CN105736376A - Rotary compressor - Google Patents

Abstract

The invention discloses a rotary compressor, which comprises a sealed casing, a motor and a compression mechanism part. The compression mechanism part comprises: a first cylinder and a second cylinder; an intermediate partition between the first cylinder and the second cylinder; Main bearing and auxiliary bearing; crankshaft, crankshaft includes main shaft, intermediate shaft and auxiliary shaft; first bearing, the first bearing is arranged in the center of the intermediate partition and slidingly fits with the intermediate shaft; slides with the shaft end side of the main shaft of the fixed rotor For the matched second bearing, before the motor starts for the first time, at least one of the main shaft and the auxiliary shaft is in contact with the main bearing or the auxiliary bearing. After the motor runs for a predetermined time, the main shaft and the main bearing have a clearance fit, and the auxiliary shaft and the auxiliary bearing have a clearance fit. . According to the rotary compressor of the present invention, the alignment accuracy of the compression mechanism portion and the second bearing can be ensured.

Description

rotary compressor

technical field

The invention relates to the field of compressors, in particular to a rotary compressor.

Background technique

Among home appliances, rotary compressors used in air conditioners that consume the most power require a maximum rotation speed, for example, to be increased from 120 Hz to over 200 Hz. Similar to APF improvement, it is necessary to improve the heating characteristics of air conditioners .

As a means of improvement, it is necessary to reduce the displacement of the compressor and to adopt two rolling bearings that are superior in frictional resistance and reliability to cope with the increase in speed. However, conventional sliding bearings and rolling bearings cannot be used together on one shaft due to the difference in bearing lubrication form. Therefore, alignment of rolling bearings with short bearing lengths and crankshafts is an issue.

Contents of the invention

The present invention aims to solve one of the technical problems in the related art at least to a certain extent. Therefore, the present invention proposes a rotary compressor capable of ensuring the alignment accuracy of the compression mechanism and the second bearing.

A rotary compressor according to an embodiment of the present invention includes a sealed casing, a motor, and a compression mechanism part driven by the motor, the motor and the compression mechanism part are arranged in the sealed casing, and the motor includes a stator and the rotor, the sealed casing is composed of a cylindrical casing and an end plate sealing the open ends of the two ends of the cylindrical casing, and the compression mechanism part includes: a first cylinder and a second cylinder; The intermediate partition between the second cylinders; the main bearing and the auxiliary bearing that respectively seal the compression chambers of the first cylinder and the second cylinder; the crankshaft, the crankshaft includes a main shaft, an intermediate shaft and a sub shaft, The main shaft rotates in the main bearing, the intermediate shaft rotates in the middle partition, and the auxiliary shaft rotates in the auxiliary bearing; the first bearing is arranged in the middle The center of the partition and is slidingly fitted with the intermediate shaft; the second bearing is slidingly fitted with the shaft end side of the main shaft that fixes the rotor, and the main shaft and the sub shaft are connected before the motor is initially started. At least one of them is in contact with the main bearing or the auxiliary bearing, and after the motor runs for a predetermined time, the main shaft is in clearance fit with the main bearing, and the auxiliary shaft is in clearance fit with the auxiliary bearing.

According to the rotary compressor of the embodiment of the present invention, the alignment accuracy of the compression mechanism part and the second bearing can be ensured, and the second bearing can be slidably matched with the crankshaft, and at the same time, the wear of the crankshaft can be reduced, and the service life of the crankshaft can be prolonged.

In some embodiments of the present invention, before the motor starts for the first time, between the outer peripheral wall of the main shaft and the inner peripheral wall of the main bearing, or between the outer peripheral wall of the auxiliary shaft and the inner peripheral wall of the auxiliary bearing There is a non-contact gap between them.

In some embodiments of the present invention, before the motor is started for the first time, the position of the main bearing and/or the auxiliary bearing adjacent to the open end is in contact with the crankshaft.

In some embodiments of the present invention, the value of the fit clearance between the first bearing and the intermediate shaft is less than or equal to 1/1000 of the shaft diameter of the main shaft or the auxiliary shaft; The fitting clearance of the main shaft is less than or equal to 1/1000 of the shaft diameter of the main shaft or the auxiliary shaft.

In some embodiments of the present invention, the width of the contact fitting portion is less than or equal to 20% of the outer diameter of the main shaft or the auxiliary shaft.

In some embodiments of the present invention, the outer peripheral wall of the main shaft or the inner peripheral wall of the main bearing is provided with a surface film; and/or the outer peripheral wall of the auxiliary shaft or the inner peripheral wall of the auxiliary bearing is provided with a surface film .

In some embodiments of the present invention, the second bearing is located on one of the end plates; or the second bearing is located in the center of the upper part of the cylindrical shell.

In some embodiments of the present invention, any one of the first bearing and the second bearing is a rolling bearing or a bearing sleeve.

In some embodiments of the present invention, the bearing bracket accommodating the second bearing is fixed on the sealed housing by laser welding.

Description of drawings

Fig. 1 is related to embodiment 1 of the present invention, represents the assembly drawing of the overall internal structure of rotary compressor;

Fig. 2 is related to this embodiment 1, is the explanatory drawing of the problem to be solved by the present invention and the principle used to solve this problem;

Fig. 3 is related to the embodiment 1, and is an exploded view of the compression mechanism part 5;

Fig. 4 is related to this embodiment 1, is the self-aligning assembled figure of compression mechanism part 5, shows the method of aligning with the 2nd bearing 17;

FIG. 5 is an application example related to the arrangement of the second bearing 17 related to the second embodiment of the present invention.

Reference signs:

Rotary compressor 1, sealed casing 2, cylindrical casing 2a, upper end plate 2b, lower end plate 2c,

Motor 4, stator 4a, rotor 4b,

Compression mechanism part 5, intermediate partition plate 25, crankshaft 30, first eccentric shaft 31, second eccentric shaft 32, intermediate shaft 33, main shaft 35, counter shaft 36, first cylinder 11, second cylinder 21, first Compression chamber 11a, second compression chamber 21a, main bearing 40, auxiliary bearing 45, first piston 36a, second piston 36b, main shaft groove 35a, auxiliary shaft groove 36a, oil supply hole 33a, tapping hole 27, upper end shaft 37 ,

Bearing bracket 60, exhaust hole 62,

The first bearing 15, the second bearing 17,

Exhaust pipe 3,

screw 49.

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 and 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 present invention and simplifying the description, rather than indicating or implying the referred device or element Must be in a particular orientation, be constructed in a particular orientation, and operate in a particular orientation, and therefore 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 invention, "plurality" means at least two, such as two, three, etc., unless specifically defined otherwise.

In the present invention, unless otherwise clearly 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 , or integrated; can be mechanically connected, can also be electrically connected or can communicate with each other; can be directly connected, can also be indirectly connected through an intermediary, 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 invention according to specific situations.

A rotary compressor 1 according to an embodiment of the present invention will be described in detail below with reference to FIGS. 1-5 .

A rotary compressor 1 according to an embodiment of the present invention includes a sealed housing 2, a motor 4 and a compression mechanism part 5 driven by the motor 4, the motor 4 and the compression mechanism part 5 are arranged in the sealed housing 2, and the motor 4 includes a stator 4a and the rotor 4b, the sealed housing 2 is composed of a cylindrical housing 2a and an end plate that seals the open ends at both ends of the cylindrical housing 2a. That is to say, the sealing shell 2 is composed of a cylindrical shell 2a, an upper end plate 2b and a lower end plate 2c, and the upper end plate 2b and the lower end plate 2c are respectively used to seal the open ends of the two ends of the cylindrical shell 2a.

The compression mechanism unit 5 includes a first cylinder 11 , a second cylinder 21 , an intermediate partition 25 , a main bearing 40 , an auxiliary bearing 45 , a crankshaft 30 , a first bearing 15 , and a second bearing 17 . The middle partition 25 is located between the first cylinder 11 and the second cylinder 21 , and the main bearing 40 and the auxiliary bearing 45 respectively seal the compression chambers of the first cylinder 11 and the second cylinder 21 .

The crankshaft 30 includes a main shaft 35 , an intermediate shaft 33 and an auxiliary shaft 36 , the main shaft 35 rotates in the main bearing 40 , the intermediate shaft 33 rotates in the middle partition 25 , and the auxiliary shaft 36 rotates in the auxiliary bearing 45 . The first bearing 15 is arranged at the center of the intermediate partition 25 and is slidingly fitted with the intermediate shaft 33 .

The second bearing 17 is slidably engaged with the shaft end side of the main shaft 35 of the fixed rotor 4b.

Before the motor 4 starts for the first time, at least one of the main shaft 35 and the auxiliary shaft 36 is in contact with the main bearing 40 or the auxiliary bearing 45. The bearing 45 has a clearance fit. That is to say, before the initial operation of the rotary compressor 1, that is, before the motor 4 starts for the first time, the main shaft 35 may be in contact with the main bearing 40, or the auxiliary shaft 36 may be in contact with the auxiliary bearing 45, or the main shaft 35 may be in contact with the main bearing 45. The main bearing 40 is a contact fit and the secondary shaft 36 is a contact fit with a secondary bearing 45 . When the motor 4 is running, the rotation of the crankshaft 30 will cause the above-mentioned contact fitting parts to wear. After a predetermined time, the main shaft 35 and the main bearing 40 are in clearance fit and the auxiliary shaft 36 is in clearance fit with the auxiliary bearing 45 .

When the compression mechanism part 5 is installed, since at least one of the main shaft 35 and the auxiliary shaft 36 is in contact with the main bearing 40 or the auxiliary bearing 45, it can be ensured that the crankshaft 30 is upright relative to the middle partition plate 25, ensuring that the compression mechanism part 5 and the second 2. The centering accuracy of the bearing 17. At the same time, after the motor 4 runs for a predetermined time, the main shaft 35 is in clearance fit with the main bearing 40 and the auxiliary shaft 36 is in clearance fit with the auxiliary bearing 45. The crankshaft 30 is only in contact with the first bearing 15 and the second bearing 17 The sliding fit can reduce the wear of the crankshaft 30 and prolong the service life of the crankshaft 30 .

According to the rotary compressor 1 of the embodiment of the present invention, the alignment accuracy of the compression mechanism part 5 and the second bearing 17 can be ensured, and the second bearing 17 can be slidably matched with the crankshaft 30, and at the same time, the wear of the crankshaft 30 can be reduced, and the crankshaft can be extended. 30 service life.

In some embodiments of the present invention, before the motor 4 starts for the first time, there is no contact between the outer peripheral wall of the main shaft 35 and the inner peripheral wall of the main bearing 40, or between the outer peripheral wall of the auxiliary shaft 36 and the inner peripheral wall of the auxiliary bearing 45. Clearance. Preferably, before the initial start of the motor 4, a part of the outer peripheral wall of the main shaft 35 is in contact with the inner peripheral wall of the main bearing 40 and there is a non-contact gap between the outer peripheral wall of the main shaft 35 and the inner peripheral wall of the main bearing 40, A part of the outer peripheral wall of the auxiliary shaft 36 is in contact with the inner peripheral wall of the auxiliary bearing 45 and there is a non-contact gap between the outer peripheral wall of the auxiliary shaft 36 and the inner peripheral wall of the auxiliary bearing 45 .

In some embodiments of the invention, the main bearing 40 and/or the auxiliary bearing 45 are in contact with the crankshaft 30 adjacent to the open end before the motor 4 is initially started. In the example of Fig. 3 and Fig. 4, there are two contact fitting positions between the main bearing 40 and the crankshaft 30, the above two contact fitting positions are arranged adjacent to the two open ends of the main bearing 40 respectively, There is a contact fit position between them, and the above-mentioned one contact fit position is arranged adjacent to the open end of the auxiliary bearing 45 . Thus, the structure of the compression mechanism part 5 is simplified.

According to some embodiments of the present invention, the fit clearance between the first bearing 15 and the intermediate shaft 33 is less than or equal to 1/1000 of the shaft diameter of the main shaft 35 or the auxiliary shaft 36 . That is to say, the value of the fit clearance between the first bearing 15 and the intermediate shaft 33 is less than or equal to 1/1000 of the shaft diameter of the main shaft 35, or the value of the fit clearance between the first bearing 15 and the intermediate shaft 33 is less than or equal to the auxiliary shaft 36 1/1000 of the shaft diameter.

The matching gap between the second bearing 17 and the main shaft 35 is less than or equal to 1/1000 of the shaft diameter of the main shaft 35 or the auxiliary shaft 36 . That is to say, the value of the fit clearance between the second bearing 17 and the main shaft 35 is less than or equal to 1/1000 of the shaft diameter of the main shaft 35, or the value of the fit clearance between the second bearing 17 and the main shaft 35 is less than or equal to that of the auxiliary shaft 36. 1/1000 of the diameter. Therefore, it can be ensured that the fluid lubrication state is maintained between the first bearing 15 and the intermediate shaft 33 , and the fluid lubrication state is maintained between the second bearing 17 and the main shaft 35 .

In some embodiments of the present invention, the width of the contact fitting portion is less than or equal to 20% of the outer diameter of the main shaft 35 or the auxiliary shaft 36 . That is to say, the width of the contact fitting part is less than or equal to 20% of the outer diameter of the main shaft 35 , or the width of the contact fitting part is less than or equal to 20% of the outer diameter of the auxiliary shaft 36 . Therefore, on the premise of ensuring the centering accuracy of the crankshaft 30, the amount of wear can be reduced, the initial wear time can be shortened, and the initial running torque can be reduced.

In some embodiments of the present invention, the outer peripheral wall of the main shaft 35 or the inner peripheral wall of the main bearing 40 is provided with a surface film; and/or the outer peripheral wall of the auxiliary shaft 36 or the inner peripheral wall of the auxiliary bearing 45 is provided with a surface film. The size of the contact fit can thus be reduced by providing a surface coating.

In some embodiments of the present invention, the second bearing 17 is located on one of the end plates; or the second bearing 17 is located in the upper center of the cylindrical shell 2a. More specifically, the bearing bracket housing the second bearing 17 is fixed to the sealed case 2 by laser welding.

In some specific embodiments of the present invention, any one of the first bearing 15 and the second bearing 17 is a rolling bearing or a bearing sleeve. That is to say, the first bearing 15 is a rolling bearing or a bearing sleeve; and/or, the second bearing 17 is a rolling bearing or a bearing sleeve.

The 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 rotary compressor 1 shown in FIG. 1 , the outer peripheral wall of the stator 4 a of the motor 4 and the outer peripheral wall of the intermediate partition 25 provided at the center of the compression mechanism part 5 are fixed to the inner peripheral wall of the cylindrical hermetic casing 2 . The sealed casing 2 is composed of a cylindrical casing 2a, an upper end plate 2b and a lower end plate 2c welded at both ends thereof.

The crankshaft 30 rotating at the center of the compression mechanism unit 5 is in sliding engagement with the first bearing 15 and the second bearing 17 . The first bearing 15 is at the center of the intermediate partition plate 25, and the second bearing 17 is press-fitted and fixed to the bearing bracket 60 fixed at the center of the upper end plate 2b. As these bearings, Example 1 uses a needle bearing which is a rolling bearing. The first cylinder 11 and the second cylinder 21 are respectively connected with the main bearing 40 and the auxiliary bearing 45 which seal the first compression chamber 11a and the second compression chamber 21a (marked in FIG. 3 ).

In order to complete the assembly of the rotary compressor 1 , three assembly steps are required. The first assembling step is an aligning assembly of the compression mechanism section 5 , and after the assembly, the rotor 4 b is shrink-fitted on the outer peripheral wall of the crankshaft 30 . The second assembly process is the self-aligning assembly of the compression mechanism part 5 and the stator 4a, so that the air gap of the motor can be uniform, and the stator 4a and the compression mechanism part 5 are fixed on the inner peripheral wall of the cylindrical shell 2a.

In the second assembly step: the compression mechanism part 5 and the stator 4a are concentrically placed on one assembly jig, and the cylindrical case 2a after induction heating is placed toward the compression mechanism part 5 from the upper side of the stator 4a. The cylindrical shell 2a and the stator 4a are to be connected by shrink fit. The cylindrical case 2a and the intermediate partition plate 25 are welded and connected by spot welding at three points from the outer periphery of the cylindrical case 2a.

Compared with the conventional process, the following third assembly process adds the alignment assembly of the crankshaft 30 and the second bearing 17, and the fixing process of the bearing bracket 60 and the upper end plate 2b. The exhaust pipe 3 is welded to the bearing bracket 60 in advance, and the inner periphery of the bearing bracket 60 is press-fitted with the second bearing 17 . After the bearing bracket 60 is inserted into the upper end of the crankshaft 30 of the compression mechanism unit 5 , the inner peripheral wall of the second bearing 17 fits into the outer peripheral wall of the crankshaft 30 .

Next, the open end of the exhaust pipe 3 is inserted into the central hole of the upper end plate 2b, and the outer periphery of the upper end plate 2b is welded to the open end of the cylindrical case 2a completed in the second assembly process. At the same time, the upper end of the cylindrical part of the bearing bracket 60 is fixed by laser welding from the outer side of the upper end plate 2b. Therefore, the bearing bracket 60 will not be thermally deformed, and can be fixed in the upper end plate 2b. After the third assembling step is completed, the compressor can be completed by welding the lower end plate 2c to the lower opening end of the cylindrical casing 2.

The first assembly process is an important process related to the alignment of the crankshaft 30 of the present invention, and by adding the main bearing 40 and the sub-bearing 45, there is no need to change the conventional assembly method. In the second assembly process, the gap between the inner peripheral wall of the stator 4a and the outer peripheral wall of the rotor 4b, that is, the air gap of the motor, is uniformly adjusted. This process can also borrow the conventional method. On the other hand, as described above, the third assembly process includes a new process by adding the second bearing 17 compared to the conventional one.

Next, the reason why two sliding bearings are used together in the first assembly step will be described. In the left figure of FIG. 2 , the first cylinder 11 and the second cylinder 21 are respectively connected with a flange 41 and a flange 46 , and the crankshaft 30 is only in sliding fit with the first bearing 15 .

Therefore, in the alignment process of the compression mechanism part ( 5 ) in the left figure, the crankshaft 30 rotates obliquely, so that the crankshaft 30 and the second bearing 17 cannot be correctly slidably fitted. In addition, in the first compression chamber 11a and the second compression chamber 21a, the first piston 36a and the second piston 36b rotate while rocking up and down. Moreover, in the second assembly process and the third assembly process, there is still a big problem that the air gap of the motor cannot be adjusted evenly.

The right figure is the same as the previous sliding bearings, the main bearing 40 and the auxiliary bearing 45 are designed with flange 41 and cylindrical bearing 43, flange 46 and cylindrical bearing 46 respectively. Therefore, as for the crankshaft 30, the same alignment assembly as conventional can be performed. That is, the alignment of the crankshaft 30 can be ensured, and the crankshaft 30 can stand upright with respect to the intermediate partition plate 25 .

In addition, in the figure on the right, the cooperation range between the crankshaft 30 and the cylindrical bearing 43 or the cylindrical bearing 46 is limited. Matching A, B, and C corresponds to this range. In addition, these fits wear out in a short period of time and become gaps. That is, the present invention does not use the bearing functions provided in the cylindrical bearing 43 and the cylindrical bearing 46 , and it can be understood that they are functional designs for aligning the crankshaft 30 .

FIG. 3 is a design example of Embodiment 1. The main bearing 40 and the sub-bearing 45 are separated from the crankshaft 30 which is a constituent member of the compression mechanism unit 5, and the structure of the slide bearing they constitute is shown. The first piston 36a and the second piston 36b are driven by the first eccentric shaft 31 and the second eccentric shaft 32, respectively, and rotate eccentrically in the first compression chamber 11a and the second compression chamber 21a.

The crankshaft 30 is composed of an intermediate shaft 33 slidingly fitted with the first bearing 15 in the intermediate partition 25, a main shaft 35 (outer diameter dm1) and a countershaft 36 (outer diameter ds1) connected on both sides thereof, the main shaft 35 and the countershaft 36 are respectively It consists of the first eccentric shaft 31 and the second eccentric shaft 32. In addition, the main shaft 35 and the sub shaft 36 respectively have a main shaft groove 35a (outer diameter dm2) and a sub shaft groove 36a (outer diameter ds2), the intermediate shaft 33 has an oil supply hole 33a, and the first eccentric shaft 31 and the second eccentric shaft The shafts 32 each have oil supply holes for the pistons.

If the groove depths of the main shaft groove 35 a and the sub shaft groove 36 a are 0.15 and 0.1 mm respectively, the outer diameter differences between the main shaft 35 and the sub shaft 36 are dm1−dm2=0.3 and ds1−ds2=0.2 mm, respectively. These grooves prevent the outer peripheral walls of the rotating main shaft 35 and sub shaft 36 from coming into contact with the inner peripheral walls of the cylindrical bearings 43 and 46 , and are means for greatly restricting the fitting length.

The components of the compression mechanism part 5 are precisely aligned, and then the screws 49 are connected to the tapped holes 27 of the middle partition plate 25. As shown in FIG. 4, the compression mechanism part 5 is assembled. The alignment of the compression mechanism part 5 can be completed by borrowing the alignment assembly equipment of the conventional two-cylinder rotary compressor.

The outer peripheral wall (dm1) of the main shaft 35 and the inner peripheral wall 43a (dimension D1) of the cylindrical bearing 43, and the outer peripheral wall (ds1) of the secondary shaft 36 and the inner peripheral wall 46a (dimension D2) of the cylindrical bearing 46 are engaged. However, these fitting lengths are defined by the grooves, the main bearing 40 has two fittings (A) 50 and fitting (B) 51 , and the sub-bearing 45 has one fitting (C) 52 . They correspond to symbols A, B, and C in FIG. 2 .

Usually, L1>L2, so the matching dimension of the fitting (A) 50 is the largest when going out from the center of the first bearing 15 . However, in rare designs such as L1<L2, fit (C) 52 has the largest fit size. In Example 1, L1>L2. In addition, the thin groove 43 b and the thin groove 46 b respectively provided in the fitting (A) 50 and the fitting (C) 52 are discharge passages for abrasion powder generated by the wear of the fitting part due to the rotation of the crankshaft 30 . In addition, the above-mentioned thin grooves may be spiral grooves provided on the inner surfaces of the main bearing 40 and the sub-bearing 45 , respectively.

When the radial gap formed between the first bearing 15 and the intermediate shaft 33 (vibration in the direction perpendicular to the axis of the intermediate shaft 33 ) is large, fit (B) 51 is required. That is, by increasing the fit (B) 51, the crankshaft 30 can be less shaken in the horizontal direction. In addition, the radial clearance mentioned above includes the clearance of rolling bearing components.

In the present invention, in the alignment of the crankshaft 30 included in the compression mechanism unit 5, the alignment accuracy can be improved compared to the conventional design using a sliding bearing. The method has the following two points: (1) lengthen the dimension L1 as much as possible, (2) fit (A) 50 and fit (C) 52, or only fit (A) 50 to have the smallest fit value. The aspect of (2) will be described later, and the interference fit is the most effective.

(1) On the one hand, the appropriate value of the dimension L1 of conventional models is usually not more than three times the inner diameter D1 of the cylindrical bearing 43, and if the dimension L1 is too long, the sliding loss will increase. However, in the first embodiment, the above-mentioned three sliding fit parts will become a sliding fit with a gap due to initial wear, so the dimension L1 has nothing to do with the sliding loss, and the centering can be easily adjusted by lengthening the dimension L1. However, the dimension L1 is limited by the position of the rotor 4b to which the main shaft 35 is fixed.

(2) According to the previous design using sliding bearings, the sliding fit clearance is about 1/1000 of the shaft diameter. For example, if dm1 is 16mm, the sliding fit clearance is about 16μm, and if ds1 is 16mm, the sliding fit clearance is about 16μm. That is, the sliding fit clearance is a boundary value where fluid lubrication can be maintained without metal-to-metal contact between sliding parts due to various load fluctuations.

On the other hand, the present embodiment 1 is based on initial wear, so the matching size should be reduced within the range where the crankshaft 30 can rotate, so that the alignment and assembly accuracy of the crankshaft 30 in the compression mechanism part 5 can be improved easily. For example, the fit size is approximately 1/2000 of the shaft diameter, which can easily be halved. In the above example, the fitting dimensions of fit (A) 50 and fit (C) 52 are respectively 9 μm and 6 μm, and the centering accuracy of crankshaft 30 can be improved compared with previous designs.

As one means for further reducing the fit size, a low-temperature surface film such as a phosphate film may be added to the inner peripheral wall of the cylindrical bearing 43 or the outer peripheral wall of the crankshaft 30 . If the film thickness is 5 μm, the inner diameter is smaller than 10 μm, and the fit size is small. Due to its low friction, the inner peripheral wall of the cylindrical bearing 43 is pressed into the main shaft 35, and a fit without clearance can be formed.

Next, as shown in Figure 3, if the fit width (W) of fit (A) 50, fit (B) 51 and fit (C) 52 is 3.6mm respectively, the fit width (W) is the outer diameter of the main shaft 35 (16mm ) of 20%. 3.6mm or as small as 2mm will not affect the alignment accuracy of the crankshaft 30 . Therefore, if the matching width (W) is reduced, the total amount of wear generated in the matching part is not only the smallest, but also has the effect of shortening the initial wear time and reducing the initial running torque.

Next, the bearing bracket 60 used in the third assembling step will be supplemented with description based on FIG. 4 . After the second assembly step is completed, the bearing bracket 60 is inserted into the upper end of the main shaft 35 , and the second bearing 17 is fitted outside the main shaft 35 . The opening end of the exhaust pipe 3 is inserted into the center hole of the upper end plate 2 b, and the upper end plate 2 b is welded to the outer circumference of the opening end of the cylindrical shell 2 .

Afterwards, the bushing nut 61 is inserted into the outer circumference of the exhaust pipe 3 and the exhaust pipe 3 is lifted up. The upper surface of the bearing bracket 60 is in contact with the inner surface of the upper end plate 2b without gaps. Therefore, from the outer side of the upper end plate 2b to the upper surface of the bearing bracket 60 The third assembly process is completed by laser welding and fixing the entire circumference.

In addition, due to the alignment gap 60a provided in the upper end plate 2b, the exhaust pipe 3 does not come into contact with the center hole of the upper end plate 2b. Therefore, the second bearing 17 maintains the alignment with the main shaft 35 . In addition, when the laser welding and fixing of the upper end plate 2b and the bearing bracket 60 are completed, the exhaust hole 62 provided in the bearing bracket 60 opens into the bearing bracket 60 to communicate with the exhaust pipe 3 .

After the third assembling process, the lower end of the cylindrical case 2 has an opening, so that the sub-bearing 45 and the sub-bearing having only the flange 46 in which the cylindrical bearing 46 is omitted can be replaced and assembled. That is, the sub-bearing 45 can be reused as a jig for aligning between the first and third assembly steps.

Next, initial wear of the three engaging parts during operation of the rotary compressor 1 will be described. If concentric rolling bearings and sliding bearings are used together on one shaft, the rolling bearings (both boundary lubrication and fluid lubrication can be used) will not wear out, and the sliding bearings (fluid lubrication can be used) will start to wear. In particular, in a design in which the width of the three fitting parts is small and there is no means of supplying oil to these fitting parts, the sliding bearing will wear out in the initial operation stage, and a gap will be formed in the fitting parts.

This initial wear may end within 2 minutes after the initial operation, so the inspection process at the production site can be completed. Abrasive powders are discharged from the slots 43b and 46b, respectively, and stored in the bottom of the sealed case 2 (in the oil), so that the magnets provided in the oil can gather them to prevent diffusion.

However, the amount of initial wear is very small, so it is not much different from the amount of initial wear that occurs when a conventional rotary compressor is run-in for about 1,000 hours. Therefore, magnets can also be omitted. In addition, like the scroll machine, the operation stops after about 100 hours of initial wear due to the contact between the movable plate and the stationary plate. However, the amount of initial wear is large, so magnets are often used.

In Embodiment 1, rolling bearings were used for the first bearing 15 and the second bearing 17 , but bushings may be used instead of them. In addition, in Embodiment 1, the outer peripheral wall of the intermediate partition 25 is fixed on the inner peripheral wall of the cylindrical housing 2, but the outer circumference of the flange 41 of the main bearing 40 or the outer circumference of the first cylinder 11 is lengthened and fixed on the cylindrical housing 2. Inner circle methods can also be used.

Example 2:

In FIG. 5 , the second embodiment follows the compression mechanism unit 5 of the first embodiment. The second bearing 17 is supported by the bearing bracket 55 and the bearing bracket 65 fixed to the upper end side of the cylindrical case 2 a, and the second bearing 17 is slidably engaged with the upper end shaft 37 of the main shaft 35 . In addition, the connection between the bearing bracket 55 and the bearing bracket 65 can be fixed 70 by laser welding.

In Embodiment 2, the second bearing 17 adopts the design of a shaft sleeve. In this way, the first bearing 15 serves as a rolling bearing, and the second bearing 17 can be selected as a bushing.

The rotary compressor of the present invention can be mounted in an air conditioner, a refrigerator, a water heater, a vehicle-mounted refrigerator or air conditioner, and the like.

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 and second feature may be in direct contact with the second feature through an intermediary. touch. 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 referring 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 , structure, material or characteristic is 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 embodiments are exemplary and should not be construed as limiting the present invention, and those skilled in the art can make the above-mentioned The embodiments are subject to changes, modifications, substitutions and variations.

Claims (9)

1. a rotary compressor, it is characterized in that, including seal casinghousing, motor and by described motor-driven compression mechanical part, described motor and described compression mechanical part are located in described seal casinghousing, described motor includes stator and rotor, described seal casinghousing is made up of the end plate of cylindrical shell and the opening sealing described cylindrical shell two ends, and described compression mechanical part includes:

1st cylinder and the 2nd cylinder；

Median septum between described 1st cylinder and described 2nd cylinder；

The base bearing that the compression chamber of described 1st cylinder and described 2nd cylinder is sealed respectively and supplementary bearing；

Bent axle, described bent axle includes main shaft, jackshaft and countershaft, and described main shaft rotates in described base bearing, and described jackshaft rotates in septum plate, and described countershaft rotates in described supplementary bearing；

1st bearing, described 1st bearing is located at the center of septum plate and is slidably matched with described jackshaft；

The 2nd bearing that is slidably matched is carried out with the shaft end side of the described main shaft of fixing described rotor,

Before described motor initial start-up, described main shaft contact cooperation with at least one in described countershaft with described base bearing or described supplementary bearing, running after the scheduled time at described motor, described main shaft coordinates with described main bearing journal clearance and described countershaft and described supplementary bearing matched in clearance.

2. rotary compressor according to claim 1, it is characterized in that, before described motor initial start-up, between periphery wall and the internal perisporium of described base bearing of described main shaft or between periphery wall and the internal perisporium of described supplementary bearing of described countershaft, possesses discontiguous gap.

3. rotary compressor according to claim 1, it is characterised in that before described motor initial start-up, the position of described base bearing and/or described supplementary bearing neighbouring open end contacts cooperation with described bent axle.

4. rotary compressor according to claim 1, it is characterised in that the value of the fit clearance of described 1st bearing and described jackshaft is 1/1000 less than or equal to described main shaft or the diameter of axle of described countershaft；

The value of the fit clearance of described 2nd bearing and described main shaft is 1/1000 less than or equal to described main shaft or the diameter of axle of described countershaft.

5. rotary compressor according to claim 1, it is characterised in that the value of the width of contact mating part is 20% less than or equal to described main shaft or the external diameter of described countershaft.

6. rotary compressor according to claim 1, it is characterised in that the periphery wall of described main shaft or the internal perisporium of described base bearing are provided with surface epithelium；And/or

The periphery wall of described countershaft or the internal perisporium of described supplementary bearing are provided with surface epithelium.

7. rotary compressor according to claim 1, it is characterised in that described 2nd bearing is located in one of on described end plate；Or described 2nd bearing is positioned at described cylindrical shell center upper portion.

8. rotary compressor according to claim 1, it is characterised in that any one of described 1st bearing and described 2nd bearing is rolling bearing or bearing axle sleeve.

9. rotary compressor according to claim 1, it is characterised in that the support of bearing receiving described 2nd bearing is fixed on described seal casinghousing by laser weld.