is used for the lower valve of the lower relief opening of sealing when air-breathing on the lower flange, upper valve block head diameter is d1, and the lower valve head diameter is d2, β=d1/d2,0.87≤β≤1.Preferably, β=0.88.The size of upper valve block and upper relief opening is proportional; The size of lower valve and lower relief opening is proportional.With rivet or screw valve block 20, valve block backboard 30 are fixed on the flange 10, the head of valve block 20 covers on the flange relief opening.By the proportional setting of the size of valve block and relief opening, in the identical situation of refrigerant flow, reduced the compressor air-discharging resistance, improve the technique effect of efficiency.
Valve block head area is less, and exhaust windage area is less, and drag losses is just less.Because upper cylinder exhaust volume flow is less, the head diameter of upper valve block is selected the value less than lower valve, and exhaust resistance is less.
Referring to Fig. 1, Fig. 2 and Fig. 4, upper valve block length is a1, and lower valve length is a2, α=a1/a2,0.7≤α≤1.Preferably, α=0.74.
Along with the α value reduces, upper valve block length shortens, and as α during less than certain value, the valve block elasticity coefficient sharply increases, and resistance to motion is apart from become large thereupon, so that exhaust resistance increases.
Referring to Fig. 1, Fig. 2 and Fig. 5, upper valve block waist width is b1, and lower valve waist width is b2, γ=b1/b2,0.52≤γ≤1.Preferably, γ=0.54.
The valve block waist is wide less, and the valve block elasticity coefficient is less, and then valve block opens resistance apart from reducing, and exhaust is used for overcoming resistance and reduces apart from acting, and the exhaust resistance loss reduces.
Referring to Fig. 1 and Fig. 2, upper valve block length is a1, and the upper cylinder internal diameter is c1, δ 1=a1/c1, and 0.55≤δ 1≤0.73, preferably, δ 1=0.59.Lower valve length is a2, and the lower cylinder internal diameter is c2, δ 2=a2/c2, and 0.6≤δ 2≤0.8, preferably, δ 2=0.8.Along with δ 1 or δ 2 ratios increase, valve block 20 length increase, and same function power lower valve 20 is stressed apart from increase, and movement velocity increases, and the exhaust resistance meeting reduces, and increase the reliability reduction but the movement velocity increase can make valve block 20 impact with backboard 30.
Referring to Fig. 1 and Fig. 2, upper valve block length is a1, upper diameter of outlet e1, and ε 1=a1/e1,3.4≤ε 1≤4.4, preferably, ε 1=4; Lower valve length is a2, lower diameter of outlet e2, and ε 2=a2/e2,3.4≤ε 2≤4.4, preferably, ε 2=4.4.
Referring to Fig. 1 and Fig. 2, upper valve block head diameter is d1, upper diameter of outlet e1, and ζ 1=d1/e1,1.4≤ζ 1≤1.8, preferably, ζ 1=1.6; The lower valve head diameter is d2, lower diameter of outlet e2, and ζ 2=d2/e2,1.3≤ζ 2≤1.5, preferably, ζ 2=1.5.
Table 1
As shown in table 1, ζ 1 value reduces, and upper valve block head diameter reduces, and as shown in Table 1, the exhaust resistance loss reduces.If but head diameter is too small, can reduce the sealing of valve block and relief opening, leakage rate sharply increases, and affects the refrigerating capacity of compressor.
For ζ 2 values, owing to be compound compressor, the lower cylinder working pressure is low, and the valve block inside and outside differential pressure is low, and the lower valve head can be less than upper valve block head, also can guarantee sealing.
The the underlying cause of valve block 20 each adopting parameters is size, and the position of exhaust port of size, the exhaust port of its air displacement.Under the certain condition of valve block material, thickness, all adopting parameters all can have influence on lifting surface area, moment, the movement velocity of valve block, and then affect exhaust resistance.
Not digital being labeled as the parameters definition of conception of band among the figure among the application, for example e represents diameter of outlet, d represents the valve block head diameter, a represents valve block length, and b represents valve block waist width, and the mark of band numeral (for example: a1, a2,) in numeral " 1 " and " 2 " refer to respectively mark to upper member and lower member, for example a1 is upper valve block length, a2 is lower valve length.
As can be seen from the above description, the utility model the above embodiments have realized following technique effect:
By the proportional setting of the size of valve block and relief opening, in the identical situation of refrigerant flow, reduced the compressor air-discharging resistance, improve the technique effect of efficiency.
The above is preferred embodiment of the present utility model only, is not limited to the utility model, and for a person skilled in the art, the utility model can have various modifications and variations.All within spirit of the present utility model and principle, any modification of doing, be equal to replacement, improvement etc., all should be included within the protection domain of the present utility model.
Claims (9)
1. a Dual-level enthalpy adding compressor is characterized in that, comprising:
Upper flange is provided with relief opening and is used for sealing when air-breathing the upper valve block of described upper relief opening on the described upper flange;
Lower flange is provided with lower relief opening and is used for sealing when air-breathing the lower valve of described lower relief opening on the described lower flange;
Described upper valve block head diameter is d1, and described lower valve head diameter is d2, β=d1/d2,0.87≤β≤1.
2. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described upper valve block length is a1, and described lower valve length is a2, α=a1/a2,0.7≤α≤1.
3. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described upper valve block waist width is b1, and described lower valve waist width is b2, γ=b1/b2,0.52≤γ≤1.
4. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described upper valve block length is a1, and the upper cylinder internal diameter is c1, δ 1=a1/c1, and 0.55≤δ 1≤0.73.
5. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described lower valve length is a2, and the lower cylinder internal diameter is c2, δ 2=a2/c2, and 0.6≤δ 2≤0.8.
6. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described upper valve block length is a1, described upper diameter of outlet e1, and ε 1=a1/e1,3.4≤ε 1≤4.4.
7. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described lower valve length is a2, described lower diameter of outlet e2, and ε 2=a2/e2,3.4≤ε 2≤4.4.
8. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described upper valve block head diameter is d1, described upper diameter of outlet e1, and ζ 1=d1/e1,1.4≤ζ 1≤1.8.
9. Dual-level enthalpy adding compressor according to claim 1 is characterized in that,
Described lower valve head diameter is d2, described lower diameter of outlet e2, and ζ 2=d2/e2,1.3≤ζ 2≤1.5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220494645 CN202789525U (en) | 2012-09-25 | 2012-09-25 | Twin-stage enthalpy increasing compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220494645 CN202789525U (en) | 2012-09-25 | 2012-09-25 | Twin-stage enthalpy increasing compressor |
Publications (1)
| Publication Number | Publication Date |
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| CN202789525U true CN202789525U (en) | 2013-03-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201220494645 Withdrawn - After Issue CN202789525U (en) | 2012-09-25 | 2012-09-25 | Twin-stage enthalpy increasing compressor |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103591027A (en) * | 2013-11-18 | 2014-02-19 | 广东美芝制冷设备有限公司 | Discharge valve plate for compressor and compressor provided with same |
| CN103671116A (en) * | 2012-09-25 | 2014-03-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Two-stage enthalpy-increasing compressor |
| CN104989627A (en) * | 2015-07-23 | 2015-10-21 | 珠海凌达压缩机有限公司 | Compressor and flapper valve block thereof |
| CN109595168A (en) * | 2017-09-30 | 2019-04-09 | 广东美芝制冷设备有限公司 | Compressor |
-
2012
- 2012-09-25 CN CN 201220494645 patent/CN202789525U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671116A (en) * | 2012-09-25 | 2014-03-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Two-stage enthalpy-increasing compressor |
| CN103591027A (en) * | 2013-11-18 | 2014-02-19 | 广东美芝制冷设备有限公司 | Discharge valve plate for compressor and compressor provided with same |
| CN104989627A (en) * | 2015-07-23 | 2015-10-21 | 珠海凌达压缩机有限公司 | Compressor and flapper valve block thereof |
| CN109595168A (en) * | 2017-09-30 | 2019-04-09 | 广东美芝制冷设备有限公司 | Compressor |
| CN109595168B (en) * | 2017-09-30 | 2024-06-11 | 广东美芝制冷设备有限公司 | Compressor with a compressor body having a rotor with a rotor shaft |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130313 Effective date of abandoning: 20161005 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |