CN101387298B - Double cylinders rotary compressor and freezing cycle device using the same - Google Patents

Abstract

The invention provides a double cylinder rotary compressor and a refrigerating cycle device using the same. The double cylinder rotary compressor (1) is provided with a compressing mechanism part, which guides working air into two cylinders for compression from an induction pipe (63) arranged on a separator for separating the two cylinders, through two suction passages (70, 71) separated from a fork part arranged in the separator. When exit area of the suction passages in a separator area is Ad and the smallest area of the induction pipe is As, wherein Ad/As >= 1, each angle theta formed by an axis of the induction pipe and the axis of the two suction passages satisfies 28 degrees <= theta <= 43 degrees.

Description

Two-cylinder rotary compressor and refrigeration cycle device using the same

technical field

The present invention relates to a two-cylinder rotary compressor and a refrigerating cycle device using the compressor, and more particularly to a rotary compressor having an improved shape of a suction passage and a refrigerating cycle device using the compressor.

Background technique

Conventionally, in air conditioners, refrigerators, etc., a rotary compressor is often used to compress a refrigerant. Such a rotary compressor is provided with a compression mechanism section having a cylinder, a roller mounted on a rotating shaft and rotating eccentrically in the cylinder, vanes that divide a suction chamber and a compression chamber, and a two-cylinder rotary compressor is composed of a partition. The board divides into 2 cylinders.

The gap between the outer peripheral surface of the drum and the cylinder generates the most leakage loss of the rotary compressor. Therefore, in order to reduce the leakage loss to improve the efficiency of the compressor, it should be considered to make the thickness of the cylinder thinner.

However, for a two-cylinder rotary compressor, if the thickness of the cylinder is reduced, the diameter of the suction pipe connected to the cylinder must be reduced. Reducing the diameter of the suction pipe will increase the suction resistance and cause excessive expansion. The problem of large losses.

In order to solve this problem, a two-cylinder rotary compressor has been proposed, which is provided with a compression mechanism section having two cylinders arranged side by side with a partition interposed therebetween, and rotating eccentrically in each cylinder. The drum discharges the working gas sucked in through the suction port from the discharge port, and the suction pipe communicating with the suction port of each cylinder is connected to the partition plate. For example, see Japanese Laid-Open Patent Document, JP-A-9-250477 (hereinafter referred to as Patent Document 1).

However, in the two-cylinder rotary compressor described in Patent Document 1, a high COP (Coefficient of Performance) cannot be obtained because the branching angle and area of the suction passage for sucking refrigerant gas are not improved. ).

In addition, a two-cylinder rotary compressor has been proposed, in which the thickness of the partition is made thicker than that of the two cylinders, and one suction passage extending from the side opening to the center is formed on the partition, A communication hole branching from the suction passage to both sides and reaching the suction chamber is formed, and a suction pipeline passing through the airtight container is connected to the suction passage. For example, see Japanese Laid-Open Patent Document, JP-A-2003-161278 (hereinafter referred to as Patent Document 2).

However, the two-cylinder rotary compressor described in Patent Document 2 is also the same as the two-cylinder rotary compressor described in Patent Document 1, because the branching angle and area of the suction passage for sucking refrigerant gas are not improved. , therefore, a high COP (coefficient of performance) cannot be obtained.

[Patent Document 1] JP-9-250477 Gazette

[Patent Document 2] JP-2003-161278 Gazette

Contents of the invention

Therefore, the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a two-cylinder rotary compressor capable of obtaining a high COP.

Another object of the present invention is to provide a refrigeration cycle apparatus using a twin-cylinder rotary compressor capable of achieving a high COP.

In order to achieve the above object, the two-cylinder rotary compressor related to the present invention includes a compression mechanism part and a rotary drive part. The first cylinder and the second cylinder, the first cover member and the second cover member provided on the end surface of these cylinders on the side opposite to the partition plate and covering the cylinder chamber, have two eccentric parts, and the cover member The rotary shaft supported by rotation and the roller engaged with the eccentric part, the compression mechanism part passes the working gas from one suction pipe connected to the partition plate through the branch provided in the partition plate The 2 suction passages that are partly drawn are introduced into the two cylinder chambers, and it is characterized in that: the outlet area of the suction passage on the two end faces of the partition plate is Ad and the minimum cross-sectional area of the suction pipe is In the case of As, there is a relationship of Ad/As≧1, and each angle θ formed by the axis line of the suction pipe and the axis lines of the two suction channels is 28°≦θ≦43°.

In addition, the refrigeration cycle apparatus using the twin-cylinder rotary compressor of the present invention is characterized in that it is formed by sequentially connecting the above-mentioned twin-cylinder rotary compressor, condenser, expansion device, and evaporator with pipelines.

According to the twin-cylinder rotary compressor of the present invention, it is possible to provide a twin-cylinder rotary compressor capable of obtaining a high COP.

In addition, according to the refrigeration cycle apparatus using the twin-cylinder rotary compressor of the present invention, it is possible to provide a refrigeration cycle apparatus using the twin-cylinder rotary compressor capable of obtaining a high COP.

Description of drawings

Fig. 1 is a schematic view of a refrigeration cycle apparatus employing a twin-cylinder rotary compressor according to a first embodiment of the present invention.

Fig. 2 is a plan view of a partition used in the two-cylinder rotary compressor according to the first embodiment of the present invention.

Fig. 3 is a longitudinal sectional view of a partition used in the two-cylinder rotary compressor according to the first embodiment of the present invention.

Fig. 4 is a graph showing the correlation between the crank angle and the suction flow rate of a separator used in a two-cylinder rotary compressor having the same structure as that of the present invention.

Fig. 5 is a correlation diagram between As/Ad and COP of the twin-cylinder rotary compressor according to the first embodiment of the present invention.

6 is a correlation diagram of θ and COP formed by the axis line of the suction pipe and the axis line of the suction passage of the twin-cylinder rotary compressor according to the first embodiment of the present invention.

Fig. 7 is a plan view of a partition used in the two-cylinder rotary compressor according to the first embodiment of the present invention.

Fig. 8 is a longitudinal sectional view of a partition used in the two-cylinder rotary compressor according to the first embodiment of the present invention.

Fig. 9 is a longitudinal sectional view of a two-cylinder rotary compressor of a comparative example.

Fig. 10 is a plan view of the partition plate of the two-cylinder rotary compressor seen in the direction of arrow A in Fig. 9 .

Fig. 11 is a longitudinal sectional view of a partition used in a two-cylinder rotary compressor according to a second embodiment of the present invention.

Fig. 12 is a longitudinal sectional view of a partition used in a twin-cylinder rotary compressor according to a third embodiment of the present invention.

Symbol Description

1...Double-cylinder rotary compressor 2...Airtight container 3...Electric motor department

4...rotating shaft 41, 42...eccentric shaft part 5...compression mechanism part

51...1st cylinder 52...2nd cylinder 53...partition

53c…End face 54…Main bearing 55…Auxiliary bearing

58...1st drum 59...2nd drum 63...suction pipe

64...suction port 68, 69...compression chamber 70...suction channel

70a...Channel exit 71...Suction channel 71a...Channel exit

72...Branch part 73, 74...On-off valve 75...1st muffler chamber

76...2nd muffler room 21...refrigeration cycle device 22...condenser

23...expansion device 24...evaporator

Detailed ways

Hereinafter, a two-cylinder rotary compressor and a refrigeration cycle apparatus using the compressor according to a first embodiment of the present invention will be described with reference to the drawings.

Fig. 1 is a schematic view of a refrigeration cycle apparatus employing a twin-cylinder rotary compressor according to a first embodiment of the present invention.

As shown in FIG. 1 , the refrigerating cycle device 21 of the present invention is connected with the double-cylinder rotary compressor 1 of the present invention, the condenser 22 , the expansion device 23 and the evaporator 24 in sequence through pipelines.

The two-cylinder rotary compressor 1 of the present invention is provided with an airtight container 2 , and a motor part 3 and a compression mechanism part 5 driven to rotate by the motor part 3 through a rotating shaft 4 are accommodated in the airtight container 2 .

The motor section 3 is constituted by a stator 31 and a rotor 32 that rotates within the stator 31 and is mounted on one end side of the rotary shaft 4 .

The compression mechanism unit 5 is composed of a first cylinder 51 and a second cylinder 52 through which the rotating shaft 4 penetrates, and the first and second cylinders 51 and 52 are separated by a partition plate 53 and are independent from each other.

Both ends of the rotating shaft 4 are rotatably supported by a main bearing 54 serving as a cover covering the first cylinder 51 and the second cylinder 52 and by a sub bearing 55 .

The first and second cylinders 51 and 52 are formed with substantially the same thickness.

The thickness of the partition plate 53 is greater than the thickness of the first and second cylinders 51 and 52, and the first and second cylinders 51 and 52 are installed through the main bearing 54 side and the auxiliary bearing 55 side by clamping the partition plate 53. Bolts 56, 57 are integrally mounted together in a threaded manner.

On the other end side of the rotating shaft 4, two eccentric shaft portions 41, 42 which are mutually shifted in phase by 180 degrees are provided at portions corresponding to the first and second cylinders 51, 52. The first roller 58 and the second roller 59 arranged in the first and second cylinders 51, 52 cooperate with the eccentric shaft parts 41, 42, and each roller 58, 59 is rotated by each eccentric shaft part 41, 42, Produces eccentric rotation out of phase by 180 degrees.

The main bearing 54 and the sub-bearing 55 are provided with discharge holes 61 , 62 communicating with a discharge pipe 60 whose outlet is directed into the airtight container 2 . In addition, vanes 67 are provided on the first and second cylinders 51 and 52 through springs 66 and the outer peripheral surfaces of the rollers 58 and 59 are constantly in contact with each other, thereby forming compression chambers for compressing the working gas through the respective rollers 58 and 59 and the vanes 67 68, 69. The working gas uses HFC (Hydro Fluoro Carbon) refrigerant containing R32.

As shown in FIGS. 2 and 3 , the partition plate 53 is formed in a substantially disc shape, and has a shaft through hole 53 a through which the rotating shaft 4 penetrates and a threaded hole 53 b through which the mounting bolts 56 and 57 are screwed. In addition, on the partition plate 53, a suction hole 53d with one end leading to the outer peripheral surface is provided in the horizontal direction, and a suction pipe 63 passing through the airtight container 2 to communicate with the evaporator 24 of the refrigeration cycle device 21 is connected to the suction hole 53d. The other end side of the suction hole 53d is divided into upper and lower two by a branch portion 72 to form inclined suction passages 70 and 71 . The passage outlet 70a of the suction passage 70 on the upper side of one branch is connected and communicated with the suction port (not shown) formed on the first cylinder 51, and the passage outlet 71a of the suction passage 71 on the other lower side is connected to the first cylinder 51. The suction ports 64 of the two cylinders 52 are connected and communicated.

The area (the area shown by hatching in FIG. 2 ) Ad of the passage outlets 70a, 71a of the above-mentioned suction passages 70, 71 in both end faces 53c, 53c of the partition plate 53 is set so that the minimum suction pipe 63 When the area is As, there is a relationship of Ad/As≧1.

The reason for setting Ad/As≧1 is as follows.

FIG. 4 shows an example of the theoretical value of the suction flow rate before and after branching in the suction part of the two-cylinder rotary compressor having the same structure as the present invention. As shown in Figure 4, since the maximum flow rate after the bifurcation reaches about 80% of the maximum flow rate before the bifurcation, in order to suppress the pressure loss of the working gas, ensure that the cross-sectional area of the flow channel after the bifurcation is equal to that before the bifurcation. 80% or more is required. In addition, since the pressure loss due to the shape of the flow channel caused by the change of the flow direction of the working gas increases after the branch, it is desirable to ensure that the cross-sectional area of the flow channel before and after the branch is equal.

In addition, each angle θ formed by the axis ₁₁ of the suction pipe 63 and the axis ₁₂ of the two suction passages 70, 71 is set to be 28°≦θ≦43°.

The reason for setting 28°≦θ≦43° is as follows.

As shown in Fig. 5, using the twin-cylinder rotary compressor of the present invention, an experiment of varying θ was carried out to study the relationship between Ad/As and COP.

When θ=25° exceeds 28°≦θ≦43°, the desired COP value cannot be achieved.

The reason for this is that, as shown in the comparative example in FIG. 9 and FIG. 10 , if Ad is increased, in the suction passage outlet (flow passage outlet 71 a ′) of the end surface 53 c of the partition plate 53 , with respect to the minor axis of the ellipse, If the major diameter is too long, the seal portion s on the end surface of the drum cannot be sufficiently secured, resulting in a decrease in COP.

In addition, when θ=45° exceeds 28°≦θ≦43°, the desired COP value cannot be achieved. The reason for this is considered to be that the suction interference between the two cylinder chambers is large.

In contrast, in the case of θ=30° and 40° within 28°≦θ≦43°, both exceeded the desired COP value and performed well, and the smaller θ within this range, the higher the COP. high. The reason for this is considered to be that the change in the flow direction can be reduced and the suction interference between the two cylinder chambers can be reduced.

Fig. 6 shows the relationship between θ and COP when Ad/As = 1.05 obtained through the experiment using the two-cylinder rotary compressor of the present invention.

When 28°≦θ≦43°, a high COP can be achieved, and 28°<θ,θ>43 beyond this range. In the case of , the COP will be significantly reduced. The reason why the COP decreases when θ exceeds 43° is considered to be that the flow direction of the working gas changes greatly, resulting in a large resistance of the flow path.

In addition, as shown in FIGS. 7 and 8 , it is preferable to make the projected area of the opening of the bifurcated portion 72 of the partition 53 in the direction perpendicular to the partition surface, that is, the two openings that penetrate the partition viewed from the axial direction of the partition 53. The opening area of the end surface (the area indicated by hatching in FIG. 7 ) Ap is 1/2≧Ap/Ad≧1/5.

By setting 1/2≧Ap/Ad, suction interference can be further reduced, and by setting Ap/Ad≧1/5, both end faces 53c of the partition plate 53 and the partitions can be easily cleaned with a brush or the like. By removing the burr on the branch portion 72, a high-reliability two-cylinder rotary compressor can be obtained at low cost.

On the other hand, on-off valves 73 , 74 are respectively provided in the discharge holes 61 , 62 , and the discharge hole 61 of the first cylinder 51 is surrounded by the first muffler chamber 75 and communicates with the inside of the airtight container 2 . The discharge hole 62 of the second cylinder 52 is surrounded by the second muffler chamber 76 and communicates with the inside of the airtight container 2 .

According to the two-cylinder rotary compressor 1 of the above-mentioned first embodiment, the working gas from the suction pipe 63 is divided by the branch part 72, and passes through the suction passages 70, 71, passage outlets 70a, 71a, and a part of them is discharged from the suction port. 64 is sent into the compression chamber 68 of the first cylinder 51, and the other part is sent into the compression chamber 69 of the second cylinder 52 from the suction port, so as to discharge the work compressed in each compression chamber 68, 69 from the discharge holes 61, 62 gas.

In the compression process of the above-mentioned working gas, since the relationship between the outlet area Ad of the suction channel and the minimum cross-sectional area As of the suction pipe is Ad/As≧1 and the angles θ formed by the axis of the suction pipe and the axis of the suction channel are: 28°≦θ≦43°, therefore, a high COP can be obtained.

According to the twin-cylinder rotary compressor 1 of the present first embodiment, it is possible to realize a twin-cylinder rotary compressor that achieves a high COP.

Next, a two-cylinder rotary compressor according to a second embodiment of the present invention will be described.

In the second embodiment, a surface perpendicular or obtuse to the end face of the partition is provided at the corner portion where the inner peripheral surface of the suction passage of the first embodiment forms an acute angle with the end face of the partition.

For example, as shown in FIG. 11, the compression mechanism part of the two-cylinder rotary compressor of the second embodiment of the present invention is provided with a partition 53, and a suction hole with one end leading to the outer peripheral surface is provided on the partition 53 in the horizontal direction. 53d, a suction pipe (not shown) is connected to the suction hole 53d. The other end side of the suction hole 53d is divided into upper and lower two by the branch portion 72 to form inclined suction passages 70 and 71 . The suction passages 70, 71 have a bifurcating angle of angle θ, and are provided on the corners 70d, 71d at which the inner peripheral surfaces 70b, 71b of the suction passages 70, 71 form an acute angle with the partition plates 70c, 71c and are perpendicular to the partition plates 70c, 71c. Or faces 70e, 71e at an obtuse angle α. If the axial thickness of the surfaces 70e, 71e that are perpendicular or at an obtuse angle α is H, the relationship between the minimum value Hmin and the diameter φDs of the suction passages 70, 71 preferably satisfies the following formula.

[Formula 1]

Minimum value Hmin≧0.02·Ds

With the above structure, the rigidity near the corners 70d, 71d of the partition plate 53 and the suction passages 70, 71 can be ensured, and the deformation of the partition plate end faces 70c, 71c can be prevented even during the deburring process, thereby obtaining a high-performance compressor. .

On the other hand, when the inner peripheral surface of the suction passage forms an acute angle with the end surface of the partition, burrs or burrs are likely to be generated at the corners, and when the generated burrs fall off, they will still flow into the compression chamber, causing the most unfavorable In addition, even if you want to remove the burrs in advance, the sharp corners are thin and easy to deform, so in the process of removing burrs, the flatness of the end face of the separator will also deteriorate, resulting in poor performance due to poor sealing performance. reduce.

Since other structures are not different from those of the separator shown in FIG. 3, the same reference numerals are used, and descriptions thereof are omitted.

As shown in Fig. 12, as the twin-cylinder rotary compressor of the third embodiment of the present invention, the vertical or obtuse surfaces 70e, 71e are preferably formed by through holes 53p vertically opened on the end surfaces 70c, 71c of the partition.

Therefore, the above-mentioned size and shape can be realized easily and accurately, and the burrs of the branch portion 72 can also be easily removed.

Furthermore, the diameter φDk of the through hole 53p is equal to the diameter φDs of the suction passages 70 and 71 . Therefore, the through-hole 53p and the suction passages 70, 71 can be processed with the same tool, so that the manufacturing time can be shortened and the manufacturing cost can be reduced.

In addition, according to the refrigeration cycle apparatus using the twin-cylinder rotary compressor of the present invention, it is possible to realize a refrigeration cycle apparatus using the twin-cylinder rotary compressor capable of obtaining a high COP.

Claims (6)

1. a double cylinders rotary compressor comprises compression mechanical part and revolution drive portion,

Described compression mechanical part comprises: dividing plate, be arranged on two end faces of this dividing plate and form the cylinder chamber the 1st cylinder and the 2nd cylinder, be arranged on the end face of a side opposite of these cylinders with dividing plate and cover described cylinder chamber the 1st cover piece and the 2nd cover piece, have 2 eccentric parts and by the rotatingshaft of described cover piece rotating support and the cylinder that engages with described eccentric part

Described compression mechanical part is the 1 piece suction pipe of working gas from linking to each other with described dividing plate, and by 2 suction passages being told by the branched portion that is arranged in the described dividing plate, it is indoor to import two described cylinders,

It is characterized in that:

The discharge area of the described suction passage on two end faces of described dividing plate is Ad and the minimum sectional area of described suction pipe when being As, has the relation of Ad/As 〉=1,

The formed all angles θ of the shaft axis of the shaft axis of described suction pipe and two suction passages is 28 °≤θ≤43 °.

2. double cylinders rotary compressor according to claim 1 is characterized in that: when the opening area that connects two end faces of dividing plate from the end on observation of described dividing plate is Ap, and 1/2 〉=Ap/Ad 〉=1/5.

3. double cylinders rotary compressor according to claim 1 is characterized in that: the inner peripheral surface of described suction passage is provided with face vertical with the dividing plate end face or in obtuse angle acutangulating crossing bight with the dividing plate end face.

4. double cylinders rotary compressor according to claim 3 is characterized in that: the face vertical with described dividing plate end face formed by the vertical through hole that is opened on the described dividing plate end face.

5. double cylinders rotary compressor according to claim 4 is characterized in that: the aperture of described through hole and the equal diameters of described suction passage.

6. freezing cycle device, it is characterized in that: each described double cylinders rotary compressor, condenser, expansion gear, vaporizer form in the claim 1～5 by having connected in turn with pipeline.

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