CN205036580U - Multi -cylinder rotary compressor - Google Patents

Abstract

The utility model discloses a multi-cylinder rotary compressor. A sealed casing accommodates a compression mechanism part and a motor, and the motor includes a stator and a rotor. The compression mechanism part includes: the first cylinder and the second cylinder; the middle partition; the first cylinder and the second cylinder respectively accommodate the piston and the sliding plate; the crankshaft includes the first eccentric shaft and the second eccentric which drive the two pistons respectively shaft, the intermediate shaft connecting the first eccentric shaft and the second eccentric shaft, the counter shaft connecting the first eccentric shaft, the main shaft connecting the second eccentric shaft; The sealing plate and the second sealing plate; the intermediate shaft is in sliding fit with the intermediate bearing provided in the intermediate partition, the main shaft is in sliding fit with the motor bearing provided in the housing, and at least one of the first eccentric shaft and the second eccentric shaft is in contact with the Described crankshaft is separate assembly type. According to the multi-cylinder rotary compressor of the utility model, the reliability of the crankshaft running at high speed and under high load is improved.

Description

Multi-cylinder rotary compressor

technical field

The utility model relates to the field of compressors, in particular to a multi-cylinder rotary compressor.

Background technique

Rotary compressors, which are widely used in air conditioners, which consume the most power among home appliances, are strongly requested to improve APF and improve noise and vibration. In addition, increasing the heating capacity of the air conditioner and further improving the APF by reducing the size and weight of the rotary compressor and the high-speed operation of the inverter motor are also attracting attention.

On the other hand, the most common market failure in rotary compressors is the wear failure of the crankshaft and bearings. Most of them are caused by the increase of bearing load during high-speed and high-load operation, and the lack of oil caused by high-speed operation. Therefore, improvements in the reliability of crankshafts and bearings are also strongly demanded.

Utility model content

The utility model aims to solve one of the technical problems in the related art at least to a certain extent. For this reason, the utility model proposes a multi-cylinder rotary compressor, which improves the reliability of the crankshaft running at high speed and under high load.

According to the multi-cylinder rotary compressor of the present utility model, the sealed casing accommodates the compression mechanism part and the motor, and the motor includes a stator and a rotor; the compression mechanism part includes: a first cylinder and a second cylinder; The intermediate partition between the first cylinder and the second cylinder and combined with them; the first cylinder and the second cylinder are respectively accommodated with pistons and slides; crankshaft, which includes driving two cylinders respectively The first eccentric shaft and the second eccentric shaft of the piston, the intermediate shaft connecting the first eccentric shaft and the second eccentric shaft, the secondary shaft connecting the first eccentric shaft, and the second eccentric shaft the main shaft; the first sealing plate and the second sealing plate that respectively seal the compression chambers provided in the first cylinder and the second cylinder; the intermediate shaft is slidingly fitted with the intermediate bearing provided in the intermediate partition, The main shaft is in sliding fit with a motor bearing provided in the housing, and at least one of the first eccentric shaft and the second eccentric shaft is separately combined with the crankshaft.

According to the multi-cylinder rotary compressor of the present invention, by making the crankshaft slide and fit with the intermediate bearing and the motor bearing respectively, the compressive force and centrifugal force acting on the two pistons and the rotation and swing of the rotor are slidably supported by the above sliding fit, reducing The sliding wear between the eccentric shaft and the bearing and the vibration of the compressor are reduced, and the reliability of the crankshaft running at high speed and under high load is improved.

In some embodiments of the present invention, at least one of the intermediate bearing and the motor bearing includes a rolling bearing that is in sliding fit with the crankshaft.

In some embodiments of the present utility model, the crankshaft is in sliding fit with at least one of the first sealing plate and the second sealing plate.

In some embodiments of the present invention, the main shaft outer peripheral hole opening to the outer circumference of the main shaft communicates with the exhaust pipe connected to the housing through the interior of the main shaft.

Furthermore, the main shaft or the rotor is equipped with an oil separator, and the oil separation device communicates with the outer peripheral hole of the main shaft.

In some embodiments of the present invention, the intermediate bearing is composed of a cylindrical portion for receiving the rolling bearing and two end surfaces open to both ends of the cylindrical portion, and the inner diameter of the two end surfaces is smaller than the inner diameter of the cylindrical portion.

In some embodiments of the present invention, the displacements of the first cylinder and the second cylinder are different, and the cylinder with a larger displacement is arranged on the side of the motor bearing relative to the intermediate bearing.

In some embodiments of the present utility model, the outer periphery of the middle partition is fixed on the inner wall of the housing.

In some embodiments of the present utility model, the material of the crankshaft is any one of casting, steel pipe and steel.

Description of drawings

Fig. 1 is related to embodiment 1 of the present utility model, shows the longitudinal sectional view of multi-cylinder rotary compressor internal structure;

Fig. 2 is related to this embodiment 1, shows the details of the crankshaft and the assembly method of the needle roller bearing and the eccentric shaft of the crankshaft;

Fig. 3 is relevant to this embodiment 1, becomes the detailed view of the cylindrical plate of motor bearing and oil separator;

Fig. 4 is related to this embodiment 1, the assembly diagram of the rolling bearing with large outer diameter and the middle partition;

Fig. 5 is a vertical cross-sectional view showing the internal structure of a multi-cylinder rotary compressor related to Embodiment 2 of the present utility model.

Reference signs:

Multi-cylinder rotary compressor 1, casing 2, end plate 2b, motor 4, stator 4a, rotor 4b,

Compression mechanism part 5, intermediate partition plate 50, first cylinder 11, second cylinder 21, first piston 61, second piston 62, first seal plate 45, second seal plate 40, exhaust device 40c (45c), Intermediate bearing 52, first needle roller bearing 15, crankshaft 30, main shaft outer peripheral hole 35c, shaft center hole 35d, intermediate shaft 33, first eccentric shaft 31, main shaft 35, second eccentric shaft 32, counter shaft 36, eccentric shaft keyway 31b, key 18, shaft center hole 30a, shaft side keyway 36b, shaft thrust lower part 32a,

Motor bearing plate 48, motor bearing 49, second needle roller bearing 17, end plate cylinder 2d, muffler 45b (40b), sealing plate 38, circular plate 38a, slider 38b, ball bearing 16, slide bearing 19,

Cylindrical plate 66, peripheral window 66a, exhaust pipe 3, suction pipe 28, outdoor heat exchanger 81, liquid reservoir 85, expansion valve 82, indoor heat exchanger 83, bushing nut 67.

detailed description

Embodiments of the invention are described in detail below, examples of which are illustrated in the accompanying drawings. The embodiments described below by referring to the figures are exemplary and are intended to explain the present invention, but should not be construed as limiting the present invention.

In describing the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "Back", "Left", "Right", "Vertical", "Horizontal", "Top", "Bottom", "Inner", "Outer", "Clockwise", "Counterclockwise", "Axial" The orientation or positional relationship indicated by , "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the utility model and simplifying the description, rather than indicating or implying the referred device Or elements must have a specific orientation, be constructed and operate in a specific orientation, and thus should not be construed as limiting the invention.

In addition, the terms "first" and "second" are used for descriptive purposes only, and cannot be interpreted as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features. Thus, the features defined as "first" and "second" may explicitly or implicitly include at least one of these features. In the description of the present utility model, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

In this utility model, unless otherwise specified and limited, terms such as "installation", "connection", "connection" and "fixation" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection. Connected, or integrated; it can be mechanically connected, or electrically connected, or can communicate with each other; it can be directly connected, or indirectly connected through an intermediary, and it can be the internal communication of two components or the interaction relationship between two components , unless expressly defined otherwise. Those of ordinary skill in the art can understand the specific meanings of the above terms in the present utility model according to specific situations.

The multi-cylinder rotary compressor 1 according to the embodiment of the present utility model will be described in detail below with reference to FIGS. 1. A horizontal rotary compressor or a swing rotary compressor. The hermetic rotary compressor can be a rotary compressor whose casing pressure is the high pressure side, or a rotary compressor whose casing pressure is the low pressure side. The multi-cylinder rotary compressor 1 can be installed in an air conditioner, a refrigerator, a water heater, a vehicle-mounted refrigerator or an air conditioner.

According to the multi-cylinder rotary compressor 1 of the embodiment of the present invention, the sealed casing 2 accommodates the compression mechanism part 5 and the motor 4, and the motor 4 includes a stator 4a and a rotor 4b. The compression mechanism part 5 includes: the first air cylinder 11, the second air cylinder 21, the middle partition plate 50 combined with them between the first air cylinder 11 and the second air cylinder 21, and the first air cylinder 11 and the second air cylinder 21 respectively accommodate There are a piston, a slide plate, a crankshaft 30 , and a first seal plate 45 and a second seal plate 40 for sealing the compression chambers provided in the first cylinder 11 and the second cylinder 21 , respectively.

The crankshaft 30 includes a first eccentric shaft 31 and a second eccentric shaft 32 that respectively drive two pistons, an intermediate shaft 33 that connects the first eccentric shaft 31 and the second eccentric shaft 32, a secondary shaft 36 that connects the first eccentric shaft 31, and connects The main shaft 35 of the second eccentric shaft 32 .

The intermediate shaft 33 is in sliding fit with the intermediate bearing 52 provided in the middle partition plate 50, the main shaft 35 is in sliding fit with the motor bearing 49 provided in the casing 2, and at least one of the first eccentric shaft 31 and the second eccentric shaft 32 is in contact with the crankshaft. 30 is a separate combined formula. The motor bearing 49 is located above the motor 4 , and the motor bearing 49 is fixed on the inner wall of the housing 2 through the motor bearing plate 48 .

That is, the multi-cylinder rotary compressor 1 includes a sealed casing 2 , a motor 4 and a compression mechanism part 5 .

The motor 4 includes a stator 4a and a rotor 4b. The compression mechanism part 5 includes the first cylinder 11, the second cylinder 21, the middle partition plate 50, the first piston 61, the second piston 62, the first sliding plate, the second sliding plate, the crankshaft 30, the first sealing plate 45 and the second 2 sealing plate 40.

The first cylinder 11 has a first compression chamber, the second cylinder 21 has a second compression chamber, and the intermediate partition plate 50 is provided between the first cylinder 11 and the second cylinder 21 and has an intermediate bearing 52 .

The crankshaft 30 has a main shaft 35 , a counter shaft 36 , an intermediate shaft 33 , a first eccentric shaft 31 , and a second eccentric shaft 32 . Wherein the main shaft 35 is fixed on the rotor 4b to be driven to rotate by the rotor 4b. The main shaft 35 is connected to the second eccentric shaft 32 , the sub shaft 36 is connected to the first eccentric shaft 31 , and the intermediate shaft 33 is located between the first eccentric shaft 31 and the second eccentric shaft 32 . The first piston 61 is sleeved on the first eccentric shaft 31 to rotate eccentrically driven by the first eccentric shaft 31 , and the second piston 62 is sleeved on the second eccentric shaft 32 to rotate eccentrically driven by the second eccentric shaft 32 .

The first piston 61 is located in the first compression chamber, the second piston 62 is located in the second compression chamber, the first slide is arranged on the first cylinder 11, the second slide is arranged on the second cylinder 21, and the first slide Cooperate with the first piston 61 for reciprocating motion, and cooperate with the second piston 62 for reciprocating motion.

The first sealing plate 45 is provided on the first cylinder 11 to connect to the opening surface of the first compression chamber, and the second sealing plate 40 is provided on the second cylinder 21 to connect to the opening surface of the second compression chamber.

The intermediate shaft 33 is in sliding fit with the intermediate bearing 52 , and the main shaft 35 is in sliding fit with the motor bearing 49 . Wherein, the intermediate shaft 33 and the intermediate bearing 52 can be directly slidably fitted, or bearings such as rolling bearings and sliding bearings are arranged between the intermediate shaft 33 and the intermediate bearing 52 . The main shaft 35 and the motor bearing 49 can be slidably fitted directly, or bearings such as rolling bearings and sliding bearings can be arranged between the main shaft 35 and the motor bearing 49 .

According to the multi-cylinder rotary compressor 1 of the embodiment of the present utility model, by making the crankshaft 30 slide and fit with the intermediate bearing 52 and the motor bearing 49 respectively, the compression force and centrifugal force acting on the two pistons and the rotation and oscillation of the rotor 4b are determined by the above-mentioned Sliding fit for sliding support reduces the sliding wear between the eccentric shaft and the bearing and the vibration of the compressor, and improves the reliability of the crankshaft 30 running at high speed and under high load.

In some embodiments of the present invention, at least one of the intermediate bearing 52 and the motor bearing 49 is provided with a rolling bearing that is slidingly fitted with the crankshaft 30 .

In a preferred embodiment of the present invention, the crankshaft 30 is in sliding fit with at least one of the first sealing plate 45 and the second sealing plate 40 . That is to say, one of the first sealing plate 45 and the second sealing plate 40 may be slidably engaged with the crankshaft 30 , or both the first sealing plate 45 and the second sealing plate 40 may be slidably engaged with the crankshaft 30 .

In some embodiments of the present invention, the main shaft outer peripheral hole 35c opening to the outer periphery of the main shaft 35 communicates with the exhaust pipe 3 connected to the housing 2 through the interior of the main shaft 35 . That is to say, there is a shaft center hole 35d in the main shaft 35, and the outer periphery of the main shaft 35 has a main shaft outer peripheral hole 35c communicating with the shaft middle hole 35d. The gas exhausted from the shaft center hole 35d is exhausted from the casing 2 through the exhaust pipe 3 . Since the main shaft 35 is in a rotating state, it has the effect of centrifugal separation, which prevents the oil with a large specific gravity from entering the shaft central hole 35d, and has the effect of separating oil and gas. Therefore, by providing the main shaft outer peripheral hole 35c, the oil discharge amount of the compressor can be reduced.

Furthermore, the main shaft 35 or the rotor 4b is provided with an oil separator, and the oil separator communicates with the main shaft outer peripheral hole 35c. Thereby, the effect of oil-gas separation can be further improved, and the oil discharge volume of the compressor can be further reduced. For example, as shown in Figures 1 and 3, a hollow cylindrical plate 66 can be fixed on the rotor 4b, the outer peripheral hole 35c of the main shaft is located in the cylindrical plate 66, the cylindrical plate 66 is provided with a peripheral window 66a, and the cylindrical plate 66 defines an oil separation device.

In some embodiments of the present invention, the intermediate bearing 52 is composed of a cylindrical part for accommodating the rolling bearing and two end surfaces open to both ends of the cylindrical part, and the inner diameters of the two end surfaces are smaller than the inner diameter of the cylindrical part. That is to say, the intermediate shaft 33 is in sliding fit with the rolling bearing.

In some embodiments of the present invention, the displacements of the first cylinder 11 and the second cylinder 21 are different, and the cylinder with a large displacement is arranged on the side of the motor bearing 49 relative to the intermediate bearing 52 . That is, the cylinder with a large displacement is arranged adjacent to the motor bearing 49, so that the bearing load of the intermediate bearing 52 can be reduced.

In some embodiments of the present invention, the outer periphery of the middle partition 50 is fixed on the inner wall of the casing 2 .

Optionally, the material of the crankshaft 30 is any one of casting, steel pipe and steel.

The multi-cylinder rotary compressor 1 according to two specific embodiments of the present invention will be described in detail below with reference to FIGS. 1-5 .

Example 1:

In the multi-cylinder rotary compressor 1 shown in FIG. 1 , the outer periphery of the stator 4 a constituting the electric motor 4 and the outer periphery of the intermediate partition plate 50 provided at the center of the compression mechanism unit 5 are fixed to the inner diameter of the casing 2 . The casing 2 is composed of a cylindrical casing and two end plates welded at its upper and lower ends. In addition, the lubricating oil (oil) stored at the bottom of the casing 2 is not shown in the figure.

The compression mechanism part 5 is equipped with a first cylinder 11 and a second cylinder 21, a first piston 61 and a second piston 62 accommodated in these cylinders, a sliding plate (not shown) that reciprocates together with these pistons, and a The first sealing plate 45 and the second sealing plate 40 on the opening surface of the compression chamber formed in the cylinder. Moreover, the 1st sealing plate 45 and the 2nd sealing plate 40 are equipped with the exhaust device 40c and the exhaust device 45c, respectively.

The first needle roller bearing 15 is press-fitted and fixed to the intermediate partition plate 50 connected between the first cylinder 11 and the second cylinder 21 and an intermediate bearing 52 provided at the center thereof. Furthermore, the motor bearing 49 provided at the center of the motor bearing plate 48 fixed to the inner diameter of the housing 2 is press-fitted and fixed to the second needle roller bearing 17 . It is therefore characteristic that the crankshaft 30 is in a sliding fit with these two needle bearings.

In Embodiment 1, there are gaps between the first seal plate 45 and the second seal plate 40 and the crankshaft 30, so the crankshaft 30 and these seal plates are not slidably fitted. Therefore, the hub protruding from the center of each sealing plate serves as means for sealing the central openings of the muffler 45b and the muffler 40b.

A rotor 4 b is fixed in the crankshaft 30 . In the rotor 4b and the motor bearing 49, a cylindrical plate 66 is provided at the upper end of the rotor 4b. Furthermore, in the cylindrical plate 66, the main shaft outer peripheral hole 35c penetrating through the outer periphery of the crankshaft 30 communicates with the exhaust pipe 3 through the shaft center hole 35d and the end plate tube 2d.

The exhaust pipe 3 connected to the end plate 2b of the housing 2 and the suction pipe 28 connected to the middle partition 50 are respectively connected to the outdoor heat exchanger 81 and the accumulator 85 constituting the refrigeration cycle. Therefore, the high-pressure gas discharged from the exhaust pipe 3 flows in the order of the outdoor heat exchanger 81 and the expansion valve 82, and the decompressed low-pressure gas flows in the order of the indoor heat exchanger 83, the liquid reservoir 85, and the suction pipe 28. Flow, split into 2 cylinders. Here, the internal pressure of the housing 2 is the high-pressure side, but the disclosed technology of the present invention can be applied to the design of the internal pressure of the housing 2 as the low-pressure side.

The low-pressure gas sucked into each cylinder is compressed by the first piston 61 and the second piston 62 driven by the crankshaft 30, and then discharged into the muffler 45b and the muffler 40b. These high-pressure gases are exhausted between the second sealing plate 40 and the motor 4 . Thereafter, the high-pressure gas passing through the motor 4 flows into the spindle outer peripheral hole 35c through the cylindrical plate 66 rotating at a high speed.

In addition, the first needle bearing 15 is effectively slip-fitted against the load of the intermediate shaft 33 due to compression of the first piston 61 and the second piston 62 . That is, since the first needle bearing 15 is located at the center of the two pistons and is adjacent to the two pistons, the coupling force of the pistons that rotate and compress at a phase angle of 180 degrees can be minimized.

One of the second needle bearings 17 supports the rotational load of the rotor 4b in a sliding fit with the first needle bearing 15, and can prevent the crankshaft 30 from tilting. Therefore, it is possible to prevent the rotational vibration of the rotor 4b and maintain a necessary air gap between the stator 4a and the rotor 4b. In addition, in a design in which the displacements of the first cylinder 11 and the second cylinder 21 are different, the cylinder with the larger displacement should be arranged as the second cylinder 21 . That is, the second cylinder 21 with a large displacement is supported by two needle bearings for sliding fit.

FIG. 2 shows an assembly process of the crankshaft 30 , the intermediate partition plate 50 and the first eccentric shaft 31 . In the crankshaft 30 before assembly, the main shaft 35, the second eccentric shaft 32, the intermediate shaft 33, and the counter shaft 36 are integrated. The inner diameter of the first needle roller bearing 15 is assembled and fixed in the intermediate bearing 52 of the intermediate partition plate 50 in advance, and is inserted from the end of the counter shaft 36 . Thereafter, the first eccentric shaft 31 is inserted from the end of the secondary shaft 36 . The eccentric shaft key groove 31 b of the first eccentric shaft 31 is fitted into the key 18 preliminarily attached to the sub shaft 36 .

Through the above assembly, the intermediate partition plate 50 for fixing the first needle roller bearing 15 is accommodated between the first eccentric shaft 31 and the second eccentric shaft 32 . As a result, the intermediate shaft 33 is in sliding fit with the first needle bearing 15 . The axial center hole 30a opened to the end of the auxiliary shaft 36 is an oil supply passage for the first needle bearing 15 and the above-mentioned eccentric shaft, piston, sliding plate, and the like.

The spindle outer peripheral hole 35c passing through the spindle 35 perpendicularly intersects with the shaft center hole 35d. The key 18 is connected to the first eccentric shaft 31 and the shaft-side key groove 36 b, and is means for transmitting the moment of the crankshaft 30 to the first eccentric shaft 31 . Here, the first eccentric shaft 31 and the crankshaft 30 are assembled separately. Furthermore, the second eccentric shaft 32 and the crankshaft 30 may be of a separate and combined type. At this time, the first needle bearing 15 and the second eccentric shaft 32 are inserted from the shaft end side of the main shaft 35 .

The material of the crankshaft 30 can be selected from any of castings, steel pipes, and steel materials. In particular, a steel pipe or a steel material can increase the rigidity of the crankshaft 30, and surface hardening can improve the wear resistance of bearings. In the case of a steel pipe or a steel material, if the above-mentioned eccentric shaft is a separate and combined type, it is easy to configure the eccentric shaft.

In addition, in terms of the completed state of the compressor shown in FIG. 1 , the shaft thrust lower portion 32 a of the second eccentric shaft 32 becomes a thrust surface supporting the crankshaft 30 , and is slidingly engaged with the plane of the intermediate partition plate 50 . There is a thrust gap (C) between the shaft thrust upper portion 32 b and the second seal plate 40 . This thrust clearance (C) is a clearance where the crankshaft 30 can move up and down, and also a clearance between the end plate cylinder 2d and the seal plate 38 as shown in the figure below.

3 shows the details of the motor bearing 49 equipped with the second needle bearing 17. The cylindrical plate 66 with several outer peripheral windows 66a fixed on the upper end of the rotor 4b is pressed and fixed on the end plate of the housing 2 by a bushing nut 67. Section of the end plate tube 2d. The cap-shaped sealing plate 38 provided on the upper end of the main shaft 35 is composed of a circular plate 38a covering the opening end of the end plate cylinder 2d and a slider 38b slidable along the main shaft 35 .

The action and effect of the sealing plate 38 will be described. First, when the end plate 2b is welded to the open end of the case 2, the circular plate 38a and the end plate cylinder 2d are brought into contact. In the final assembly process or painting process in which the compression mechanism part 5 and the end plate 2b are assembled and fixed in the housing 2, the housing must be turned upside down at least once.

Due to this inversion, the seal plate 38 slides on the outer diameter of the main shaft 35 . Therefore, a clearance equal to the already mentioned thrust clearance (C) of the crankshaft 30 can be formed between the open end of the end plate cylinder 2d and the circular plate 38a. For example, if the thrust clearance (C)=0.3 mm, the gap between the open end of the end plate tube 2 d and the circular plate 38 a is 0.3 mm, and the end plate tube 2 d passes through the sealing plate 38 and is basically in a sealed state. That is, the sealing plate 38 prevents the exhaust gas from short-circuiting and flowing into the end plate cylinder 2 d, and promotes the flow to the cylindrical plate 66 .

The amount of oil mixed in the high-pressure gas discharged from the two cylinders increases in proportion to the rotational speed of the two pistons or the rotor 4b. High-pressure gas containing a large amount of oil flows toward the peripheral window 66 a of the cylindrical plate 66 . However, the high-speed rotating cylindrical plate 66, due to its centrifugal separation effect, prevents the oil with a large specificity from going from the outside to the inside of the peripheral window 66a. On the other hand, gas with a small specific gravity easily enters the cylindrical plate 66 . Therefore, the cylindrical plate 66 can exert a highly effective oil separation effect.

The gas separated from the oil by the cylindrical plate 66 is exhausted from the exhaust pipe 3 from the outer peripheral hole 35c of the main shaft, through the central shaft hole 35d and the end plate cylinder 2d. Therefore, while the oil discharge to the refrigeration cycle system is greatly reduced, the oil storage capacity of the casing 2 can be stably ensured.

In terms of the design and arrangement of the cylindrical plate 66, it is not limited to the above design as long as it is an oil separation means that rotates together with the rotor 4b. For example, the rotor 4b is provided with a main shaft outer peripheral hole 35c, and the upper end surface or the lower end surface of the rotor 4b has a channel communicating with the main shaft outer peripheral hole 35c.

Alternatively, the cylindrical plate 66 and the main shaft outer peripheral hole 35c may be arranged between the second seal plate 40 and the rotor 4b. In addition, even if the cylindrical plate 66 is omitted and only the main shaft outer peripheral hole 35c is used, the oil separation effect equivalent to or better than that of the conventional oil discharge reduction device can be exhibited.

The outer diameter of the needle roller bearing is small, so it is suitable for the application of centering the spacer 50 bearing. However, as shown in FIG. 4, if the center partition 50 is divided, even if the outer diameter (Db) of the ball bearing 16 is large, the inner diameter (Dm) of the opening 52a of the intermediate bearing 52 can be reduced. Therefore, a ball bearing may be used instead of the first needle bearing 15 . In addition, if the inner diameter (Dm) is large, the outer diameter of the piston needs to be increased, the inner diameter of the compression chamber will be enlarged, and the compression efficiency will decrease.

As described above, the intermediate partition plate 50 provided with the intermediate bearing 52 is a member that supports the compression load of the two pistons and the rotational load of the rotor 4b. Therefore, it is desirable that the outer periphery of the middle partition plate 50 of a highly rigid design be fixed at the inner periphery of the housing 2 .

Example 2:

Embodiment 2 shown in FIG. 5 is different from Embodiment 1 in two points. (1) In the compression mechanism part 5, the crankshaft 30 which is slidably engaged with the first needle bearing 15 is slidably engaged with both the second seal plate 40 and the first seal plate 45, (2) as the second needle bearing 17 As an alternative, a sliding bearing 19 is used. Furthermore, a bearing bush can be used as the slide bearing 19 . In addition, related centrifugal oil separation devices such as the cylindrical plate 66 fixed in the rotor 4b used in the first embodiment and the main shaft outer peripheral hole 35c opening to the main shaft 35 are not shown in the figure.

In Embodiment 2, even if abrasion occurs between the crankshaft 30 and one or both of the second seal plate 40 and the first seal plate 45 , the reliability of the compressor can be maintained due to the function of the first needle bearing 15 . In addition, among the above four sliding fits, it is also possible to omit the less important sliding fit between the first seal plate 45 and the crankshaft 30 . In this case, the inner diameter of the first sealing plate 45 as shown in FIG. 1 may be increased or the sub-shaft 36 may be shortened.

The multi-cylinder rotary compressor of the utility model can be mounted in an air conditioner, a refrigeration device, a water heater, a vehicle-mounted refrigerator or an air conditioner. In addition, it can also be used in horizontal multi-cylinder rotary compressors.

In summary, a specific problem to be solved by the utility model is: the high-speed rotating multi-cylinder rotary compressor has a long length between the bearings of the crankshaft (equal to the thickness of 2 cylinders and the middle partition), and the motor rotor rotates Shaft vibration is also large. Therefore, the subject is the sliding wear of the crankshaft and the bearing and the vibration of the compressor.

To this end, a specific means adopted to solve the above-mentioned problems is as follows:

The intermediate partition plate 50 and the motor bearing 49 are provided with a first needle roller bearing 15 and a second needle roller bearing 17 , respectively. The first needle bearing 15 is in sliding fit with the intermediate shaft 33 to support the compression load of the rotary pistons in the two cylinders. The second needle bearing 17 prevents rotational vibration of the rotor 4b together with the first needle bearing 15 . The high-pressure gas discharged from the cylinder passes through the mufflers 45b and 40b, respectively, from the lower side to the upper side of the electric motor 4. At this time, the gas flows from the cylindrical plate 66 to the main shaft outer peripheral hole 35 c and the shaft center hole 35 d of the crankshaft 30 in this order, and is discharged into the exhaust pipe 3 .

The beneficial effects that adopt above-mentioned specific means to bring for the utility model are:

(1) The reliability of crankshafts operating at high speeds such as 200rps or under high loads is improved.

(2) The heating capacity of the air conditioner is improved due to high-speed operation and increased refrigeration capacity. Or reduce the displacement and realize the miniaturization of the compressor. In addition, wide range operation from low speed to high speed can improve APF.

(3) The centrifugal oil separator installed in the crankshaft reduces the amount of oil discharged and ensures the necessary amount of oil inside the compressor.

(4) It can be applied in horizontal rotary compressors or swing rotary compressors. Also, it can be applied to the application of multi-cylinder rotary compressors whose casing pressure is on the low-pressure side.

In the present invention, unless otherwise clearly specified and limited, the first feature may be in direct contact with the first feature or the first feature and the second feature through an intermediary indirect contact. Moreover, "above", "above" and "above" the first feature on the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. "Below", "beneath" and "beneath" the first feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is less horizontally than the second feature.

In the description of this specification, descriptions with reference to the terms "one embodiment", "some embodiments", "example", "specific examples", or "some examples" mean that specific features described in connection with the embodiment or example , structures, materials or features are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the described specific features, structures, materials or characteristics may be combined in any suitable manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine different embodiments or examples and features of different embodiments or examples described in this specification without conflicting with each other.

Although the embodiments of the present invention have been shown and described above, it can be understood that the above-mentioned embodiments are exemplary, and should not be construed as limitations of the present invention, and those of ordinary skill in the art are within the scope of the present invention. Variations, modifications, substitutions and variations can be made to the above-described embodiments.

Claims (9)

1. A multi-cylinder rotary compressor, characterized in that the sealed housing accommodates a compression mechanism and a motor, and the motor includes a stator and a rotor; The compression mechanism part includes: 1st cylinder and 2nd cylinder; a central partition between and associated with the first cylinder and the second cylinder; The first cylinder and the second cylinder respectively house a piston and a slide; crankshaft, the crankshaft includes a first eccentric shaft and a second eccentric shaft that respectively drive the two pistons, an intermediate shaft that connects the first eccentric shaft and the second eccentric shaft, an intermediate shaft that connects the first eccentric shaft a secondary shaft, a main shaft connected to the second eccentric shaft; a first sealing plate and a second sealing plate respectively sealing the compression chambers provided in the first cylinder and the second cylinder; The intermediate shaft is in sliding fit with the intermediate bearing provided in the intermediate partition, the main shaft is in sliding fit with the motor bearing provided in the housing, and the first eccentric shaft and the second eccentric shaft are in sliding fit. At least one is separately combined with the crankshaft. 2 . The multi-cylinder rotary compressor according to claim 1 , wherein at least one of the intermediate bearing and the motor bearing includes a rolling bearing that is in sliding engagement with the crankshaft. 3 . 3. The multi-cylinder rotary compressor according to claim 1, wherein the crankshaft is slidably engaged with at least one of the first sealing plate and the second sealing plate. 4 . The multi-cylinder rotary compressor according to claim 1 , wherein a main shaft outer peripheral hole opened to the outer periphery of the main shaft communicates with an exhaust pipe connected to the housing through the inside of the main shaft. 5 . The multi-cylinder rotary compressor according to claim 4 , wherein the main shaft or the rotor is provided with an oil separator, and the oil separator communicates with the outer peripheral hole of the main shaft. 6. The multi-cylinder rotary compressor according to claim 2, wherein the intermediate bearing is composed of a cylindrical portion for accommodating the rolling bearing and two end surfaces that are open to both ends of the cylindrical portion, and the two end surfaces The inner diameter is smaller than the inner diameter of the cylindrical part. 7. The multi-cylinder rotary compressor according to claim 1, wherein the displacements of the first cylinder and the second cylinder are different, and the cylinder with the larger displacement is arranged at the position relative to the intermediate bearing. on one side of the motor bearing. 8 . The multi-cylinder rotary compressor according to claim 1 , wherein the outer periphery of the middle partition is fixed on the inner wall of the casing. 9. The multi-cylinder rotary compressor according to claim 1, characterized in that the material of the crankshaft is any one of castings, steel pipes and steel.