CN205036575U - Multi -cylinder rotary compressor - Google Patents

Abstract

The utility model discloses a multi-cylinder rotary compressor, which comprises: several cylinders formed in sequence from the first cylinder to the Nth cylinder; compression chambers in each cylinder; eccentric operation in each compression chamber pistons; sliding plates that reciprocate synchronously with the pistons; crankshafts, the crankshafts are provided with eccentric shafts that drive the pistons, and intermediate shafts provided in the middle of the adjacent eccentric shafts, and the first The main shaft that slides with the main bearing combined with the cylinder, and the sub-shaft that slides with the sub-bearing combined with the Nth cylinder; at least one of the eccentric shafts and the crankshaft is separately assembled; the middle of the adjacent cylinders The provided intermediate bearing plate is in sliding fit with the intermediate shaft. According to the multi-cylinder rotary compressor of the present invention, the reliability is improved, the operating speed is increased, the capacity of the compressor is improved, and the compression efficiency is improved.

Description

Multi-cylinder rotary compressor

technical field

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

Background technique

Compared with the single-cylinder rotary compressor, the multi-cylinder rotary compressor that was officially mass-produced around 1988 can operate from a low speed of 15rps to 120rps, and has advantages especially in terms of vibration. In addition, in recent years, in order to be used in large-scale systems, application to 10HP-class systems using inverter-type motors has been promoted.

On the other hand, multi-cylinder rotary compressors increase the inter-shaft length (the length between the main shaft and the counter shaft) due to the addition of cylinders, and the vibration of the crankshaft that drives the two pistons increases, resulting in wear failure of the crankshaft. In addition, the center hole of the conventional intermediate partition provided between the two cylinders has an eccentric shaft passing through it during assembly, so the center hole becomes larger, and the amount of eccentricity of the crankshaft is small and limited.

Utility model content

The utility model aims to solve one of the technical problems in the related art at least to a certain extent. Therefore, the utility model proposes a multi-cylinder rotary compressor, which improves reliability, expands operating speed, improves the capacity of the compressor, and improves compression efficiency.

According to the multi-cylinder rotary compressor of the present invention, it includes: several cylinders formed in sequence from the first cylinder to the Nth cylinder; compression chambers in each cylinder; pistons that operate eccentrically in each compression chamber a sliding plate that reciprocates synchronously with the pistons; a crankshaft, the crankshaft is provided with an eccentric shaft that drives the pistons, and an intermediate shaft provided in the middle of the adjacent eccentric shafts, and is connected to the first cylinder. The combined main bearing slides the main shaft, and the sub-bearing combined with the Nth cylinder slides; at least one of the eccentric shafts is separately assembled from the crankshaft; the adjacent cylinders are equipped with The intermediate bearing plate is in sliding fit with the intermediate shaft.

According to the multi-cylinder rotary compressor of the present invention, since at least one eccentric shaft and the crankshaft are separately assembled, and the middle bearing plate is slidingly fitted with the middle shaft, the reliability of the multi-cylinder rotary compressor can be improved, and it can also be expanded Many improvements have been made in terms of operating speed, larger capacity of the compressor, and improvement of compression efficiency.

In a specific example of the present utility model, in the separately assembled eccentric shaft and the crankshaft, the cylindrical hole provided in the eccentric shaft and the crankshaft can be connected by embedding, pressing, shrinking, laser Either way in welding.

According to some specific embodiments of the present utility model, a torque transmission member is provided between the cylindrical hole provided in the eccentric shaft and the crankshaft.

According to some embodiments of the present utility model, the outer diameter of any one of the eccentric shafts is De, the outer diameter of the main shaft is Dm, the outer diameter of any one of the intermediate shafts is Dc, and the outer diameter of the auxiliary shaft is Ds, De≧Dc≧Dm or De≧Dc≧Ds.

Optionally, the outer diameter of the secondary shaft is smaller than the outer diameter of the main shaft.

In some embodiments of the present utility model, the high-pressure gas discharged from at least one of the compression chambers passes through the intermediate muffler formed inside the intermediate bearing plate.

Further, the intermediate muffler is equipped with an exhaust device opening to at least one of the compression chambers.

Specifically, there is provided a channel for branching from one suction pipe connecting the intermediate bearing plate to the two compression chambers connecting the intermediate bearing plate.

According to a preferred embodiment of the present invention, at least one annular groove is provided along the inner diameter of the bearing of the intermediate bearing plate, and each annular groove opens a hole on the end surface of the intermediate bearing plate.

In a specific embodiment of the present utility model, any one of a bushing, a rolling bearing and a needle bearing is provided in the inner diameter of the bearing of the intermediate bearing plate.

According to some embodiments of the present utility model, the intermediate bearing plate is a thrust sliding surface supporting the load of the crankshaft.

Optionally, the eccentric shaft assembled separately is a powder metallurgy formed part or a forged formed part.

According to some specific embodiments of the present utility model, a motor for driving the main shaft is provided between the main shaft end bearing that slides and supports the end of the main shaft and the main bearing.

Description of drawings

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

Fig. 2 is related to this embodiment 1, shows the cross-sectional view of compression mechanism part;

Fig. 3 relates to this embodiment 1, shows the longitudinal sectional view of compression mechanism part;

Fig. 4 is related to embodiment 1 of the present utility model, represents the assembly drawing of intermediate bearing plate;

Fig. 5 is relevant to this embodiment 1, represents the exterior view of crankshaft;

Fig. 6 is relevant to this embodiment 1, shows the detailed view of split eccentric shaft and key;

Fig. 7 is related to embodiment 2 of the present utility model, shows the longitudinal sectional view of compression mechanism part;

Fig. 8 is related to embodiment 3 of the present utility model, the cross-sectional view of the intermediate bearing plate;

Fig. 9 is related to Embodiment 3 of the present utility model, a sectional view of the intermediate bearing plate;

Fig. 10 is related to Embodiment 3 of the present utility model, a sectional view of the intermediate bearing plate;

Fig. 11 is related to Embodiment 4 of the present utility model, the sectional view of the intermediate bearing plate;

Fig. 12 is related to embodiment 5 of the present utility model, the longitudinal sectional view of compression mechanism;

Fig. 13 is related to Embodiment 6 of the present utility model, the assembly diagram of the intermediate bearing plate of the multi-cylinder rotary compressor;

Figure 14 is related to Embodiment 6, the assembly diagram of the intermediate bearing plate of the multi-cylinder rotary compressor;

Fig. 15 is a longitudinal sectional view showing a multi-cylinder rotary compressor to which a fourth bearing is added, relating to Embodiment 7 of the present invention.

Reference signs:

Multi-cylinder rotary compressor 1, shell 2,

Motor 4, motor rotor 4a,

Compression mechanism part 5, intermediate bearing plate 40 (50), first cylinder 11, second cylinder 21, main bearing 43, sub-bearing 45, first compression chamber 11a, second compression chamber 21a, first piston 51, second Piston 52, first sliding piece 53, second sliding piece 54, key 37, second thrust 35a, channel 41a (41b), intermediate bearing inner diameter 40a, intermediate bearing plate hole 40c, first thrust 34b,

Crankshaft 30, main shaft 31, first eccentric shaft 34, intermediate shaft 32, second eccentric shaft 35, counter shaft 33, shaft center hole 30a, oil hole 32b, oil key 32a, first thrust upper part 34a, key groove 33a (35e ), key 37, oil groove 35c, third eccentric shaft 36, auxiliary shaft 31a,

Exhaust pipe 3, intermediate suction pipe 41, liquid reservoir 60, first muffler 43a, second muffler 45a, screw 43b (45b), clearance C1 (C2), intermediate bearing plate assembly 8 (9), annular groove 46 , sliding bearing 65, needle bearing 66,

Split middle plate 50a, bushing 67, middle muffler 50b, first exhaust hole 70a, second exhaust hole 70b, exhaust valve 71, coil spring 72, horizontal channel 50c, vertical channel 50d, flange 67a, first Suction pipe 55, the 2nd suction pipe 56, bearing pressure equalizing hole 44, bearing air hole 40b,

Frame 48, upper end bearing 48a.

detailed description

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

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

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

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

The multi-cylinder rotary compressor 1 according to the embodiment of the present invention will be described in detail below with reference to FIGS. 1-15 . The multi-cylinder rotary compressor 1 can be applied in air conditioners, refrigerators, water heaters, vehicle-mounted refrigerators or air conditioners.

The multi-cylinder rotary compressor 1 according to the embodiment of the present utility model includes: several cylinders formed in order from the first cylinder to the Nth cylinder, compression chambers provided in each cylinder, and eccentrically operated cylinders in each compression chamber Pistons, sliding vanes that reciprocate synchronously with each piston, and a crankshaft 30 .

The crankshaft 30 includes an eccentric shaft that drives each piston, an intermediate shaft provided between adjacent eccentric shafts, a main shaft 31 that slides with a main bearing 43 coupled to the first cylinder, and a sub bearing 45 that slides with the Nth cylinder. secondary shaft 33.

At least one eccentric shaft and the crankshaft 30 are separately assembled. The intermediate bearing plate 40 provided in the middle of adjacent cylinders is slidingly fitted with the intermediate shaft.

In other words, the multi-cylinder rotary compressor 1 has N cylinders, N pistons, N vanes, and the crankshaft 30 . Wherein each cylinder has a compression chamber, and each compression chamber has a piston that performs eccentric operation, and each cylinder is provided with a sliding plate that cooperates with the piston to perform reciprocating motion. The main bearing 43 is provided on the first cylinder, and the sub-bearing 45 is provided on the Nth cylinder. An intermediate bearing plate 40 is arranged between every two adjacent cylinders.

The crankshaft 30 includes a plurality of eccentric shafts, an intermediate shaft, a main shaft 31 and a counter shaft 33. The plurality of eccentric shafts are arranged in one-to-one correspondence with the plurality of pistons. Each eccentric shaft is sleeved in a corresponding piston to drive the corresponding piston to run eccentrically. An intermediate shaft is arranged between two adjacent eccentric shafts, and each intermediate bearing plate 40 is slidably fitted with the corresponding intermediate shaft, the main shaft 31 is slidably fitted with the main bearing 43 , and the auxiliary shaft 33 is slidably fitted with the auxiliary bearing 45 . At least one eccentric shaft is separately assembled from the crankshaft 30 .

It can be understood that the multi-cylinder rotary compressor 1 may be a hermetic rotary compressor, a belt-driven open rotary compressor, a horizontal multi-cylinder rotary compressor or a swing multi-cylinder rotary compressor. When the multi-cylinder rotary compressor 1 is a hermetic rotary compressor, the multi-cylinder rotary compressor 1 further includes a motor 4 , and the motor rotor 4 a of the motor 4 cooperates with the crankshaft 30 to drive the crankshaft 30 to rotate. In the specific example of FIG. 15 , the motor 4 that drives the main shaft 31 is provided between the main shaft end bearing 48 a that slidably supports the end of the main shaft 31 and the main bearing 43 .

According to the multi-cylinder rotary compressor 1 of the embodiment of the present invention, since at least one eccentric shaft and the crankshaft 30 are separately assembled, and the intermediate bearing plate 40 is slidingly fitted with the intermediate shaft, the reliability of the multi-cylinder rotary compressor 1 can be improved. It can also be improved in terms of expanding the operating speed, increasing the capacity of the compressor, and improving the compression efficiency.

In a specific embodiment of the present utility model, in the separately assembled eccentric shaft and the crankshaft 30, the cylindrical hole provided in the eccentric shaft and the crankshaft 30 can be connected by any one of embedding, press-fitting, shrink fitting, and laser welding. Way. That is to say, the eccentric shaft can be assembled on the crankshaft 30 by embedding, press-fitting, heat-fitting or laser welding.

According to some embodiments of the present invention, a torque transmission member is provided between the cylindrical hole provided in the eccentric shaft and the crankshaft 30 . For example, as shown in FIGS. 3-6 , there is a key 37 between the eccentric shaft and the crankshaft 30 , and the key 37 is a means for transmitting the rotational moment of the crankshaft 30 to the eccentric shaft.

In some embodiments of the present utility model, the outer diameter of any eccentric shaft is De, the outer diameter of the main shaft 31 is Dm, the outer diameter of any intermediate shaft is Dc, the outer diameter of the auxiliary shaft 33 is Ds, De≧Dc ≧ Dm or Ds. That is, De≧Dc≧Dm, or De≧Dc≧Ds.

Optionally, the outer diameter of the auxiliary shaft 33 is smaller than the outer diameter of the main shaft 31 .

In some embodiments of the present invention, the high-pressure gas discharged from at least one compression chamber passes through the intermediate muffler 50 b formed inside the intermediate bearing plate 40 . That is, the intermediate bearing plate 40 has a cavity inside to define an intermediate muffler 50b, and high-pressure gas discharged from at least one compression chamber enters the intermediate muffler 50b. Thereby, the noise of the multi-cylinder rotary compressor 1 can be reduced.

Furthermore, the intermediate muffler 50b is provided with an exhaust device opening to at least one compression chamber. That is to say, there is an exhaust device in the intermediate muffler 50b, and the exhaust device can open to at least one compression chamber. For example, in the example shown in FIG. 11 , in the middle muffler 50b, there are exhaust holes opening to the two compression chambers respectively, and exhaust valves 71 are respectively arranged in the two exhaust holes, and the two exhaust valves 71 are connected to each other. There is a coil spring 72 to control the stroke amount of the exhaust valve 71 .

In some embodiments of the present invention, there is a channel that starts from one suction pipe connected to the middle bearing plate 40 and divides flow to two compression chambers connected to the middle bearing plate 40 . That is to say, the low-pressure gas enters the channel from the suction pipe, and is divided into the two compression chambers through the channel.

According to a preferred embodiment of the present invention, at least one annular groove 46 is provided along the bearing inner diameter of the intermediate bearing plate 40 , and each annular groove 46 opens a hole in the end face of the intermediate bearing plate 40 . In other words, at least one annular groove 46 may be provided on the intermediate bearing plate 40 , and each annular groove 46 has an opening on the end surface of the intermediate bearing plate 40 . For example, in the example of FIG. 8 , the intermediate bearing plate 40 has two annular grooves 46 , and the two annular grooves 46 are respectively provided on two opposite end surfaces of the intermediate bearing plate 40 . Therefore, by providing the annular groove 46, it is possible to prevent the load of the intermediate shaft from concentrating on the open end of the inner diameter 40a of the intermediate bearing plate 40, and to avoid the increase of wear from the open end.

In some specific embodiments of the present invention, any one of a bush 65 , a rolling bearing and a needle bearing 66 is provided in the inner diameter of the bearing of the intermediate bearing plate 40 . Thereby, the wear resistance of the intermediate shaft can be improved.

According to some embodiments of the present invention, the intermediate bearing plate 40 is a thrust sliding surface supporting the load of the crankshaft 30 . For example, there is a small gap C2 between the upper end of the second eccentric shaft 35 and the lower end surface of the intermediate bearing plate 40, so that the up and down movement of the second eccentric shaft 35 is limited so as not to be too large.

Optionally, the separately assembled eccentric shaft is a powder metallurgy formed part or a forged formed part. That is to say, the eccentric shaft can be shaped by powder metallurgy or forging.

The multi-cylinder rotary compressor according to several specific embodiments of the present utility model will be described in detail below with reference to FIGS. 1-15 .

Example 1:

In the multi-cylinder rotary compressor 1 shown in FIG. 1 , the outer circumference of a motor 4 and the outer circumference of an intermediate bearing plate 40 provided at the center of a compression mechanism unit 5 are fixed to the inner diameter of a cylindrical housing 2 . The compression mechanism part 5 is composed of: the first cylinder 11 and the second cylinder 21, the main bearing 43 combined with it and the auxiliary bearing 45, the intermediate bearing plate 40 combined with it between the first cylinder 11 and the second cylinder 21, and the three A crankshaft 30 with sliding bearings and so on. In addition, the motor rotor 4 a is fixed in the crankshaft 30 .

The exhaust pipe 3 connected to the upper end of the housing 2, the intermediate suction pipe 41 connected to the outer periphery of the intermediate bearing plate 40 and the liquid reservoir 60 are respectively connected to the high pressure side and the low pressure side of the refrigeration cycle device. The main bearing 43 and the sub bearing 45 are equipped with a 1st muffler 43a and a 2nd muffler 45a, respectively. The internal pressure of the housing 2 in FIG. 1 is the high pressure side, but the internal pressure of the housing 2 in the present invention may be the low pressure side.

Fig. 2 is the XX section of Fig. 1 . The second compression chamber 21a provided in the center of the second cylinder 21 includes a second piston 52 that eccentrically rotates by the second eccentric shaft 35 (eccentricity e), and a second slide that reciprocates by the eccentric operation of the piston. 54. The maximum stroke (S) of the second sliding piece 54 is twice the eccentricity e. As described later, the utility model can increase the eccentricity (e) of the eccentric shaft. Therefore, the characteristic is that the displacement of the compression chamber can be enlarged due to the increase of the maximum stroke amount (S) of the slide plate.

The secondary shaft 33 and the second eccentric shaft 35 are separately assembled. Therefore, the rotational moment of the crankshaft 30 can be transmitted to the countershaft 33 through the key 37 indicated by a dotted line, and the second eccentric shaft 35 rotates clockwise. In addition, the second piston 52 revolves along the inner diameter of the second compression chamber 21a. Simultaneously, the second slide plate 54 is reciprocating. The second thrust 35 a provided on the second eccentric shaft 35 can support the load of the crankshaft 30 and rotate and slide on the plane of the sub-bearing 45 . In addition, the swing type in which the piston and the slide plate are integrated is also applicable.

FIG. 3 is a longitudinal sectional view of the compression mechanism unit 5 . In addition, the two mufflers shown in FIG. 1 and the exhaust devices housed in these mufflers and provided in the main bearing 43 and the sub-bearing 45 are not shown in the figure. Between the first cylinder 11 and the second cylinder 21, there is an intermediate bearing plate 40 corresponding to a conventional intermediate partition plate (or intermediate plate), and an intermediate intake pipe 41 is connected to the outer periphery thereof. The channel 41a and the channel 41b that the intermediate air intake pipe 41 divides are respectively connected to the first compression chamber 11a and the second compression chamber 21a, and are opened.

This design can increase the height of the intermediate bearing plate 40 . Therefore, the bearing length of the intermediate bearing plate 40 and the inner diameter of the intermediate suction pipe 41 can be enlarged. The enlarged effect of the middle air suction pipe 41 is to ensure the necessary air suction passages in the two compression chambers and divide them.

The first compression chamber 11a and the second compression chamber 21a respectively have a first piston 51, a second piston 52, and slide plates (not shown). These pistons are driven by a first eccentric shaft 34 and a second eccentric shaft 35 of the crankshaft 30 . The crankshaft 30 is composed of a main shaft 31 , a first eccentric shaft 34 , an intermediate shaft 32 , a second eccentric shaft 35 , and a counter shaft 33 in this order. The main shaft 31, the intermediate shaft 32, and the auxiliary shaft 33 slide with the main bearing 43, the intermediate bearing inner diameter 40a, and the auxiliary bearing 45, respectively. These element parts slide with 5 screws. These element parts are respectively fixed to the intermediate bearing plate 40 by five screws 43b and 45b.

Repeated loads due to compression and centrifugal force of the first piston 51 and second piston 52 rotating at a phase angle of 180 degrees are supported by the intermediate bearing plate 40 and the main bearing 43, and the intermediate bearing plate 40 and the sub bearing 45, respectively. In addition, in air-conditioning rotary compressor of 1.5HP, repetition load is approximately 200Kgf each. In the present invention, by adding the intermediate bearing plate 40 slidingly supported by the intermediate shaft 32, the runout of the sliding parts linked with the crankshaft 30 and the crankshaft 30 can be reduced, and the surface pressure generated by each bearing can be greatly reduced.

Here, the outer diameter of the sub-shaft 33 is 10 to 15% smaller than that of the main shaft 31, and the eccentricity of the second eccentric shaft 35 assembled separately from the sub-shaft 33 and the first eccentric shaft 34 integrated with the main shaft 31 are equivalent. , or make adjustments to increase the amount of eccentricity compared to conventional ones.

The lubricating oil supplied to the oil hole 32b from the axial center hole 30a (FIG. 5) penetrating inside the crankshaft 30 flows out to the oil key 32a provided in the intermediate shaft 32, and lubricates the sliding surface of the intermediate shaft 32 and the inner diameter 40a of the intermediate bearing plate. . After that, it flows out to the inner diameters of the first piston 51 and the second piston 52 to lubricate the sliding surfaces of the pistons. In addition, the oil groove 32a may be arranged on the inner diameter 40a side of the intermediate bearing plate.

The load on the crankshaft 30 that fixes the motor rotor 4a is the thrust load of the second thrust 35a. There is a small clearance C1 between the first thrust upper portion 34a provided on the first eccentric shaft 34 and the lower end surface of the main bearing 43, so as to prevent the crankshaft 30 from excessive vertical movement. In addition, there is a small gap C2 between the upper end of the second eccentric shaft 35 and the lower end surface of the intermediate bearing plate 40, so as not to limit the vertical movement of the second eccentric shaft 35 too much.

FIG. 4 shows the intermediate bearing plate assembly 8 . This assembling method will be described. First, the secondary shaft 33 of the crankshaft 30 shown in FIG. 5 passes through the intermediate bearing plate inner diameter 40 a of the intermediate bearing plate 40 . Next, the key 37 fixed to the secondary shaft 33 along the key groove 35e provided in the inner diameter 35b of the second eccentric shaft 35 after the key 37 shown in FIG. 6 is inserted into the key groove 33a of the secondary shaft 33 is inserted. According to the above steps, the intermediate bearing plate assembly 8 is completed. In this way, if the intermediate bearing plate assembly 8 is completed in advance, the assembly process of the compression mechanism section 5 described later will be relatively easy. In addition, the crankshaft 30 shown in FIG. 5 is rotated by 90 degrees with respect to the crankshaft 30 shown in FIG. 3 or 4 .

The auxiliary shaft 33 and the second eccentric shaft 35 are combined by sliding, press-fitting or shrink fit, and the key 37 is a means for transmitting the rotational moment of the crankshaft 30 to the second eccentric shaft 35 . In addition, if the second eccentric shaft 35 is molded by powder metallurgy or forging, the processing of the second eccentric shaft 35 is relatively easy.

In addition, a method of laser welding the crankshaft 30 and the second eccentric shaft 35 in a CO2 atmosphere or a YAG atmosphere can also be used. In this laser welding, there is only a small bulge in the laser welded part. Therefore, laser irradiation on the outer diameter sliding surface of the eccentric shaft should be avoided, such as welding along the bottom surface of the relatively thin oil groove 35c. In addition, it is also advantageous to add a groove for welding to the eccentric shaft.

Next, the main points of the method of assembling the compression mechanism unit 5 will be described. First, the main shaft hole of the main bearing 43 is aligned with the first compression chamber 11a of the first cylinder 11, and after being temporarily fixed, the first sliding piece 53 and the first piston 51 are respectively accommodated in the sliding piece groove of the first cylinder 11 and the first piston 51. 1 in the compression chamber 11a.

Next, after the main shaft 31 of the pre-finished intermediate bearing plate assembly 8 passes through the main shaft hole provided in the middle of the main bearing 43, the intermediate shaft 32 and the inner diameter 40a of the intermediate bearing plate are aligned, and the intermediate bearing plate 40 and the first cylinder 11 are pre-fixed. . Thereafter, it is assembled according to the assembly process of the conventional multi-cylinder rotary compressor.

Here, the minimum dimension (w), which is the difference between the inner diameter 40a of the intermediate bearing plate and the outer diameter of the minimum revolution of the first piston 51 shown in FIG. Dimensions necessary for gas leakage (low pressure side). In the conventional multi-cylinder rotary compressor, in order to establish the intermediate bearing plate assembly 8 shown in FIG. 4, the inner diameter of the intermediate bearing plate cannot be larger than any one of the outer diameters of the two eccentric shafts. That is to say, in the previous design, due to the limitation of the minimum size (w), the eccentricity (e) of the eccentric shaft cannot be large.

On the other hand, in Embodiment 1, the inner diameter 40a of the intermediate bearing plate can be equivalent to the outer diameter of the main shaft 31 or the auxiliary shaft 33 by separately assembling the second eccentric shaft 35 . Therefore, the amount of eccentricity (e) can be enlarged. Due to this effect, the displacement can be expanded without changing the inner diameter size of the compression chamber or the size of the crankshaft. Due to this effect, the degree of freedom in designing the inner diameter of the compression chamber and the outer diameter of the piston increases, enabling optimization of compression efficiency and expansion of cooling capacity.

In this way, the utility model separates and assembles the second eccentric shaft 35, and adds an inner diameter 40a of the intermediate bearing plate to the intermediate bearing plate 40, which not only improves the reliability of the multi-cylinder rotary compressor, but also can expand the operation. Many improvements have been made in terms of speed, increase in compressor capacity, and improvement in compression efficiency.

Example 2:

Example 2 shown in FIG. 7 is related to the improvement of the sliding loss of the intermediate shaft 32 by reducing the diameter of the intermediate shaft 32 . Compared with the first compression chamber 11a, the inner diameter and height of the second compression chamber 21a are small, and the displacement is small. Under such design conditions, the intermediate shaft 32 can be reduced in diameter relative to the main shaft 31, and the sliding loss generated between the shaft and the bearing can be reduced.

In Example 2, the inner diameter 40 a of the intermediate shaft 32 and the intermediate bearing plate is reduced to be equivalent to the outer diameter of the auxiliary shaft 33 . As a result, the sliding loss can be improved without impairing the wear reliability of the intermediate shaft 32 . In addition, the outer diameter of the intermediate shaft 32 can be selected between the outer diameter of the main shaft 31 and the outer diameter of the auxiliary shaft 33 .

Example 3:

Embodiment 3 is concerned with the improvement of the bearing performance of the intermediate bearing plate 40 . In FIG. 8, an annular groove 46 opening along the inner diameter 40a of the intermediate bearing plate is added. The annular groove 46 prevents the load of the intermediate shaft 32 from concentrating on the opening end of the inner diameter 40a of the intermediate bearing plate, avoiding the expansion of wear from the opening end. Furthermore, one of the annular grooves 46 may optionally be omitted due to the wear mode of the inner diameter 40a of the intermediate bearing plate.

Fig. 9 press-fits the sliding bearing (bushing) 65 into the middle bearing plate hole 40c. The self-lubricating surface treatment material included in the sliding bearing 65 is effective in the initial run-in of the intermediate shaft 32 and the reduction of the oil film for a short time, and can improve the wear resistance of the intermediate shaft 32 .

Fig. 10 press-fits the needle bearing 66 into the middle bearing plate hole 40c. As a result, the problem of wear can be avoided even in a short period of non-lubricated operation. This improvement in wear resistance is advantageous, for example, in terms of high-speed operation of 150rps or reliability assurance of 5-10HP models. In addition, a general rolling bearing can be applied to a design in which the expansion of the intermediate bearing plate hole 40c is allowed.

Example 4:

The embodiment 4 shown in FIG. 11 is that two sets of divided middle plates 50 a which are plane-symmetrical are assembled and combined with bushings to form the middle bearing plate 50 . Through this assembly, the inside of the intermediate bearing plate 50 constitutes the intermediate muffler 50b.

There are two options for how to use the intermediate muffler 50b. (A) Each divided intermediate plate 50a is equipped with an exhaust device that opens to the first compression chamber 11a and the second compression chamber 21a, as a method of exhaust muffler for the compression chamber; 2 mufflers or the method of the 3rd muffler of the 1st muffler 43a.

Fig. 11 shows (A) method. The intermediate muffler 50b includes a first exhaust hole 70a and a second exhaust hole 70b that open to the first compression chamber 11a and the second compression chamber 21a, respectively. A circular exhaust valve 71 is disposed in each of these exhaust holes, and a coil spring 72 for controlling the stroke amount of the valve is disposed between them.

The high-pressure gas compressed in the first compression chamber 11a and the second compression chamber 21a is discharged into the intermediate muffler 50b, and flows out into the first muffler 43a (FIG. 1) through the transverse channel 50c and the vertical channel 50d. At this time, it merges with the gas exhausted from the exhaust hole provided in the main bearing 43 .

In the design of (B), the high-pressure gas discharged from the second muffler 45a or the first muffler 43a passes through the intermediate muffler 50b. Therefore, the intermediate muffler 50b is an additional noise reduction muffler.

In the option (A), each of the first compression chamber 11 a and the second compression chamber 21 a has two exhaust holes. The addition of exhaust holes is very important as a means to reduce exhaust pressure loss during high-speed operation above 90rps. In addition, if the capacity of one of the two compression chambers is small, the exhaust device for the compression chamber can be omitted.

In the option (B), the middle muffler 50b made of a thick casting can exhibit a large noise reduction effect. In addition, the arrangement volume of the muffler of the multi-cylinder rotary compressor can be limited to a small size, so the use of the intermediate muffler 50b housed in the intermediate bearing plate 50 is advantageous.

In the assembly of the two divided intermediate plates 50a and the bushing 67, after the bushing 67 is pressed into the center of the two sets of divided intermediate plates 50a, both ends of the bushing 67 are stamped to connect the two sets of divided intermediate plates 50a. At this time, both ends of the bush 67 may have flanges 67a. Thereafter, machining of the inner diameter of the bush 67 is performed. In addition, the two air cylinders connected to both sides of the intermediate bearing plate 50 can press the two divided intermediate plates 50a.

Example 5:

Embodiment 5 shown in FIG. 12 , the outer circumference of the first cylinder 11 is fixed at the inner diameter of the housing 2 . In addition, the first eccentric shaft 34 is separately combined with the crankshaft 30 . The first suction pipe 55 and the second suction pipe 56 are connected to the first compression chamber 11a and the second compression chamber 21a, respectively.

Embodiment 5. In order to complete the intermediate bearing plate assembly 8, the first eccentric shaft 34 is installed in front of the crankshaft 30, and the inner diameter 40a of the intermediate bearing plate needs to pass through the main shaft 31. Therefore, the inner diameter 40 a of the intermediate bearing plate and the outer diameter of the intermediate shaft 32 must be equal to or greater than the outer diameter of the main shaft 31 . However, for example, in Embodiment 1, it is established that the intermediate shaft 32≧the auxiliary shaft 33 . In addition, the basic requirement of the present invention is that the outer diameter of the eccentric shaft≧the outer diameter of the intermediate shaft. Therefore, the inequality that the outer diameter of the eccentric shaft ≧ the outer diameter of the intermediate shaft ≧ the outer diameter of the main shaft or the outer diameter of the auxiliary shaft is established.

Here, the first thrust 34 b added to the first eccentric shaft 34 is the thrust of the crankshaft 30 . Therefore, the first thrust 34b rotates and slides on the plane of the intermediate bearing plate 50 . In addition, the second thrust 35 a of the second eccentric shaft 35 does not receive the load of the crankshaft 30 and does not slide on the surface of the sub-bearing 45 .

By changing the thrust sliding surface to the intermediate bearing plate 40, an annular groove 46 can be added on the auxiliary bearing 45. In addition, if necessary, an annular groove 46 may be added to the main bearing 43 . These annular grooves 46, like the annular grooves 46 of FIG. 8, can improve the wear of the auxiliary bearing 45 and the main bearing 43, and the auxiliary shaft 33 and the main shaft 31 which are slidably coupled with them.

Through the bearing pressure equalizing hole 44 of the annular groove 46 and the bearing air hole 40b of the intermediate bearing plate 50, the pressure of the inner diameter of the two pistons is equivalent to the internal pressure of the housing 2, and the pressure of the crankshaft 30, the first piston 51 and the second piston 52 The oil supply pressure is the same for each sliding surface.

Embodiment 6:

13 shows a design example of the intermediate bearing plate assembly 9 used in a 3-cylinder rotary compressor, in which the crankshaft 30 is assembled separately from the second eccentric shaft 35 and the third eccentric shaft 36 in addition to the first eccentric shaft 34 . Therefore, between the third eccentric shaft 36 and the first eccentric shaft 34 , or between the first eccentric shaft 34 and the second eccentric shaft 35 , the assembly of the respective intermediate bearing plates 40A and 40B is established.

As in the fifth embodiment, the intermediate bearing plate 40A can pass through the main shaft 31 , so the outer diameter of the intermediate shaft 32A is equal to or greater than that of the main shaft 31 . One intermediate bearing plate 40B passes through the auxiliary shaft 33, so the outer diameters of the two intermediate shafts are equivalent to the outer diameter of the intermediate shaft 32A, or the intermediate shaft 32B can be made smaller in diameter than the intermediate shaft 32A.

Moreover, as shown in FIG. 14, if the first eccentric shaft 34 and the second eccentric shaft 35 are assembled separately without separating the third eccentric shaft 36, the outer diameter of the intermediate shaft 32A and the intermediate shaft 32B and the outer diameter of the secondary shaft 33 after being made smaller It can be the same. Alternatively, these intermediate shaft diameters may be larger than the outer diameter of the auxiliary shaft 33 . The assembly method is as follows: from the countershaft 33 side to the third eccentric shaft 36, ① pass the intermediate bearing plate 40A, then assemble the first eccentric shaft 34 in the crankshaft 30, ② put the second cylinder 21 containing the piston 52 Insert the first eccentric shaft 34, ③ insert the intermediate bearing plate 40B, and then assemble the second eccentric shaft 35 into the crankshaft 30 in this order.

In addition, according to the definition of Claim 1, the first cylinder 11 is arranged at the position of the third eccentric shaft 36 , the second cylinder 21 is arranged at the position of the first eccentric shaft 34 , and the third cylinder is arranged at the position of the second eccentric shaft 35 . Therefore, in the compression mechanism unit, the first cylinder 11 has the main bearing 43 and the third cylinder has the sub-bearing 45 .

According to embodiment 6, the 3-cylinder rotary compressor with 4 bearings that is made up of 3 cylinders, the main bearing 43 and the auxiliary bearing 45 and 2 intermediate bearing plates has just been completed. In addition, it is possible to further increase the number of eccentric shafts and cylinders. Even a multi-cylinder rotary compressor with more than 3 cylinders can be completed by the disclosed technology of the present utility model.

Embodiment 7:

FIG. 15 , a frame 48 is fixed in the upper space of the motor 4 and the inner periphery of the housing 2 . The auxiliary shaft 31 a formed in the main shaft 31 is in sliding engagement with an upper end bearing 48 a provided at the center of the bearing frame 48 . The upper end bearing 48a is the 4th bearing (multiple cylinders), or the 5th bearing (3 cylinders), and the vibration of the motor rotor 4a and the abrasion of the upper end of the main shaft 31 can be prevented. The upper end bearing 48a is necessary especially for large multi-cylinder rotary compressors.

Industrial Utilization Possibility

The multi-cylinder rotary compressor of the present invention can be mounted in air conditioners, refrigeration devices, water heaters, vehicle-mounted refrigeration or air conditioning devices, and the like.

In summary,

The problems to be solved by the utility model are as follows:

The crankshaft of the multi-cylinder rotary compressor has a long inter-shaft length (the length between the main shaft and the counter shaft), the crankshaft is weak in rigidity, and the rotational vibration is large. Therefore, during high-speed operation, etc., there is a problem that the main shaft or the sub shaft may wear out.

A specific means adopted to solve the above problems:

The second eccentric shaft 35 and the crankshaft 30 are separately assembled. First, the intermediate shaft 32 of the crankshaft 30 without the second eccentric shaft 35 is inserted into the intermediate bearing plate inner diameter 40 a provided at the center of the intermediate bearing plate 40 . Thereafter, the second eccentric shaft 35 is connected to the sub shaft 33 . Therefore, the main shaft 31, the intermediate shaft 32, and the sub shaft 33 of the crankshaft 30 slide at three positions of the main bearing 43, the intermediate bearing plate 40, and the sub bearing 45, respectively. There is no vibration of the crankshaft 30 at all, and the wear problem can be solved.

The effect of the utility model:

The utility model, by slidingly supporting the intermediate bearing plate of the intermediate shaft of the crankshaft, (1) improves the reliability of the crankshaft, realizes high-speed operation, and increases the size of the compressor; (2) greatly reduces the central aperture of the intermediate bearing plate, thereby realizing the improvement of compression efficiency , the displacement increases. The utility model requires less additional parts, and the compression part is easy to assemble. In addition, the previous centering process can be borrowed.

In addition, it can be applied not only to hermetic rotary compressors, but also to conveyor-driven open rotary compressors, horizontal multi-cylinder rotary compressors, and swing-type multi-cylinder rotary compressors. In multi-cylinder rotary compressors where the shell pressure is low.

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

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

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

Claims (13)

1. a multi-cylindrical rotary compressor, is characterized in that, comprising:

From the 1st cylinder to several cylinders that the order of N cylinder forms;

The compression chamber possessed in respective cylinder;

The piston of eccentric operating is carried out in described each compression chamber;

The slide plate moved back and forth with described each piston synchronous;

Bent axle, described bent axle possess drive the jack shaft possessed in the middle of the eccentric shaft of described each piston and adjacent described eccentric shaft, the main shaft carrying out sliding with the main bearing that described 1st cylinder combines, the supplementary bearing that is combined with described N cylinder carries out the countershaft that slides;

At least 1 described eccentric shaft with described bent axle for being separated assembly type;

The jack shaft board possessed in the middle of adjacent described cylinder and described jack shaft are slidably matched.

2. multi-cylindrical rotary compressor according to claim 1, is characterized in that,

Being separated in modular described eccentric shaft and described bent axle, the connection of the cylindrical hole that possesses in described eccentric shaft and described bent axle can use any one mode in embedding, press-in, hot jacket, laser bonding.

3. multi-cylindrical rotary compressor according to claim 1, is characterized in that, possesses moment transferring member in described eccentric shaft between the cylindrical hole possessed and described bent axle.

4. multi-cylindrical rotary compressor according to claim 1, is characterized in that,

The external diameter of eccentric shaft described in any one is De, the external diameter of described main shaft is Dm, the external diameter of jack shaft described in any one is Dc, the external diameter of described countershaft is Ds, De≤Dc≤Dm or De≤Dc≤Ds.

5. multi-cylindrical rotary compressor according to claim 1, is characterized in that, the external diameter of described countershaft is less than the external diameter of described main shaft.

6. multi-cylindrical rotary compressor according to claim 1, is characterized in that, from the central silencer that the pressurized gas of compression chamber discharge described at least one are consisted of described intermediate bearing intralamellar part.

7. multi-cylindrical rotary compressor according to claim 6, is characterized in that,

The venting gas appliance to compression chamber opening described at least one is possessed in described central silencer.

8. multi-cylindrical rotary compressor according to claim 1, is characterized in that,

Possess from connecting 1 sucking pipe of described jack shaft board, to the passage of two that connect described jack shaft board described compression chamber shuntings.

9. multi-cylindrical rotary compressor according to claim 1, is characterized in that, the bearing bore diameter along described jack shaft board possesses at least one circular groove, and each circular groove is to the end face perforate of described jack shaft board.

10. multi-cylindrical rotary compressor according to claim 1, is characterized in that,

Possess any one of lining, rolling bearing and nail bearing in the bearing bore diameter of described jack shaft board.

11. multi-cylindrical rotary compressors according to claim 1, is characterized in that,

Described jack shaft board is the thrust slip surface supporting described bent axle load.

12. multi-cylindrical rotary compressors according to claim 1, is characterized in that, the described eccentric shaft being separated assembling is powder metallurgic method profiled member or forging method profiled member.

13. multi-cylindrical rotary compressors according to claim 1, is characterized in that, carry out between the spindle end bearing of sliding support and described main bearing to the end of described main shaft, possess the motor driving described main shaft.