Gas flow segmentation variable-pressure structure of scroll compressor

Abstract

The utility model relates to the technical field of an electric scroll compressor of a vehicle air conditioner, in particular to a gas flow division variable pressure structure of a scroll compressor, which comprises a static disc, a valve plate, a limiting plate, an end cover, a plurality of independent cavities, a plurality of end cover reinforcing ribs, a flow guide cover and a plurality of static disc reinforcing ribs. The flow guide effect is achieved, so that the orderly, regular and disordered turbulence condition of gas flowing in the multiple independent cavities is improved, the pressure loss of the gas is reduced, and the performance is improved; a plurality of designed independent cavities can be considered as resistance silencing cavities connected in series, and air passing holes formed in the independent cavities are different in height and size, so that the functions of the resistance silencing cavities are achieved; an original centrifugal oil-gas separator structure is omitted, and the cost of a centrifugal tube and the like is omitted.

Description

Technical Field

[0001] The utility model relates to the technical field of automotive air-conditioning electric scroll compressors, and particularly relates to a scroll compressor gas flow splitting and pressure-changing structure. Background Art

[0002] The inner cavity structure of the end cover of an automotive electric scroll compressor is the main path for high-pressure gas to flow to the compressor exhaust hole and enter the air-conditioning system pipeline. Its structure is relatively simple and consists of a large cavity structure. The height of the cavity has a certain influence on noise, and of course, the cavity height also depends on the height boundary of the entire compressor.

[0003] Generally, a centrifugal oil-gas separator is designed in the cavity. High-pressure gas enters the oil-gas separator through the end cover cavity. Generally, the inlet aperture of the oil-gas separator is very small, resulting in throttling, which will cause a large pressure loss and affect the performance of the compressor. At the same time, the gas will form disordered and chaotic turbulence in the high-pressure cavity, and the turbulence scale is relatively large, which is likely to cause vibration of the end cover and form vibration noise. At the same time, the lubricating oil separated by the oil-gas separator has no structural guidance, resulting in the separated lubricating oil entering the high-pressure cavity again and being easily carried away by the high-pressure gas into the oil-gas separator again, thereby leading to poor separation effect, increased pressure loss, and reduced performance. Summary of the Utility Model

[0004] The purpose of the utility model is to provide a scroll compressor gas flow splitting and pressure-changing structure, which solves the problems in the prior art that when high-pressure gas enters the oil-gas separator through the end cover cavity, generally the inlet aperture of the oil-gas separator is very small, resulting in throttling, which will cause a large pressure loss and affect the performance of the compressor. At the same time, the gas will form disordered and chaotic turbulence in the high-pressure cavity, and the turbulence scale is relatively large, which is likely to cause vibration of the end cover and form vibration noise. At the same time, the lubricating oil separated by the oil-gas separator has no structural guidance, resulting in the separated lubricating oil entering the high-pressure cavity again and being easily carried away by the high-pressure gas into the oil-gas separator again, thereby leading to poor separation effect, increased pressure loss, and reduced performance.

[0005] To achieve the above purpose, the utility model provides a scroll compressor gas flow splitting and pressure-changing structure, which includes a stationary disk, a valve plate, a limiting plate, an end cover, a plurality of independent cavities, a plurality of end cover reinforcing ribs, a flow guiding cover, and a plurality of stationary disk reinforcing ribs. The end cover is arranged on one side of the stationary disk. The stationary disk has a stationary disk exhaust hole. The limiting plate is arranged inside the end cover. The valve plate is arranged on the limiting plate. A plurality of the end cover reinforcing ribs are sequentially arranged inside the end cover. The end cover has a plurality of independent cavities. The end cover also has an end cover exhaust hole and an oil return hole. The flow guiding cover is arranged inside the end cover. A plurality of the stationary disk reinforcing ribs are all arranged on the stationary disk. The flow guiding cover has a flow guiding cover exhaust hole. Each of the end cover reinforcing ribs has a plurality of air passing holes.

[0006] Among them, a plurality of the end cover reinforcing ribs are sequentially distributed around the outside of the fairing.

[0007] Among them, a plurality of the static disk reinforcing ribs are sequentially distributed around the inside of the static disk.

[0008] Among them, the limiting plate is located inside the fairing.

[0009] Among them, the valve plate is located inside the exhaust hole of the fairing.

[0010] For a vortex compressor gas flow segmentation and variable pressure structure of the present utility model, since the cavity volumes of the plurality of independent cavities do not change much, the shapes are regular, and there is a guiding effect, the gas flow in the plurality of independent cavities is orderly and regular, and the disordered turbulent flow situation is improved. Therefore, the gas pressure loss is reduced and the performance is improved; the designed plurality of independent cavities can be regarded as series-connected resistance muffler cavities, and the heights and sizes of the through holes opened in the plurality of independent cavities are different, playing the role of a resistance muffler cavity; the original centrifugal oil-gas separator structure is cancelled, and the costs such as the centrifugal tube are cancelled. Since the oil-gas separator is cancelled, considering the oil-gas separation effect, the plurality of independent cavities and the opened through holes here play the role of a labyrinth oil-gas separation. Moreover, when the compressor is assembled on the whole vehicle, the end cover exhaust hole faces upward, and the oil return hole of the oil passage for the separated oil is at the bottommost end, which is more conducive to the separation and oil return effect under the action of gravity. Description of the Drawings

[0011] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art.

[0012] Figure 1 It is a schematic structural diagram of the whole of the present utility model.

[0013] Figure 2 It is of the present utility model Figure 1 Cross-sectional view taken along line A-A.

[0014] Figure 3 It is an internal structure diagram of the whole of the present utility model.

[0015] Figure 4 It is a high-pressure gas flow direction diagram of the present utility model.

[0016] Figure 5 It is a side view of the whole of the present utility model.

[0017] Figure 6 It is of the present utility model Figure 5 Cross-sectional view taken along line B-B.

[0018] Figure 7 This is a schematic structural view of the stationary disk of the present utility model.

[0019] 1 - Stationary disk, 2 - Stationary disk exhaust hole, 3 - Valve plate, 4 - Limiting plate, 5 - End cover, 6 - Oil return hole, 7 - Independent cavity, 8 - End cover exhaust hole, 9 - End cover reinforcing rib, 10 - Flow guide cover, 11 - Air passing hole, 12 - Flow guide cover exhaust hole, 13 - Stationary disk reinforcing rib. Specific embodiments

[0020] The embodiments of the present utility model will be described in detail below. The examples of the embodiments are shown in the drawings. The embodiments described below with reference to the drawings are exemplary and are intended to explain the present utility model and should not be construed as a limitation to the present utility model.

[0021] Please refer to Figures 1 to 7 , the present utility model provides a vortex compressor gas flow splitting and variable pressure structure, including a stationary disk 1, a valve plate 3, a limiting plate 4, an end cover 5, a plurality of independent cavities 7, a plurality of end cover reinforcing ribs 9, a flow guide cover 10, and a plurality of stationary disk reinforcing ribs 13. The end cover 5 is arranged on one side of the stationary disk 1. The stationary disk 1 has a stationary disk exhaust hole 2. The limiting plate 4 is arranged inside the end cover 5. The valve plate 3 is arranged on the limiting plate 4. A plurality of the end cover reinforcing ribs 9 are sequentially arranged inside the end cover 5. The end cover 5 has a plurality of independent cavities 7. The end cover 5 also has an end cover exhaust hole 8 and an oil return hole 6. The flow guide cover 10 is arranged inside the end cover 5. A plurality of the stationary disk reinforcing ribs 13 are all arranged on the stationary disk 1. The flow guide cover 10 has a flow guide cover exhaust hole 12. Each of the end cover reinforcing ribs 9 has a plurality of air passing holes 11.

[0022] Further, a plurality of the end cover reinforcing ribs 9 are sequentially and circumferentially distributed outside the flow guide cover 10.

[0023] Further, a plurality of the stationary disk reinforcing ribs 13 are sequentially and circumferentially distributed inside the stationary disk 1.

[0024] Further, the limiting plate 4 is located inside the flow guide cover 10.

[0025] Further, the valve plate 3 is located inside the flow guide cover exhaust hole 12.

[0026] In this embodiment, there is a notch on the fairing 10 for installing the valve plate 3 and the limit plate 4 (the limit plate 4 is used to control the opening height of the valve plate 3). A relatively large exhaust hole 12 of the fairing is opened on the fairing 10. After the valve plate 3 is opened, the high-pressure gas enters the fairing 10 through the static plate exhaust hole 2, and then enters the plurality of independent chambers 7 through the exhaust hole 12 of the fairing. Each independent chamber 7 is divided by the end cover reinforcing ribs 9 with a certain thickness. The end cover reinforcing ribs 9 are provided with the air passing holes 11 with different heights and sizes. After the high-pressure gas flows out of the exhaust hole 12 of the fairing, it is divided into two paths and passes through the air passing holes 11 on the end cover reinforcing ribs 9, thereby splitting the original high-pressure and high-speed gas into two gases and respectively entering the end cover exhaust hole 8 through the air passing holes 11. Figure 4 The arrow in it indicates the flow direction of the high-pressure gas;

[0027] Since the cavity volumes of the plurality of independent chambers 7 change little, have regular shapes, and have a guiding effect, the gas flow in the plurality of independent chambers 7 is orderly and regular, and the disordered turbulent flow situation is improved. Therefore, the gas pressure loss is reduced and the performance is improved. After experimental verification, the COP is increased by 8.3% compared with the original state, and the improvement effect is quite obvious;

[0028] The designed plurality of independent chambers 7 can be considered as series-connected resistance muffler chambers. The heights and sizes of the air passing holes 11 opened in the plurality of independent chambers 7 play the role of resistance muffler chambers. Moreover, the area of the air passing holes 11 on the end cover reinforcing ribs 9 at the end cover exhaust hole 8 is relatively large. According to Bernoulli's theorem, when the whole gas enters the area of the end cover exhaust hole 8, the pressure decreases and the speed increases. Although it will increase the pressure loss, due to the improvement of the structure, the gas flow state is improved and the chaotic turbulent flow is reduced. Compared with the original state, the degree of pressure loss reduction is limited, the flow rate is guaranteed, and thus the performance of the compressor is also guaranteed. After experimental verification, the noise is reduced by 3 dB compared with the original state, achieving the expected effect;

[0029] The original centrifugal oil-gas separator structure is cancelled, and the costs such as the centrifugal tube are cancelled. Since the oil-gas separator is cancelled, considering the oil-gas separation effect, the plurality of independent chambers 7 and the opened air passing holes 11 here play the role of a labyrinth oil-gas separation. Moreover, when the compressor is assembled on the whole vehicle, the end cover exhaust hole 8 faces upward, and the oil return hole 6 of the oil channel for the separated oil is at the bottommost end, which is more conducive to the oil separation and return effect under the action of gravity.

[0030] The above disclosure is only one or more preferred embodiments of the present application, and cannot be used to limit the scope of rights of the present application. Those of ordinary skill in the art can understand all or part of the processes of implementing the above embodiments, and the equivalent changes made according to the claims of the present application still fall within the scope covered by the present application.

Claims

1. A scroll compressor gas flow division and pressure transformation structure, characterized in that: It includes a static disk, a valve plate, a limit plate, an end cover, a plurality of independent cavities, a plurality of end cover reinforcement ribs, a guide cover, and a plurality of static disk reinforcement ribs, wherein the end cover is arranged on one side of the static disk, the static disk has a static disk exhaust hole, the limit plate is arranged inside the end cover, the valve plate is arranged on the limit plate, a plurality of end cover reinforcement ribs are arranged inside the end cover in sequence, the end cover has a plurality of independent cavities, the end cover also has an end cover exhaust hole and an oil return hole, the guide cover is arranged inside the end cover, a plurality of static disk reinforcement ribs are all arranged on the static disk, the guide cover has a guide cover exhaust hole, and each end cover reinforcement rib has a plurality of air holes.

2. The scroll compressor gas flow division and pressure transformation structure according to claim 1, characterized in that: A plurality of end cover reinforcement ribs are sequentially distributed around the outside of the air guide cover.

3. The scroll compressor gas flow division and pressure transformation structure according to claim 2, characterized in that: A plurality of the static disk reinforcement ribs are sequentially distributed around the interior of the static disk.

4. The scroll compressor gas flow division and pressure transformation structure according to claim 3, characterized in that: The limiting plate is located inside the air guide cover.

5. The scroll compressor gas flow division and pressure transformation structure according to claim 4, characterized in that: The valve sheet is located inside the exhaust hole of the air guide cover.

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