WO2019085501A1

WO2019085501A1 - Compressor and an air-conditioning system having same

Info

Publication number: WO2019085501A1
Application number: PCT/CN2018/091619
Authority: WO
Inventors: 胡余生; 魏会军; 余冰; 杨欧翔; 王珺; 张心爱; 苗朋柯
Original assignee: 珠海格力节能环保制冷技术研究中心有限公司; 珠海格力电器股份有限公司
Priority date: 2017-11-03
Filing date: 2018-06-15
Publication date: 2019-05-09
Also published as: CN108087238B; CN108087238A

Abstract

Disclosed are a compressor (100) and an air-conditioning system having same. The compressor (100) comprises a housing (10), a pump body assembly and an enthalpy-adding component (70), wherein the pump body assembly comprises: a first-level compression cylinder (20) and a second-level compression cylinder (30) both arranged in the housing (10); and a central cavity (40) arranged in the housing (10), wherein a refrigerant flowing out from the first-level compression cylinder (20) passes through the central cavity (40) and then enters the second-level compression cylinder (30), the central cavity (40) is provided with a supplementary air inlet (41) in communication with the enthalpy-adding component (70), and a working volume V1 of the first-level compression cylinder (20) and a working volume V2 of the second-level compression cylinder (30) meet the following condition that a value range of V2/V1 is 0.56 - 0.75.

Description

Compressor and air conditioning system therewith

Related application

This application claims the benefit of priority to the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the benefit of the disclosure.

Technical field

The present application relates to the field of air conditioning, and in particular to a compressor and an air conditioning system therewith.

Background technique

As the outdoor ambient temperature increases, the demand for indoor cooling capacity increases, but the air conditioning cooling capacity decreases as the outdoor temperature increases. This is because the ambient temperature rises and the condensing temperature of the air conditioner rises, which leads to an increase in the compressor discharge pressure, an increase in the compressor operating pressure difference, a decrease in volumetric efficiency, and a decrease in the refrigerant circulation flow rate. As the superheat of the exhaust gas increases, the liquid supercooling temperature rises, which causes the refrigerant enthalpy difference at the inlet and outlet of the evaporator to decrease, further reducing the air conditioning refrigeration capacity.

In tropical and desert areas (such as the Middle East), the outdoor ambient temperature can reach up to 50 °C, and the cooling capacity of air conditioners is seriously attenuated, which is difficult to meet indoor refrigeration demand. On the other hand, due to the high exhaust pressure, the compressor runs for a long time. Under the conditions of high pressure difference and high temperature discharge, the compressor has large running load, faster wear and short life.

Summary of the invention

The present application is directed to providing a compressor and an air conditioning system therewith, which solves the problem that the refrigeration capacity of the prior art air conditioner is severely attenuated when it is outdoors at a high temperature, and it is difficult to meet the indoor cooling capacity requirement and the comfort is poor.

In order to achieve the above object, according to an aspect of the present application, a compressor including a housing, a pump body assembly, and a boring member, the pump body assembly including: a first stage compression cylinder and a second stage compression cylinder are provided The intermediate chamber is disposed in the housing, and the refrigerant flowing out of the first-stage compression cylinder passes through the intermediate chamber and enters into the second-stage compression cylinder, wherein the intermediate chamber has a supplementary airflow inlet communicating with the augmenting member; The working volume V1 of the first stage compression cylinder and the working volume V2 of the second stage compression cylinder satisfy the following relationship: V2/V1 ranges from 0.56 to 0.75.

Further, the working volume V1 of the first stage compression cylinder and the working volume V2 of the second stage compression cylinder further satisfy the following relationship: the value range of V2/V1 is 0.64-0.68.

Further, the ratio of the equivalent diameter Dm of the supplementary gas inlet to the equivalent diameter D1 of the inlet of the first stage compression cylinder is λ, and λ ranges from 0.3 to 0.7.

Further, a supplemental valve plate and a valve flap are provided at the inlet of the supplementary airflow.

Further, the intermediate chamber further has an intake port communicating with the exhaust port of the first stage compression cylinder and an exhaust port communicating with the intake port of the second stage compression cylinder.

Further, the second stage compression cylinder is located above the first stage compression cylinder, and a flange structure is disposed below the first stage compression cylinder, and the intermediate cavity is formed in the flange structure.

According to another aspect of the present application, an air conditioning system is provided, including a compressor, the compressor being the compressor described above.

Further, the air conditioning system further includes an evaporator, a condenser and a flasher, the evaporator is connected to the air inlet of the compressor, the condenser is connected to the exhaust port of the compressor, the inlet of the flasher is connected to the condenser, and the flasher is connected. The first outlet is connected to the evaporator, the second outlet of the flasher is connected to the augmenting component of the compressor, and a pressure relief valve is disposed between the second outlet of the flasher and the augmenting component.

Further, the pressure relief valve has an opening pressure P1, the opening pressure P1 is greater than the intake pressure Ps of the compressor and smaller than the exhaust pressure Pd, and the opening pressure P1 ranges from

Further, the opening pressure P1 ranges from

Further, a first throttling device is disposed between the condenser and the flasher, and/or a second throttling device is disposed between the flasher and the evaporator.

Applying the technical solution of the present application, the compressor is provided with a reinforcing member and an intermediate chamber, and the intermediate chamber has a supplementary airflow inlet communicating with the reinforcing member. Therefore, the compressor of the embodiment opens the air supply and the enthalpy after the outdoor temperature reaches a predetermined value. At the time of air entrainment, the refrigerant that has flowed from the entanglement member into the intermediate chamber through the make-up air inlet is mixed with the refrigerant flowing out of the first-stage compression cylinder, and then sucked into the second-stage compression cylinder. Through the above process, the refrigeration capacity is significantly higher than that of the conventional compressor, and the refrigeration capacity and comfort of the air conditioning system at high temperatures are improved. At the same time, the ratio V2/V1 of the working volume V1 of the first-stage compression cylinder and the working volume V2 of the second-stage compression cylinder is 0.56-0.75, which can simultaneously satisfy the compressor in the non-compensation mode and the supplemental air mode. The performance is better.

DRAWINGS

The accompanying drawings, which are incorporated in the claims of the claims In the drawing:

Figure 1 shows a schematic cross-sectional view of an embodiment of a compressor according to the present application;

Figure 2 shows an enlarged view of A of the compressor of Figure 1;

Figure 3 is a schematic view showing the structure of the intermediate chamber of the compressor of Figure 1;

Figure 4 shows a schematic cross-sectional view of an embodiment of an air conditioner according to the present application;

Figure 5 is a schematic view showing a comparison of the operational effects of the air conditioning system of the compressor of Figure 1 and a conventional compression system;

Figure 6 is a schematic illustration of the effect of the working volume ratio of the compressor of Figure 1 on performance in two modes of operation;

Figure 7 is a graphical representation of the effect of the makeup air inlet parameter of the compressor of Figure 1 on compressor performance.

Wherein, the above figures include the following reference numerals:

10. Housing; 20, first stage compression cylinder; 30, second stage compression cylinder; 40, intermediate chamber; 41, supplementary air inlet; 42, air supply valve; 43, valve flap; 45; exhaust port; 50, flange structure; 61, evaporator; 62, condenser; 63, flasher; 64, pressure relief valve; 65, first throttle device; 66, second throttle device 70, reinforced components; 100, compressor.

Detailed ways

The technical solutions in the embodiments of the present application are clearly and completely described in the following with reference to the drawings in the embodiments of the present application. It is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. The following description of the at least one exemplary embodiment is merely illustrative and is in no way All other embodiments obtained by a person of ordinary skill in the art based on the embodiments of the present application without departing from the inventive scope are the scope of the present application.

It is to be noted that the terminology used herein is for the purpose of describing particular embodiments, and is not intended to limit the exemplary embodiments. As used herein, the singular " " " " " " There are features, steps, operations, devices, components, and/or combinations thereof.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments are not intended to limit the scope of the application, unless otherwise specified. In the meantime, it should be understood that the dimensions of the various parts shown in the drawings are not drawn in the actual scale relationship for the convenience of the description. Techniques, methods and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the techniques, methods and apparatus should be considered as part of the authorization specification. In all of the examples shown and discussed herein, any specific values are to be construed as illustrative only and not as a limitation. Accordingly, other examples of the exemplary embodiments may have different values. It should be noted that similar reference numerals and letters indicate similar items in the following figures, and therefore, once an item is defined in one figure, it is not required to be further discussed in the subsequent figures.

In view of the problems mentioned in the background art, the present application provides a two-stage 増焓 rotary compressor, which is especially suitable for air conditioning in the Middle East, which can solve the problem of air conditioning refrigeration attenuation at outdoor high temperature, and can improve the reliability of the compressor. Rotary compressors operate reliably for long periods of time in high temperature areas.

As shown in FIGS. 1 to 3, the compressor of the present embodiment includes a housing 10, a pump body assembly, and a tampering member 70. The pump body assembly includes a first stage compression cylinder 20, a second stage compression cylinder 30, and an intermediate chamber. 40. The first stage compression cylinder 20 and the second stage compression cylinder 30 are both disposed within the housing 10. The intermediate chamber 40 is disposed in the housing 10, and the refrigerant flowing out of the first stage compression cylinder 20 passes through the intermediate chamber 40 and enters into the second stage compression cylinder 30. The intermediate chamber 40 has a supplementary air inlet connected to the augmenting member 70. 41. The working volume V1 of the first stage compression cylinder 20 and the working volume V2 of the second stage compression cylinder 30 satisfy the following relationship:

V2/V1 ranges from 0.56 to 0.75.

With the technical solution of the present embodiment, the compressor is provided with a reinforcing member 70 and an intermediate chamber 40 having a supplementary air inlet 41 communicating with the reinforcing member 70. Therefore, the compressor of the embodiment opens the air supply and the enthalpy after the outdoor temperature reaches a predetermined value. At the time of air entrainment, the refrigerant that has flowed into the intermediate chamber from the replenishing air inlet 41 through the replenishing air inlet 41 is mixed with the refrigerant that has flowed out of the first-stage compression cylinder 20, and then sucked into the second-stage compression cylinder 30. Through the above process, the refrigeration capacity is significantly higher than that of the conventional compressor, and the refrigeration capacity and comfort of the air conditioning system at high temperatures are improved. At the same time, the ratio V2/V1 of the working volume V1 of the first-stage compression cylinder 20 and the working volume V2 of the second-stage compression cylinder 30 is 0.56-0.75, which can satisfy both the non-compensation mode and the qi mode. The performance of the compressor is superior.

Fig. 5 is a view showing a comparison of the operational effects of the air conditioning system of the compressor of Fig. 1 and a conventional compression system. The broken line in the figure indicates the operation effect of the conventional single-machine compression system, and the solid line in the figure indicates the operation effect of the air-conditioning system to which the compressor of Fig. 1 is applied. It can be seen from FIG. 5 that the air conditioning system of the compressor of the present embodiment is in the state of shutting off when the outdoor temperature does not reach T043 ° C, and when the outdoor temperature reaches T043 ° C, the air supply is turned on, and the cooling capacity is turned on. Significantly higher than the refrigeration system using conventional compressors, improving the cooling capacity and comfort of air conditioners at high temperatures.

Figure 6 is a graphical representation of the effect of the working volume ratio of the compressor of Figure 1 on performance in both modes of operation. The upper curve in the figure is the performance curve in the open air mode, and the lower curve in the figure is the performance curve in the closed air mode. In the venting mode, the volume ratio is too large or too small, which affects the balance of the compression ratio of the two cylinders, thus affecting the overall efficiency; when the venting gas is opened, the volume ratio is too large, and the compression power is increased due to the increase of the qi volume. The COP energy efficiency ratio is reduced, and the volume ratio is too small. The amount of cooling caused by qi is too small, and the COP energy efficiency ratio is also reduced. It can be seen from the figure that the ratio V2/V1 of the working volume V1 of the first stage compression cylinder 20 to the working volume V2 of the second stage compression cylinder 30 is 0.56-0.75, which can simultaneously satisfy the compression in two modes. Machine performance is better. The compressor of the embodiment can improve the refrigeration efficiency of the compressor under the condition of the off-gas, and realize the optimal energy efficiency under the condition of the open air.

Further preferably, the working volume V1 of the first stage compression cylinder 20 and the working volume V2 of the second stage compression cylinder 30 further satisfy the following relationship: V2 / V1 ranges from 0.64 to 0.68. At this point the compressor performs best.

As shown in Fig. 2, in the present embodiment, the ratio of the equivalent diameter Dm of the supplementary airflow inlet 41 to the equivalent diameter D1 of the intake port of the first-stage compression cylinder 20 is λ, and λ is in the range of 0.3-0.7. At this time, the compressor performance is superior. This is because if λ is too small, the resistance of the qi flow increases rapidly, and if the λ is too large and the qi flow is too slow, the qi heat loss is too large, which affects the qi quality. Figure 7 is a graphical representation of the effect of the makeup air inlet parameter of the compressor of Figure 1 on compressor performance. It can also be seen from the figure that the compressor performance is better when the value of λ is in the range of 0.3-0.7.

As shown in FIG. 3, in the present embodiment, the supplemental airflow inlet 41 is provided with a supplemental valve piece 42 and a valve flapper 43. The makeup valve plate 42 and the valve flapper 43 determine the opening condition of the makeup air inlet 41, and the makeup air inlet 41 is opened when the refrigerant pressure at the makeup air inlet 41 is greater than a predetermined value.

As shown in FIG. 3, in the present embodiment, the intermediate chamber 40 further has an intake port 44 communicating with the exhaust port of the first stage compression cylinder 20 and exhaust gas communicating with the intake port of the second stage compression cylinder 30. Mouth 45. A valve disc is also provided at the suction port 44. The suction port 44, the exhaust port 45, and the makeup air inlet 41 are all disposed on the outer wall of the intermediate chamber and are located on the same plane.

As shown in FIG. 1, the second stage compression cylinder 30 is located above the first stage compression cylinder 20, and a flange structure 50 is disposed below the first stage compression cylinder 20, and the intermediate chamber 40 is formed in the flange structure 50. The flange structure 50 is a lower flange, and the lower flange is recessed to form an intermediate cavity 40.

The first stage compression cylinder 20 is further provided with an overflow passage that communicates the intake port of the second stage compression cylinder 30 and the exhaust port 45 of the intermediate chamber 40, and an overcurrent passage that communicates the augmenting member 70 and the makeup air inlet 41.

The compressor of this embodiment further includes a liquid separator, a motor, a crankshaft, a flange, a cover plate, a partition plate, and a refrigerating oil. These structures are basically the same as those in the prior art, and are not described herein again.

The present application also provides an air conditioning system. As shown in FIG. 4, the air conditioning system according to the present application includes a compressor, and the compressor is the above-described compressor. Due to the use of the above compressor, the refrigeration capacity and comfort of the air conditioning system at high temperatures are improved. At the same time, it can simultaneously satisfy the performance of the compressor in the non-compensation mode and the supplemental air mode.

As shown in FIG. 4, in the present embodiment, the air conditioning system further includes an evaporator 61, a condenser 62, and a flasher 63. The evaporator 61 is connected to the intake port of the compressor 100, and the condenser 62 and the row of the compressor 100 are connected. The port is connected, the inlet of the flasher 63 is connected to the condenser 62, the first outlet (gas outlet) of the flasher 63 is connected to the evaporator 61, and the second outlet of the flasher 63 is connected to the augmenting unit 70 of the compressor. A pressure relief valve 64 is disposed between the second outlet (liquid outlet) of the steamer 63 and the augmenting member 70. The air conditioning system of the present embodiment can automatically switch the qi through the pressure relief valve 64 according to the operating pressure.

The pressure relief valve 64 has an opening pressure P1. When the working pressure is greater than P1, the pressure relief valve 64 is opened; when the working pressure is less than P1, the pressure relief valve 64 is closed. The opening pressure P1 is greater than the intake pressure Ps of the compressor and smaller than the exhaust pressure Pd, and the opening pressure P1 ranges from

The compressor operates at the best energy efficiency when the opening pressure P1 satisfies the above conditions.

Further preferably, the opening pressure P1 ranges from

As shown in FIG. 4, a first throttle device 65 is disposed between the condenser 62 and the flasher 63, and a second throttle device 66 is disposed between the flasher 63 and the evaporator 61.

Referring to FIGS. 1 and 4, the refrigerant flow process of the air conditioning system of the present embodiment is as follows:

The compressor 100 sucks in the low-temperature low-pressure refrigerant (refer to reference numeral 1 in Fig. 1) flowing out from the evaporator 61, is compressed by the first-stage compression cylinder 20, and is discharged to the intermediate chamber 40 (see reference numeral 2 in Fig. 1), second. The stage compression cylinder 30 draws air from the intermediate chamber 40, compresses the refrigerant to a high temperature and high pressure, and then discharges the pump body (see reference numeral 5 in Fig. 1), flows through the motor and is discharged through the compressor exhaust pipe (see reference numeral 6 in Fig. 1). The high-temperature and high-pressure gas refrigerant is heated by the condenser 62 to form a high-pressure liquid refrigerant, which is changed into a gas-liquid two-phase medium-pressure refrigerant through the first throttling device 65, and the medium-pressure gas state after the gas-liquid separation of the flasher 63 The refrigerant flows into the intermediate chamber through the pressure relief valve 64 (see reference numeral 3 in Fig. 1), is mixed with the exhaust gas of the first stage compression cylinder 20, and is sucked into the second stage compression cylinder (see reference numeral 4 in Fig. 1). The pressurized refrigerant enters the evaporator 61 after being throttled by the second throttling device 66, and becomes a liquid separator that enters the compressor 100 by low temperature and low pressure gas cooling after the heat absorption.

From the above description, it can be seen that the above-mentioned embodiments of the present application achieve the following technical effects:

1. This application proposes a two-stage rotary compressor and air conditioning circulation system, which can ensure the high energy efficiency of the air conditioner under normal refrigeration conditions, and can realize the output of the cooling capacity under high temperature environment, especially Significant advantages in energy saving and comfort in hot climates such as the Middle East;

2. The present application provides a switching device for controlling the switching of the two-stage helium compressor switch, which can automatically switch the air supply according to the outdoor temperature, and has the characteristics of low cost and reliable switching;

3. The two-stage rotary compressor of the present application proposes an optimal volume ratio (the ratio of the working volume of the high-pressure cylinder to the working volume of the low-pressure cylinder), which can improve the compressor indication under the condition of shut-off gas. Efficiency, and achieve the optimal energy efficiency under the conditions of open air.

In the description of the present application, it is to be understood that orientations such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" and the like are indicated. Or the positional relationship is generally based on the orientation or positional relationship shown in the drawings, and is merely for the convenience of the description of the present application and the simplified description, which are not intended to indicate or imply the indicated device or component. It must be constructed and operated in a specific orientation or in a specific orientation, and thus is not to be construed as limiting the scope of the application; the orientations "inside and outside" refer to the inside and outside of the contour of the components themselves.

For ease of description, spatially relative terms such as "above", "above", "on top", "above" may be used herein. And the like, used to describe the spatial positional relationship of one device or feature as shown in the figures with other devices or features. It will be understood that the spatially relative terms are intended to encompass different orientations in the <RTIgt; For example, if the device in the figures is inverted, the device described as "above other devices or configurations" or "above other devices or configurations" will be positioned "below other devices or configurations" or "at Under other devices or configurations." Thus, the exemplary term "above" can include both "over" and "under". The device can also be positioned in other different ways (rotated 90 degrees or at other orientations) and the corresponding description of the space used herein is interpreted accordingly.

In addition, it should be noted that the use of the words "first", "second", etc. to limit the components is only to facilitate the distinction between the corresponding components, if not stated otherwise, the above words have no special meaning, so can not understand Limitations on the scope of protection of this application.

The above description is only the preferred embodiment of the present application, and is not intended to limit the present application, and various changes and modifications may be made to the present application. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of this application are intended to be included within the scope of the present application.

Claims

A compressor comprising a housing (10), a pump body assembly, and a tamping member (70), the pump body assembly comprising:

a first stage compression cylinder (20) and a second stage compression cylinder (30) are disposed in the housing (10);

An intermediate chamber (40) disposed in the housing (10), and refrigerant flowing out of the first stage compression cylinder (20) passes through the intermediate chamber (40) and enters the second stage compression cylinder (30), the intermediate chamber (40) has a supplemental airflow inlet (41) in communication with the augmenting member (70);

Wherein, the working volume V1 of the first-stage compression cylinder (20) and the working volume V2 of the second-stage compression cylinder (30) satisfy the following relationship:

V2/V1 ranges from 0.56 to 0.75.
The compressor according to claim 1, characterized in that the working volume V1 of the first stage compression cylinder (20) and the working volume V2 of the second stage compression cylinder (30) further satisfy the following relationship:

V2/V1 ranges from 0.64 to 0.68.
The compressor according to claim 1, wherein a ratio of an equivalent diameter Dm of said make-up air inlet (41) to an equivalent diameter D1 of an intake port of said first-stage compression cylinder (20) is λ, The value of λ ranges from 0.3 to 0.7.
The compressor according to claim 1, characterized in that the makeup air inlet (41) is provided with a gas supply valve piece (42) and a valve flap (43).
The compressor according to claim 1, wherein said intermediate chamber (40) further has an intake port (44) communicating with an exhaust port of said first stage compression cylinder (20) and said The exhaust port (45) of the second stage compression cylinder (30) is connected to the suction port.
The compressor according to claim 1, wherein said second stage compression cylinder (30) is located above said first stage compression cylinder (20) below said first stage compression cylinder (20) A flange structure (50) is provided, and the intermediate cavity (40) is formed in the flange structure (50).
An air conditioning system comprising a compressor, wherein the compressor is the compressor of any one of claims 1 to 6.
The air conditioning system according to claim 7, wherein said air conditioning system further comprises an evaporator (61), a condenser (62), and a flasher (63), said evaporator (61) and said compressor An air inlet connection, the condenser (62) is connected to an exhaust port of the compressor, an inlet of the flasher (63) is connected to the condenser (62), and the flasher (63) The first outlet is connected to the evaporator (61), the second outlet of the flasher (63) is connected to the augmenting component (70) of the compressor, and the second outlet of the flasher (63) A pressure relief valve (64) is disposed between the augmenting member (70).
The air conditioning system according to claim 8, wherein said pressure relief valve (64) has an opening pressure P1 that is greater than an intake pressure Ps of said compressor and smaller than said exhaust pressure Pd The opening pressure P1 ranges from
The air conditioning system according to claim 9, wherein said opening pressure P1 has a value range of
The air conditioning system according to claim 8, characterized in that a first throttle device (65) is provided between the condenser (62) and the flasher (63), and/or the flasher A second throttling device (66) is disposed between the evaporator (61) and the evaporator (61).