WO2020253185A1

WO2020253185A1 - Compressor and air conditioner

Info

Publication number: WO2020253185A1
Application number: PCT/CN2019/127515
Authority: WO
Inventors: 苗旺; 阙沛祯; 梁文斌; 赵逸; 翟元彬; 马舒院
Original assignee: 珠海格力节能环保制冷技术研究中心有限公司
Priority date: 2019-06-21
Filing date: 2019-12-23
Publication date: 2020-12-24
Also published as: CN110159532A

Abstract

A compressor and an air conditioner. The compressor comprises a low-pressure stage compression portion. The low-pressure stage compression portion comprises a first compression structure and a second compression structure. The first compression structure has a first exhaust chamber (11), and the second compression structure has a second exhaust chamber (21). The first exhaust chamber (11) is in communication with the second exhaust chamber (21) by means of a gas supplement passage (3), and the gas supplement passage (3) is in communication with a gas supplement port (31).

Description

Compressor and air conditioner

This application is based on the application with the CN application number 201910544719.4 and the filing date of June 21, 2019, and claims its priority. The disclosure of the CN application is hereby incorporated into this application as a whole.

Technical field

The present disclosure belongs to the technical field of air conditioning adjustment, and specifically relates to a compressor and an air conditioner.

Background technique

The statements in this section merely provide background information related to the present disclosure, and do not necessarily constitute prior art.

With the comprehensive popularization and promotion of air conditioners, air conditioners have also been widely used in the northern extreme cold regions. However, when the ordinary air source heat pump is in a low temperature environment, as the ambient temperature drops, the system evaporation temperature will drop, and the compressor suction specific volume The increase causes the compressor compression ratio to increase, which exceeds the critical value for normal operation of the ordinary single-stage rotor compressor system (the critical value of the compression ratio of positive displacement compressor is 8-10), so that the gas transmission coefficient decreases and the heating capacity decreases. In order to increase the compression ratio of the rotor compressor and satisfy that the air conditioner can continue to work in a lower temperature environment, most of the rotor compressor adopts a two-stage compression structure, in order to further improve the refrigeration/system. The two-stage compression structure usually adopts the method of two-stage throttling to increase the enthalpy of heat and reduce the exhaust temperature. The conventional method of supplementing is to directly supplement the air at the suction port of the second cylinder of the rotor compressor. .

Summary of the invention

The first aspect of the present disclosure provides a compressor, including:

The low-pressure stage compression section has air supplement channels and air supplement ports;

Among them, the low-pressure stage compression part includes a first compression structure and a second compression structure. The first compression structure has a first exhaust chamber, the second compression structure has a second exhaust chamber, the first exhaust chamber and the second exhaust chamber They are communicated with each other through the air supplement channel, and the air supplement channel is connected with the air supplement port.

In some embodiments, the compressor further includes a crankshaft, the first compression structure includes a first flange, a first cylinder, and a first diaphragm, and the second compression structure includes a second cylinder and a second diaphragm. The first flange, The first cylinder, the first partition, the second cylinder and the second partition are sequentially sleeved on the crankshaft, the first exhaust chamber is provided on the first flange, and the second exhaust chamber is provided on the second partition.

In some embodiments, the supplemental air port is configured on the second cylinder, the first cylinder, or the first partition.

In some embodiments, the first compression structure further includes a first cover plate, the first exhaust chamber has an opening, the opening faces a side away from the first cylinder, and the first cover plate covers the opening of the first exhaust chamber; and/ Or, the second compression structure further includes a third partition, the second exhaust chamber has an opening, the opening faces a side away from the second cylinder, and the third partition covers the opening of the second exhaust chamber.

In some embodiments, a one-way stop valve is provided at the air supplement port.

In some embodiments, the first exhaust chamber has a first supplemental valve port, and the first supplemental valve port is provided with a one-way stop valve; and/or, the second exhaust chamber has a second supplemental valve port, A one-way stop valve is provided at the second air supply valve port.

In some embodiments, the one-way stop valve includes a valve disc baffle and a valve disc, and the valve disc and the valve disc baffle are stacked in sequence and formed into a whole by fasteners.

In some embodiments, the compressor further includes a high-pressure stage compression part, the high-pressure stage compression part has a suction port, and the suction port communicates with the exhaust passage of the low-pressure stage compression part.

In some embodiments, the compressor is a three-cylinder two-stage compressor.

A second aspect of the present disclosure provides an air conditioner, including the compressor as provided in any one of the first aspects of the present disclosure.

Description of the drawings

Figure 1 is a schematic diagram of the internal structure of a compressor according to an embodiment of the disclosure;

Figure 2 is a partial enlarged view of A in Figure 1;

FIG. 3 is a schematic diagram of the internal structure of the compressor of the embodiment of the disclosure from another perspective;

4 is a schematic diagram of the structure of the second partition in FIG. 1;

Fig. 5 is a graph showing the change of the compressor suction volume and the cylinder gas refrigerant working pressure with the rotation angle according to the embodiment of the disclosure.

The reference signs are indicated as:

11. The first exhaust chamber; 12. The first flange; 13. The first cylinder; 14. The first partition plate; 15. The first cover plate; 21. The second exhaust chamber; 22. The second cylinder; 23 , The second partition; 231, the exhaust port; 24, the third partition; 3. the air supplement channel; 31, the air supplement port; 4. the one-way stop valve; 41, the valve plate baffle; 42, the valve plate; 43 , Fasteners; 51, suction port; 52, exhaust passage; 61, third cylinder; 62, second flange; 100, crankshaft; 200, motor assembly.

Detailed ways

In order to make the objectives, technical solutions, and advantages of the present disclosure clearer, the compressor and the air conditioner of the present disclosure will be further described in detail below through embodiments and in conjunction with the accompanying drawings. It should be understood that the specific embodiments described herein are only used to explain the present disclosure, but not used to limit the present disclosure.

With reference to Figures 1 to 5, according to an embodiment of the present disclosure, a compressor is provided, which includes a casing (not shown in the figure) and a crankshaft 100. The casing is provided with a high-pressure stage (two-stage compression) and a low-pressure Stage compression part (first stage compression), the high-pressure stage compression part and the low-pressure stage compression part are sleeved with the crankshaft 100, and are driven by the motor assembly 200 to realize the compression of the refrigerant. As shown in Figure 1, the low-pressure stage compression part has compensation The air channel (3) and the air supplement port (31), the low-pressure stage compression part includes a first compression structure and a second compression structure, as shown in Figures 1 and 3, the first compression structure has a first exhaust cavity 11, and a second The compression structure has a second exhaust chamber 21, the first exhaust chamber 11 and the second exhaust chamber 21 are in communication through the supplemental air passage 3, and the supplemental air passage 3 is in communication with the supplemental air port 31. In this technical solution, the supplemental air refrigerant of the system is delivered to the first exhaust chamber 11 and the second exhaust chamber 21 through the supplemental air passage 3, and then enters the exhaust passage 52 of the low-pressure stage compression part after being fully mixed. Compression is achieved in the third cylinder 61 through the intake port 51 of the high-pressure stage compression section. Before being sucked into the intake port 51, the supplemental air refrigerant is fully mixed with the exhaust refrigerant of the low-pressure stage compression section, effectively reducing the secondary cylinder The compressor’s compression work and exhaust air flow pulsate, thereby improving the compressor’s exhaust pressure stability and energy efficiency, and reducing compressor vibration. It can be understood that the aforementioned first exhaust chamber 11 and second exhaust chamber 21 can also be understood as a first supplemental air chamber and a second supplemental air chamber, respectively.

As shown in FIG. 1, in some embodiments, the first compression structure includes a first flange 12, a first cylinder 13, and a first partition 14, and the second compression structure includes a second cylinder 22 and a second partition 23, The first flange 12, the first cylinder 13, the first partition 14, the second cylinder 22, and the second partition 23 are sequentially sleeved on the crankshaft 100, and the first exhaust chamber 11 is provided in the first flange 12, The second exhaust chamber 21 is provided in the second partition 23. This technical solution provides specific arrangements of the first exhaust chamber 11 and the second exhaust chamber 21, and they are arranged on the first flange 12 and the second partition 23 to prevent them from being arranged in the first cylinder 13. Or the second cylinder 22 may have an adverse effect on the structural strength of the cylinder block, and it can also facilitate the processing of the corresponding exhaust cavity.

In some embodiments, the air supplement port 31 is configured on the first cylinder 13 or the first partition 14. In other embodiments, as shown in FIG. 1, the air supplement port 31 is configured on the second cylinder 22. The distance between the supplementary port 31 and the first exhaust chamber 11 and the second exhaust chamber 21 is more moderate, which is very beneficial to match the phase difference with the rollers of the first cylinder 13 and the second cylinder 22 respectively. Similarly, in some embodiments, as shown in FIG. 1, the supplemental air passage 3 is constructed in the first cylinder 13, the first partition 14, and the second cylinder 22.

In order to further reduce the processing difficulty of the first exhaust cavity 11 and the second exhaust cavity 21, in some embodiments, as shown in FIG. 1, the first compression structure further includes a first cover 15 and a first exhaust cavity 11 It has an opening facing away from the first cylinder 13, and the first cover 15 covers the opening of the first exhaust chamber 11. In some embodiments, as shown in FIG. 1, the second compression structure further includes a third The partition 24, the second exhaust chamber 21 has an opening facing the side away from the second cylinder 22, and the third partition 24 covers the opening of the second exhaust chamber 21.

In order to prevent the retrograde phenomenon of the supplemental air refrigerant generated when the pressure of the exhaust refrigerant in the first exhaust cavity 11 or the second exhaust cavity 21 is higher than the pressure of the supplemental air refrigerant, in some embodiments, the supplementary air port 31 is provided There is a one-way stop valve 4, which opens when the pressure of the supplemental refrigerant is higher than that of the exhaust chamber (the first exhaust chamber 11 or the second exhaust chamber 21) so that the supplemental refrigerant can smoothly enter the exhaust chamber, while When the air refrigerant pressure is lower than the exhaust cavity (the first exhaust cavity 11 or the second exhaust cavity 21), it is closed so that the supplemental air refrigerant cannot enter the exhaust cavity.

In some embodiments, as shown in FIGS. 1 and 3, the first exhaust chamber 11 has a first supplementary air valve port, and a one-way stop valve 4 is provided at the first supplementary air valve port; in some embodiments, As shown in Figures 1 and 3, the second exhaust chamber 21 has a second air supplement valve port, and a one-way stop valve 4 is provided at the second air supplement valve port. In some embodiments, as shown in Figures 1 and 3 As shown, the first exhaust chamber 11 and the second exhaust chamber 21 are respectively provided with the aforementioned one-way stop valve 4 respectively. At this time, the corresponding one-way stop valve 4 is respectively provided in the first exhaust chamber 11 and the second exhaust chamber. When the exhaust pressure of the exhaust chamber 21 is too high, the through connection between the supplemental air passage 3 and the first exhaust chamber 11 and the second exhaust chamber 21 is respectively closed, and it can be understood that the first compression structure has The first roller and the second roller have a second roller in the second compression structure. The first roller and the second roller are respectively sleeved on the first eccentric circle and the second eccentric circle of the crankshaft 100, and the first eccentric circle There is a phase difference with the second eccentric circle on the plane of the axial projection of the crankshaft 100. This phase difference makes the first compression structure and the second compression structure asynchronous in the exhaust rhythm, and a one-way stop valve is specifically set here It can effectively prevent the pressure churn between the first exhaust chamber 11 and the second exhaust chamber 21, thereby effectively increasing the supplemental air flow for the first exhaust chamber 11 or the second exhaust chamber 21, and eliminate The interference from the high-pressure exhaust refrigerant from the opposite party (for example, when the pressure in the first exhaust chamber 11 is low, the supplemental air is only supplied to the first exhaust chamber 11, while the high-pressure exhaust in the second exhaust chamber 21 Therefore, it is locked in the second exhaust chamber 21 and will not flow into the first exhaust chamber 11 to affect the proportion of supplemental air refrigerant).

In some embodiments, the one-way stop valve 4 is a commonly used one-way valve. In some embodiments, as shown in FIG. 2, the one-way stop valve 4 includes a valve plate baffle 41 and a valve plate 42. The valve plate 42 Stacked with the valve plate baffle 41 in turn and formed a whole by the fastener 43, wherein the valve plate baffle 41 is used to limit the opening angle of the valve plate 42, and the valve plate 42 relies on its own deformation ability to realize the passage Through or closed. 4 shows the specific structure of the second partition 23, which has an exhaust port 231 corresponding to the second compression structure, the exhaust port 231 is correspondingly provided with a one-way stop valve 4, and the second row The air cavity 21 is arranged around the edge area of the second partition 23 and communicates with the second air supplement valve port. Of course, the second air supplement valve port is also provided with a one-way stop valve 4.

In some embodiments, as shown in FIG. 1, the high-pressure stage compression part includes a third cylinder 61 and a second flange 62. For the same reason, these two are also sleeved on the crankshaft 100 and driven by it to achieve the high-pressure stage compression. As shown in Figure 3, it has a suction port 51, which is usually referred to as a secondary suction port (corresponding to the primary suction port of the low-pressure stage compressor), the suction port 51 and the discharge of the low-pressure stage compression section The air passage 52 is connected, and when the one-way stop valve on the exhaust port 231 on the second partition 23 is opened, the second exhaust chamber 21 will communicate with the exhaust passage 52; for the same reason, the first flange 12 has When the one-way stop valve on the corresponding exhaust port is opened, the second exhaust chamber 21 is in communication with the exhaust passage 52.

Taking the compressor orientation shown in FIG. 1 as an example, in order to balance the torque of the crankshaft 100, the phases of the upper, middle, and lower eccentric portions of the crankshaft 100, as well as the first cylinder 13, the second cylinder 22, and the third cylinder There is a certain angle difference between the corresponding intake ports of 61, so the exhaust angles of the first cylinder 13, the second cylinder 22, and the third cylinder 61 have a certain phase difference. The intake and exhaust ports of the third cylinder 61 are different from those of the second cylinder. The phase difference between the intake and exhaust ports of the cylinder 22 is respectively set to β, and the phase difference between the intake and exhaust ports of the second cylinder 22 and the intake and exhaust ports of the first cylinder 13 is π. Fig. 5 shows the variation curve of the working pressure of the first cylinder 13, the working pressure of the second cylinder 22, and the suction volume of the third cylinder 61 with the rotation angle of the crankshaft 100 (X1 corresponds to the third cylinder, and X2 corresponds to the first cylinder. The second cylinder, X3 corresponds to the first cylinder), the curves ab and a1b1 are the exhaust process of the first cylinder 13, the curves cd and c1d1 are the exhaust process of the second cylinder 22, and the rows of the first cylinder 13 and the second cylinder 22 The air is not synchronized before and after. It can be seen from the suction chamber volume curve of the third cylinder 61 that the second cylinder (the third cylinder 61) has been inhaling at a different rate during the entire working process, so when the first cylinder 13 is in ab exhaust During the process, the second cylinder 22 is not exhausting and the third cylinder 61 is inhaling. At this time, the pressure in the first exhaust chamber 11 is greater than the pressure in the second exhaust chamber 21, and the enthalpy-enhanced supplementary gas is It will enter the second exhaust chamber 21 in a large amount upward through the supplemental air passage 3. Similarly, when the second cylinder 22 is in the cd exhaust process, the first cylinder 13 is not exhausted and the third cylinder 61 is inhaling. The pressure of the second exhaust chamber 21 is greater than the pressure of the first exhaust chamber 11, and the enthalpy-enhanced supplementary gas will enter the first exhaust chamber 11 through the supplementary gas passage 3, which means that The gas of the air is continuously supplemented to the second exhaust chamber 21 or the first exhaust chamber 11 through the supplemental gas channel 3, which can greatly increase the supplemental gas flow of the enthalpy-increased supplementary gas. The essence of this continuous supplemental air enthalpy is the one-way stop valve 4 corresponding to the first exhaust chamber 11 and the second exhaust chamber 21 respectively.

In some embodiments, the compressor is a three-cylinder two-stage compressor. Of course, in some other embodiments, it is a two-cylinder supplementary gas enthalpy compressor. At the same time, in some embodiments, it is a vertical or horizontal compressor. Type compressor, the disclosure is not limited.

According to an embodiment of the present disclosure, there is also provided an air conditioner including the above-mentioned compressor.

It is easy for those skilled in the art to understand that the above advantageous methods can be freely combined and superimposed on the premise of no conflict.

The above embodiments only express several implementation modes of the present disclosure, and the descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the present disclosure. It should be pointed out that for those of ordinary skill in the art, without departing from the concept of the present disclosure, several modifications and improvements can be made, and these all fall within the protection scope of the present disclosure. Therefore, the protection scope of the patent of the present disclosure should be subject to the appended claims.

Claims

A compressor, including:

The low-pressure stage compression part has a supplemental air channel (3) and a supplemental air port (31);

Wherein, the low-pressure stage compression part includes a first compression structure and a second compression structure, the first compression structure has a first exhaust chamber (11), and the second compression structure has a second exhaust chamber (21) , The first exhaust chamber (11) and the second exhaust chamber (21) are in communication through the supplemental air passage (3), and the supplemental air passage (3) is connected to the supplementary air port (31). ) Connected.
The compressor according to claim 1, further comprising a crankshaft (100), wherein the first compression structure comprises a first flange (12), a first cylinder (13) and a first partition (14), so The second compression structure includes a second cylinder (22) and a second partition (23), the first flange (12), the first cylinder (13), the first partition (14), The second cylinder (22) and the second partition (23) are sequentially sleeved on the crankshaft (100), and the first exhaust chamber (11) is provided on the first flange (12). ), the second exhaust chamber (21) is arranged in the second partition (23).
The compressor according to claim 2, wherein the supplemental air port (31) is configured on the second cylinder (22).
The compressor according to claim 2, wherein the supplemental air port (31) is configured on the first cylinder (13).
The compressor according to claim 2, wherein the supplemental air port (31) is configured on the first partition (14).
The compressor according to claim 2, wherein the first compression structure further comprises a first cover plate (15), the first exhaust cavity (11) has an opening, and the opening faces away from the first On one side of the cylinder (13), the first cover plate (15) covers the opening of the first exhaust chamber (11).
The compressor according to claim 2, wherein the second compression structure further comprises a third partition (24), the second discharge chamber (21) has an opening, and the opening faces away from the second On one side of the cylinder (22), the third partition (24) covers the opening of the second exhaust chamber (21).
The compressor according to claim 2, wherein the first compression structure further comprises a first cover plate (15), the first exhaust cavity (11) has an opening, and the opening faces away from the first On one side of the cylinder (13), the first cover (15) covers the opening of the first exhaust chamber (11); the second compression structure further includes a third partition (24), and the The second exhaust chamber (21) has an opening, the opening faces a side away from the second cylinder (22), and the third partition (24) covers the opening of the second exhaust chamber (21).
The compressor according to claim 1, wherein a one-way stop valve (4) is provided at the air supplement port (31).
The compressor according to claim 1, wherein the first exhaust chamber (11) has a first air supplement valve port, and a one-way stop valve (4) is provided at the first air supplement valve port.
The compressor according to claim 1, wherein the second discharge chamber (21) has a second air supplement valve port, and a one-way stop valve (4) is provided at the second air supplement valve port.
The compressor according to claim 1, wherein the first exhaust chamber (11) has a first air supplement valve port, and a one-way stop valve (4) is provided at the first air supplement valve port; The second exhaust chamber (21) has a second air supplement valve port, and a one-way stop valve (4) is arranged at the second air supplement valve port.
The compressor according to claim 12, wherein the one-way stop valve (4) includes a valve plate baffle (41) and a valve plate (42), the valve plate (42) and the valve plate baffle (41) Stacked one by one and formed a whole through fasteners (43).
The compressor according to claim 1, further comprising a high-pressure stage compression part, the high-pressure stage compression part has a suction port (51), which communicates with the discharge passage (52) of the low-pressure stage compression part.
The compressor of claim 1, wherein the compressor is a three-cylinder two-stage compressor.
An air conditioner, comprising the compressor according to any one of claims 1-15.