CN107288884B

CN107288884B - Rotary refrigerating device

Info

Publication number: CN107288884B
Application number: CN201710586667.8A
Authority: CN
Inventors: 叶力; 黄崇军
Original assignee: Ningbo Qichen Electronic Technology Co ltd
Current assignee: Ningbo Qichen Electronic Technology Co ltd
Priority date: 2017-07-18
Filing date: 2017-07-18
Publication date: 2020-05-05
Anticipated expiration: 2037-07-18
Also published as: CN107288884A

Abstract

The invention discloses a rotary refrigerating device which comprises a rotary compressor, a condenser, an expansion device, an evaporator and a refrigerant pipe. The rotary compressor comprises a closed box body, wherein a driving system, a plurality of compressor systems, a rotating shaft and a bearing are arranged in the closed box body; the rotating shaft transmits power generated by the driving system to the plurality of compressor systems; the bearing rotatably supports the rotating shaft. The beneficial effects are that: the invention can effectively inhibit the abrasion between the vane arranged at the bearing side and the roller, prolong the service life of the vane and solve the problems of large rotation loss and large leakage loss of the traditional vane.

Description

Rotary refrigerating device

Technical Field

The invention relates to the technical field of refrigeration, in particular to a rotary type refrigeration device.

Background

Rotary compressors have found wide use in the refrigeration industry due to their advantages of small number of parts, simple structure, high volumetric efficiency, and the like. However, the vane-type rotary compressor in the conventional rotary refrigeration apparatus has problems of excessive frictional loss and leakage loss between the outer end of the isolation vane and the inner wall surface of the cylinder bore.

Disclosure of Invention

The invention aims to provide a rotary refrigeration device which can effectively inhibit the abrasion of the front end part of a blade and prolong the service life of the blade.

Aiming at the problems mentioned in the background technology, the invention adopts the technical scheme that:

a rotary refrigeration device comprises a rotary compressor, a condenser, an expansion device, an evaporator and a refrigerant pipe. The rotary compressor comprises a closed box body, wherein a driving system, a plurality of compressor systems, a rotating shaft and a bearing are arranged in the closed box body; the rotating shaft transmits power generated by the driving system to the plurality of compressor systems; the bearing rotatably supports the rotating shaft. The plurality of compressor systems comprise a cylinder, the cylinder is provided with a cylinder chamber, the cylinder chamber is provided with a roller and a blade system, and the roller receives the rotation of the rotating shaft and makes eccentric motion; the vane system is in contact with the roller to reciprocate, and divides the cylinder chamber into a compression side and a suction side. The device can effectively overcome the problems of large rotary loss and large leakage loss of the traditional vane type.

The blade system includes a first blade and a second blade, the second blade being provided on the bearing side in the axial direction of the rotary shaft so as to overlap with the first blade, and having a shorter length in the axial direction of the rotary shaft than the first blade.

The surface of the blade system is coated with a wear-resistant coating, and the coating comprises the following components in parts by weight: 33-42 parts of organic silicon modified polyester resin, 1-2 parts of graphene, 35-40 parts of epoxy resin, 21-25 parts of phenolic resin, 2-4 parts of sodium carboxymethyl cellulose, 1-2 parts of nano zinc oxide, 20-30 parts of xylene and 3-7 parts of isopropanol. The weight of the graphene is 0.5-3% of that of the resin, the graphene can be prevented from agglomerating by controlling the proportion of the graphene and the resin, the graphene can be uniformly dispersed in the resin, the interface bonding strength is improved, the mechanical property of the coating is effectively improved, and the wear-resistant coating is excellent in wear resistance and high in strength and hardness. The wear-resistant coating is sprayed on the surface of the blade, and then the blade is dried and cured, so that the wear resistance of the blade can be effectively enhanced, the friction loss of the front end part of the blade is greatly reduced, the service life of the blade is prolonged, the wear-resistant coating has good film forming property and cohesiveness, and the coating is prevented from cracking or falling off.

The rear end portions of the first blade and the second blade are abutted with 1 coil spring, the first blade and the second blade are urged in the roller direction in such a manner that the front end portions of the first blade and the second blade are abutted with the roller, and the center of the coil spring is positioned on the bearing side with respect to the center in the height direction of the cylinder. The problems of overlarge friction and excessive loss of the front end part of the blade are effectively solved.

Refrigerant lines connect the rotary compressor, the condenser, the expansion device, and the evaporator.

Compared with the prior art, the invention has the advantages that:

1. the invention can effectively inhibit the abrasion between the vane arranged at the bearing side and the roller, prolong the service life of the vane and solve the problems of large rotation loss and large leakage loss of the traditional vane.

2. The wear-resistant coating is coated on the surface of the blade system, the graphene in the coating accounts for 0.5-3% of the weight of the resin, the graphene can be prevented from agglomerating by controlling the proportion of the graphene to the resin, the graphene can be uniformly dispersed in the resin, the interface bonding strength is improved, the mechanical property of the coating is effectively improved, and the wear-resistant coating is excellent in wear resistance and high in strength and hardness. The wear-resistant coating is sprayed on the surface of the blade, and then the blade is dried and cured, so that the wear resistance of the blade can be effectively enhanced, the friction loss of the front end part of the blade is greatly reduced, the service life of the blade is prolonged, the wear-resistant coating has good film forming property and cohesiveness, and the coating is prevented from cracking or falling off.

Description of the drawings:

fig. 1 is a schematic view showing a refrigeration cycle apparatus according to an embodiment;

fig. 2 is a plan view showing a first cylinder chamber of a rotary compressor of an embodiment and its vicinity;

fig. 3 is an enlarged cross-sectional view of the vicinity of the first and second cylinders of the rotary compressor of the refrigeration cycle apparatus according to the embodiment.

Description of reference numerals: 1, sealing the box body; 2, driving the system; 3 a compressor system; 4a rotating shaft; 4a middle part of the rotating shaft; 4b lower end of the rotating shaft; 5a first cylinder; 5b a second cylinder; 6a middle partition plate; 7, a main bearing; 8 pairs of bearings; 9a first roller; 9b a second roller; 10a first cylinder chamber; 10b a second cylinder chamber; 11. 13 discharging silencer; 12a, 12b discharge valve mechanisms; 16a, 16b coil springs; 17a, 17b slots; 18a, 18b vane back chamber; 19a, 19b spring setting holes; 20 a condenser; 21 an expansion device; 22 an evaporator; 23 a reservoir; 25 a suction hole; 26 an ejection hole; 30a helical spring mounting groove; 41 a first eccentric portion; 42 a second eccentric portion; 51a first blade system; 51a, 52a first blade; 51b, 52b second blades; 52a second blade system; 60 a refrigeration cycle device; 70 bolt C1, C2 centerline; ranges F31, F32; h11, H21 height of first blade; h12, H22 height of second blade; k, a rotary compressor; a P refrigerant pipe; r a refrigeration cycle loop; x center of the first cylinder in the height direction; y center of the second cylinder in the height direction.

Detailed Description

The invention is further illustrated by the following figures and examples:

example 1:

as shown in fig. 1, the refrigeration cycle apparatus 60 includes a rotary compressor K, a condenser 20, an expansion device 21, an evaporator 22, an accumulator 23, and a refrigerant pipe P. The refrigerant pipe P connects these devices in the described order.

The rotary compressor K is of a double cylinder type including a plurality of cylinders, two cylinders in the present embodiment. A sectional view of the rotary compressor K is shown in fig. 1. The rotary compressor K includes a hermetic casing 1, a motor unit 2, a compressor system 3, a rotary shaft 4, a main bearing 7, and an auxiliary bearing 8.

The motor unit 2 is provided in the hermetic container 1 and is provided above the hermetic container 1. The compressor system 3 is provided in the hermetic container 1 and in a lower portion of the hermetic container 1. The lower part of the closed casing 1 is filled with lubricating oil in which the majority of the compressor system 3 is located. The motor unit 2 and the compressor system 3 are connected by a rotating shaft 4. The rotary shaft 4 transmits power generated by the motor unit 2 to the compressor system 3. The motor unit 2 drives the rotary shaft 4 to rotate, thereby the compressor system 3 sucks in a gas refrigerant, compresses the refrigerant, and discharges the refrigerant as described later.

The compressor system 3 is provided with a first cylinder 5a at the upper part and a second cylinder 5b at the lower part. The partition plate 6 partitions the first cylinder 5a and the second cylinder 5 b. A main bearing 7 is provided to overlap the upper surface of the first cylinder 5 a. The main bearing 7 is provided on the inner peripheral wall of the sealed casing 1. A sub-bearing 8 is provided to overlap the lower surface of the second cylinder 5 b. The sub-bearing 8 is fixed to the first cylinder 5a together with the second cylinder 5b and the intermediate partition plate 6 by bolts 70.

The intermediate portion 4a of the rotating shaft 4 is rotatably connected to the main bearing 7. The lower end 4b of the rotary shaft 4 is rotatably pivoted to the sub-bearing 8. The rotary shaft 4 passes through the first cylinder 5a, the intermediate partition plate 6, and the second cylinder 5 b.

The rotating shaft 4 includes a first eccentric portion 41 and a second eccentric portion 42. The first eccentric portion 41 is provided in the first cylinder chamber 10a of the first cylinder 5 a. The second eccentric portion 42 is provided in the second cylinder chamber 10b of the second cylinder 5 b. The first eccentric portion 41 and the second eccentric portion 42 have the same diameter and are disposed to be offset from each other with a phase difference of approximately 180 °.

The first roller 9a fitted on the circumferential surface of the first eccentric portion 41 is provided in the first cylinder chamber 10a of the first cylinder 5 a. The second roller 9b fitted on the circumferential surface of the second eccentric portion 42 is provided in the second cylinder chamber 10b in the second cylinder 5 b. The first roller 9a and the second roller 9b eccentrically move while contacting a part of the peripheral wall thereof along the peripheral wall of the first cylinder chamber 10a and the second cylinder chamber 10b in accordance with the rotation of the rotary shaft 4. The first cylinder chamber 10a is a space inside the first cylinder 5a, and is formed by the main bearing 7 and the intermediate partition plate 6 in a closed manner. The second cylinder chamber 10b is a space inside the second cylinder 5b, and is formed by the intermediate partition plate 6 and the sub-bearing 8 in a closed manner. The diameters and lengths along the axial direction of the rotary shaft 4, i.e., the height dimensions of the first cylinder chamber 10a and the second cylinder chamber 10b are set to be equal to each other. The first roller 9a is disposed in the first cylinder chamber 10a, and the second roller 9b is disposed in the second cylinder chamber 10 b.

Two discharge mufflers 11 are attached to the main bearing 7. The two discharge mufflers 11 are overlapped in a double manner. The two discharge mufflers 11 are provided with discharge holes. The discharge muffler 11 covers a discharge valve mechanism 12a provided in the main bearing 7. A discharge muffler 13 is attached to the sub-bearing 8. The discharge muffler 13 covers the discharge valve mechanism 12b provided in the sub-bearing 8. The discharge muffler 13 is not provided with a discharge hole. The discharge valve mechanism 12a of the main bearing 7 is connected to the first cylinder chamber 10a, and opens when the pressure in the first cylinder chamber 10a rises and reaches a predetermined pressure value in accordance with the compression action, and the compressed gas refrigerant is discharged into the discharge muffler 11.

The discharge valve mechanism 12b of the sub-bearing 8 is connected to the second cylinder chamber 10b, and opens when the pressure in the second cylinder chamber 10b rises and reaches a predetermined value as a result of the compression action, and the compressed gas refrigerant is discharged to the discharge muffler 13. The discharge gas guide path is provided over the sub-bearing 8, the second cylinder 5b, the intermediate partition plate 6, the first cylinder 5a, and the main bearing 7. The discharge gas guide passage guides the gas refrigerant compressed in the second cylinder chamber 10b and discharged through the discharge valve mechanism 12b to the discharge muffler 13 into the double discharge muffler 11 on the upper side.

A first vane system 51 is provided in the first cylinder 5 a. The first vane system 51 includes a first vane 51a and a second vane 51b provided along the axial direction of the rotary shaft 4, that is, the height direction of the first cylinder 5 a. The second blade 51b is provided on the main bearing 7 side, i.e., on the upper side in the drawing, with respect to the first blade 51 a.

As described later, one end of each of the 1 coil springs 16a abuts against the rear ends of the first blade 51a and the second blade 51 b. The rear end portion referred to herein is an end portion of the first blade 51a and the second blade 51b opposite to the first roller 9 a. The coil spring 16a biases (energizes) the first blade 51a and the second blade 51b toward the first roller 9a such that the tip portions of the first blade 51a and the second blade 51b are in contact with the first roller 9 a. The mounting structure of the coil spring 16a to the first blade 51a and the second blade 51b will be described in detail later.

The first cylinder 5a is provided with a vane groove 17a that opens into the first cylinder chamber 10 a. Further, in the first cylinder 5a, a vane back chamber 18a is provided at a rear end portion of the vane groove 17. The vane groove 17a is provided with the first vane 51a and the second vane 51b provided in the height direction of the first cylinder 5a so as to be able to reciprocate. The first vane 51a and the second vane 51b have distal ends that freely protrude and retreat into the first cylinder chamber 10a, and rear ends that freely protrude and retreat into the vane back chamber 18 a. The tip end portion referred to herein is an end portion on the first roller 9a side. The vane back chamber 18a is open into the hermetic container 1. Therefore, the pressure in the hermetic container 1 acts on the rear ends of the first and

second blades

51a and 51 b.

The tip portions of the first blade 51a and the second blade 51b are formed in a substantially arc shape in a plan view. The tip portions of these vanes are in line contact with the circumferential wall of the circular first roller 9a in plan view regardless of the rotation angle of the first roller 9a in a state of protruding into the first cylinder chamber 10 a. Further, a spring installation hole 19a is provided in the outer peripheral wall of the first cylinder 5 a. The spring installation hole 19a is provided through the vane back chamber 18 to the front of the first cylinder chamber 10 a.

The coil spring 16a is disposed in the spring disposition hole 19 a. When the coil spring 16a is assembled as the compressor system 3, one end of the coil spring 16a abuts against the inner peripheral wall of the hermetic container 1. The other end portion of the coil spring 16a abuts on both the first blade 51a and the second blade 51b, and presses the first blade 51a and the second blade 51b to bias (energize) the first roller 9 a.

In the second cylinder 5b, a second vane system 52 is provided. The second vane system 52 includes the first vane 52a and the second vane 52b provided along the axial direction of the rotary shaft 4, that is, the height direction of the second cylinder 5 b. The second vane 52b is provided on the side of the sub-bearing 8, i.e., on the lower side in the drawing, with respect to the first vane 52 a.

As described later, one end of each of the 1 coil springs 16b abuts against the rear ends of the first blade 52a and the second blade 52 b. The rear end portion referred to herein is an end portion of the first blade 52a and the second blade 52b opposite to the second roller 9 b. The coil spring 16b biases (energizes) the first blade 52a and the second blade 52b toward the second roller 9b such that the tip portions of the first blade 52a and the second blade 52b contact the second roller 9 b. The mounting structure of the coil spring 16b to the first blade 52a and the second blade 52b will be described in detail later. The second cylinder 5b is provided with a vane groove 17b that opens into the second cylinder chamber 10 b. Further, in the second cylinder 5b, a vane back chamber 18b is provided at a rear end portion of the vane groove 17 b. The first vane 52a and the second vane 52b provided in the height direction of the second cylinder 5b are provided in the vane groove 17b so as to be able to reciprocate. The first vane 52a and the second vane 52b have distal ends that freely protrude and retreat into the second cylinder chamber 10b, and rear ends that freely protrude and retreat into the vane back chamber 18 b. The tip end portion referred to herein is an end portion on the second roller 9b side. The vane back chamber 18b is open into the closed casing 1. Therefore, the pressure in the hermetic container 1 acts on the rear ends of the first and

second blades

52a and 52 b. The tip portions of the first blade 52a and the second blade 52b are formed in a substantially arc shape in plan view. The tip end portions of these vanes are in line contact with the circumferential wall of the circular second roller 9b in plan view regardless of the rotation angle of the second roller 9b in a state of protruding into the second cylinder chamber 10 b.

Further, a spring installation hole 19b is provided in the outer peripheral wall of the second cylinder 5 b. The spring installation hole 19b is provided through the vane back chamber 18b to the front of the second cylinder chamber 10 b. The coil spring 16b is disposed in the spring disposition hole 19 b. When the coil spring 16b is assembled as the compressor system 3, one end of the coil spring 16b abuts against the inner peripheral wall of the hermetic container 1. The other end portion of the coil spring 16b abuts on both the first blade 52a and the second blade 52b, and presses the first blade 52a and the second blade 52b to bias (energize) the second roller 9 b.

In a state where the pressure in the hermetic container 1 is low, the first vane 51a and the second vane 51b cannot be sufficiently pressed against the first roller 9a only by the pressure in the hermetic container 1, and therefore, the interior of the first cylinder chamber 10a cannot be divided into the suction side and the compression side, and in this case, the coil spring 16a is provided for assisting the biasing. The same applies to the coil spring 16 b. The refrigerant pipe P for discharge is connected to the upper end of the sealed casing 1. The condenser 20, the expansion device 21, the evaporator 22, and the accumulator 23 are provided so as to be connected to the refrigerant pipe P in this order.

From the accumulator 23, 2 refrigerant pipes P for suction extend, and the refrigerant pipes P penetrate the hermetic casing 1 of the rotary compressor K and are connected to the first cylinder chamber 10a and the second cylinder chamber 10 b. In this way, the refrigeration cycle R of the refrigeration cycle apparatus is constituted.

Fig. 2 is a plan view showing the first cylinder chamber 10a and its vicinity. The plan shape of the second cylinder chamber 10b and its vicinity. Similarly, in fig. 2, the reference numerals of the structures provided in the second cylinder chamber 10b and the vicinity thereof are shown in parentheses and are described in parallel with the reference numerals of the structures of the first cylinder chamber 10a and the vicinity thereof, and fig. 2 is also used for the description of the structures of the second cylinder chamber 10b and the vicinity thereof.

As shown in fig. 2, a suction port 25 is provided from the outer peripheral wall of the closed casing 1 and the first cylinder 5a to the first cylinder chamber 10 a. Similarly, a suction hole 25 is provided from the outer peripheral walls of the sealed casing 1 and the second cylinder 5b to the second cylinder chamber 10 b. The refrigerant pipe P for suction branched from the accumulator 23 is inserted and fixed to both the suction holes 25. In the first cylinder 5a and the second cylinder 5b, a suction hole is provided at one circumferential side of the first cylinder 5a and the second cylinder 5b with the first vane system 51 and the second vane system 52 interposed therebetween and the

grooves

17a and 17b, and a discharge hole 26 connected to the discharge valve mechanisms 12a and 12b is provided at the other circumferential side.

In the rotary compressor K configured in this manner, when the motor section 2 is energized and the rotary shaft 4 is rotationally driven, the pressure in the hermetic container 1 and the biasing force of the coil spring 16a act on the rear ends of the first vane 51a and the second vane 51b in the first cylinder chamber 10a, the first vane 51a and the second vane 51b elastically abut against the peripheral wall of the first roller 9a, and the first roller 9a eccentrically moves.

Similarly, in the second cylinder chamber 10b, the pressure in the hermetic container 1 and the biasing force of the coil spring 16b act on the rear ends of the first vane 52a and the second vane 52b, the first vane 52a and the second vane 52b elastically contact the peripheral wall of the second roller 9b, and the second roller 9b eccentrically moves. As the first and

second rollers

9a and 9b eccentrically move, the gas refrigerant is sucked from the refrigerant pipe P for suction into the suction sides of the first and

second cylinder chambers

10a and 10b partitioned by the first and

second vane systems

51 and 52. The gas refrigerant moves toward the compression side of the first and

second cylinder chambers

10a and 10b partitioned by the first and

second vane systems

51 and 52 and is compressed. When the volume on the compression side becomes smaller and the pressure of the gas refrigerant rises to a predetermined pressure, the gas refrigerant is discharged from the discharge port 26 to the discharge valve mechanisms 12a and 12 b.

In the 2 discharge mufflers 11 overlapped on the upper side of the compressor system 3, the gas refrigerant discharged from the first cylinder chamber 10a and the gas refrigerant discharged from the second cylinder chamber 10b merge with each other. Then, the merged gas refrigerant is discharged into the sealed casing 1. The gas refrigerant discharged into the hermetic container 1 fills the upper end portion of the hermetic container 1 through a gas guide path provided between the components constituting the motor unit 2, and is discharged to the outside of the rotary compressor K from the refrigerant pipe P. Then, the pressure of the gas refrigerant compressed to a high pressure acts on the rear ends of the first and

second blades

51a and 51b and the first and

second blades

52a and 52b in the first and

second blade systems

51 and 52, and the high-pressure gas refrigerant is guided to the condenser 20 and condensed to become a liquid refrigerant. The liquid refrigerant is guided to the expansion device 21 to be adiabatically expanded, and is guided to the evaporator 22 to be evaporated, thereby becoming a gas refrigerant. In the evaporator 22, latent heat of evaporation is taken from the ambient air, and a freezing action is performed.

The rotary compressor K is mounted in an air conditioner and serves as cooling air. Further, a heat pump (heat pump) type refrigeration cycle may be configured by providing a four-way switching valve on the discharge side of the rotary compressor K in the refrigeration cycle. The four-way switching valve is switched to switch the flow of the refrigerant in the reverse direction, and the gas refrigerant discharged from the rotary compressor K is directly guided to the indoor heat exchanger, thereby performing a heating function.

Then, as the pressure in the hermetic container 1 increases by the operation of the rotary compressor K, the pressing force of the first and

second vanes

51a and 51b against the first roller 9a increases. Similarly, the pressing force of the first blade 52a and the second blade 52b against the second roller 9b increases. Here, the mounting structure of the coil spring 16a to the first blade 51a and the second blade 51b of the first blade system 51 and the mounting structure of the coil spring 16b to the first blade 52a and the second blade 52b of the second blade system 52 will be specifically described.

Fig. 3 is an enlarged cross-sectional view of the vicinity of the first cylinder 5a and the second cylinder 5 b. The heights H11 and H12 of the 1 st blade 51a and the second blade 51b in the first blade system 51 will be described. The height H11 of the first blade 51a is the length along the axis of the rotary shaft 4 in the first blade 51 a. The height H12 of the second blade 51b is the length along the axis of the rotary shaft 4 in the second blade 51 b. The height H12 of the second blade 51b is less than the height H11 of the first blade 51a, and is H12 < H11.

In other words, the first and

second blades

51a and 51b have a lower height on the side of the main bearing 7 supporting the rotary shaft 4 than on the other side. As shown enlarged in a range F31 in fig. 3, the coil spring 16a that biases (energizes) the first vane 51a and the second vane 51b of the first vane system 51 is provided such that the center line C1 thereof is positioned on the second vane 51b side with respect to the center X in the height direction of the first cylinder 5 a. The range F31 is an enlarged representation of the first blade 51a and the second blade 51b to which the coil spring 16a is attached.

Coil spring mounting grooves 30a formed so that one end of the coil spring 16a is fitted into the rear end portions of the first blade 51a and the second blade 51b are formed. When the coil spring 16a is fitted into the coil spring mounting groove 30a, the center line C1 of the coil spring 16a is located closer to the second vane 51b side than the center X in the height direction of the first cylinder 5 a.

Therefore, although the spring installation hole 19a is formed so that the coil spring 16a is installed at the above-described position, the spring installation hole can be stably biased (energized) by 1 coil spring 16a having a small winding diameter even if the first blade 51a and the second blade 51b have different height dimensions. Further, the heights H21, H22 of the first blade 52a and the second blade 52b in the second blade system 52 will be described. The height H21 of the first blade 52a is the length along the axis of the rotary shaft 4 in the first blade 52 a. The height H22 of the second blade 52b is the length along the axis of the rotary shaft 4 in the second blade 52 b. The height H22 of the second blade 52b is less than the height H21 of the first blade 52a, H22 < H21. In other words, the first and

second blades

52a and 52b are arranged such that the blades on the side of the sub-bearing 8 supporting the rotary shaft 4 are lower in height than the blades on the other sides.

As shown enlarged in the range F32 in fig. 3, the coil spring 16b that biases (energizes) the first vane 52a and the second vane 52b of the second vane body system 52 is provided such that the center line C2 thereof is positioned on the second vane 52b side with respect to the center Y in the height direction of the second cylinder 5 b. Further, coil spring mounting grooves 30b formed so that one end of the coil spring 16b is fitted are formed in the rear end portions of the first blade 52a and the second blade 52b, respectively. When the coil spring 16b is fitted into the coil spring mounting groove 30b, the center line C2 of the coil spring 16b is located closer to the second vane 52b than the center Y in the height direction of the second cylinder 5 b.

Therefore, although the spring installation hole 19b is formed so that the coil spring 16b is installed at the above-described position, the coil spring 16a having a small winding diameter can stably apply force (energized) even if the first blade 52a and the second blade 52b have different height dimensions. In the rotary compressor K configured in this manner, the second vane 51b (main bearing side) and the second vane 52b (sub bearing side) provided on the bearing side in the first vane system 51 and the second vane system 52 can be prevented from being worn more severely than the first vane 51a and the first vane 52a provided on the other side (counter bearing side).

This is explained in detail below:

when 2 vanes are provided in the height direction of the cylinder due to various factors such as the structure of the first cylinder 5a and the second cylinder 5b, the vanes provided on the bearing side partially contact the roller, and therefore, the degree of wear tends to be higher than that of the vanes on the other side (anti-bearing side).

In the present embodiment, in the first cylinder 5a, the height H12 of the second vane 51b provided on the main bearing 7 side is lower than the height H11 of the other first vane 51 a. Therefore, the pressing force acting on the second blade 51b toward the first roller 9a is smaller than the pressing force acting on the first blade 51a toward the first roller 9 a.

This is because the area of the rear end of the second blade 51b is smaller than the area of the rear end of the first blade 51a by making the height H12 lower than the height H11. Since the area becomes smaller, the area on which the pressure of the refrigerant gas in the sealed casing 1 acts becomes smaller, and thus the pressing force acting on the second vane 51b is smaller than the pressing force acting on the first vane 51 a. By making the pressing force acting on the second blade 51b smaller than the pressing force acting on the first blade 51a, even if the second blade 51b partially contacts the first roller 9a as described above, the load acting on the partially contacted portion becomes small, and therefore, the occurrence of abrasion can be suppressed.

In other words, the wear of the tip end portion of the vane can be suppressed, as in the second cylinder 5b, and therefore, the phenomenon that the degree of wear of the second vane 52b provided on the sub-bearing 8 side in the second cylinder 5b is more severe than that of the first vane 52a can be suppressed. In other words, the front end portion of the vane can be suppressed from being worn.

In addition, although 1 coil spring 16a is used to press the first blade 51a and the second blade 51b of the first blade system 51 against the first roller 9a in a state where the pressure of the refrigerant gas has not increased, the number of components can be reduced because 1 coil spring 16 is used in common. Similarly, in the second blade system 52, the number of components can be reduced by sharing 1 coil spring 16b for the first blade 52a and the second blade 52 b. In the first vane system 51, the center line C1 of the coil spring 16 is offset toward the second vane 51b with respect to the center X in the height direction of the first cylinder 5 a.

Therefore, even if the first blade 52a and the second blade 52b have different height dimensions, the 1 coil spring 16a having a small winding diameter can stably apply a force (bias). In this way, a phenomenon in which the degree of wear of the second blade 51b is more severe than that of the first blade 51a can be suppressed. The same applies to the second blade system 52. Therefore, in the second blade system 52, the abrasion of the second blade system 52b can be suppressed from being more serious than that of the first blade 52 a.

In the present embodiment, the vane back chamber 18a that opens into the inside of the sealed casing 1 is an example of a pressure supply means that guides the pressure in the inside of the sealed casing 1 to the end portion of the first and

second vanes

51a and 51b opposite to the first roller 9 a. Similarly, the vane back chamber 18b that opens into the inside of the sealed casing 1 is an example of a pressure supply means that guides the pressure in the inside of the sealed casing 1 to the end portion of the first and

second vanes

52a and 52b opposite to the second roller 9 b.

In the present embodiment, the motor unit is an example of a drive system.

Example 2:

the surface of the blade system is coated with a wear-resistant coating, and the coating comprises the following components in parts by weight: 40 parts of organic silicon modified polyester resin, 1.0 part of graphene, 35 parts of epoxy resin, 22 parts of phenolic resin, 3 parts of sodium carboxymethylcellulose, 1.5 parts of nano zinc oxide, 26 parts of xylene and 6 parts of isopropanol. The graphene accounts for 2.5% of the weight of the resin, and the graphene can be prevented from being agglomerated by controlling the proportion of the graphene to the resin, can be uniformly dispersed in the resin, improves the interface bonding strength, and effectively improves the mechanical property of the coating, so that the wear-resistant coating has excellent wear resistance and high strength and hardness. The wear-resistant coating is sprayed on the surface of the blade, and then the blade is dried and cured, so that the wear resistance of the blade can be effectively enhanced, the friction loss of the front end part of the blade is greatly reduced, the service life of the blade is prolonged, the wear-resistant coating has good film forming property and cohesiveness, and the coating is prevented from cracking or falling off.

The preparation steps of the wear-resistant coating are as follows: adding organic silicon modified polyester resin, graphene, epoxy resin, phenolic resin and isopropanol into a reaction kettle according to the formula amount, reacting for 20min at 60 ℃ and the stirring speed of 300r/min, adding sodium carboxymethylcellulose, nano zinc oxide and xylene, reacting for 20min at 40 ℃, adding 0.4 part of active polypeptide, uniformly stirring, uniformly coating on the surface of a blade, and curing at normal temperature. The amino acid sequence of the active polypeptide is HSHACKLCVCVNAKCYLCRVLHPGKLCVCNCSK. The active polypeptide can obviously enhance the chemical reaction stabilization effect of each component of the coating in the preparation process, reduces the layering of the coating, ensures that the coating system is uniform and stable, prolongs the shelf life, is favorable for improving the salt spray resistance effect of the anti-corrosion coating, and is favorable for enhancing the anti-corrosion effect and the anti-corrosion effective time of the anti-corrosion coating.

According to the embodiments, a rotary compressor capable of suppressing the wear of the leading end portion of the vane can be provided.

Conventional operations in the operation steps of the present invention are well known to those skilled in the art and will not be described herein.

The embodiments described above are intended to illustrate the technical solutions of the present invention in detail, and it should be understood that the above-mentioned embodiments are only specific embodiments of the present invention, and are not intended to limit the present invention, and any modification, supplement or similar substitution made within the scope of the principles of the present invention should be included in the protection scope of the present invention.

SEQUENCE LISTING

<110> Ningbo dust electronics technology Limited

<120> a rotary refrigerating device

<130>1

<160>1

<170>PatentIn version 3.5

<210>1

<211>33

<212>PRT

<213> Artificial Synthesis

<400>1

His Ser His Ala Cys Lys Leu Cys Val Cys Val Asn Ala Lys Cys Tyr

1 5 10 15

Leu Cys Arg Val Leu His Pro Gly Lys Leu Cys Val Cys Asn Cys Ser

20 25 30

Lys

Claims

1. A rotary refrigeration unit comprising a rotary compressor, a condenser (20), an expansion device (21), an evaporator (22) and a refrigerant pipe (P), characterized in that: the rotary compressor comprises a closed box body (1), wherein a driving system (2), a plurality of compressor systems (3), a rotating shaft (4) and a bearing are arranged in the closed box body (1); the rotating shaft (4) transmits the power generated by the driving system (2) to the plurality of compressor trains (3); the bearing rotatably supports the rotary shaft (4); the compressor system (3) comprises a cylinder, the cylinder is provided with a cylinder chamber, the cylinder chamber is provided with a roller and a blade system, and the roller receives the rotation of the rotating shaft and performs eccentric motion; the blade system is abutted against the roller to reciprocate, and the cylinder chamber is divided into a compression side and a suction side; the surface of the blade system is coated with a wear-resistant coating, and the coating comprises the following components in parts by weight: 33-42 parts of organic silicon modified polyester resin, 1-2 parts of graphene, 35-40 parts of epoxy resin, 21-25 parts of phenolic resin, 2-4 parts of sodium carboxymethyl cellulose, 1-2 parts of nano zinc oxide, 20-30 parts of xylene and 3-7 parts of isopropanol;

the preparation steps of the wear-resistant coating are as follows: adding organic silicon modified polyester resin, graphene, epoxy resin, phenolic resin and isopropanol into a reaction kettle according to the formula amount, reacting for 20min at the temperature of 60 ℃ and the stirring speed of 300r/min, adding sodium carboxymethylcellulose, nano zinc oxide and xylene, reacting for 20min at the temperature of 40 ℃, adding 0.4 part of active polypeptide, uniformly stirring, and then uniformly coating on the surface of a blade for curing at normal temperature, wherein the amino acid sequence of the active polypeptide is HSHACKLCVCVNAKCYLCRVLHPGKLCVCNCSK.

2. A rotary refrigeration unit according to claim 1 wherein: the blade system includes a first blade (51 a, 52 a) and a second blade (51 b, 52 b), the second blade (51 b, 52 b) being provided on the bearing side in the axial direction of the rotary shaft so as to overlap with the first blade (51 a, 52 a), and having a length in the axial direction of the rotary shaft (4) shorter than that of the first blade (51 a, 52 a).

3. A rotary refrigeration unit according to claim 2 wherein: the rear end portions of the first and second blades (51 a, 52a, 51b, 52 b) are in contact with 1 coil spring, the first and second blades (51 b, 52 b) are biased in the roller direction so that the tip portions of the first and second blades (51 a, 52a, 51b, 52 b) are in contact with the roller, and the center of the coil spring is located on the bearing side with respect to the center in the height direction of the cylinder.

4. A rotary refrigeration unit according to claim 1 wherein: the refrigerant pipe (P) is connected with the rotary compressor, the condenser (20), the expansion device (21) and the evaporator (22).