CN110762010A - Compression mechanism of rotary compressor and rotary compressor - Google Patents

Abstract

The invention discloses a compression mechanism of a rotary compressor and a rotary compressor, comprising: a first cylinder, a second cylinder, a crankshaft, a first end plate, a second end plate and a partition plate, and the end surface of the intermediate shaft is provided with a first limiting part; the end face of at least one of the first eccentric part and the second eccentric part facing the intermediate shaft is provided with a second limiting part matched with the first limiting part; the partition plate has a shaft hole and the intermediate shaft is matched In the shaft hole, the outer diameter of the first rotary shaft is d0, the outer diameter of the second rotary shaft is d1, the outer diameter of the intermediate shaft is d2, the diameter of the shaft hole is d3, and the outer diameter of the first eccentric portion is D1, the outer diameter of the second eccentric portion is D2, d0≤d1<d2≤d3<D1, and d0≤d1<d2≤d3<D2. According to the compression mechanism of the rotary compressor of the present invention, the displacement of the rotary compressor can be enlarged, the compression efficiency can be improved, and the rigidity of the crankshaft can be enhanced, and the reliability and durability of torque transmission are high, and the production efficiency is high.

Description

Compression mechanism of rotary compressor and rotary compressor

technical field

The present invention relates to the technical field of compressors, and in particular, to a compression mechanism of a rotary compressor and a rotary compressor having the compression mechanism of the rotary compressor.

Background technique

Compared with the single-cylinder rotary compressor, the variable frequency double-cylinder rotary compressor can operate at less than 30Hz due to the small change in the compression torque, so it has great advantages in air conditioning comfort, food preservation and seasonal energy efficiency (APF). etc. have advantages.

In the related art twin-cylinder rotary compressor, if the inner diameter of the partition plate between the two cylinders is smaller than the outer diameter of the eccentric shaft and the outer diameter of the intermediate shaft pre-fixed on the crankshaft, the compression mechanism cannot be assembled. Therefore, the inner diameter (d3) of the separator ≧ the outer diameter (D) of the eccentric shaft.

Due to the limitation of this design condition, the inner diameter of the diaphragm increases, the eccentricity of the eccentric shaft becomes smaller, and the smaller the eccentricity of the eccentric shaft reduces the cooling capacity, so it is difficult to expand the displacement of the compressor and improve the compression efficiency. ; And, because the outer diameter (d2) of the intermediate shaft connecting the two eccentric shafts cannot be enlarged, the rigidity of the crankshaft is difficult to ensure.

For this reason, the separator is usually divided into two parts, or the intermediate shaft is divided into two sections of machining shaft, so as to satisfy the outer diameter of the rotary shaft d1 < the outer diameter of the intermediate shaft d2 ≤ the inner diameter of the separator d3 < the outer diameter of the eccentric shaft D.

However, it is difficult to maintain the plane accuracy of the partition that is divided into two parts, and the intermediate shaft is divided into two parts for processing mainly to improve the strength of the intermediate shaft (just make d1 < d2). Practical applications are very few.

SUMMARY OF THE INVENTION

The present invention aims to solve at least one of the technical problems existing in the prior art. Therefore, the present invention proposes a compression mechanism for a rotary compressor, which can expand the displacement of the rotary compressor, improve the compression efficiency, improve the rigidity of the crankshaft, and ensure the reliability of torque transmission. And durable reliability, high production efficiency.

The present invention also provides a rotary compressor having the compression mechanism of the rotary compressor.

The compression mechanism of the rotary compressor according to the embodiment of the first aspect of the present invention includes: a first cylinder and a second cylinder; a crankshaft, the crankshaft is rotatable and includes: a first rotary shaft and a second rotary shaft; an intermediate shaft, Both ends of the intermediate shaft are respectively connected with the first rotary shaft and the second rotary shaft, and the end face of the intermediate shaft is provided with a first limiting part; a first eccentric part and a second eccentric part, the The first eccentric part is sleeved on the first rotating shaft and is eccentrically arranged, the second eccentric part is sleeved on the second rotating shaft and is eccentrically arranged, the first eccentric part and the second eccentric part are At least one of the end faces facing the intermediate shaft is provided with a second limiting portion that cooperates with the first limiting portion, and one of the first limiting portion and the second limiting portion is configured to a limit protrusion and the other is configured as a limit groove; a first end plate, a second end plate and a partition plate, the first air cylinder and the second air cylinder are provided on the first end plate and the The second end plates are spaced apart by and between the baffle plates, the baffle plates have a shaft hole and the intermediate shaft is fitted in the shaft hole, the first eccentric portion is provided in the first cylinder and The second eccentric part is arranged in the second cylinder, wherein the outer diameter of the first rotary shaft is d0, the outer diameter of the second rotary shaft is d1, and the outer diameter of the intermediate shaft is d2 , the diameter of the shaft hole is d3, the outer diameter of the first eccentric part is D1, the outer diameter of the second eccentric part is D2, d0≤d1<d2≤d3<D1, d0≤d1<d2≤ d3<D2.

According to the compression mechanism of the rotary compressor according to the embodiment of the present invention, the displacement of the rotary compressor can be enlarged, the compression efficiency can be improved, and the rigidity of the crankshaft can be improved, and the reliability and durability of torque transmission are high, and the production efficiency is high.

In addition, the compression mechanism of the rotary compressor according to the embodiment of the present invention also has the following additional technical features:

According to some embodiments of the present invention, the first rotary shaft, the second rotary shaft and the intermediate shaft are arranged coaxially, and the first limiting portion is eccentrically arranged with respect to the intermediate shaft.

Further, the first limiting portion is disposed around the central axis of the intermediate shaft and extends along the circumferential direction of the intermediate shaft.

Advantageously, in the projection plane perpendicular to the central axis of the intermediate shaft, the projected outer contour of the first limiting portion and the projected outer contour of the first rotation axis or the second rotation axis Lines form incisions.

Optionally, the first limiting portion is located on the side of the intermediate shaft facing the first eccentric portion, and the second limiting portion is provided on the end face of the first eccentric portion facing the intermediate shaft part, the second eccentric part is integrally formed on the side of the intermediate shaft facing away from the first eccentric part.

In some specific embodiments of the present invention, there are two intermediate shafts and two partition plates, the two intermediate shafts are matched with the two partition plates in a one-to-one correspondence, and the crankshaft further includes: an eccentric The eccentric shaft connects the two intermediate shafts, and the central axis is deviated from the central axis of the intermediate shaft. The first limiting portion is located on the side of the intermediate shaft facing away from the eccentric shaft. The compression mechanism further includes: a third cylinder, which has a third compression chamber and a third piston that can roll along the inner peripheral wall of the third cylinder, and the eccentric shaft is arranged in the third compression chamber. inside the cavity and the third piston is sleeved on the outer peripheral wall of the eccentric shaft.

Advantageously, in a projection plane perpendicular to the central axis of the intermediate shaft, the center of the projection of the first eccentric portion, the center of the projection of the second eccentric portion and the center of the projection of the eccentric shaft are along the The circumferential direction of the intermediate shaft is evenly distributed.

In some embodiments of the present invention, the axial width of the at least one of the first eccentric portion and the second eccentric portion is W1, and the axial widths of the second limiting portion are W1, W2 =25%-30%W1.

In some specific embodiments of the present invention, the first limiting portion is configured as the limiting protrusion and the second limiting portion is configured as the limiting groove, and the end surface of the intermediate shaft An installation groove extending along its axial direction is provided, and both ends of the limiting protrusion are fitted in the limiting groove and the installation groove respectively.

According to some embodiments of the present invention, an end face of the at least one of the first eccentric portion and the second eccentric portion facing away from the intermediate shaft is provided with a C-shaped stop ring, the C-shaped stop ring The ring is sleeved between the first rotating shaft and the first eccentric part or the second rotating shaft and the second eccentric part.

According to some embodiments of the present invention, the first end plate is provided with a first bearing fitted with the first rotary shaft and the second end plate is provided with a second bearing fitted with the second rotary shaft.

According to some embodiments of the present invention, an intermediate bearing is provided between the intermediate shaft and the partition plate, and a shaft end bearing is provided at an end of the second rotating shaft away from the second end plate.

According to some embodiments of the present invention, the first rotary shaft, the second rotary shaft and the intermediate shaft are all steel parts, and the at least one of the first eccentric part and the second eccentric part For powder alloy parts.

The rotary compressor according to the embodiment of the second aspect of the present invention includes: a casing, the casing is provided with a discharge port; the compression mechanism of the rotary compressor according to the embodiment of the first aspect of the present invention, the compression mechanism The mechanism is arranged in the casing; the driving mechanism is arranged in the casing and is connected with the crankshaft in a transmission manner.

According to the rotary compressor of the embodiment of the present invention, using the above-mentioned compression mechanism of the rotary compressor, the displacement is large, the compression efficiency is high, the rigidity of the crankshaft is good, the reliability of torque transmission and durability are high, and the production efficient.

Additional aspects and advantages of the present invention will be set forth, in part, from the following description, and in part will be apparent from the following description, or may be learned by practice of the invention.

Description of drawings

1 is a longitudinal cross-sectional view of a rotary compressor according to an embodiment of the present invention;

2 is a sectional view, a front view, a left side view and a right side view of a separating eccentric shaft of a rotary compressor according to an embodiment of the present invention;

3 is a left side view and a front view of the partial structure of the crankshaft of the rotary compressor according to the embodiment of the present invention;

4 is a left view and a front view of a partial structure of a compression mechanism of a rotary compressor according to an embodiment of the present invention;

5 is a cross-sectional view of a compression mechanism of a rotary compressor according to an embodiment of the present invention;

6 is a cross-sectional view of a compression mechanism of a rotary compressor according to an embodiment of the present invention;

7 is a partial structural schematic diagram of a crankshaft of a rotary compressor according to a first alternative embodiment of the present invention;

8 is a partial cross-sectional view of a compression mechanism of a rotary compressor according to a first alternative embodiment of the present invention;

9 is a cross-sectional view of a compression mechanism of a rotary compressor according to a first alternative embodiment of the present invention;

10 is a left side view and a front view of a partial structure of a crankshaft of a rotary compressor according to a second alternative embodiment of the present invention;

11 is a cross-sectional view of a compression mechanism of a rotary compressor according to a second alternative embodiment of the present invention;

12 is a longitudinal cross-sectional view of a rotary compressor according to a third alternative embodiment of the present invention;

13 is a partial structural schematic diagram of a crankshaft of a rotary compressor according to a third alternative embodiment of the present invention;

14 is a partial cross-sectional view of a compression mechanism of a rotary compressor according to a fourth alternative embodiment of the present invention;

15 is a partial cross-sectional view of a compression mechanism of a rotary compressor according to a fifth alternative embodiment of the present invention.

Reference number:

The first two-cylinder rotary compressor 102, the second two-cylinder rotary compressor 103,

Housing 2, electric motor 3, stator 3a, rotor 3b,

The first compression mechanism part 4A, the second compression mechanism part 4B, the third compression mechanism part 4C,

The first crankshaft 10A, the second crankshaft 10B, the third crankshaft 10C, the first rotary shaft 11, the second rotary shaft 12, the intermediate shaft 13, the circular protrusion 13a,

The first end plate 5, the first bearing 5a, the second end plate 6, the second bearing 6a, the partition plate 7, the shaft hole 7a,

The first cylinder 8, the first compression chamber 8a, the second cylinder 9, the second compression chamber 9a, the third cylinder 14,

Separation eccentric shaft 15, shaft hole 15a, circular groove 15b, thrust protrusion 15c, ejector pin 15d,

Upper shaft 16 , fixed eccentric shaft 20 , rolling piston 21 , intermediate bearing 22 , shaft end bearing 23 , C-shaped snap ring 25 , oiling vane cylinder 27 , suction pipe 30 , exhaust pipe 31 , bearing cylinder 32 .

Detailed ways

The following describes in detail the embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary, only used to explain the present invention, and should not be construed as a limitation of the present invention.

The compression mechanism of the rotary compressor according to the embodiment of the first aspect of the present invention will be described below with reference to the accompanying drawings.

Alternatively, the rotary compressor may be a vertical compressor. In the following description of the present application, the rotary compressor is taken as an example of a vertical compressor for illustration. Of course, those skilled in the art can understand that the rotary compressor may also be a horizontal compressor (not shown in the figure). Here, it should be noted that "vertical compressor" can be understood as a compressor in which the central axis of the cylinder of the compression mechanism of the rotary compressor is perpendicular to the installation surface of the rotary compressor. For example, as shown in Figure 1, the cylinder The central axis of , extends in the vertical direction. Correspondingly, a "horizontal compressor" can be understood as a compressor in which the central axis of the cylinder is parallel to the mounting surface of the rotary compressor.

As shown in FIG. 1-FIG. 15, the compression mechanism of the rotary compressor according to the embodiment of the present invention includes: a first cylinder 8, a second cylinder 9, a crankshaft, a first end plate 5, a second end plate 6 and a spacer plate 7.

Specifically, the first cylinder 8 and the second cylinder 9 are provided between the first end plate 5 and the second end plate 6 and are spaced apart by the partition plate 7, ie, the first end plate 5, the first cylinder 8, the partition The plate 7, the second cylinder 9 and the second end plate 6 are arranged in order in the up-down direction. The first cylinder 8 has a first compression chamber 8 a and is provided with a first piston that can roll along the inner peripheral wall of the first cylinder 8 . A second piston with a rollable peripheral wall.

The crankshaft is rotatable, and the crankshaft includes a first rotary shaft 11 , a second rotary shaft 12 , an intermediate shaft 13 , a first eccentric portion and a second eccentric portion. Both ends of the intermediate shaft 13 are respectively connected with the first rotary shaft 11 and the second rotary shaft 12 , and the intermediate shaft 13 is provided with a first limiting portion, and the first limiting portion is configured to be along the axial direction of the intermediate shaft 13 ( For example, in the up and down direction), the limit protrusion protrudes from its end face. The first eccentric part is sleeved on the first rotating shaft 11, and the first eccentric part is eccentrically disposed, that is, the central axis of the first eccentric part deviates from the central axis of the first rotating shaft 11; the second eccentric part is sleeved on the second rotating shaft 11. The second eccentric part is eccentrically arranged, that is, the central axis of the second eccentric part deviates from the central axis of the second rotary shaft 12 .

The end face of at least one of the first eccentric portion and the second eccentric portion facing the intermediate shaft 13 is provided with a second limiting portion, the first limiting portion is fitted in the second limiting portion, and the second limiting portion is configured to limit. Bit groove. Here, "at least one" means that the upper end surface of the first eccentric portion is provided with a second limiting portion, and the first limiting portion protrudes downward from the lower end surface of the intermediate shaft 13, so that the first eccentric portion and the first The rotating shaft 11 can be separated; or, the lower end surface of the second eccentric portion is provided with a second limiting portion, and the first limiting portion extends upward from the upper end surface of the intermediate shaft 13, so that the second eccentric portion and the second rotating shaft 12 can be separated Alternatively, the upper end surface of the first eccentric portion is provided with a second limiting portion, the first limiting portion extends downward from the lower end surface of the intermediate shaft 13, and the lower end surface of the second eccentric portion is provided with a second limiting portion The upper end surface of the intermediate shaft 13 protrudes upwardly from the first limiting portion and the first eccentric portion, so that the first eccentric portion is separable from the first rotary shaft 11 and the second eccentric portion is separable from the second rotary shaft 12 .

It can be understood that the first limiting portion can also be configured as a limiting groove and the second limiting portion can be configured as a limiting protrusion, as long as it is ensured that the first limiting portion and the second limiting portion can be matched together. Yes, the present invention does not make any special limitation on this. It should be noted that the embodiments given in this application only take the first limiting portion as a limiting protrusion and the second limiting portion as a limiting groove for relevant description, and should not be construed as a limitation of the present invention.

The partition plate 7 has a shaft hole 7a and the intermediate shaft 13 is fitted in the shaft hole 7a. The first eccentric part is arranged in the first compression chamber 8a and the first piston is sleeved on the outer peripheral wall of the first eccentric part, the second eccentric part is arranged in the second compression chamber 9a and the second piston is sleeved in the second eccentric part the peripheral wall.

The outer diameter of the first rotary shaft 11 is d0, the outer diameter of the second rotary shaft 12 is d1, the outer diameter of the intermediate shaft 13 is d2, the diameter of the shaft hole 7a is d3, and the outer diameter of the first eccentric portion is D1 , the outer diameter of the second eccentric portion is D2, d0≤d1<d2≤d3<D1, and d0≤d1<d2≤d3<D2.

According to the compression mechanism of the rotary compressor according to the embodiment of the present invention, the torque connection is realized by the cooperation of the first limit part protruding from the axial direction of the intermediate shaft 13 and the second limit part provided on the end face, so that the crankshaft is After the torque is transmitted to the intermediate shaft 13, it becomes the torque of the intermediate shaft 13, and then is transmitted to the first eccentric part and the second eccentric part through the intermediate shaft 13, and becomes the torque of the first eccentric part and the second eccentric part, and the torque transmission is optimized. High reliability and durability reliability; since d1<d2≤d3<D1 and d1<d2≤d3<D2 are satisfied, the refrigeration capacity of the rotary compressor and the displacement of each cylinder can be expanded, thereby realizing the displacement of the rotary compressor. expansion, compression efficiency, and crankshaft rigidity.

At the same time, since the above-mentioned moment connection structures are formed by concave-convex matching structures, these structures can be processed by an automatic lathe, with high processing precision and easy assembly, thereby improving production efficiency. In addition, since the conventional integrally formed crankshaft is divided into multiple parts, it is easier to introduce steel pipes, powder alloys and forging processes into the crankshaft.

According to some embodiments of the present invention, as shown in FIGS. 1-15 , the first rotary shaft 11 , the second rotary shaft 12 and the intermediate shaft 13 are coaxially arranged, that is, the central axis of the first rotary shaft 11 , the second rotary shaft 11 The central axis of the rotating shaft 12 is coincident with the central axis of the intermediate shaft 13, so as to facilitate the manufacture and molding of the crankshaft. The first limiting portion is eccentrically arranged relative to the intermediate shaft 13, that is, the center line of the first limiting portion is deviated from the central axis of the intermediate shaft 13, so as to ensure that the first eccentric portion or the second limiting portion cooperates with the first limiting portion. The eccentric setting of the second eccentric part.

Further, as shown in FIGS. 1-13 and 15 , the first limiting portion is arranged around the central axis of the intermediate shaft 13 , and the first limiting portion extends along the circumferential direction of the intermediate shaft 13 , thereby improving the torque transmission efficiency. reliability and durability. In order to simplify the structure of the first limiting portion and the second limiting portion and facilitate manufacturing and molding, the first limiting portion and the second limiting portion can be designed to be circular, that is, the first limiting portion is configured to be circular At least one of the protrusion 13a, the first eccentric portion and the second eccentric portion is the separating eccentric shaft 15, and the second limiting portion on the separating eccentric shaft 15 is configured as a circular groove 15b.

Advantageously, as shown in FIG. 2 and FIG. 4 , in the projection plane perpendicular to the central axis of the intermediate shaft 13 , the projected outer contour of the first limiting portion is the same as that of the first rotary shaft 11 or the second rotary shaft 12 . The projected outer contour line forms an inscribed incision, which facilitates machining. For example, the separating eccentric shaft 15 has a shaft hole 15a, the central axis of the circular groove 15b is deviated from the central axis of the shaft hole 15a, and in the projection plane perpendicular to the central axis of the shaft hole 15a, the projected outline of the shaft hole 15a is the same as the circle The projected contour line of the groove 15b forms an inscribed.

Optionally, as shown in FIGS. 7 and 8 , the first limiting portion is located on the side of the intermediate shaft 13 facing the first eccentric portion (ie, the lower side), and the end face of the first eccentric portion facing the intermediate shaft 13 (ie, the lower side). The upper end surface) is provided with a second limiting portion, and the second eccentric portion is integrally formed on the side (ie, the upper side) of the intermediate shaft 13 that faces away from the first eccentric portion. For example, the first eccentric portion is configured to separate the eccentric shaft 15, the second eccentric portion is configured to fix the eccentric shaft 20, the first rotary shaft 11, the second rotary shaft 12, the intermediate shaft 13, the first stopper and the fixed eccentric The shaft 20 is integrally formed. When assembling, the first rotating shaft 11 is first extended into the first cylinder 8, and then the separating eccentric shaft 15 is assembled on the first rotating shaft 11 and the first limiting portion.

In some specific embodiments of the present invention, as shown in FIGS. 10 and 11 , there are two intermediate shafts 13 and two partitions 7 , and the two intermediate shafts 13 are matched with the two partitions 7 in one-to-one correspondence. The crankshaft also includes an eccentric shaft. The eccentric shaft connects the two intermediate shafts 13 , and the central axis of the eccentric shaft deviates from the central axis of the intermediate shaft 13 . side. The compression mechanism further includes a third cylinder 14, the third cylinder 14 has a third compression chamber and is provided with a third piston that can roll along the inner peripheral wall of the third cylinder 14, the eccentric shaft is arranged in the third compression chamber and the third piston is It is sleeved on the outer peripheral wall of the eccentric shaft. The first piston, the second piston and the third piston are all rolling pistons 21 . For example, the eccentric shaft is the fixed eccentric shaft 20 , and the first first limiting portion and the second first limiting portion are both separated from the eccentric shaft 15 and located on the upper and lower sides of the fixed eccentric shaft 20 respectively.

Advantageously, as shown in FIG. 11 , in the projection plane perpendicular to the central axis of the intermediate shaft 13, the center of the projection of the first eccentric portion, the center of the projection of the second eccentric portion and the center of the projection of the eccentric shaft are along the intermediate axis. The circumferential direction of 13 is uniformly distributed, that is, the angle between the projection of the first eccentric portion, the projection of the second eccentric portion and the projection of the eccentric axis is 120°, with an average compression moment.

In some embodiments of the present invention, as shown in FIG. 2 , the axial width of the at least one of the first eccentric portion and the second eccentric portion (ie, the separation eccentric shaft 15 ) is W1, and the width of the second limiting portion is W1. The axial width is W1, and W2=25%-30% of W1, so that the contact area can be controlled within a reasonable range and the friction can be reduced.

In some specific embodiments of the present invention, as shown in FIG. 14 , the end surface of the intermediate shaft 13 is provided with a mounting groove extending along its axial direction, and the two ends of the first limiting portion are respectively matched with the second limiting portion and the mounting groove. In this way, the connection of the separation eccentric shaft 15 can be realized in a simpler form, which is suitable for small double-cylinder rotary compressors with low operating pressure and small crankshaft torque. For example, the first limiting portion is an ejector pin 15d, and the ejector pin 15d assembles the intermediate shaft 13 and the separating eccentric shaft 15 together.

According to some embodiments of the present invention, as shown in FIG. 15 , the end face of the at least one of the first eccentric part and the second eccentric part facing away from the intermediate shaft 13 is provided with a C-shaped stop ring 25 , and the C-shaped stop The ring 25 is sleeved between the first rotating shaft 11 and the first eccentric part or the second rotating shaft 12 and the second eccentric part, so as to fix the separating eccentric shaft 15 . Therefore, through the fixed connection of the C-shaped retaining ring 25 , the intermediate shaft 13 and the separating eccentric shaft 15 , the subsequent alignment assembly will be easier.

For example, the lower end surface of the first eccentric portion has a thrust projection 15c as a thrust surface sliding on the end surface of the first end plate 5, and a C-shaped stop ring 25 is provided in the thrust projection 15c. In addition, in the present embodiment, the outer diameter d0 of the first rotary shaft 11 < the outer diameter d1 of the second rotary shaft 12 .

According to some embodiments of the present invention, as shown in FIGS. 1 and 5 , the first end plate 5 is provided with a first bearing 5 a that cooperates with the first rotary shaft 11 and the second end plate 6 is provided with a second rotary shaft 12 . The second bearing 6a is fitted to support the load of the crankshaft.

According to some embodiments of the present invention, as shown in FIG. 12 , an intermediate bearing 22 is provided between the intermediate shaft 13 and the partition plate 7 , and an end (ie, the upper end) of the second rotary shaft 12 away from the second end plate 6 is provided with a shaft The end bearing 23 can simplify the structure of the first end plate 5 and the second end plate 6 .

According to some embodiments of the present invention, the first rotary shaft 11 , the second rotary shaft 12 and the intermediate shaft 13 are all steel pieces, and the at least one of the first eccentric part and the second eccentric part (ie, the separation eccentric shaft 15 ) Suitable for powder molding, for example, the separating eccentric shaft 15 is a powder alloy piece.

The rotary compressor according to the embodiment of the second aspect of the present invention includes: a casing 2, a compression mechanism and a driving mechanism of the rotary compressor according to the embodiment of the first aspect of the present invention.

Specifically, the housing 2 is provided with a discharge port, the compression mechanism and the driving mechanism are both provided in the housing 2, and the driving mechanism is connected to the crankshaft in a transmission. For example, the drive mechanism is the electric motor 3 .

According to the rotary compressor of the embodiment of the present invention, using the above-mentioned compression mechanism of the rotary compressor, the displacement is large, the compression efficiency is high, the rigidity of the crankshaft is good, the reliability of torque transmission and durability are high, and the production efficient.

Rotary compressors according to various embodiments of the present invention will be described below with reference to the accompanying drawings.

Embodiment 1

FIG. 1 shows a longitudinal cross-sectional view when the rotary compressor is the first two-cylinder rotary compressor 102 , the compression mechanism is the compression mechanism portion 4A, and the crankshaft is the crankshaft 10A.

Specifically, the electric motor 3 and the compression mechanism portion 4A are fixed to the inner circumference of the airtight case 2 . The electric motor 3 is composed of a stator 3a fixed to the airtight case 2 and a rotor 3b fixed to the crankshaft 10A, and drives the compression mechanism part 4A to rotate.

The compression mechanism portion 4A is composed of the following components: a second cylinder 9 fixed to the first cylinder 8 and the inner circumference of the hermetic case 2, a partition 7 between the two cylinders, a first compression chamber 8a that seals the cylinders, and The first end plate 5 and the second end plate 6 at the opening end of the second compression chamber 9a, the first rotary shaft 11 and the second rotary shaft 12 slidably fitted with the bearings on the center of these parts, fixed to the first rotary shaft 11 and the two separation eccentric shafts 15 on the second rotary shaft 12 , the rolling piston 21 that is slidably fitted on the outer periphery of these separation eccentric shafts 15 and rotates eccentrically, and the like. In addition, the shaft end of the first rotary shaft 11 is provided with an oiling vane tube 27 .

In the above-described structure of the compression mechanism portion 4A, before the first end plate 5 and the second end plate 6 are fixed to the first cylinder 8 and the second cylinder 9, the two separation eccentric shafts 15 are respectively removed from the first The shaft ends of the rotating shaft 11 and the second rotating shaft 12 are inserted, and the circular grooves 15 b on the end surface of the separating eccentric shaft 15 are inserted into the circular protrusions 13 a provided at both ends of the intermediate shaft 13 .

Since the circular groove 15b and the circular protrusion 13a are eccentric by the eccentric amount e1 with respect to the rotation center line 10a of the crankshaft 10A, the two separating eccentric shafts 15 are eccentrically rotated by the eccentric amount e2 according to the torque of the crankshaft 10A. Likewise, the two rolling pistons 21 are opposed to each other at an angle of 180° and rotate eccentrically in the first compression chamber 8a and the second compression chamber 9a.

The low-pressure gas flowing from the two suction pipes 30 connecting the first cylinder 8 and the second cylinder 9 respectively flows into the first compression chamber 8a and the second compression chamber 9a, and the compressed high-pressure gas passes through the first end plate 5 and the second compression chamber 9a. The muffler and the electric motor 3 on the end plate 6 are discharged from the exhaust pipe 31 . After that, it is cycled once in the refrigeration cycle device and returned to the two suction pipes 30 .

As shown in FIG. 2 , the separation eccentric shaft 15 is characterized in that a circular groove 15b is provided on the end surface thereof, and a shaft hole 15a is opened in the circular groove 15b. The circular groove 15b is eccentric to the shaft hole 15a by an eccentric amount e1, and the outer diameter D of the separating eccentric shaft 15 is eccentric to the center axis of the shaft hole 15a by an eccentric amount e2. That is, e2 is also the eccentric amount of the rolling piston 21 revolving in the compression chamber. In addition, the inner diameter circle of the shaft hole 15a is not outside the circle of the circular groove 15b. The inner diameter end of the shaft hole 15 shown in FIG. 2 is the same as the circular diameter of the eccentric circular groove 15b.

The amount of eccentricity e1 plays an important role in the torque of the crankshaft 10A to revolve the separation eccentric shaft 15 via the circular projection 13a of the intermediate shaft 13. The outer diameter D of the separation eccentric shaft 15 is the cylindrical surface on which the inner diameter of the rolling piston 21 slides, and the thrust projection 15c It is a thrust surface sliding on the plane of the first end plate 5 .

Since the shaft hole 15a does not slide on the outer diameters of the first rotary shaft 11 and the second rotary shaft 12, the clearance between them should be reduced as much as possible, and the clearance should be less than 1/2000 of the outer diameter of the corresponding shaft. For example, the outer diameter of the first rotary shaft 11 is 16 mm, the gap between the shaft hole 15 a and the first rotary shaft 11 is 8 μm or less, and the gap when the separation eccentric shaft 15 is shrink-fitted to the first rotary shaft 11 To be smaller. Among them, the depth of the circular groove 15b is W2, which accounts for 25 to 30% of the width W1 of the separation eccentric shaft 15. As shown in FIG.

In addition, the shape of the separation eccentric shaft 15 is cylindrical, and can be machined by an automatic lathe. After that, the outer diameter of the shaft hole 15a and the separation eccentric shaft 15 needs to be ground. The separation eccentric shaft 15 can use the same material as the crankshaft - spherical black lead cast iron (FCD500, etc.), preferably, because the shape of the separation eccentric shaft 15 is suitable for powder molding, powder alloys can also be used.

As shown in FIG. 4 , the first compression chamber 8a of the first cylinder 8 and the second compression chamber 9a of the second cylinder 9 are aligned, and the two cylinders are fixed to the diaphragm through the pins 24 on the diaphragm 7 7 on the upper and lower sides. Next, the shaft end of the first rotary shaft 11 is inserted into the rotary shaft hole 7a. Then, the separation eccentric shaft 15 is inserted from the shaft ends of the second rotary shaft 12 and the first rotary shaft 11, respectively, and the circular groove 15b of the separation eccentric shaft 15 is inserted into the circular protrusion 13a, and the two opposite separation eccentric shafts 15 assembly is complete. The gap between the intermediate shaft 13 and the shaft hole 7a is about 0.2 mm.

After the above-mentioned structure of the compression mechanism part 4A is assembled, the two rolling pistons 21 are respectively inserted into the two separating eccentric shafts 15 and the sliding vanes (not shown in the figure) are assembled. Next, the second end plate 6 is fixed to the second cylinder 9 with screws, and then the alignment of the second compression chamber 9a and the second rotary shaft 12 is performed. Next, the first end plate 5 is inserted into the first rotary shaft 11 and fixed to the first cylinder 8 with screws, and then the alignment of the first compression chamber 8a and the first rotary shaft 11 is performed. So far, the compression mechanism portion 4A shown in FIG. 5 is completed by the above assembly.

It should be noted that the torque of the crankshaft 10A slidably fitted with the first bearing 5 a and the second bearing 6 a provided on the first end plate 5 and the second end plate 6 , respectively, passes through the two circular protrusions on the intermediate shaft 13 . The eccentricity e1 of 13a is transmitted to the two separating eccentric shafts 15, and the two separating eccentric shafts 15 and the two rolling pistons 21 rotate eccentrically.

Since the two separation eccentric shafts 15 are respectively fixed on the first rotary shaft 11 and the second rotary shaft 12, the eccentricity e2 and the rotation accuracy of the outer diameter of the separation eccentric shaft 15 are based on the separation eccentric shaft 15 shown in FIG. 2 . It is determined by the shape accuracy of the eccentric shaft 15 and the fixed clearance between the first rotary shaft 11 and the second rotary shaft 12, and has nothing to do with the accuracy of the eccentric amount e1 of the torque transmission means. However, the matching gap between the circular protrusion 13a and the circular groove 15b has an influence on the relative angle (180°) of the two separating eccentric shafts 15 .

Next, the vertical movement of the crankshaft 10A caused by the load on the crankshaft 10A and the magnetic force fluctuation of the rotor 3b will be described.

As shown in FIG. 5 , the load in the downward direction abuts against the first end plate 5 through the thrust projections 15 c of the separation eccentric shaft 15 , and the load in the upper direction passes through the thrust projections 15 c of the separation eccentric shaft 15 through the second end plate 6 . the limiter, thereby restricting the up and down movement of the crankshaft 10A.

Next, as shown in FIG. 6 , the outer diameters of the first rotary shaft 11 and the second rotary shaft 12 are both d1, the outer diameter of the intermediate shaft 13 is d2, the diameter of the rotary shaft hole 7a is d3, and the outer diameter of the separation eccentric shaft 15 is d3. When the diameter is D, d1<d2≦d3<D holds, and the separator 7 can be reduced in diameter and the outer diameter of the intermediate shaft 13 can be enlarged by assembling the separate eccentric shaft 15 .

Since d3<D, the minimum gap m between the inner diameter of the shaft hole 7a and the outer diameter of the rolling piston 21 is increased, and the high-pressure side gas of the partition plate 7 does not leak to the low pressure of the first compression chamber 8a and the second compression chamber 9a Therefore, the re-expansion loss of the high-pressure gas can be improved. At the same time, since d1<d2, the rigidity of the intermediate shaft 13 is improved, and the deformation of the intermediate shaft 13 caused by the compressive loads generated interactively by the rolling pistons 21 in the first compression chamber 8a and the second compression chamber 9a is greatly improved. .

In addition, d3<D, the eccentric amount e2 of the separation eccentric shaft 15 can be increased, and the displacement can be increased without enlarging the inner diameter of the compressor. That is, it is not only effective in securing a large cooling capacity in the compression chamber of a small cylinder, but also effective in improving the compression efficiency, and is also advantageous in increasing the size of the two-cylinder rotary compressor.

As shown in FIG. 3 , the crankshaft 10A is a rod-shaped shaft, and the material selection and manufacturing method of the crankshaft 10A are wide. For example, the crankshaft 10A may be cast iron, or the crankshaft 10A may be an SCM steel bar (ie, chrome-molybdenum steel) that has wear resistance and high rigidity, and can be treated for wear resistance, or the crankshaft 10A may be forged intermediate Shaft 13 Shaping Method. Thereby, the durability reliability of the crankshaft 10A and the improvement of the production efficiency can be simultaneously achieved.

Embodiment 2

The present embodiment relates to a twin-cylinder rotary compressor in which the separation eccentric shaft 15 and the fixed eccentric shaft 20 are used in combination.

As shown in FIG. 7 , the second rotating shaft 12 of the crankshaft 10B has a fixed eccentric shaft 20 , the first rotating shaft 11 is assembled with a separating eccentric shaft 15 , and the intermediate shaft 13 is equipped with a circle only on the side facing the first rotating shaft 11 . shaped protrusion 13a.

As shown in FIG. 8 , after the diaphragm 7, the first cylinder 8 and the second cylinder 9 are aligned and assembled, the first rotating shaft 11 of the crankshaft 10B is inserted into the rotating shaft hole 7a, and the intermediate shaft 13a is stationary in the rotating shaft hole 7a at this time. Then, the separating eccentric shaft 15 is inserted from the shaft end of the first rotary shaft 11, and the circular groove 15b is embedded in the circular protrusion 13a. After that, complete the partial assembly.

Then, in the same procedure as in the first embodiment, the assembly of the compression mechanism portion 4B shown in FIG. 9 is completed. In the second embodiment, even if one of the first eccentric portion and the second eccentric portion is used as the fixed eccentric shaft 20, the compression mechanism portion 4B can be assembled in the same manner as in the first embodiment. In addition, d1<d2≦d3<D also holds.

Embodiment 3

As shown in FIG. 10 , there is a fixed eccentric shaft 20 between the first rotary shaft 11 and the second rotary shaft 12 of the crankshaft 10C of the three-cylinder rotary compressor, and the two sides of the fixed eccentric shaft 20 are connected with an intermediate shaft 13 and a circular shaped protrusion 13a. In order to average the compression moment, in the projection plane perpendicular to the crankshaft 10C, the angle between the two separated eccentric shafts 15 and the fixed eccentric shaft 20 of the three-cylinder rotary compressor is 120°. are the vertices of an equilateral triangle and rotate in one direction respectively.

Thus, the assembly sequence of the two separating eccentric shafts 15 and the two partition plates 7 of the crankshaft 10C is as follows:

First, the rolling piston 21 is inserted into the fixed eccentric shaft 20 , and the outer circumference of the rolling piston 21 is press-fitted into the second compression chamber of the third cylinder 14 . Next, the two partitions 7 are fixed at predetermined positions on the two side planes of the third cylinder 14 .

Then, the separation eccentric shafts 15 are inserted into the shaft ends of the second rotary shaft 12 and the first rotary shaft 11, respectively, and the circular grooves 15b are fitted into the circular protrusions 13a. Next, the first cylinder 8 and the second cylinder 9 are respectively fixed to the predetermined positions of the assembled two partition plates 7 and the alignment with the third cylinder 14 is performed. Next, after inserting the rolling piston 21 on the outer periphery of the assembled two separating eccentric shafts 15, the first end plate 5 and the second end plate 6 are respectively fixed to the first cylinder 8 and the second cylinder 9 with screws. After that, alignment of the first end plate 5 , the second end plate 6 , the first rotary shaft 11 and the second rotary shaft 12 is performed.

FIG. 11 shows a longitudinal sectional view of the assembled compression mechanism portion 4C. Among them, the exhaust holes of the first cylinder 8 and the second cylinder 9 are respectively arranged on the first end plate 5 and the second end plate 6, and the exhaust holes of the third cylinder 14 are installed in any one of the two partition plates 7. on the muffler.

Since the crankshaft 10C in FIG. 10 is a fixed eccentric shaft 20 connecting the two intermediate shafts 13, the rigidity of the crankshaft is greatly improved. In addition, also in Embodiment 3, d1<d2≦d3<D is satisfied.

Embodiment 4

The second two-cylinder rotary compressor 103 shown in FIG. 12 applies the feature of the outer diameter d2 of the intermediate shaft 13 > the outer diameter d1 of the first rotary shaft 11 and the second rotary shaft 12, so that the intermediate shaft 13 of the crankshaft 10D and the outer diameter d1 of the second rotary shaft 12 are used. The intermediate bearing 22 fitted in the center of the partition plate 7 is slidably fitted, and the upper end shaft 16 of the second rotary shaft 12 is slidably fitted with the shaft end bearing 23 fitted in the center of the bearing cylinder 32, so that the use in the first embodiment and the like can be omitted. The first bearing 5a and the second bearing 6a.

Thereby, the intermediate shaft 13 supports the compressive load occurring on the two rolling pistons 21 in the first cylinder 8 and the second cylinder 9 and is in sliding fit with the intermediate bearing 22 . The upper end shaft 16 supports the vibration load of the second rotary shaft 12 including the rotor 3 b and is slidably fitted with the shaft end bearing 23 . In addition, if the intermediate bearing 22 and the shaft end bearing 23 adopt the bushing and the shaft end bearing, the reliability of the bearing will be improved and the rotational speed of the crankshaft 10D will be greatly increased.

Other structures and operations of the rotary compressor according to the embodiment of the present invention are known to those of ordinary skill in the art and will not be described in detail here.

In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "upper", "lower", "vertical", "inner", The orientation or positional relationship indicated by "outer", "axial", "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 An indication or implication that the referred device or element must have a particular orientation, be constructed and operate in a particular orientation, is not to be construed as a limitation of the invention.

In addition, the terms "first" and "second" are only used for descriptive purposes, and should not be construed as indicating or implying relative importance or implying the number of indicated technical features. Thus, a feature defined as "first" or "second" may expressly or implicitly include one or more of that feature. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

In the description of the present invention, it should be noted that the terms "installed", "connected" and "connected" should be understood in a broad sense, unless otherwise expressly specified and limited, for example, it may be a fixed connection or a detachable connection Connection, or integral connection; can be mechanical connection, can also be electrical connection; can be directly connected, can also be indirectly connected through an intermediate medium, and can also be internal communication between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood in specific situations.

In the description of this specification, references to the terms "one embodiment," "some embodiments," "specific embodiments," "examples," or "some examples", etc., mean specific features described in connection with the embodiment or example. , structure, material or feature is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

Although embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that various changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, The scope of the invention is defined by the claims and their equivalents.

Claims (14)

1. A compression mechanism of a rotary compressor, characterized in that, comprising: a first cylinder and a second cylinder; a crankshaft that is rotatable and includes: The first rotary axis and the second rotary axis; an intermediate shaft, two ends of the intermediate shaft are respectively connected with the first rotating shaft and the second rotating shaft, and the end surface of the intermediate shaft is provided with a first limiting part; a first eccentric part and a second eccentric part, the first eccentric part is sleeved on the first rotating shaft and eccentrically arranged; the second eccentric part is sleeved on the second rotating shaft and eccentrically arranged; the The end face of at least one of the first eccentric portion and the second eccentric portion facing the intermediate shaft is provided with a second limiting portion that cooperates with the first limiting portion, and the first limiting portion and the One of the second limiting portions is configured as a limiting protrusion and the other is configured as a limiting groove; a first end plate, a second end plate and a bulkhead, the first and second cylinders being disposed between and spaced apart by the bulkhead, The partition plate has a shaft hole and the intermediate shaft is fitted in the shaft hole, the first eccentric part is arranged in the first cylinder and the second eccentric part is arranged in the second cylinder, in, The outer diameter of the first rotary shaft is d0, the outer diameter of the second rotary shaft is d1, the outer diameter of the intermediate shaft is d2, the diameter of the shaft hole is d3, and the diameter of the first eccentric portion is d3. The outer diameter is D1, the outer diameter of the second eccentric portion is D2, d0≤d1<d2≤d3<D1, and d0≤d1<d2≤d3<D2. 2 . The compression mechanism of a rotary compressor according to claim 1 , wherein the first rotary shaft, the second rotary shaft and the intermediate shaft are coaxially arranged, and the first limiting portion It is eccentrically arranged with respect to the intermediate shaft. 3 . The compression mechanism of the rotary compressor according to claim 2 , wherein the first limiting portion is disposed around the central axis of the intermediate shaft and extends along the circumferential direction of the intermediate shaft. 4 . 4 . The compression mechanism of the rotary compressor according to claim 3 , wherein, in a projection plane perpendicular to the central axis of the intermediate shaft, the projected outer contour of the first limiting portion is the same as the projection. 5 . The outer contour of the projection of the first rotational axis or the second rotational axis forms an inscriber. 5 . The compression mechanism of a rotary compressor according to claim 3 , wherein the first limiting portion is located on a side of the intermediate shaft facing the first eccentric portion, and the first eccentric portion is located at the side of the intermediate shaft. 6 . The end face of the intermediate shaft facing the intermediate shaft is provided with the second limiting part, and the second eccentric part is integrally formed on the side of the intermediate shaft facing away from the first eccentric part. 6 . The compression mechanism of the rotary compressor according to claim 3 , wherein the intermediate shafts and the partition plates are two, and the two intermediate shafts and the two partition plates are one by one. 7 . Correspondingly, the crankshaft further includes: an eccentric shaft, the eccentric shaft connects the two intermediate shafts and the central axis is deviated from the central axis of the intermediate shaft, the first limiting part is located on the side of the intermediate shaft facing away from the eccentric shaft, so The compression mechanism also includes: A third cylinder, the third cylinder has a third compression chamber and is provided with a third piston that can roll along the inner peripheral wall of the third cylinder, the eccentric shaft is provided in the third compression chamber and the The third piston is sleeved on the outer peripheral wall of the eccentric shaft. 7 . The compression mechanism of the rotary compressor according to claim 6 , wherein in a projection plane perpendicular to the central axis of the intermediate shaft, the center of the projection of the first eccentric portion, the first The projection centers of the two eccentric parts and the projection center of the eccentric shaft are evenly distributed along the circumferential direction of the intermediate shaft. 8 . The compression mechanism of the rotary compressor according to claim 3 , wherein the axial width of the at least one of the first eccentric portion and the second eccentric portion is W1 , and the first eccentric portion and the second eccentric portion have an axial width W1 . The axial width of the two limit parts is W1, W2=25%-30% of W1. 9 . The compression mechanism of the rotary compressor according to claim 2 , wherein the first limiting portion is configured as the limiting protrusion and the second limiting portion is configured as the limiting protrusion. 10 . In the limiting groove, the end surface of the intermediate shaft is provided with an installation groove extending along the axial direction thereof, and the two ends of the limiting protrusion are respectively fitted in the limiting groove and the mounting groove. 10. The compression mechanism of a rotary compressor according to any one of claims 1-9, wherein the at least one of the first eccentric portion and the second eccentric portion faces away from all The end surface of the intermediate shaft is provided with a C-shaped retaining ring, and the C-shaped retaining ring is sleeved on the first rotary shaft and the first eccentric part or the second rotary shaft and the second eccentric part between. 11. The compression mechanism of a rotary compressor according to any one of claims 1-9, wherein the first end plate is provided with a first bearing matched with the first rotary shaft and the The second end plate is provided with a second bearing matched with the second rotary shaft. 12. The compression mechanism of a rotary compressor according to any one of claims 1 to 9, wherein an intermediate bearing is provided between the intermediate shaft and the partition plate, and the second rotating shaft has an intermediate bearing. An end bearing away from the second end plate is provided with a shaft end bearing. 13. The compression mechanism of a rotary compressor according to any one of claims 1-9, wherein the first rotary shaft, the second rotary shaft and the intermediate shaft are all steel parts, The at least one of the first eccentric portion and the second eccentric portion is a powder alloy piece. 14. A rotary compressor, characterized in that, comprising: a casing, the casing is provided with a discharge port; The compression mechanism of a rotary compressor according to any one of claims 1-13, wherein the compression mechanism is provided in the casing; A driving mechanism, the driving mechanism is arranged in the casing and is in driving connection with the crankshaft.

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