CN110762010A

CN110762010A - Compression mechanism of rotary compressor and rotary compressor

Info

Publication number: CN110762010A
Application number: CN201810828498.9A
Authority: CN
Inventors: 小津政雄; 宋鹏杰; 王玲
Original assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2018-07-25
Filing date: 2018-07-25
Publication date: 2020-02-07

Abstract

The invention discloses a compression mechanism of a rotary compressor and the rotary compressor, comprising: the end face 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, which faces the intermediate shaft, is provided with a second limiting part matched with the first limiting part; the partition plate is provided with a rotating shaft hole, the intermediate shaft is matched in the rotating shaft hole, the outer diameter of the first rotating shaft is D0, the outer diameter of the second rotating shaft is D1, the outer diameter of the intermediate shaft is D2, the diameter of the rotating 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 is not less than D1 and not less than D2 and not less than D3 and not less than D1, D0 is not less than D1 and not less than D2 and not less than D3 and not less than D2. The compression mechanism of the rotary compressor can enlarge the displacement of the rotary compressor, improve the compression efficiency, improve the rigidity of the crankshaft, and has high reliability of torque transmission, durability, reliability and production efficiency.

Description

Compression mechanism of rotary compressor and rotary compressor

Technical Field

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

Background

Compared with a single-cylinder rotary compressor, the variable-frequency motor type double-cylinder rotary compressor has the advantages of being low in variation of compression torque and capable of running below 30Hz, and accordingly being advantageous in aspects of air conditioner comfort, food preservation performance, seasonal energy efficiency (APF) and the like.

In the related art double-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 previously fixed to the crankshaft and the outer diameter of the intermediate shaft, the assembly of the compressing mechanism cannot be completed. Therefore, the inner diameter (D3) of the spacer ≧ the outer diameter (D) of the eccentric shaft.

Due to the limitation of the design condition, the inner diameter of the partition plate is increased, the eccentric amount of the eccentric shaft is reduced, and the refrigerating capacity is low due to the reduction of the eccentric amount of the eccentric shaft, so that the displacement of the compressor is expanded and the compression efficiency is difficult to improve; also, since the outer diameter (d2) of the intermediate shaft connecting the two eccentric shafts cannot be enlarged, the rigidity of the crankshaft is hardly secured.

For this purpose, the intermediate shaft is usually divided into two parts or divided into two machined shafts, so that the outer diameter D1 of the rotary shaft < the outer diameter D2 of the intermediate shaft < the inner diameter D3 of the intermediate shaft < the outer diameter D of the eccentric shaft.

However, it is difficult to maintain the flatness accuracy of the partition plate divided into two parts, and the intermediate shaft is divided into two parts and processed mainly for improving the strength of the intermediate shaft (only d1 < d2), and the two methods are rarely used in practice.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides a compression mechanism of a rotary compressor, which can enlarge the displacement of the rotary compressor, improve the compression efficiency, improve the rigidity of a crankshaft, and has high reliability of torque transmission, durability, reliability and production efficiency.

The invention also provides a rotary compressor with 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 comprises: a first cylinder and a second cylinder; a crankshaft rotatable and including: a first rotating shaft and a second rotating shaft; the 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; 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, a second limiting part matched with the first limiting part is arranged on the end face, facing the middle shaft, of at least one of the first eccentric part and the second eccentric part, one of the first limiting part and the second limiting part is constructed into a limiting protrusion, and the other one of the first limiting part and the second limiting part is constructed into a limiting groove; the first end plate, the second end plate and the baffle, first cylinder with the second cylinder is established first end plate with between the second end plate and by the baffle is spaced apart, the baffle has the pivot hole just the jackshaft cooperation is in the pivot hole, first eccentric portion is established in the first cylinder and the second eccentric portion is established in the second cylinder, wherein, the external diameter of first revolving axle is D0, the external diameter of second revolving axle is D1, the external diameter of jackshaft is D2, the diameter of pivot hole is D3, the external diameter of first eccentric portion is D1, the external diameter of second eccentric portion is D2, D0 is no less than D1 < D2 no less than D3 < D1, D0 is no less than D1 < D2 no less than D3 < D2.

According to the compression mechanism of the rotary compressor provided by the embodiment of the invention, the displacement of the rotary compressor can be enlarged, the compression efficiency is improved, the rigidity of a crankshaft is improved, the reliability and the durability reliability 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 has the following additional technical features:

according to some embodiments of the invention, the first rotation shaft, the second rotation shaft and the intermediate shaft are coaxially arranged, and the first stopper portion is eccentrically arranged with respect to the intermediate shaft.

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

Advantageously, in a projection plane perpendicular to the central axis of the intermediate shaft, an outer contour line of a projection of the first stopper portion is inscribed in an outer contour line of a projection of the first pivot axis or the second pivot axis.

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

In some embodiments of the present invention, the intermediate shafts and the partition plates are two, and the two intermediate shafts are engaged with the two partition plates in a one-to-one correspondence, and the crankshaft further includes: the eccentric shaft, the eccentric shaft connects two jackshafts and the central axis deviates from the central axis of the jackshaft, first spacing portion is located one side of the jackshaft that faces away from the eccentric shaft, the compressing mechanism still includes: the eccentric shaft is arranged in the third compression 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 projection of the first eccentric portion, the center of projection of the second eccentric portion, and the center of projection of the eccentric shaft are uniformly distributed in the circumferential direction of the intermediate shaft.

In some embodiments of the present invention, an axial width of the at least one of the first eccentric portion and the second eccentric portion is W1, an axial width of the second stopper portion is W1, and W2 is 25% to 30% W1.

In some embodiments of the present invention, the first position-limiting portion is configured as the position-limiting protrusion and the second position-limiting portion is configured as the position-limiting groove, the end surface of the intermediate shaft is provided with a mounting groove extending along the axial direction thereof, and both ends of the position-limiting protrusion are respectively fitted in the position-limiting groove and the mounting groove.

According to some embodiments of the invention, an end face of the at least one of the first eccentric section and the second eccentric section facing away from the intermediate shaft is provided with a C-shaped stop ring which is fitted between the first rotation axis and the first eccentric section or the second rotation axis and the second eccentric section.

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

According to some embodiments of the invention, an intermediate bearing is provided between the intermediate shaft and the partition plate and an end of the second swivel shaft remote from the second end plate is provided with a shaft end bearing.

According to some embodiments of the invention, the first rotating shaft, the second rotating shaft and the intermediate shaft are all steel pieces, and the at least one of the first eccentric portion and the second eccentric portion is a powder alloy piece.

A rotary compressor according to an embodiment of a second aspect of the present invention includes: a housing provided with a discharge port; a compression mechanism of a rotary compressor according to an embodiment of the first aspect of the present invention, the compression mechanism being provided in the casing; and the driving mechanism is arranged in the shell and is in transmission connection with the crankshaft.

According to the rotary compressor of the embodiment of the invention, the compression mechanism of the rotary compressor is utilized, the displacement is large, the compression efficiency is high, the rigidity of the crankshaft is good, the reliability and the durability reliability of torque transmission are high, and the production efficiency is high.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

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

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

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

fig. 4 is a left side 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;

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

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

fig. 7 is a partial structural view of a crankshaft of a rotary compressor in accordance with a first alternative embodiment of the present invention;

fig. 8 is a partial sectional view of a compression mechanism of a rotary compressor in accordance with a first alternative embodiment of the present invention;

fig. 9 is a sectional view of a compression mechanism of a rotary compressor in accordance with a first alternative embodiment of the present invention;

fig. 10 is a left side view and a front view of a partial structure of a crankshaft of a rotary compressor in accordance with a second alternative embodiment of the present invention;

fig. 11 is a sectional view of a compression mechanism of a rotary compressor in accordance with a second alternative embodiment of the present invention;

fig. 12 is a longitudinal sectional view of a rotary compressor in accordance with a third alternative embodiment of the present invention;

fig. 13 is a partial structural view of a crankshaft of a rotary compressor in accordance with a third alternative embodiment of the present invention;

fig. 14 is a partial sectional view of a compression mechanism of a rotary compressor in accordance with a fourth alternative embodiment of the present invention;

fig. 15 is a partial sectional view of a compression mechanism of a rotary compressor in accordance with a fifth alternative embodiment of the present invention.

Reference numerals:

a first dual rotary compressor 102, a second dual rotary compressor 103,

a shell 2, an electric motor 3, a stator 3a, a rotor 3b,

a first compression mechanism part 4A, a second compression mechanism part 4B, a third compression mechanism part 4C,

a first crankshaft 10A, a second crankshaft 10B, a third crankshaft 10C, a first revolving shaft 11, a second revolving shaft 12, an intermediate shaft 13, a circular protrusion 13a,

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

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

a separation eccentric shaft 15, a shaft hole 15a, a circular groove 15b, a thrust projection 15c, an ejector pin 15d,

the device comprises an upper end shaft 16, a fixed eccentric shaft 20, a rolling piston 21, an intermediate bearing 22, a shaft end bearing 23, a C-shaped stop ring 25, an upper oil vane cylinder 27, an air suction pipe 30, an air exhaust pipe 31 and a bearing cylinder 32.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

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

Alternatively, the rotary compressor may be a vertical compressor. In the following description of the present application, a rotary compressor is exemplified as a vertical compressor. Of course, it will be understood by those skilled in the art that the rotary compressor may also be a horizontal compressor (not shown). Here, it should be noted that the "vertical compressor" may be understood as a compressor in which a central axis of a cylinder of a compression mechanism of the rotary compressor is perpendicular to a mounting surface of the rotary compressor, for example, as shown in fig. 1, the central axis of the cylinder extends in a vertical direction. Accordingly, a "horizontal compressor" may be understood as a compressor in which the center axis of the cylinder is parallel to the mounting surface of the rotary compressor.

As shown in fig. 1 to 15, a compression mechanism of a rotary compressor according to an 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 partition 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, that is, the first end plate 5, the first cylinder 8, the partition plate 7, the second cylinder 9, and the second end plate 6 are provided in this order in the up-down direction. The first cylinder 8 has a first compression chamber 8a therein and is provided with a first piston rollable along the inner circumferential wall of the first cylinder 8, and the second cylinder 9 has a second compression chamber 9a therein and is provided with a second piston rollable along the inner circumferential wall of the second cylinder 9.

The crankshaft is rotatable and includes a first revolving shaft 11, a second revolving shaft 12, an intermediate shaft 13, a first eccentric portion and a second eccentric portion. Both ends of the intermediate shaft 13 are connected to the first rotating shaft 11 and the second rotating shaft 12, respectively, and the intermediate shaft 13 is provided with a first stopper portion configured as a stopper protrusion extending from an end surface of the intermediate shaft 13 in an axial direction (e.g., up-down direction) thereof. The first eccentric part is sleeved on the first rotating shaft 11 and is eccentrically arranged, namely, the central axis of the first eccentric part deviates from the central axis of the first rotating shaft 11; the second eccentric portion is sleeved on the second rotating shaft 12, and the second eccentric portion is eccentrically disposed, that is, the central axis of the second eccentric portion deviates from the central axis of the second rotating shaft 12.

The end face of at least one of the first eccentric part and the second eccentric part, which faces the intermediate shaft 13, is provided with a second limiting part, the first limiting part is matched in the second limiting part, and the second limiting part is constructed into a limiting groove. Here, "at least one" means that the upper end surface of the first eccentric portion is provided with a second stopper portion, and the first stopper portion protrudes downward beyond the lower end surface of the intermediate shaft 13, so that the first eccentric portion is detachable from the first rotating shaft 11; or, the lower end face of the second eccentric part is provided with a second limit part, and the first limit part extends upwards out of the upper end face of the middle shaft 13, so that the second eccentric part can be separated from the second rotating shaft 12; or, the upper end surface of the first eccentric portion is provided with a second limiting portion, the first limiting portion extends downward beyond 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 first limiting portion extends upward beyond the upper end surface of the intermediate shaft 13, so that the first eccentric portion is separable from the first rotating shaft 11 and the second eccentric portion is separable from the second rotating shaft 12.

It is to be understood that the first position-limiting portion may be configured as a position-limiting groove and the second position-limiting portion may be configured as a position-limiting protrusion, as long as it is ensured that the first position-limiting portion and the second position-limiting portion can be fitted together, and the present invention is not particularly limited thereto. It should be noted that, in the embodiments provided in the present application, only the first limiting portion is taken as a limiting protrusion and the second limiting portion is taken as a limiting groove for relevant description, and the embodiments are not to be construed as limitations of the present invention.

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

The outer diameter of the first rotating shaft 11 is D0, the outer diameter of the second rotating shaft 12 is D1, the outer diameter of the intermediate shaft 13 is D2, the diameter of the rotating shaft hole 7a is D3, the outer diameter of the first eccentric part is D1, the outer diameter of the second eccentric part is D2, D1 is larger than or equal to D0 and larger than or equal to D2 and smaller than or equal to D3 and smaller than or equal to D1, and D1 is larger than or equal to D0 and larger than or equal to D2 is larger than or equal to D3 and smaller than or equal to D2.

According to the compression mechanism of the rotary compressor, the first limit part extending out of the middle shaft 13 in the axial direction is matched with the second limit part arranged on the end face, so that torque connection is realized, the torque of the crankshaft is transmitted to the middle shaft 13 to form the torque of the middle shaft 13, and then is transmitted to the first eccentric part and the second eccentric part through the middle shaft 13 to form the torque of the first eccentric part and the second eccentric part, and the reliability and the durability and the reliability of torque transmission are optimized; the requirements that D1 is more than D2 and less than D3 is more than D1, D1 is more than D2 and less than D3 is more than D2 are met, so that the refrigerating capacity and the displacement of each cylinder of the rotary compressor can be enlarged, and the expansion of the displacement of the rotary compressor, the improvement of the compression efficiency and the improvement of the rigidity of a crankshaft are realized.

Meanwhile, the moment connection structure is formed by concave-convex matched structures, the structures can be machined through an automatic lathe, machining precision is high, assembly is easy, and therefore production efficiency is improved. Further, since the conventional crankshaft integrally molded is divided into a plurality of parts, it is relatively easy to introduce a steel pipe, a powder alloy, and a forging process into the crankshaft.

According to some embodiments of the present invention, as shown in fig. 1 to 15, the first revolving shaft 11, the second revolving shaft 12 and the intermediate shaft 13 are coaxially arranged, that is, the central axis of the first revolving shaft 11 and the central axis of the second revolving shaft 12 coincide with the central axis of the intermediate shaft 13, thereby facilitating the manufacturing and forming of the crankshaft. The first position-limiting portion is eccentrically arranged relative to the intermediate shaft 13, that is, the central line of the first position-limiting portion is arranged to deviate from the central axis of the intermediate shaft 13, so as to ensure the eccentric arrangement of the first eccentric portion or the second eccentric portion matched with the first position-limiting portion.

Further, as shown in fig. 1 to 13 and 15, the first stopper portion is provided around the central axis of the intermediate shaft 13, and the first stopper portion extends in the circumferential direction of the intermediate shaft 13, so that the reliability and durability of torque transmission can be improved. In order to simplify the structure of the first and second position-limiting portions and facilitate the manufacturing and molding, the first and second position-limiting portions may be respectively designed to be circular, that is, the first position-limiting portion is configured as a circular protrusion 13a, at least one of the first and second eccentric portions is a separating eccentric shaft 15, and the second position-limiting portion on the separating eccentric shaft 15 is configured as a circular groove 15 b.

Advantageously, as shown in fig. 2 and 4, in a projection plane perpendicular to the central axis of the intermediate shaft 13, the projected outer contour of the first stopper portion is inscribed in the projected outer contour of the first revolving shaft 11 or the second revolving shaft 12, thereby facilitating the machining. For example, the eccentric shaft 15 has a shaft hole 15a, the center axis of the circular groove 15b is offset from the center axis of the shaft hole 15a, and the contour line of the projection of the shaft hole 15a is inscribed in the contour line of the projection of the circular groove 15b in the projection plane perpendicular to the center axis of the shaft hole 15 a.

Alternatively, as shown in fig. 7 and 8, the first stopper portion is located on a side (i.e., a lower side) of the intermediate shaft 13 facing the first eccentric portion, and an end surface (i.e., an upper end surface) of the first eccentric portion facing the intermediate shaft 13 is provided with a second stopper portion integrally formed on a side (i.e., an upper side) of the intermediate shaft 13 facing away from the first eccentric portion. For example, the first eccentric portion is configured as the eccentric separating shaft 15, the second eccentric portion is configured as the eccentric fixing shaft 20, the first rotation shaft 11, the second rotation shaft 12, the intermediate shaft 13, the first stopper portion and the eccentric fixing shaft 20 are integrally formed, the first rotation shaft 11 is inserted into the first cylinder 8 at the time of assembling, and the eccentric separating shaft 15 is assembled to the first rotation shaft 11 and the first stopper portion.

In some embodiments of the invention, as shown in fig. 10 and 11, there are two intermediate shafts 13 and two partition plates 7, and the two intermediate shafts 13 are fitted to the two partition plates 7 in one-to-one correspondence. The crankshaft further comprises an eccentric shaft, the eccentric shaft is connected with the two intermediate shafts 13, the central axis of the eccentric shaft deviates from the central axis of the intermediate shafts 13, and the first limiting parts are two and are respectively located on one sides, back to the eccentric shaft, of the two intermediate shafts 13. The compressing mechanism further comprises a third cylinder 14, a third compressing cavity is formed in the third cylinder 14, a third piston capable of rolling along the inner peripheral wall of the third cylinder 14 is arranged in the third cylinder 14, the eccentric shaft is arranged in the third compressing cavity, and the outer peripheral wall of the eccentric shaft is sleeved with the third piston. The first, second and third pistons are all rolling pistons 21. For example, the eccentric shaft is a fixed eccentric shaft 20, and the first position-limiting portion and the second first position-limiting portion are both separated eccentric shafts 15 and are respectively located at the upper and lower sides of the fixed eccentric shaft 20.

Advantageously, as shown in fig. 11, in a 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 uniformly distributed along the circumferential direction of the intermediate shaft 13, i.e., the included angle between the projection of the first eccentric portion, the projection of the second eccentric portion and the projection of the eccentric shaft is 120 ° to average the 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 (i.e., the eccentric shaft 15) is W1, and the axial width of the second stopper portion is W1, and W2 is 25% to 30% W1, so that the contact area can be controlled within a reasonable range and friction can be reduced.

In some 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 the axial direction thereof, and both ends of the first position-limiting portion are respectively fitted in the second position-limiting portion and the mounting groove, so that the connection of the eccentric shaft 15 is realized in a simpler manner, and the present invention is suitable for a small-sized double-cylinder rotary compressor with low operating pressure and small crankshaft moment. For example, the first stopper portion is an ejector pin 15d, and the ejector pin 15d assembles the intermediate shaft 13 and the eccentric shaft 15 together.

According to some embodiments of the invention, as shown in fig. 15, the end surface of the at least one of the first and second eccentric portions facing away from the intermediate shaft 13 is provided with a C-shaped stop ring 25, and the C-shaped stop ring 25 is fitted between the first rotary shaft 11 and the first or second rotary shaft 12 and the second eccentric portion, thereby fixing the eccentric shaft 15. Thus, by the fixed connection of the C-shaped stop ring 25, the intermediate shaft 13 and the eccentric release shaft 15, the subsequent alignment assembly is made easier.

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

According to some embodiments of the present invention, as shown in fig. 1 and 5, the first end plate 5 is provided with a first bearing 5a engaged with the first revolving shaft 11 and the second end plate 6 is provided with a second bearing 6a engaged with the second revolving shaft 12 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 7 and an end (i.e., upper end) of the second rotating shaft 12 remote from the second end plate 6 is provided with a shaft end bearing 23, so that the structures of the first end plate 5 and the second end plate 6 can be simplified.

According to some embodiments of the present invention, the first rotation shaft 11, the second rotation shaft 12 and the intermediate shaft 13 are all steel members, and the at least one of the first eccentric portion and the second eccentric portion (i.e., the eccentric separating shaft 15) is suitable for powder molding, for example, the eccentric separating shaft 15 is a powder alloy member.

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

Specifically, the housing 2 is provided with a discharge port, and the compression mechanism and the drive mechanism are both disposed in the housing 2, and the drive mechanism is drivingly connected to the crankshaft. The drive mechanism is, for example, an electric motor 3.

A rotary compressor according to various embodiments of the present invention will be described with reference to the accompanying drawings.

Embodiment 1

Fig. 1 is a vertical cross-sectional view showing a case where the rotary compressor is the first double-cylinder rotary compressor 102, the compression mechanism is the compression mechanism section 4A, and the crankshaft is the crankshaft 10A.

Specifically, the electric motor 3 and the compression mechanism portion 4A are fixed on the inner periphery of the hermetic case 2. The electric motor 3 is composed of a stator 3a fixed to the sealed casing 2 and a rotor 3b fixed to the crankshaft 10A, and rotationally drives the compression mechanism 4A.

The compression mechanism 4A is constituted by: a second cylinder 9 fixed on the inner circumference of the first cylinder 8 and the closed housing 2, a partition plate 7 between the 2 cylinders, a first end plate 5 and a second end plate 6 sealing the opening ends of the first compression chamber 8a and the second compression chamber 9a in the cylinders, a first rotating shaft 11 and a second rotating shaft 12 slidably engaged with bearings on the centers of these parts, two separate eccentric shafts 15 fixed on the first rotating shaft 11 and the second rotating shaft 12, a rolling piston 21 slidably engaged on the outer circumferences of these separate eccentric shafts 15 and eccentrically rotated, and the like. Further, an oiling blade cylinder 27 is provided at the shaft end of the first rotating shaft 11.

In the above configuration of the compression mechanism 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 eccentric separating shafts 15 are inserted from the shaft ends of the first rotation shaft 11 and the second rotation shaft 12, respectively, and the circular grooves 15b on the end faces of the eccentric separating shafts 15 are inserted into the circular protrusions 13a provided on 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 eccentric separating shafts 15 eccentrically rotate by the eccentric amount e2 according to the torque of the crankshaft 10A. Likewise, the two rolling pistons 21 are eccentrically revolved in the first compression chamber 8a and the second compression chamber 9a at an angle of 180 ° with respect to each other.

Low-pressure gas flowing in from two gas suction pipes 30 respectively continuing to the first cylinder 8 and the second cylinder 9 flows into the first compression chamber 8a and the second compression chamber 9a, and compressed high-pressure gas is discharged from the gas discharge pipe 31 via the muffler and the electric motor 3 on the first end plate 5 and the second end plate 6. Thereafter, the refrigeration cycle device cycles back again into the two suction ducts 30.

As shown in fig. 2, the eccentric separating shaft 15 is characterized in that a circular groove 15b is provided in an end surface thereof, and a shaft hole 15a is opened in the circular groove 15 b. The circular groove 15b is eccentric by an eccentric amount e1 with respect to the shaft hole 15a, and the outer diameter D of the eccentric shaft 15 is eccentric by an eccentric amount e2 with respect to the center axis of the shaft hole 15 a. That is, e2 is also the eccentric amount of the rolling piston 21 that revolves in the compression chamber. Further, the inner diameter circle of the shaft hole 15a is not outside the circle of the circular groove 15 b. The inner diameter end of the shaft hole 15 shown in fig. 2 coincides with the circular diameter of the eccentric circular groove 15 b.

The eccentricity e1 has an important effect on the revolution of the eccentric separating shaft 15 by the torque of the crankshaft 10A via the circular projection 13a of the intermediate shaft 13, the outer diameter D of the eccentric separating shaft 15 is a cylindrical surface on which the inner diameter of the rolling piston 21 slides, and the thrust projection 15c is a thrust surface on which the thrust surface slides on the plane of the first end plate 5.

Since the shaft hole 15a does not slide on the outer diameters of the first rotating shaft 11 and the second rotating shaft 12, the clearance between them is reduced as much as possible, and the clearance is below 1/2000 of the outer diameter of the corresponding shaft. For example, the outer diameter of the first rotary shaft 11 is 16mm, the clearance between the shaft hole 15a and the first rotary shaft 11 is 8 μm or less, and the clearance when the eccentric shaft 15 is shrink-fitted to the first rotary shaft 11 is set to be smaller. The depth of the circular groove 15b is W2, and the depth is 25-30% of the width W1 of the eccentric separating shaft 15.

The eccentric separating shaft 15 has a cylindrical shape and can be machined by an automatic lathe. After that, the outer diameters of the shaft hole 15a and the eccentric separating shaft 15 need to be ground. The eccentric separating shaft 15 may be made of spheroidal graphite cast iron (FCD500, etc.) which is a material for the crankshaft, and preferably, a powder alloy may be used because the shape of the eccentric separating shaft 15 is suitable for powder molding.

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 fixed to the upper and lower surfaces of the diaphragm 7 by pins 24 provided on the diaphragm 7. Next, the shaft end of the first rotating shaft 11 is inserted into the rotating shaft hole 7 a. Then, the eccentric separating shafts 15 are inserted from the shaft ends of the second rotation shaft 12 and the first rotation shaft 11, respectively, and the circular grooves 15b of the eccentric separating shafts 15 are inserted into the circular protrusions 13a, whereby the assembly of the two eccentric separating shafts 15 facing each other is completed. Wherein, the clearance between the intermediate shaft 13 and the rotating shaft hole 7a is about 0.2 mm.

After the above-described assembly of the compression mechanism 4A is completed, two rolling pistons 21 are inserted into the two eccentric separating shafts 15, respectively, and slide pieces (not shown) are assembled. Next, the second end plate 6 is fixed to the second cylinder 9 by screws, and then the second compression chamber 9a and the second rotation shaft 12 are aligned. Next, the first end plate 5 is inserted into the first rotation shaft 11 and fixed to the first cylinder 8 by screws, and the alignment of the first compression chamber 8a and the first rotation shaft 11 is performed. Thus, the compression mechanism 4A shown in fig. 5 is completed by the above assembly.

The torque of the crankshaft 10A slidably engaged with the first bearing 5a and the second bearing 6a provided in the first end plate 5 and the second end plate 6 is transmitted to the two eccentric separating shafts 15 by the eccentric amount e1 of the two circular protrusions 13a on the intermediate shaft 13, and the two eccentric separating shafts 15 and the two rolling pistons 21 are eccentrically rotated.

Since the two eccentric separating shafts 15 are fixed to the first rotation shaft 11 and the second rotation shaft 12, respectively, the eccentric amount e2 and the rotation accuracy of the outer diameter of the eccentric separating shaft 15 are determined by the shape accuracy of the eccentric separating shaft 15 and the fixing clearance between the eccentric separating shaft 15 and the first rotation shaft 11 and the second rotation shaft 12 shown in fig. 2, and are independent of the accuracy of the eccentric amount e1 of the torque transmission means. However, the fitting clearance between the circular protrusion 13a and the circular groove 15b has an influence on the relative angle (180 °) of the two eccentric separating shafts 15.

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

As shown in fig. 5, the load in the downward direction is abutted against the first end plate 5 via the thrust projection 15c of the eccentric shaft 15, and the load in the upward direction is restricted from moving up and down by the stopper serving as the thrust projection 15c of the eccentric shaft 15 by the second end plate 6.

Next, as shown in fig. 6, when the outer diameters of the first rotating shaft 11 and the second rotating shaft 12 are D1, the outer diameter of the intermediate shaft 13 is D2, the diameter of the rotating shaft hole 7a is D3, and the outer diameter of the eccentric separating shaft 15 is D, D1 < D2 < D3 < D holds, and the assembly of the eccentric separating shaft 15 can reduce the diameter of the partition plate 7 and enlarge the outer diameter of the intermediate shaft 13.

Since D3 < D, the minimum clearance m between the inner diameter of the rotating shaft hole 7a and the outer diameter of the rolling piston 21 is increased, and the high-pressure side gas of the diaphragm 7 does not leak to the low-pressure sides of the first compression chamber 8a and the second compression chamber 9a, the re-expansion loss of the high-pressure gas can be improved. Meanwhile, since d1 < d2, the rigidity of the intermediate shaft 13 is improved, and the deformation of the intermediate shaft 13 caused by the compression load in the first and

second compression chambers

8a and 9a alternately generated by the rolling piston 21 is greatly improved.

In addition, D3 < D, so that the eccentric amount e2 of the eccentric separating shaft 15 can be increased, and the displacement can be increased without enlarging the inner diameter of the compressor. That is, it is effective to improve the compression efficiency not only by securing a large cooling capacity in the small cylinder compression chamber, but also by enlarging the size of the twin 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 an iron casting, or the crankshaft 10A may be an SCM steel bar (i.e., a chromium-molybdenum steel) having wear resistance and high rigidity and capable of being subjected to wear resistance treatment, or the crankshaft 10A may be formed by forging the intermediate shaft 13. Thereby, improvement of the endurance reliability and the production efficiency of the crankshaft 10A can be achieved at the same time.

Embodiment 2

The present embodiment relates to a double-cylinder rotary compressor using a separate eccentric shaft 15 and a fixed eccentric shaft 20 in combination.

As shown in fig. 7, the second rotation shaft 12 of the crankshaft 10B has a fixed eccentric shaft 20, the first rotation shaft 11 has a separation eccentric shaft 15, and the intermediate shaft 13 is provided with a circular protrusion 13a only on the side facing the first rotation shaft 11.

As shown in fig. 8, after the partition plate 7, the first cylinder 8 and the second cylinder 9 are assembled, the first rotating shaft 11 of the crankshaft 10B is inserted into the rotating shaft hole 7a, the intermediate shaft 13a is stationary in the rotating shaft hole 7a, the eccentric separating shaft 15 is inserted from the shaft end of the first rotating shaft 11, and the circular groove 15B is fitted into the circular protrusion 13 a. Thereafter, the partial assembly is completed.

Then, the assembly of the compression mechanism 4B shown in fig. 9 is completed in the same manner as in embodiment 1. Embodiment 2 gives an example in which even if one of the first eccentric portion and the second eccentric portion is used as the fixed eccentric shaft 20, the assembly of the compression mechanism portion 4B can be completed as in embodiment 1. Also, D1 < D2. ltoreq.d 3 < D is also true.

Embodiment 3

As shown in fig. 10, a fixed eccentric shaft 20 is provided between a first rotation shaft 11 and a second rotation shaft 12 of a crankshaft 10C of the three-cylinder rotary compressor, and an intermediate shaft 13 and a circular protrusion 13a are connected to both sides of the fixed eccentric shaft 20. In order to average the compression moment, the angle between the two eccentric separating shafts 15 and the eccentric fixed shaft 20 of the three-cylinder rotary compressor is 120 ° in the projection plane perpendicular to the crankshaft 10C, and the centers of the three eccentric shafts are the vertexes of a regular triangle and rotate in one direction.

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

first, the rolling piston 21 is inserted into the fixed eccentric shaft 20, and the second compression chamber of the third cylinder 14 is pressed into the outer periphery of the rolling piston 21. Next, the two partition plates 7 are fixed at predetermined positions on both side planes of the third cylinder 14.

Then, the eccentric shaft 15 is inserted into the shaft ends of the second rotating shaft 12 and the first rotating shaft 11, and the circular groove 15b is fitted into the circular protrusion 13 a. Next, the first cylinder 8 and the second cylinder 9 are fixed to predetermined positions of the two assembled separators 7, respectively, and alignment with the third cylinder 14 is performed. Next, after inserting the rolling piston 21 on the outer peripheries of the assembled two separate eccentric shafts 15, the first end plate 5 and the second end plate 6 are fixed to the first cylinder 8 and the second cylinder 9 with screws, respectively. Thereafter, the alignment of the first end plate 5, the second end plate 6, the first revolving shaft 11, and the second revolving shaft 12 is performed.

Fig. 11 is a longitudinal sectional view of the assembled compression mechanism 4C. 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 hole of the third cylinder 14 is arranged on any one built-in silencer in the two partition plates 7.

Since the crankshaft 10C in fig. 10 connects the two intermediate shafts 13 for the fixed eccentric shaft 20, the rigidity of the crankshaft is greatly improved. In addition, in embodiment 3, D1 < D2. ltoreq.d 3 < D is also achieved.

Embodiment 4

In the second double-cylinder rotary compressor 103 shown in fig. 12, the intermediate shaft 13 of the crankshaft 10D is slidably fitted to the intermediate bearing 22 fitted to the center of the partition plate 7, and the upper end shaft 16 of the second rotary shaft 12 is slidably fitted to the shaft end bearing 23 fitted to the center of the bearing cartridge 32, by applying the feature that the outer diameter D2 of the intermediate shaft 13 is larger than the outer diameter D1 of the first rotary shaft 11 and the second rotary shaft 12, so that the first bearing 5a and the second bearing 6a used in embodiment 1 and the like can be omitted.

The intermediate shaft 13 thus supports the compression loads occurring on the two rolling pistons 21 in the first and

second cylinders

8, 9 and is in sliding engagement with the intermediate bearing 22. The upper end shaft 16 supports the vibration load of the second rotating shaft 12 including the rotor 3b and is slidably fitted to the shaft end bearing 23. Further, if the intermediate bearing 22 and the shaft end bearing 23 are bushings or shaft end bearings, the reliability of the bearings is improved and the rotational speed of the crankshaft 10D is greatly increased.

Other constructions and operations of the rotary compressor according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail herein.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "upper," "lower," "vertical," "inner," "outer," "axial," "radial," "circumferential," and the like are used in the indicated orientations and positional relationships based on the drawings for ease of description and simplicity of description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be construed as limiting the present invention.

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

In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; either directly or indirectly through intervening media, or through the communication between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "a specific embodiment," "an example" or "some examples" or the like are intended to mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above 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.

While embodiments of the 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 to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A compression mechanism of a rotary compressor, comprising:

a first cylinder and a second cylinder;

a crankshaft rotatable and including:

a first rotating shaft and a second rotating shaft;

the 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;

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, a second limiting part matched with the first limiting part is arranged on the end face, facing the middle shaft, of at least one of the first eccentric part and the second eccentric part, one of the first limiting part and the second limiting part is constructed into a limiting protrusion, and the other one of the first limiting part and the second limiting part is constructed into a limiting groove;

a first end plate, a second end plate and a partition plate, the first cylinder and the second cylinder being provided between the first end plate and the second end plate and being spaced apart by the partition plate, the partition plate having a rotation shaft hole and the intermediate shaft being fitted in the rotation shaft hole, the first eccentric portion being provided in the first cylinder and the second eccentric portion being provided in the second cylinder, wherein,

the outer diameter of the first rotating shaft is D0, the outer diameter of the second rotating shaft is D1, the outer diameter of the intermediate shaft is D2, the diameter of the rotating shaft hole is D3, the outer diameter of the first eccentric part is D1, the outer diameter of the second eccentric part is D2, D1 is larger than or equal to D0, D2 is larger than or equal to D3, D1 is larger than or equal to D1, D2 is larger than or equal to D3, and D2 are larger than or equal to D0.

2. The compressing mechanism of a rotary compressor as set forth in claim 1, wherein said first rotating shaft, said second rotating shaft and said intermediate shaft are coaxially disposed, and said first stopper portion is eccentrically disposed with respect to said intermediate shaft.

3. The compression mechanism of a rotary compressor according to claim 2, wherein the first stopper portion is disposed around a central axis of the intermediate shaft and extends in a circumferential direction of the intermediate shaft.

4. The compressing mechanism of a rotary compressor as set forth in claim 3, wherein an outer contour line of a projection of said first stopper part is inscribed in an outer contour line of a projection of said first rotating shaft or said second rotating shaft in a projection plane perpendicular to a central axis of said intermediate shaft.

5. The compressing mechanism of rotary compressor as set forth in claim 3, wherein said first stopper portion is located at a side of said intermediate shaft facing said first eccentric portion, and an end surface of said first eccentric portion facing said intermediate shaft is provided with said second stopper portion, and said second eccentric portion is integrally formed at a side of said intermediate shaft facing away from said first eccentric portion.

6. The compressing mechanism of a rotary compressor as set forth in claim 3, wherein there are two of said intermediate shafts and said partition plates, and two of said intermediate shafts are engaged with the two of said partition plates in a one-to-one correspondence, said crankshaft further comprising:

the eccentric shaft, the eccentric shaft connects two jackshafts and the central axis deviates from the central axis of the jackshaft, first spacing portion is located one side of the jackshaft that faces away from the eccentric shaft, the compressing mechanism still includes:

the eccentric shaft is arranged in the third compression cavity, and the third piston is sleeved on the outer peripheral wall of the eccentric shaft.

7. The compressing mechanism of a rotary compressor as set forth in claim 6, wherein a center of a projection of said first eccentric portion, a center of a projection of said second eccentric portion and a center of a projection of said eccentric shaft are uniformly distributed along a circumferential direction of said intermediate shaft in a projection plane perpendicular to a central axis of said intermediate shaft.

8. The compressing mechanism of the rotary compressor as claimed in claim 3, wherein the at least one of the first eccentric portion and the second eccentric portion has an axial width of W1, the second stopper portion has an axial width of W1, and W2 is 25-30% W1.

9. The compressing mechanism of a rotary compressor as set forth in claim 2, wherein the first position-limiting portion is configured as the position-limiting projection and the second position-limiting portion is configured as the position-limiting groove, the end surface of the intermediate shaft is provided with a mounting groove extending in the axial direction thereof, and both ends of the position-limiting projection are fitted in the position-limiting groove and the mounting groove, respectively.

10. The compressing mechanism of rotary compressor as set forth in any one of claims 1 to 9, wherein an end surface of said at least one of said first eccentric portion and said second eccentric portion facing away from said intermediate shaft is provided with a C-shaped stopper ring fitted between said first rotating shaft and said first eccentric portion or between said second rotating shaft and said second eccentric portion.

11. The compressing mechanism of the rotary compressor as set forth in any one of claims 1 to 9, wherein the first end plate is provided with a first bearing engaged with the first rotary shaft and the second end plate is provided with a second bearing engaged with the second rotary shaft.

12. The compressing mechanism of the rotary compressor as set forth in any one of claims 1 to 9, wherein an intermediate bearing is provided between said intermediate shaft and said partition plate and an end of said second rotating shaft remote from said second end plate is provided with an axial end bearing.

13. The compressing mechanism of rotary compressor as set forth in any one of claims 1 to 9, wherein said first rotating shaft, said second rotating shaft and said intermediate shaft are all steel members, and said at least one of said first eccentric portion and said second eccentric portion is a powder alloy member.

14. A rotary compressor, comprising:

a housing provided with a discharge port;

the compression mechanism of a rotary compressor according to any one of claims 1 to 13, which is provided in the housing;

and the driving mechanism is arranged in the shell and is in transmission connection with the crankshaft.