CN207111444U - Double-exhaust compression assembly and rotary compressor - Google Patents
Double-exhaust compression assembly and rotary compressor Download PDFInfo
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- CN207111444U CN207111444U CN201721103376.0U CN201721103376U CN207111444U CN 207111444 U CN207111444 U CN 207111444U CN 201721103376 U CN201721103376 U CN 201721103376U CN 207111444 U CN207111444 U CN 207111444U
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- exhaust
- row stomata
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- otch
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Abstract
It the utility model is related to compressor arrangement field, disclose a kind of double-exhaust compression assembly and rotary compressor, the double-exhaust compression assembly includes cylinder (1) and is sealedly attached to the upper bearing (metal) (2) and lower bearing (3) at cylinder (1) both ends respectively, the upper bearing (metal) (2) is formed with first row stomata (20), the lower bearing (3) is formed with second row stomata (30), the aperture d2 of the second row stomata (30) is less than the aperture d1 of the first row stomata (20), to cause the capacity of the upper bearing (metal) (2) to be more than the capacity of the lower bearing (3), thus integrally-built exhaust resistance is reduced, improve compressor performance.
Description
Technical field
Compressor arrangement is the utility model is related to, more particularly to a kind of double-exhaust compression assembly and rotary compressor.
Background technology
The existing rotary compressor with double-exhaust structure, its exhaust structure as shown in Figure 1, the row on cylinder
Gas port corresponds to the first row stomata and second row stomata of upper and lower bearing respectively, and Kong Yukong axis, which overlaps, to be set, so as to obtain cylinder
The gas of discharge can discharge upper and lower bearing by first row stomata and second row stomata.With the diameter of the exhaust outlet on cylinder
For D2, a diameter of D1 of first row stomata, a diameter of D3 of second row stomata, in general design is D1=D2=D3, to cause
Exhaust outlet on cylinder is coaxial with first row stomata and second row stomata three and equal diameter it is mutually corresponding, formed and continuously arranged
Gas passage, to be exhausted by upper and lower bearing simultaneously.
However, when considering compressor efficiency, how the direction of research often reduces exhaust resistance, is vented with reducing
Efficiency caused by journey is lost.Such as the technical scheme disclosed in existing patent (application publication number CN105736374A), its
The technical problem aimed to solve the problem that is the influence for how reducing exhaust resistance for compressor efficiency, and the technological means that it is taken
It is the exhaust outlet quantity for increasing cylinder, to reduce discharge loss.
Although increase exhaust outlet quantity can substantially reduce the exhaust resistance of cylinder, such measure is typically to increase
The radial dimension of big exhaust structure or the quantity for increasing exhaust structure.But what this kind of measure often directly resulted in is structure
The increase of complexity, the structure in existing patent described above, after the exhaust outlet quantity on cylinder is added, whole compressor
Structure be required to do accommodation.
Utility model content
The purpose of this utility model is to overcome above mentioned problem existing for prior art, there is provided a kind of double-exhaust compression group
Part and rotary compressor, the double-exhaust compression assembly can make the capacity of upper bearing (metal) be more than the capacity of lower bearing, subtract
Small integrally-built exhaust resistance, improve compressor performance.
To achieve these goals, on the one hand the utility model provides a kind of double-exhaust compression assembly, including cylinder and
The upper bearing (metal) and lower bearing at the cylinder both ends are sealedly attached to respectively, and the upper bearing (metal) is formed with first row stomata, the lower axle
Hold formed with second row stomata, the aperture d2 of the second row stomata is less than the aperture d1 of the first row stomata, to cause
The capacity for stating upper bearing (metal) is more than the capacity of the lower bearing.
Preferably, such as ShiShimonoseki is met between the aperture d1 of the aperture d2 of the second row stomata and the first row stomata
System：d1>d2≥4/5d1.
Preferably, the both ends of the cylinder are formed with corresponding with the first row stomata and the second row stomata respectively
Upper exhaust otch and lower exhaust otch, the upper exhaust otch and the lower exhaust otch are formed as the cone mouth of flaring, also, institute
State the cutting-in h2 of lower exhaust otch vertically and be less than the cutting-in h1 of the upper exhaust otch vertically.
Preferably, cutting-in h1s of the cutting-in h2 of the lower exhaust otch vertically with the upper exhaust otch vertically meets
Following relation：H2 >=2/3h1, and h1 >=1/5H, wherein, H is the height of the cylinder.
Preferably, meet between the upper exhaust otch cutting-in h1 vertically and the height H of the cylinder：h1≤2/
5H。
Preferably, the upper exhaust otch is in the diameter of the upper surface of the cylinder and the aperture d1 of the first row stomata
It is equal, also, diameter of the lower exhaust otch in the lower surface of the cylinder is equal with the aperture d2 of the second row stomata.
Preferably, the gradient of the cone mouth of the upper exhaust otch and the lower exhaust otch is 30 °.
Preferably, the upper bearing (metal) is provided with upper bearing (metal) silencer, and the lower bearing is provided with lower bearing silencer.
Preferably, formed with passage on the cylinder, the refrigerant through second row stomata discharge can be logical by this
Stomata converges with the refrigerant discharged through the first row stomata.
The utility model second aspect provides a kind of rotary compressor, and the rotary compressor has above-mentioned double
Gas compression assembly.
Pass through above-mentioned technical proposal, is different from conventional thought of the prior art, and the utility model is based on to exhaust resistance
The cognition of loss occurrence position, i.e. the exhaust resistance of the gas of lower bearing discharge is to cause overall exhaust resistance to be lost most
For the point of key, because the gas discharged from lower bearing needs the same period structure ability such as hole by lower bearing silencer, cylinder
Converge with the gas of upper bearing (metal) discharge, this process causes substantial amounts of loss of refrigeration capacity and exhaust resistance to lose.Recognized based on this,
The improvement direction of inventor is to try to reduce the capacity of lower bearing, and allows gas as much as possible to be discharged by upper bearing (metal), and
The means for realizing the purpose are the exhaust resistances for increasing lower bearing relative to upper bearing (metal), to cause the exhaust resistance of lower bearing relative
Larger, according to the rule of flow of fluid, the first row stomata that more gases can pass through the less upper bearing (metal) of resistance is discharged, on a small quantity
Gas by lower bearing second row stomata discharge, therefore, caused by reducing the exhaust of lower bearing air resistance lose, lifting
Overall compressor efficiency.This improves the other positions structure that need not change double-exhaust compression assembly, only by upper
The relative size relation of the steam vent of lower bearing, which is set, to be realized, simple in construction, easy to spread, also, actual for rotary pressure
The raising effect of the efficiency of contracting machine is very notable.
Other beneficial effects of the present utility model, and the evidence for the effect above, will be entered in embodiment
One step explanation.
Brief description of the drawings
The accompanying drawing that Fig. 1 background technologies refer to
Fig. 2 is the topology view of cylinder；
Fig. 3 is to be Fig. 1 A-A that display inner structure of air cylinder is done to sectional view；
Fig. 4 is the topology view of upper bearing (metal)；
Fig. 5 is to be Fig. 4 W-W that display first row stomata set location is done to sectional view；
Fig. 6 is the topology view of lower bearing；
Fig. 7 is to be Fig. 6 P-P that display second row stomata set location is done to sectional view；
Fig. 8 is compressor efficiency by diameter ratio and the curve map of cutting-in ratio compound influence.
Description of reference numerals
1- cylinders；10- passages；2- upper bearing (metal)s；20- first row stomatas；Otch is vented on 21-；3- lower bearings；30-
Two steam vents；Otch is vented under 31-.
Embodiment
In the utility model, in the case where not making opposite explanation, the noun of locality such as " upper and lower, left and right " used is usual
Refer to typically refer to each portion for direction shown in the drawings or on vertical, vertical or neutral direction
The relationship description word of part mutual alignment." inside and outside " refers to the shell wall relative to main casing, the tube wall of each body, the side of cylinder
For wall, the space coated by the side wall of the main casing, cylinder is " interior ", and opposite side is " outer ".
According to a kind of double-exhaust compression assembly of preferred embodiment of the present utility model, including cylinder 1 is (in Fig. 2 and Fig. 3
It is shown) and the both ends that are sealedly attached to cylinder 1 respectively upper bearing (metal) 2 (Fig. 4 and Fig. 5 shown in) and lower bearing 3 (Fig. 6 and Fig. 7
Shown in), upper bearing (metal) 2 and 3 common revolving support of lower bearing have the bent axle of the piston eccentric rotary in drive cylinder 1, to cause
Double-exhaust compression assembly works.Upper bearing (metal) 2 is provided with upper bearing (metal) silencer, lower bearing 3 is provided with lower bearing silencer, with corresponding
Eliminate the exhaust noise of upper bearing (metal) 2 and lower bearing 3.
Formed with first row stomata 20 on upper bearing (metal) 2, formed with second row stomata 30 on lower bearing 3, discharge in cylinder 1
Gas is discharged by first row stomata 20 and second row stomata 30 respectively.Wherein：The aperture of first row stomata 20 is d1, second row
The aperture of stomata 30 is d2, then in order that the capacity of upper bearing (metal) 2 is more than the capacity of lower bearing 3, by the first and second exhausts
The aperture in hole is arranged to d1 ＞ d2.
When taking d1 ＞ d2, the vapour lock of first row stomata 20 is less than second row stomata 30, and the gas discharged in cylinder 1 is preferential
Discharged by first row stomata 20, remaining gas is discharged by second row stomata 30, so as to reduce the capacity of lower bearing 3.
Following checking of the above-mentioned setting based on inventor：Since long-term practice, to expand the aperture of steam vent or increase
The mode of exhaust hole number reduces exhaust resistance, to improve the mode of compressor efficiency, structure often be present and becomes increasingly complex,
But the efficiency of compressor improves degree and is obstructed.Influence the factor that compressor efficiency further improves, non-simple reduction gas
Discharge resistance.And in compression assembly exhaust process, not all exhaust resistance all improves generation to the efficiency of compressor
Adverse effect.The gas discharged by lower bearing 3 is, it is necessary to could be with after the passage 10 on cylinder 1, lower bearing silencer
The gas of discharge converges in one steam vent 20, and in this process, exhaust resistance, loss of refrigeration capacity are all higher than by the row of upper bearing (metal) 2
Gas.Therefore, in order to reduce the capacity of lower bearing 3, appropriate second row stomata 30 relative to first row stomata 20 exhaust resistance,
That is, d1 ＞ d2 are taken, compared to d1 and d2 are taken into equal value and all had more according to the efficiency of compressor during larger d1 values
It is obvious to improve.
To verify this discovery, following several groups of experiments are carried out.Experimental data is as shown in table 1, wherein, as d1 ＞ d2,
1.2% is improved relative to the d1 standard sample function effects equal with d2.As it is further preferred that further meeting between d1 and d2
It is as follows：d1>d2≥4/5d1.Comparative example 1 is as can be seen that when the difference between d2 and d1 exceeds above range, i.e. d2 is set
It is too small, the reason for also resulting in the decline of compressor efficiency, causing the phenomenon is, although the exhaust resistance of increase lower bearing can be with
The amount that gas flows through lower bearing 3 is reduced, it is still, increased on lower bearing 3 when the aperture of second row stomata 30 further reduces
Exhaust resistance influences the overall exhaust resistance of compressor, is unfavorable for the raising of compressor efficiency on the contrary.
| Bodyguard sample | H | h1 | h2 | d1 | d2 | COP |
| Standard model machine | 24 | 4.33 | 4.33 | φ8 | φ8 | 447.3 |
| Diameter factor 1 | 24 | 4.91 | 4.91 | φ8 | φ6.6 | 448.5 |
| Comparative example 1 | 24 | 4.91 | 4.91 | φ8 | φ6.3 | 446.5 |
Table 1
The both ends of cylinder 1 formed with upper exhaust otch 21 corresponding with first row stomata 20 and second row stomata 30 respectively and
Lower exhaust otch 31, upper exhaust otch 21 and lower exhaust otch 31 be formed as the cone mouth of flaring, and lower exhaust otch 31 is vertically
Cutting-in h2 is less than the cutting-in h1 of upper exhaust otch 21 vertically.Also, coordinate with foregoing d1 and d2 relative size relation,
Upper exhaust otch 21 is equal in the diameter of the upper surface of cylinder 1 and the aperture d1 of first row stomata 20, and lower exhaust otch 31 is in gas
The diameter of the lower surface of cylinder 1 is equal with the aperture d2 of second row stomata 30.Further, when upper exhaust otch 21 and lower exhaust are cut
When the gradient of the cone mouth of mouth 31 is 30 °, cutting-in is smaller, and the opening diameter of the exhaust otch end face relative with steam vent is with regard to smaller.
The efficiency of compressor can be improved to a certain extent by limiting d1 and d2 relative size relation, however, discharge
Gas comes from cylinder 1, therefore, exhaust otch up and down is further set on cylinder 1, to reduce the exhaust resistance of cylinder 1, is
The guiding of discharge directions is formed to gas when gas discharges cylinder 1, h2 is set smaller than to h1 numerical value, with relative to upper
The exhaust resistance further lower exhaust resistance of increase.
As it is further preferred that h2 and h1 meets following relation：H2 >=2/3h1, and h1 >=1/5H, and further limit
H1≤2/5H, compared with standard model machine, the efficiency of compressor is further lifted.Wherein, H is the height of the cylinder 1.Above-mentioned
Function effect experiment is compressed in parameter area, obtained experimental data is as shown in table 2, and h1 and h2 are arranged into equal value
Standard model machine, compared with the compressor of value in the range of above-mentioned parameter, efficiency is relatively low.
| Bodyguard sample | H | h1 | h2 | d1 | d2 | Efficiency |
| Standard model machine | 24 | 4.33 | 4.33 | φ8 | φ8 | 447.3 |
| Height factors 1 | 24 | 4.33 | 2.91 | φ8 | φ8 | 446.4 |
| Height factors 2 | 24 | 4.91 | 3.96 | φ8 | φ8 | 448.8 |
Table 2
Two above-mentioned unitary variant experimentations are summarized, can be obtained, it was concluded that influenceing the parameter of compressor efficiency
There are two：Diameter factor and height factors, i.e. the ratio relation between the aperture of the first and second steam vents, and on cylinder
Up and down be vented otch depth relationship.Multigroup experiment is carried out in selected parameter area, obtains data and figure in table 3
It curve map shown in 8, can be known by the data in table 3, while be set according to the direction of above-mentioned raising compressor efficiency
Therefore diameter factor and height, i.e., meet simultaneously：2/5H≥h1≥1/5H；h2≥2/3h1；D1 ＞ d2 >=4/5d1 can be obtained
Optimal compressor performance, the efficiency of compressor changes as shown in the curve in Fig. 8 under both collective effects.
| Bodyguard sample | H | h1 | h2 | d1 | d2 | Efficiency |
| Standard model machine | 24 | 4.33 | 4.33 | φ8 | φ8 | 447.3 |
| Height and diameter factor | 24 | 4.91 | 3.96 | φ8 | φ7 | 450.6 |
| Height and diameter factor | 24 | 4.91 | 3.96 | φ8 | φ6.5 | 449.5 |
Table 3
In addition, the utility model also provides a kind of rotary compressor with double-exhaust compression assembly as described above.
Preferred embodiment of the present utility model, still, the utility model and unlimited is described in detail above in association with accompanying drawing
In this.In range of the technology design of the present utility model, a variety of simple variants can be carried out to the technical solution of the utility model,
It is combined in any suitable manner including each particular technique feature, in order to avoid unnecessary repetition, the utility model
Various combinations of possible ways are no longer separately illustrated.But these simple variants and combination should equally be considered as the utility model institute
Disclosure, belong to the scope of protection of the utility model.
Claims (10)
1. a kind of double-exhaust compression assembly, including cylinder (1) and the upper bearing (metal) for being sealedly attached to cylinder (1) both ends respectively
(2) and lower bearing (3), the upper bearing (metal) (2) is formed with first row stomata (20), and the lower bearing (3) is formed with second exhaust
Hole (30), it is characterised in that the aperture d2 of the second row stomata (30) is less than the aperture d1 of the first row stomata (20), with
So that the capacity of the upper bearing (metal) (2) is more than the capacity of the lower bearing (3).
2. double-exhaust compression assembly according to claim 1, it is characterised in that the aperture d2 of the second row stomata (30)
Meet following relation between the aperture d1 of the first row stomata (20)：d1>d2≥4/5d1.
3. double-exhaust compression assembly according to claim 1 or 2, it is characterised in that the both ends of the cylinder (1) formed with
Upper exhaust otch (21) corresponding with the first row stomata (20) and the second row stomata (30) and lower exhaust otch respectively
(31), the upper exhaust otch (21) and the lower exhaust otch (31) are formed as the cone mouth of flaring, also, the lower exhaust is cut
The cutting-in h2 of mouth (31) vertically is less than the cutting-in h1 of the upper exhaust otch (21) vertically.
4. double-exhaust compression assembly according to claim 3, it is characterised in that the lower exhaust otch (31) is vertically
Cutting-in h1s of the cutting-in h2 with the upper exhaust otch (21) vertically meets following relation：H2 >=2/3h1, and h1 >=1/5H, its
In, H is the height of the cylinder (1).
5. double-exhaust compression assembly according to claim 4, it is characterised in that the upper exhaust otch (21) is vertically
Meet between the height H of cutting-in h1 and the cylinder (1)：h1≤2/5H.
6. double-exhaust compression assembly according to claim 4, it is characterised in that the upper exhaust otch (21) is in the gas
The diameter of the upper surface of cylinder (1) is equal with the aperture d1 of the first row stomata (20), also, the lower exhaust otch (31) exists
The diameter of the lower surface of the cylinder (1) is equal with the aperture d2 of the second row stomata (30).
7. double-exhaust compression assembly according to claim 4, it is characterised in that it is described it is upper exhaust otch (21) and it is described under
The gradient for being vented the cone mouth of otch (31) is 30 °.
8. double-exhaust compression assembly according to claim 1, it is characterised in that the upper bearing (metal) (2) is provided with upper bearing (metal)
Silencer, the lower bearing (3) are provided with lower bearing silencer.
9. double-exhaust compression assembly according to claim 1, it is characterised in that formed with passage on the cylinder (1)
(10) refrigerant, through the second row stomata (30) discharge can pass through the passage (10) and through the first row stomata (20)
The refrigerant of discharge converges.
10. a kind of rotary compressor, it is characterised in that the rotary compressor has as any one in claim 1-6
Double-exhaust compression assembly described in.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721103376.0U CN207111444U (en) | 2017-08-31 | 2017-08-31 | Double-exhaust compression assembly and rotary compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721103376.0U CN207111444U (en) | 2017-08-31 | 2017-08-31 | Double-exhaust compression assembly and rotary compressor |
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| CN207111444U true CN207111444U (en) | 2018-03-16 |
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| CN201721103376.0U Active CN207111444U (en) | 2017-08-31 | 2017-08-31 | Double-exhaust compression assembly and rotary compressor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107355385A (en) * | 2017-08-31 | 2017-11-17 | 广东美芝制冷设备有限公司 | Double-exhaust compression assembly and rotary compressor |
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- 2017-08-31 CN CN201721103376.0U patent/CN207111444U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107355385A (en) * | 2017-08-31 | 2017-11-17 | 广东美芝制冷设备有限公司 | Double-exhaust compression assembly and rotary compressor |
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