WO2023035643A1 - Compressor and air conditioner - Google Patents

Abstract

A compressor and an air conditioner. The compressor comprises a crankshaft (1), a first air cylinder (2), a second air cylinder (3) and a separator plate assembly (4), wherein the separator plate assembly (4) is arranged between the first air cylinder (2) and the second air cylinder (3); the crankshaft (1) comprises an intermediate shaft section (11) located between the first air cylinder (2) and the second air cylinder (3), and the separator plate assembly (4) is arranged on the intermediate shaft section (11) in a penetrating manner; and the separator plate assembly (4) comprises a first separator plate (41), and the first separator plate (41) is in connection with the intermediate shaft section (11) to form a separator plate bearing for supporting the intermediate shaft section (11).

Description

Compressors and Air Conditioners

Cross References to Related Applications

This application claims the priority of the Chinese patent application with the application number 202111043220.9 and the application name "A Compressor and Air Conditioner" submitted to the China Patent Office on September 7, 2021, which is hereby incorporated by reference in its entirety.

technical field

The present disclosure relates to the technical field of compressors, in particular to a compressor and an air conditioner.

Background technique

In recent years, the miniaturization, large displacement, and high-speed development of rotary compressors have become a trend, that is, the outer diameter of rotary compressors is getting smaller and smaller, and the displacement of the corresponding compressors is getting bigger and bigger. Machine high-speed operation requirements.

The total displacement of the compressor _Vtotal =N×V, N represents the number of cylinders, V represents the displacement of a single cylinder, that is, the total displacement of the compressor depends on the displacement of a single cylinder and the number of cylinders. And the displacement of a single cylinder of the compressor V=π×H×e×(De), where H represents the height of the cylinder, D represents the inner diameter of the cylinder, and e represents the eccentricity of the crankshaft, that is, the displacement of a single cylinder is related to the height of the cylinder, the inner diameter of the cylinder, Proportional to crankshaft eccentricity. When the inner diameter of the compressor shell is constant, the inner diameter of the cylinder has a maximum maximum value, and when the inner diameter of the cylinder reaches the maximum maximum limit range, when the displacement of the cylinder needs to be further increased, the cylinder height H can only be increased. The higher the cylinder height, the greater the force on the roller slides and the eccentric part of the crankshaft, and the greater the risk of wear. At the same time, the higher the cylinder height corresponds to the larger span of the bearing, the contact stress on the edge of the crankshaft bearing is too large, and the bearing system is prone to wear problems , The risk of compressor reliability is high. In addition, after the displacement of a single cylinder increases, the corresponding exhaust passage needs to be enlarged.

A technical route of a multi-cylinder rotary compressor (including at least 4 cylinders) in the related art realizes a large displacement by increasing the number of cylinders, and can effectively reduce the compressor crankshaft on the premise of improving the refrigeration capacity of the compressor. The resultant force of the gas reduces the bending degree of the crankshaft, reduces the abrasion of the crankshaft, and ensures the reliability of the operation of the compressor. However, the multi-cylinder technical route has complex structure, high cost and uneconomical problems.

When the displacement of compressors with more than two cylinders in the related art increases, the height of the cylinder increases and the length of the crankshaft becomes longer. When the crankshaft is running at high frequency, the length of the crankshaft will increase between the first bearing and the second bearing. Bending will cause technical problems such as serious wear and tear between parts such as the crankshaft and the cylinder. Therefore, this application researches and designs a compressor and an air conditioner.

Contents of the invention

In order to overcome the defect of shafting wear in the compressor with more than two cylinders in the related art when the displacement is increased and the compressor operates at high frequency, the present application provides a compressor and an air conditioner.

The present application provides a compressor, including: a crankshaft, a first cylinder, a second cylinder and a diaphragm assembly, the crankshaft includes an intermediate shaft section located between the first cylinder and the second cylinder, the diaphragm The plate assembly is arranged between the first cylinder and the second cylinder, and the baffle assembly is passed through the intermediate shaft section; the baffle assembly includes a first baffle, and the first baffle It is connected with the intermediate shaft segment to form a diaphragm bearing for supporting the intermediate shaft segment.

In some embodiments, the baffle assembly further includes a second baffle. One axial side of the first baffle is in contact with one axial end of the first cylinder, and one axial side of the second baffle is in contact with the other axial end of the first baffle, The other end surface in the axial direction of the second partition is in contact with the one end surface in the axial direction of the second cylinder.

The intermediate shaft segment includes a first intermediate segment and a second intermediate segment that are connected in the axial direction, the first partition is sleeved on the outer periphery of the first intermediate segment and is in contact with the first intermediate segment, And the first intermediate section can rotate relative to the first partition; the second partition is located on the outer periphery of the second intermediate section and there is a gap between the second intermediate section and the second intermediate section.

In some embodiments, the first intermediate section is a concentric circular section, and the central axis of the concentric circular section coincides with the rotation centerline of the crankshaft.

In some embodiments, the first partition is fixedly connected to the first cylinder, and the second partition is fixedly connected to the second cylinder.

In some embodiments, the axial height of the first separator is greater than the axial height of the second separator.

In some embodiments, a first cavity is provided on a side of the first partition opposite to the second partition, and a first cavity is provided on a side of the second partition opposite to the first partition. There is a second cavity, the first cavity is connected with the second cavity to form a separator exhaust cavity, the first separator is provided with a first exhaust hole, and the first exhaust hole One end of the first exhaust hole communicates with the inside of the first cylinder, and the other end of the first exhaust hole communicates with the first cavity. The second separator is provided with a second exhaust hole, one end of the second exhaust hole can communicate with the inside of the second cylinder, and the other end of the second exhaust hole can communicate with the second air cylinder. cavities connected.

In some embodiments, a first exhaust valve is disposed at the first exhaust hole, and a second exhaust valve is disposed at the second exhaust hole.

In some embodiments, it also includes a casing, the crankshaft, the first cylinder, the second cylinder and the separator assembly are located inside the casing; the first cylinder and the second The height of at least one of the two cylinders is H, the inner diameter of the cylinder is D, and the inner diameter of the housing is F, satisfying: H/D≥0.45 and H/F≥0.21.

In some embodiments, the maximum rotational speed of the compressor is greater than or equal to 120rps.

In some embodiments, the outer diameter of the housing is greater than or equal to 160mm.

In some embodiments, the crankshaft further includes a first eccentric portion and a second eccentric portion, the intermediate shaft segment is located between the first eccentric portion and the second eccentric portion, and the compressor further includes a first eccentric portion. A roller and a second roller, the first roller is sheathed on the outer periphery of the first eccentric part, the first roller is located in the first cylinder, and is drivingly connected with the first eccentric part ; The second roller is sleeved on the outer periphery of the second eccentric part, the second roller is located in the second cylinder, and is drivingly connected with the second eccentric part.

In some embodiments, it also includes a rotor balance weight, a crankshaft balance weight and a motor rotor, the crankshaft also includes a major axis and a minor axis, the crankshaft balance weight is arranged on the minor axis, the motor rotor is arranged on On the long axis, the rotor balance weight is connected to the motor rotor, the first eccentric part is closer to the long axis relative to the second eccentric part, and the second eccentric part is closer to the long axis than the second eccentric part. The first eccentric part is close to the short axis, the mass center of the rotor balance weight and the first eccentric part are arranged symmetrically with respect to the rotation center line of the crankshaft; the mass center of the crankshaft balance weight and the second eccentric part The arrangement is symmetrical about the rotational center line of the crankshaft.

In some embodiments, it further includes a first bearing and a second bearing, the first bearing is sleeved on the long axis and connected to the first cylinder, the first eccentric part is located on the first Between the bearing and the separator assembly; the rotor balance weight is arranged at the end of the motor rotor close to the first bearing, or the rotor balance weight is arranged at the end of the motor rotor away from the first bearing.

In some embodiments, the rotor balance weight includes a first rotor balance weight and a second rotor balance weight, the first rotor balance weight is arranged at one end of the motor rotor close to the first bearing, and the first rotor balance weight The second rotor balance weight is arranged at the end of the motor rotor away from the first bearing.

In some embodiments, in a projection plane perpendicular to the axis of the crankshaft, the center of mass of the first rotor balance weight and the center of mass of the second rotor balance weight are sandwiched by the center of rotation of the crankshaft. The central angle of <180°.

In some embodiments, the second bearing is sleeved on the short shaft to support the short shaft, and a cover plate is also provided on the short shaft, and a cover plate is formed between the cover plate and the second bearing. A main exhaust chamber, the crankshaft balance weight is connected to the short shaft and is located in the main exhaust chamber.

In some embodiments, in a projection plane perpendicular to the axis of the crankshaft, the center of mass of the crankshaft balance weight and the center of mass of the rotor balance weight are relatively distributed with a phase difference of 180°.

In some embodiments, in a projection plane perpendicular to the axis of the crankshaft, the crankshaft balance weight has a fan-shaped structure.

In some embodiments, the crankshaft balance weight is interference-fitted with the short shaft.

The present application also provides an air conditioner, which includes the compressor described in any one of the above embodiments.

The compressor and air conditioner provided by the application have the following beneficial effects:

By setting a baffle assembly between the first cylinder and the second cylinder, the baffle assembly is passed through the intermediate shaft section of the crankshaft, and the baffle assembly includes a first baffle, the first baffle connects to the intermediate shaft section and Form the structural form of the bearing to support the intermediate shaft section of the crankshaft, which can effectively reduce the disturbance and deflection of the crankshaft, and effectively reduce the connection between the intermediate shaft section of the crankshaft due to bending and the first cylinder, the second cylinder, the first bearing and The wear at the junction of the second bearing reduces the contact stress and the force on the first and second bearings, effectively solving the problem of shaft wear when the compressor operates at high frequency, and improving the large displacement of the small casing The reliability of the high-frequency operation of the twin-cylinder compressor, on the premise of ensuring the performance, improves the wear of the shaft system, increases the operating frequency of the compressor, and realizes the effective wear reduction of the small-shell and large-displacement twin-cylinder compressor. The compressor has a compact and simple structure, stable and reliable operation, and can especially meet the needs of large displacement and high speed compressors.

Description of drawings

Fig. 1 is a sectional view of a complete compressor of an embodiment of the present application;

Fig. 2 schematically shows a cross-sectional view of the pump body assembly in Fig. 1;

Fig. 3 schematically shows a sectional view of the pump body assembly and the rotor in Fig. 1;

Fig. 4 schematically shows a cross-sectional view of a pump body assembly and a rotor according to another embodiment of the present application;

Fig. 5 is the top view of the second cylinder in Fig. 1;

FIG. 6 is a side sectional view of the second cylinder in FIG. 1 .

The reference signs are indicated as:

1. Crankshaft; 11. Intermediate shaft section; 11a, first intermediate section; 11b, second intermediate section; 12. First eccentric part; 13. Second eccentric part; 2. First cylinder; 3. Second cylinder; 4. Partition board assembly; 41. First partition; 42. Second partition; 5. Housing; 61. First roller; 62. Second roller; 7. Partition exhaust cavity; 71. The second 1 cavity; 72, second cavity; 8, rotor balance weight; 81, first rotor balance weight; 82, second rotor balance weight; 9, crankshaft balance weight; 10, motor rotor; 14, long axis; 15 , short shaft; 16, first bearing; 17, second bearing; 18, cover plate; 19, motor stator; 20, pump body assembly; 21, upper cover; 100, main exhaust chamber.

Detailed ways

As shown in Figures 1-3, 5-6, some embodiments of the present application provide a compressor, including: a crankshaft 1, a first cylinder 2, a second cylinder 3 and a baffle assembly 4, the baffle assembly 4 is arranged between the first cylinder 2 and the second cylinder 3, the crankshaft 1 includes an intermediate shaft section 11 located between the first cylinder 2 and the second cylinder 3, the separator The assembly 4 is passed through the intermediate shaft section 11; the baffle assembly 4 includes a first baffle 41, and the first baffle 41 connects with the intermediate shaft section 11 to form a baffle bearing for The intermediate shaft section 11 is supported.

In the present application, a baffle assembly is provided between the first cylinder and the second cylinder, the baffle assembly is penetrated on the intermediate shaft section of the crankshaft, and the baffle assembly includes a first baffle, and the first baffle is connected to the intermediate shaft section. The structural form of connecting and forming the diaphragm bearing is used to support the intermediate shaft section of the crankshaft, which can effectively reduce the disturbance and deflection of the crankshaft, and effectively reduce the connection between the intermediate shaft section of the crankshaft and the first cylinder, the second cylinder, and the first cylinder due to bending. The wear at the junction of the first bearing and the second bearing reduces the contact stress, reduces the stress on the first bearing and the second bearing, effectively solves the problem of shaft wear when the compressor operates at high frequency, and improves the small casing. The reliability of the high-frequency operation of the large-displacement twin-cylinder compressor, on the premise of ensuring performance, improves the wear of the shaft system, increases the operating frequency of the compressor, and realizes the effective wear reduction of the small-housing large-displacement twin-cylinder compressor. The compressor has a compact and simple structure, stable and reliable operation, and can especially meet the demands of a compressor with a large displacement and a high rotational speed. In the compressor of the present application, as shown in Table 1, after adding the auxiliary bearing, that is, the diaphragm bearing, compared with the compressor without the diaphragm bearing in the related art, the contact stress of the major axis and the short axis, and the eccentric portion The upper eccentric deformation and the lower eccentric deformation are reduced by 40% to 50%, and the load reduction effect is obvious.

Table 1

plan Spacerless bearings With spacer bearing Upper eccentric deformation mm/inclination angle° 0.0251/0.00767 0.0134/0.0049 Lower eccentric deformation mm/inclination angle° 0.0262/0.0066 0.0152/0.0032 Minor axis contact stress/Mpa 35.5 22.1 Long axis contact stress/Mpa 39.2 21.3 Intermediate shaft contact stress/Mpa / 28.9

In some embodiments, the baffle assembly 4 further includes a second baffle 42 . An axial end surface of the first partition 41 is in contact with an axial end surface of the first cylinder 2 , and an axial end surface of the second partition 42 is in contact with the axial end surface of the first partition 41 . The other end surface is connected, and the other axial end surface of the second partition plate 42 is connected to the axial one end surface of the second cylinder 3 .

In an embodiment of the separator assembly of the present application, the intermediate shaft segment 11 includes a first intermediate segment 11a and a second intermediate segment 11b connected in the axial direction, and the first separator 41 is sleeved on the The outer periphery of the first intermediate section 11a is in contact with the first intermediate section 11a, and the first partition plate 41 is rotatably arranged relative to the first intermediate section 11a. The second separator 42 is located on the outer periphery of the second middle section 11b and has a gap with the second middle section 11b. The first baffle and the second baffle can be respectively connected with the first cylinder and the second cylinder to play a sealing role, and at the same time, the contact and cooperation between the first baffle and the intermediate shaft section can effectively protect the intermediate shaft section. The supporting function prevents the middle part of the crankshaft from bending, reduces the stress, and thus reduces the wear of the shaft system. There is a gap between the second partition 42 and the second intermediate section 11b, and the second partition serves as an axial seal for the first cylinder or the second cylinder.

In an embodiment of the present application, the first cylinder is an upper cylinder, and the first partition connected to it is an upper partition, while the second cylinder is a lower cylinder, and the second partition connected to it is a lower partition. In another embodiment of the present application, the first cylinder is the lower cylinder, and the first partition connected to it is the lower partition, while the second cylinder is the upper cylinder, and the second partition connected to it is the upper partition .

In some embodiments, the first middle section 11 a is a concentric circular section, and the central axis of the concentric circular section coincides with the rotation centerline of the crankshaft 1 . The first intermediate section 11a of the present disclosure cooperates with the first partition plate 41, and the central axis of the first intermediate section 11a coincides with the crankshaft rotation centerline, so that the first intermediate section 11a and the crankshaft 1 can rotate concentrically, passing through the first partition The plate 41 plays the role of an effective rotation support for the first middle section 11a, that is, a bearing support without eccentricity, thereby improving the supporting capacity of the middle shaft section and reducing the wear of the crankshaft.

In some embodiments, the first partition 41 is fixedly connected to the first cylinder 2 , and the second partition 42 is fixedly connected to the second cylinder 3 .

In some embodiments, the axial height of the first partition 41 is greater than the axial height of the second partition 42 . As shown in Figure 2, the first partition 41 is a partition bearing, and the second partition 42 is a non-partition bearing, which cooperates concentrically with the crankshaft 1, and the height H1 of the first partition of the partition bearing is greater than that of the non-partition bearing. The height H2 of the second partition, that is, H1>H2, can effectively improve the supporting effect on the crankshaft.

In some embodiments, as shown in FIG. 2 , a first cavity 71 is provided on the side of the first partition 41 opposite to the second partition 42 , and the second partition 42 is connected to the second partition 42 . A second cavity 72 is provided on the opposite side of the first partition 41 , and the first cavity 71 and the second cavity 72 are connected to form a partition exhaust chamber 7 . The first separator 41 is provided with a first exhaust hole (not shown), one end of the first exhaust hole (not shown) can communicate with the inside of the first cylinder 2, the first The other end of the exhaust hole can communicate with the first cavity 71 , so as to introduce the exhaust gas in the first cylinder 2 into the first cavity 71 . The second separator 42 is provided with a second exhaust hole (not shown), one end of the second exhaust hole (not shown) can communicate with the inside of the second cylinder 3, the second The other end of the exhaust hole can communicate with the second cavity 72 , so as to introduce the exhaust gas in the second cylinder 3 into the second cavity 72 . In the present application, the first cavity and the second cavity are opened on the first partition and the second partition to communicate with the discharge cavity forming the partition, which can increase the volume of the discharge cavity and improve the volumetric efficiency of the compressor. .

The inner diameter of the cylinder is limited by the outer diameter of the housing, and there is an optimal range of values, beyond which there will be various reliability problems. When the inner diameter of the cylinder is limited, increasing the displacement to an extreme range by increasing the height of the cylinder will inevitably lead to the problem of insufficient exhaust passages. The compressor of the present application increases the number of exhaust passages to four through the diaphragm exhaust, which can meet the large displacement under the limit cylinder height and cylinder inner diameter, and the exhaust loss is within a reasonable range. In the compressor baffle assembly of the present application, the first baffle 41 and the second baffle 42 are provided with exhaust holes, and an exhaust valve is arranged at the exhaust hole, and the first baffle 42 The plate 41 and the second partition 42 enclose a partition exhaust cavity 7 .

In some embodiments, a first exhaust valve is disposed at the first exhaust hole, and a second exhaust valve is disposed at the second exhaust hole. The effect of opening and closing the exhaust chamber of the partition can be respectively achieved through the two exhaust valves.

In some embodiments, the compressor further includes a casing 5 . The crankshaft 1 , the first cylinder 2 , the second cylinder 3 and the separator assembly 4 are all located inside the housing 5 . The height H of at least one of the first cylinder 2 and the second cylinder 3, the inner diameter D of the cylinder and the inner diameter F of the housing 5 satisfy: H/D≥0.45 and H/F≥0.21 . The total displacement of the rotary compressor is equal to the displacement of each cylinder, that is, the large displacement can be realized by increasing the number of cylinders and the displacement of a single cylinder. The rotary twin-cylinder compressor proposed by the present application has limited the number of cylinders to two, and the large displacement can only be realized by increasing the volume of a single cylinder. And the displacement of a single cylinder V=π×H×e×(D-e), where H represents the height of the cylinder, D represents the inner diameter of the cylinder, and e represents the eccentricity of the crankshaft, that is, the displacement of a single cylinder is related to the height of the cylinder, the inner diameter of the cylinder, and the eccentricity of the crankshaft The amount is directly proportional. When the inner diameter F of the compressor shell is constant, the inner diameter of the cylinder has a maximum maximum value, and when the inner diameter of the cylinder reaches the maximum maximum limit range, when the displacement of the cylinder needs to be further increased, the cylinder height H can only be increased. Therefore, the present application provides a small-housing large-displacement rotary twin-cylinder compressor that satisfies H/D>0.45 and H/F>0.21.

The twin-cylinder compressor provided by the present application is a rotary twin-cylinder compressor, which is characterized by a small shell inner diameter, a large displacement, and a small number of cylinders (two). In one of the embodiments, as shown in Fig. 1, Fig. 5 and Fig. 6, the pump body assembly includes a first cylinder 2 and a second cylinder 3, wherein the height H of at least one of the cylinders, the inner diameter D of the cylinder and the compression The inner diameter F of the casing meets the following three requirements: H/D≥0.45 and H/F≥0.21.

As shown in Figure 2, as the height H of the cylinder increases, the bearing span H between the first bearing 16 and the second bearing 17 increases, the eccentric part of the crankshaft is greatly disturbed, the piston is seriously inclined, and the contact stress between the crankshaft and the edge of the bearing is excessive. Large, resulting in unstable operation of the compressor, and the bearing system is prone to wear and tear. For the compressor with this structural characteristic, by adding an auxiliary bearing between the first bearing 16 and the second bearing 17, that is, the diaphragm bearing, the crankshaft disturbance and the impact on the first bearing 41 and the second bearing 42 can be effectively reduced. force, reducing the wear of the crankshaft 1.

In some embodiments, the maximum rotational speed of the compressor is greater than or equal to 120rps; and/or, the outer diameter of the housing 5 is greater than or equal to 160mm.

In some embodiments, as shown in FIG. 2 and FIG. 4 , the crankshaft 1 further includes a first eccentric portion 12 and a second eccentric portion 13 , and the compressor further includes a first roller 61 and a second roller 62 , the first roller 61 is sheathed on the outer periphery of the first eccentric part 12, the first roller 61 is located in the first cylinder 2, is drivingly connected with the first eccentric part 12, and is driven by the first eccentric part 12. The first eccentric part 12 is driven to move in the first cylinder 2 . The second roller 62 is sheathed on the outer periphery of the second eccentric part 13, the second roller 62 is located in the second cylinder 3, and is drivingly connected with the second eccentric part 13, and is driven by the second eccentric part 13. The second eccentric part 13 is driven to move in the second cylinder 3 . The intermediate shaft segment 11 is located between the first eccentric portion 12 and the second eccentric portion 13 .

In some embodiments, as shown in FIG. 4 , the compressor further includes a rotor balance weight 8, a crankshaft balance weight 9 and a motor rotor 10, and the crankshaft 1 further includes a major axis 14 and a minor axis 15, and the crankshaft balance The block 9 is arranged on the short axis 15, the motor rotor 10 is arranged on the long axis 14, the rotor balance weight 8 is connected and arranged on the motor rotor 10, and the first eccentric part 12 is relatively The second eccentric part 13 is closer to the major axis 14, the second eccentric part 13 is closer to the minor axis 15 relative to the first eccentric part 12, and the center of mass of the rotor balance weight 8 is closer to the The first eccentric portion 12 is arranged symmetrically with respect to the rotation centerline of the crankshaft 1 ; the center of mass of the crankshaft balance weight 9 and the second eccentric portion 13 are arranged symmetrically with respect to the rotation centerline of the crankshaft 1 .

During the operation of the crankshaft, the piston and the eccentric part follow the eccentric movement, which will generate unbalanced force and moment. When the height and bore of the cylinder are in the range of relatively large values, the mass of the eccentric part of the corresponding piston and crankshaft is large, so the corresponding unbalanced force and moment need to be balanced by the balance system, and the conventional single rotor balance weight is set. Cannot take into account performance, operation stability and shafting reliability: the conventional single rotor balance weight system can improve the reliability of the shafting at a certain high speed by reducing the height of the motor, but the performance attenuation is large; the conventional single rotor balancing system can reduce the The balance factor can improve the reliability of the shaft system at a certain high speed, but the compressor vibrates greatly and the running stability is poor. Therefore, by setting the rotor balance weight and the crankshaft balance weight, it can effectively ensure the reliability at a certain high speed and at the same time ensure the stability and performance of the compressor at high speed. The balance system related to the compressor of the present invention includes a rotor balance weight and a crankshaft balance weight, the rotor balance weight is arranged on the rotor, and the crankshaft balance weight is arranged on the crankshaft.

The crankshaft of the compressor has a first eccentric part, a second eccentric part and a concentric circular segment arranged between the first eccentric part and the second eccentric part, the first piston is sleeved on the first eccentric part, and the first The two pistons are sheathed on the second eccentric part; the baffle includes a first baffle and a second baffle, one of which is a baffle bearing and matches with the concentric circular section of the crankshaft.

In some implementations, as shown in FIGS. 2 and 4 , the compressor further includes a first bearing 16 and a second bearing 17 . The first bearing 16 is sleeved on the long axis 14 and connected to the first cylinder 2 , and the first eccentric portion 12 is located between the first bearing 16 and the partition assembly 4 . The rotor balance weight 8 is arranged at an end of the motor rotor 10 close to the first bearing 16 , or the rotor balance weight 8 is arranged at an end of the motor rotor 10 away from the first bearing 16 .

In some embodiments, as shown in FIG. 4 , the rotor balance weight 8 includes a first rotor balance weight 81 and a second rotor balance weight 82 , and the first rotor balance weight 81 is arranged near the motor rotor 10 At one end of the first bearing 16 , the second rotor balance weight 82 is disposed at an end of the motor rotor 10 away from the first bearing 16 .

In some embodiments, in a projection plane perpendicular to the axis of the crankshaft 1 , the center of mass of the first rotor balance weight 81 and the center of mass of the second rotor balance weight 82 are centered on the rotation center of the crankshaft 1 The center angle contained by the center of the circle is <180°. That is, the center of mass of the first rotor balance weight 81 and the center of mass of the second rotor balance weight 82 are arranged on the same side relative to the rotation centerline of the crankshaft.

The center of mass of the rotor balance weight 8 is arranged opposite to the rotation centerline of the crankshaft of the first eccentric portion. The center of mass of the crankshaft balance weight 9 is arranged opposite to the second eccentric portion around the rotation centerline of the crankshaft. The rotor balance weight 8 can be arranged on the side of the rotor close to the first bearing, as shown in FIG. 3 , or it can be arranged on the side of the rotor away from the first bearing. It is also possible to set two rotor balance weights, which are respectively arranged on the upper and lower ends of the motor rotor, and the center of mass is arranged on the same side as the center of the crankshaft, as shown in Fig. 4 . The rotor balance weights 8 are arranged in different positions and in different numbers, and the weight can be adjusted accordingly to meet a certain balance coefficient. The rotor balance weight 8 shown in Fig. 2 and Fig. 3 is arranged on the side of the rotor close to the first bearing.

In some embodiments, as shown in FIG. 2, the second bearing 17 is sleeved on the short shaft 15 to support the short shaft 15, and a cover plate 18 is also provided on the short shaft 15. A main exhaust chamber 100 is formed between the cover plate 18 and the second bearing 17 , and the crankshaft balance weight 9 connects with the short shaft 15 and is located in the main exhaust chamber 100 . The crankshaft balance weight 9 is set in the exhaust chamber of the second bearing 17, which can effectively isolate the oil pool, avoiding the crankshaft balance weight 9 from stirring the oil pool during rotation, and adopting a fan-shaped structure, which can minimize the airflow disturbance and reduce the loss.

In the present disclosure, the crankshaft balance weight 9 can be operated by setting the exhaust chamber between the sealing structure and the lower flange, and setting the crankshaft balance weight 9 in the main exhaust chamber 100 and connecting with the short shaft 15 of the crankshaft. To balance the eccentric part of the crankshaft, and there is no need to add a separate cavity to place the crankshaft balance weight 9, avoiding a series of problems caused by adding a single balance cavity to the lengthening of the lower cavity, preventing the center of gravity of the extended pump from moving upward, and solving the problem of moving the center of gravity of the pump To solve the problem of displacement, make full use of the space, and greatly reduce the size of the pump body in the axial direction, which is conducive to the stability of the compressor operation, thereby improving the vibration and reliability of the compressor. And the crankshaft balance weight 9 of the present disclosure is arranged in the exhaust cavity of the lower flange, and is installed in cooperation with the crankshaft short shaft 15. There is a sealing structure between the crankshaft 1 and the cover plate 18, which is completely isolated from the oil pool, so as to prevent the crankshaft balance weight 9 from being in the air. Oil stirring during operation will cause problems such as increased power consumption, unstable shafting and poor reliability, which effectively solves the problem of oil stirring in the balance block. Moreover, the shape design of the crankshaft balance weight 9 of the present disclosure is not limited, and it is easy to realize processing and assembly. The pump body structure of the crankshaft balance block of the present application has a simple structure and a reasonable layout, does not increase the power consumption of the compressor, and has a stable shaft system, high reliability and low vibration.

The compressor provided by the application has the advantages of compact structure, simple structure, stable and reliable operation, and can especially meet the demands of compressors with large displacement and high rotation speed.

In some embodiments, in the projection plane perpendicular to the axis of the crankshaft 1, the centroid of the crankshaft balance weight 9 and the centroid of the rotor balance weight 8 are in a relative distribution with a phase difference of 180°; and/or, in the vertical In the projection plane of the axis of the crankshaft 1 , the crankshaft balance weight is a fan-shaped structure; and/or, the crankshaft balance weight 9 and the short shaft 15 are interference fitted.

The present disclosure also provides an air conditioner, including the compressor of any one of the above embodiments. The compressor also includes a motor stator 19 and an upper cover 21 . The pump body assembly 20 includes a first cylinder 2 , a second cylinder 3 , a first roller 61 , a second roller 62 , a crankshaft 1 and a diaphragm assembly 4 .

The above descriptions are only preferred embodiments of the present disclosure, and are not intended to limit the present disclosure. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present disclosure shall be included in the protection of the present disclosure. within range. The above descriptions are only preferred implementations of the present disclosure. It should be pointed out that those skilled in the art can make several improvements and modifications without departing from the technical principles of the present disclosure. These improvements and modifications are also It should be regarded as the protection scope of the present disclosure.

Claims (19)

A compressor, characterized in that it comprises a crankshaft (1), a first cylinder (2), a second cylinder (3) and a baffle assembly (4); The crankshaft (1) comprises an intermediate shaft section (11) located between the first cylinder (2) and the second cylinder (3); The baffle assembly (4) is arranged between the first cylinder (2) and the second cylinder (3), and the baffle assembly (4) is passed through the intermediate shaft section (11) , the baffle assembly (4) includes a first baffle (41), and the first baffle (41) connects with the intermediate shaft segment (11) to form a baffle bearing for the intermediate Shaft section (11) supports. The compressor according to claim 1, characterized in that: The baffle assembly (4) also includes a second baffle (42); One axial end surface of the first baffle (41) is in contact with the first axial end surface of the first cylinder (2), and one axial end surface of the second baffle (42) is in contact with the first The other axial end surface of the partition (41) is connected; the other axial end surface of the second partition (42) is connected to the axial one end surface of the second cylinder (3); The intermediate shaft segment (11) includes a first intermediate segment (11a) and a second intermediate segment (11b) connected axially; The first partition (41) is sheathed on the outer periphery of the first middle section (11a) and is in contact with the first middle section (11a), and the first middle section (11a) can be relatively The first partition (41) rotates; the second partition (42) is located on the outer periphery of the second middle section (11b) and has a gap with the second middle section (11b). The compressor according to claim 2, characterized in that: The first intermediate section (11a) is a concentric circle section, the central axis of which coincides with the rotation centerline of the crankshaft (1). The compressor according to claim 2, characterized in that: The first partition (41) is fixedly connected with the first cylinder (2), and the second partition (42) is fixedly connected with the second cylinder (3). The compressor according to claim 2 or 4, characterized in that: The axial height of the first partition (41) is greater than the axial height of the second partition (42). The compressor according to claim 2, characterized in that: The side opposite to the second partition (42) of the first partition (41) is provided with a first cavity (71), and the second partition (42) is connected to the first partition A second cavity (72) is provided on the opposite side of the plate (41), and the first cavity (71) is connected to the second cavity (72) to form a separator exhaust cavity (7); The first separator (41) is provided with a first exhaust hole, one end of the first exhaust hole communicates with the inside of the first cylinder (2), and the other end of the first exhaust hole can communicating with said first cavity (71); The second partition (42) is provided with a second exhaust hole, one end of the second exhaust hole can communicate with the inside of the second cylinder (3), and the other end of the second exhaust hole Can communicate with said second cavity (72). The compressor according to claim 6, characterized in that: A first exhaust valve is arranged at the first exhaust hole, and a second exhaust valve is arranged at the second exhaust hole. The compressor according to any one of claims 1-7, characterized in that: It also includes a housing (5), the crankshaft (1), the first cylinder (2), the second cylinder (3) and the separator assembly (4) are located in the housing (5) internal; The height of at least one of the first cylinder (2) and the second cylinder (3) is H, the inner diameter of the cylinder is D, and the inner diameter of the housing (5) is F, satisfying: H/D≥ 0.45 and H/F≥0.21. The compressor according to claim 8, characterized in that: The maximum rotational speed of said compressor is greater than or equal to 120rps; or The outer diameter of the casing (5) is greater than or equal to 160mm. The compressor according to any one of claims 1-9, characterized in that: The crankshaft (1) further includes a first eccentric portion (12) and a second eccentric portion (13); The intermediate shaft segment (11) is located between the first eccentric portion (12) and the second eccentric portion (13); The compressor also includes a first roller (61) and a second roller (62); The first roller (61) is sleeved on the outer circumference of the first eccentric part (12), the first roller (61) is located in the first cylinder (2), and the first eccentric Part (12) drives the connection; The second roller (62) is sheathed on the outer periphery of the second eccentric part (13), and the second roller (62) is located in the second cylinder (3), and the second eccentric Part (13) drives the connection. The compressor according to claim 10, characterized in that: It also includes a rotor balance weight (8), a crankshaft balance weight (9) and a motor rotor (10); The crankshaft (1) also includes a major axis (14) and a minor axis (15); The crankshaft balance weight (9) is arranged on the short axis (15), and the motor rotor (10) is arranged on the long axis (14); The rotor balance weight (8) is connected and arranged on the motor rotor (10); The first eccentric portion (12) is closer to the long axis (14) than the second eccentric portion (13); The second eccentric portion (13) is closer to the short axis (15) than the first eccentric portion (12); The center of mass of the rotor balance weight (8) and the first eccentric portion (12) are arranged symmetrically with respect to the rotation center line of the crankshaft (1); The center of mass of the crankshaft balance weight (9) and the second eccentric portion (13) are arranged symmetrically with respect to the rotation center line of the crankshaft (1). The compressor of claim 11, wherein: Also comprising a first bearing (16) and a second bearing (17); The first bearing (16) is sleeved on the long axis (14) and connected with the first cylinder (2); The first eccentric portion (12) is located between the first bearing (16) and the separator assembly (4); The rotor balance weight (8) is arranged at one end of the motor rotor (10) close to the first bearing (16), or the rotor balance weight (8) is arranged at the end of the motor rotor (10) away from the first bearing (16). One end of the bearing (16). The compressor of claim 12, wherein: The rotor balance weight (8) includes a first rotor balance weight (81) and a second rotor balance weight (82), and the first rotor balance weight (81) is arranged near the motor rotor (10) At one end of the first bearing (16), the second rotor balance weight (82) is arranged at the end of the motor rotor (10) away from the first bearing (16). The compressor of claim 13, wherein: In the projection plane perpendicular to the axis of the crankshaft (1), the center of mass of the first rotor balance weight (81) and the second rotor balance weight (82) are The center is the center of the circle and the central angle between them is <180°. The compressor of claim 12, wherein: The second bearing (17) is sleeved on the short shaft (15) to support the short shaft (15); A cover plate (18) is also arranged on the short shaft (15); The main exhaust chamber (100) is formed between the cover plate (18) and the second bearing (17), and the crankshaft balance weight (9) is connected to the short shaft (15) and is located on the main In the exhaust cavity (100). The compressor of claim 11, wherein: In a projection plane perpendicular to the axis of the crankshaft (1), the center of mass of the crankshaft balance weight (9) and the center of mass of the rotor balance weight (8) are relatively distributed with a phase difference of 180°. The compressor according to claim 11 or 16, characterized in that: In a projection plane perpendicular to the axis of the crankshaft (1), the crankshaft balance weight (9) is a fan-shaped structure. The compressor according to claim 11 or 16, characterized in that: The crankshaft balance weight (9) is interference fitted with the short shaft (15). An air conditioner, characterized by comprising the compressor described in any one of claims 1-18.

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