CN107061276B

CN107061276B - Rotary compressor

Info

Publication number: CN107061276B
Application number: CN201710184715.0A
Authority: CN
Inventors: 小津政雄; 吴延平
Original assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2017-03-24
Filing date: 2017-03-24
Publication date: 2019-12-06
Anticipated expiration: 2037-03-24
Also published as: CN107061276A

Abstract

The invention discloses a rotary compressor, which comprises: the compressor comprises a piston, a first slide sheet and a second slide sheet, wherein the piston revolves in a cylindrical compression cavity formed by a cylinder, and the first slide sheet and the second slide sheet are arranged in a first slide sheet groove and a second slide sheet groove of the cylinder; at least one vent hole formed in the first slide and opening into the compression chamber; an exhaust valve for opening and closing the exhaust hole is arranged on the side surface of the first sliding sheet; the high pressure gas passing through the exhaust hole is exhausted to a high pressure chamber enclosed between the first slide plate, the second slide plate and the outer periphery of the piston. By adding the second vane, a high-pressure chamber, which is a rectangular chamber, is disposed at the tip of the two vanes and the outer periphery of the piston. The high-pressure gas passing through the exhaust hole is exhausted into the high-pressure cavity, so that the volume of the exhaust gap can be effectively reduced.

Description

Rotary compressor

Technical Field

The present invention relates to a rotary compressor.

Background

The exhaust device of the rotary compressor is composed of an exhaust hole and an exhaust valve, and the exhaust hole is generally disposed in any one of a main bearing and a sub-bearing of a sealed compression chamber. As a result, the exhaust hole is positioned to face the vane side surface and is oriented in a right angle direction, and the exhaust hole is separated from the vane side surface. Thus, after the piston moves from the exhaust stroke to the intake stroke, an exhaust gap volume occurs. The volume of the discharge gap is about 1% of the discharge volume of the rotary compressor in the conventional design.

in an application example of the air conditioner (refrigerant R410A), the compression ratio (ratio of high pressure to low pressure) is about 3.4, and the loss of the cooling capacity in the re-expansion loss caused by the exhaust gap volume of 1% is: 1.0% X3.4 ═ 3.4%. In the application of the refrigerating apparatus, the compression ratio becomes large, and the loss of the refrigerating capacity further increases. The re-expansion loss is a phenomenon in which a substantial amount of intake gas is reduced because high-pressure gas (exhaust gap volume) remaining in the compression chamber without being discharged flows out to a low-pressure side (intake side) of the compression chamber during revolution of the piston and re-expands.

Disclosure of Invention

The present invention is directed to solving, at least to some extent, one of the technical problems in the related art. To this end, the invention proposes a rotary compressor having a small discharge gap volume.

the rotary compressor according to the present invention comprises: the compressor comprises a piston, a first slide sheet and a second slide sheet, wherein the piston revolves in a cylindrical compression cavity formed by a cylinder, and the first slide sheet and the second slide sheet are arranged in a first slide sheet groove and a second slide sheet groove of the cylinder, and the first slide sheet and the second slide sheet respectively reciprocate through the piston; at least one vent hole in said first slide opening to said compression chamber; an exhaust valve for opening and closing the exhaust hole is arranged on the side surface of the first sliding sheet; and high-pressure gas passing through the exhaust hole is exhausted to a high-pressure cavity enclosed among the first sliding sheet, the second sliding sheet and the periphery of the piston.

According to the rotary compressor of the present invention, the second vane is added, and a high-pressure chamber, which is a rectangular chamber surrounded by the tip ends of the two vanes and the outer periphery of the piston, is disposed. The high-pressure gas passing through the exhaust hole is exhausted into the high-pressure cavity, so that the volume of an exhaust gap can be effectively reduced, and the performance of the rotary compressor can be improved.

In some examples of the present invention, a curved surface that enlarges an opening degree of the exhaust valve is provided on a side of the first vane groove opening end.

in some examples of the present invention, the open hole end wall of the first vane groove is provided with a notch groove that opens to the exhaust hole.

In some examples of the invention, a high pressure chamber between the first vane and the second vane communicates with a muffler disposed on a bearing sealing an open end of the compression chamber.

In some examples of the invention, a cutout is provided that enlarges the volume of the high pressure chamber.

In some examples of the present invention, any one of the first vane and the second vane is a swinging vane.

In some examples of the present invention, springs respectively pressing the first vane and the second vane to the piston side are provided, and the spring of the first vane is larger than the spring of the second vane.

in some examples of the present invention, the first vane and the second vane are located on a same side of a suction hole of the cylinder and the second vane is located close to the suction hole with respect to the first vane.

In some examples of the present invention, the discharge valve is integrated on the first vane, and the rotary compressor further includes: and the fixed valve is fixed at the fixed end part of the exhaust valve.

In some examples of the present invention, the exhaust holes are two and spaced apart in a height direction of the first vane, and the exhaust valves are two and correspond to the two exhaust holes, respectively.

Drawings

Fig. 1 is a longitudinal sectional view of a rotary compressor according to embodiment 1;

FIG. 2 is a plan view showing a cross section of FIG. 1X-X in relation to embodiment 1;

FIG. 3 is a component diagram of a first vane relating to embodiment 1;

FIG. 4 is a view showing the completion of the assembly of the first vane relating to embodiment 1;

FIG. 5 is a detailed view of a vane groove of the cylinder according to embodiment 1;

FIG. 6 is a plan view showing a cross section of FIG. 1Y-Y in relation to embodiment 1;

FIG. 7 is a completed assembled view of the first vane relating to embodiment 2;

FIG. 8 is a longitudinal sectional view of the rotary compressor according to embodiment 2;

Fig. 9 is a cross-sectional view of the cylinder center according to embodiment 3.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

Embodiment 1:

Fig. 1 is a longitudinal sectional view of the rotary compressor 1. An electric motor 6 and a compression element 5 driven by the motor 6 are fixed in the cylindrical housing 2. The compression element 5 includes a cylinder 10 fixed in the housing 2, and a main bearing 50 and a sub-bearing 55 fixed to the cylinder 10 by screws, and the main bearing 50 and the sub-bearing 55 are disposed to face each other in the vertical direction. The compression chamber 15 disposed at the center of the cylinder 10 may be sealed by the main bearing 50 and the sub-bearing 55. Lubricating oil is sealed in the bottom of the housing 2, and the lubricating oil is used to lubricate the kinematic pairs, i.e., the mating parts that move relative to each other.

The motor 6 includes a stator and a rotor 6b, a crankshaft 40 driven by the rotor 6b includes a main shaft 41, a sub shaft 43, and an eccentric shaft 44, the main shaft 41 and the sub shaft 43 are slidably engaged with a main bearing 50 and a sub bearing 55, respectively, the eccentric shaft 44 is capable of revolving, the eccentric shaft 44 is used for driving the piston 35 disposed in the compression chamber 15, and the eccentric shaft 44 is capable of revolving the piston 35. Wherein the compression chamber 15 is cylindrical. As shown in fig. 2, the compression element 5 may further include a first vane 20 contacting an outer periphery of the piston 35, and the first vane 20 reciprocates in the first vane groove 12 of the cylinder 10 by the revolution of the piston 35.

Fig. 2 is a cross section in the X-X direction of fig. 1, which is a plan view of a center cross section of the cylinder 10. As shown in fig. 2, the central side of the front end of the first sliding vane 20 is provided with a vent hole 25, the vent hole 25 is opened in the compression chamber 15, in other words, the vent hole 25 is in communication with the compression chamber 15. The front end, i.e. the end of the first vane 20 close to the compression chamber 15. As the first vane 20 reciprocates, the opening area of the discharge hole 25 inside the compression chamber 15 changes. That is, the circular exhaust hole 25 is fully opened in a range where the stroke length of the first vane 20 is large, and is reduced when the stroke length becomes zero.

As shown in fig. 2, the rotary compressor 1 further includes a second vane 30 disposed in a second vane groove of the cylinder 10, and the first vane 20 and the second vane 30 reciprocate by the piston 35. The first vane 20 and the second vane 30 are adjacent to each other. The first sliding piece 20 has a surface opened in the exhaust hole 25, and an exhaust valve 23 is provided inside the first sliding piece, and the exhaust valve 23 is used for opening and closing the exhaust hole 25. The second vane 30 on one side has a structure that is basically the same as that of the conventional vane, and the description thereof is omitted. The second vane 30 is characterized by being located between the first vane 20 and the suction hole 16, in other words, the first vane 20 and the second vane 30 are located on the same side of the suction hole 16, and the second vane 30 is located close to the suction hole 16 with respect to the first vane 20.

In the present invention, the second vane 30 is added, and a high-pressure chamber 14, which is a rectangular chamber, is disposed at the tip of the two vanes and the outer periphery of the piston 35. The high pressure gas passing through the discharge hole 25 is discharged to the high pressure chamber 14 enclosed between the first vane 20, the second vane 30, and the outer circumference of the piston 35. The high-pressure chamber 14 is a chamber in which high-pressure gas discharged from the gas discharge hole 25 is temporarily accumulated and a gas discharge passage to the main bearing gas hole 51 (fig. 1), and the volume thereof is constantly changed in accordance with the revolution of the piston 35.

As shown in fig. 1, the rotary compressor 1 is further provided with a suction pipe 4 connected to the casing 2, and the suction pipe 4 is connected to a reservoir tank 7. The rotary compressor 1 is further provided with an exhaust pipe 3 connected to an upper end of the casing 2, and the exhaust pipe 3 is connected to a condenser of the refrigeration cycle.

The low-pressure refrigerant discharged from the liquid storage tank 7 is discharged from the air suction pipe 4, flows into the compression cavity 15 and is discharged to the high-pressure cavity 14; wherein the main bearing 50 is formed with a main bearing air hole 51, and the main bearing 50 is further provided with a silencer 52. The high-pressure refrigerant flows out from the main bearing air hole 51 to the muffler 52, and is discharged to the casing 2 through the muffler discharge hole 52 a. Therefore, the internal pressure of the casing 2 of the rotary compressor 1 is on the high-pressure side as in the conventional art. However, the present invention can be easily applied even if the internal pressure of the casing 2 is on the low pressure side. Also, it can be easily applied to a two-cylinder rotary compressor composed of two cylinders and a 2-stage compression method.

next, referring to fig. 2, the revolution angle Θ of the piston 35, which is an angle from the center of the first vane 20 to the minimum gap between the outer periphery of the piston 35 and the inner diameter of the compression chamber 15, will be described in detail. In the compression chamber 15, the left chamber at the angle Θ is the suction side chamber 15a, and the right chamber is the compression side chamber 15 b. When the rotary compressor 1 is applied to an air conditioner (refrigerant R410A), the theoretical discharge angle Θ of high-pressure gas under high-load operating conditions is 201 degrees, and Θ under practical conditions (APF (annual performance Factor-annual energy consumption rate) conditions or the like) in which the operating time is the longest is about 180 degrees, and at this angle, the gas in the compression-side chamber 15b reaches the discharge pressure and the discharge valve 23 is opened.

When θ is 180 degrees, the stroke of the first vane 20 is maximized, the opening degree of the discharge hole 25 in the compression chamber 15 is maximized, and the high-pressure gas in the compression-side chamber 15b is discharged from the discharge hole 25 toward the high-pressure chamber 14. At this time, the exhaust amount is maximized, the gas resistance through the exhaust hole 25 is small, and the pressure loss is small.

Thereafter, as Θ moves by 360 degrees, the stroke of the first vane 20 decreases, and the effective opening degree of the exhaust valve 23 decreases. However, the amount of exhaust gas from the compression-side chamber 15b decreases, and therefore, the pressure loss through the exhaust valve 23 does not increase excessively. Means for maintaining the opening degree of the exhaust valve 23 when the stroke of the first vane 20 is reduced is shown in fig. 5.

FIG. 3 is an assembled view of the first vane 20. The first vane 20 includes a vane plate 21, and the vane plate 21 is subjected to abrasion resistance treatment after the valve accommodating groove 20a and the exhaust hole 25 are processed, and then precision grinding is performed. In the next assembly process, the exhaust valve 23 and the fixed valve 24 are fitted into the valve accommodating groove 20a, and the fixed valve 24 is fixed to the fixed end of the exhaust valve 23. The specific fixing method may be rivet fixing, in which an assembly rivet 27 is pressed into the rivet hole 26, as shown in fig. 4, to complete the assembly of the first vane 20. Wherein, the head of the exhaust valve 23 is provided with a circular structure 23a corresponding to the exhaust hole 25.

The fixed valve 24 is a means for relaxing stress concentrated on the fixed end side of the exhaust valve 23. The rivet 27 can be replaced by a small screw, which has no influence on this. The rear surface projection 21d on the slider plate 21 is a projection into which the coil spring 28 is fitted. As shown in fig. 4, the coil spring 28 can press the first vane 20 to the outer periphery of the piston 35.

referring back to fig. 3, a design of the first vane 20 will be described. The thickness of the first vane 20 was 3mm as in the conventional case; the depth of the valve receiving groove 20a may be 1.7 mm. The circular valve seat protrusion, on which the discharge valve 23 is mounted, must be on the same plane as the valve receiving groove 20a, and thus, the thickness of the discharge hole 25 may be 1.3 mm. That is, the thickness of the air vent 25 is the same as that of the conventional air vent.

The thicknesses of the exhaust valve 23 and the fixed valve 24 may be in the range of 0.2mm to 0.3mm, respectively, and thus the total is about 0.5mm, and the height of the head of the rivet 27 does not exceed 1.2mm, and there is no problem in design. However, since the inner diameter of the first spring hole 18 for housing the coil spring 28 can be about 10mm, the head of the rivet 27 does not interfere with the first vane groove 12 even if it protrudes outward from the side surface of the first vane 20.

Here, the maximum stroke of the first vane 20 is regarded as 5m, the inner diameter of the exhaust hole 25 is regarded as 6mm, and the inner diameter of the exhaust hole 25 is regarded as 0.037 cc; the exhaust volume of this model is regarded as 15cc (corresponding to 1HP level), and the ratio of the exhaust gap volume is about 0.25%, which is reduced to 1/4-1/5 of the conventional equivalent model. That is, the re-expansion loss is greatly improved.

the rotary compressor 1 is provided with a cutout that enlarges the volume of the high pressure chamber 14. Through the reasonable arrangement of the cut-outs, the volume of the high-pressure cavity 14 can be made appropriate, so that the volume of the exhaust gap can be effectively reduced.

Fig. 5 is a schematic view of a valve stopper groove 12a formed in the first vane groove 12 of the cylinder 10, a D-shaped notch groove 12b formed in the opposite surface thereof, and a U-shaped groove 14a disposed between the two vanes. A valve stopper groove 12a and a D-shaped notch groove 12b are provided on the opposite end surfaces of the first vane groove 12, respectively. First, the valve stopper groove 12a is gradually curved into a discharge surface shape facing the opening end thereof, and opens into the compression chamber 15, as in the conventional exhaust valve stopper. On one side of the opening end of the first vane groove 12, a curved surface that enlarges the opening of the exhaust valve 23, i.e., a valve stopper groove 12a, is disposed.

The D-shaped notch 12b is opened to the exhaust hole 25, in other words, the notch 12b communicates with the exhaust hole 25. The D-shaped notch groove 12b is located on the wall surface of the first vane groove 12 facing the valve stopper groove 12a, and is shown in detail in the right side of fig. 5 (indicated by an arrow in the Z direction).

When the compression-side chamber 15b reaches the discharge pressure, the discharge hole 25 opens and the discharge valve 23 opens, as shown in fig. 2. Meanwhile, the upper surface of the discharge valve 23 integrated with the first slide plate 20 moves forward and backward, so that the discharge valve 23 is slidably bent at the surface of the valve stopper groove 12 a. That is, if the curvature of the valve stopper groove 12a is designed to be larger than the curvature of the exhaust valve 23 curved in the exhaust, the front end of the exhaust valve 23 does not interfere with the surface of the valve stopper groove 12 a.

When the piston pivot angle Θ exceeds 180 degrees, the stroke length of the first vane 20 becomes short. When θ is 360 degrees, the tip of the first vane 20 is accommodated in the first vane groove 12, and the exhaust hole 25 is accommodated in the first vane groove 12, so that a part of the exhaust gas from the compression side chamber 15b is not discharged and remains.

The D-shaped notch 12b is a means for avoiding this problem. Even if Θ is 360 degrees, the opening area of the discharge hole 25 is more than 50%, and the discharge hole 25 can communicate with the compression chamber 15. After the D-shaped notch groove 12b is greatly enlarged, the exhaust gap volume is increased, and the notch width may be the same as the inner diameter of the exhaust hole 25.

The discharge hole 25 and the D-shaped notch groove 12b opened in the compression side chamber 15b become a discharge gap volume; the valve stopper groove 12a or the U-groove 14a disposed between the two vanes cannot provide an exhaust gap volume. The second vane 30 reciprocating in the second vane groove 13 is a means for preventing the high-pressure gas flowing out between the two vanes from flowing into the suction side chamber 15 a.

here, as a principle of the rotary compressor, the pressure of the vane back chamber 11 in the lubricating oil of the casing 2 is slightly lower than the pressure of the high pressure chamber 14 and higher than the pressure of the compression side chamber 15 b. Therefore, the exhaust valve 23 or the valve stopper groove 12a is lubricated by the spray oil mixed in the high-pressure gas in the high-pressure chamber 14. This is the same as in the prior art discharge valve by way of discharge lubrication from the compression chamber 15.

The sliding surface side of the first vane 20 having the exhaust hole 25 opened therein is lubricated with the lubricating oil in the vane back surface chamber 11 as in the conventional case. Therefore, there is no problem with lubrication of the first vane 20. The same is true for the second slide 30 without the exhaust valve.

Next, with respect to the first vane 20, the pressing force from the vane back surface chamber 11 side to the outer periphery of the piston 35 is confirmed. About 50% of the front end R of the first vane 20 opens into the high pressure chamber 14; the remaining about 50% ranges from low pressure to high pressure. About 50% of the tip R of the second vane 30 opens into the suction-side chamber 15 a; about 50% of the remaining, open to the high pressure chamber 14.

Therefore, the pressing force of the piston 35 is set to be the second vane 30 > the first vane 20, and it is recommended that the center positions of the leading ends of the first vane 20 and the second vane 30 be asymmetric in the shape close to the high-pressure chamber 14 instead of the design.

fig. 6 is a plan view of a section in the Y-Y direction of fig. 1. In the plane of the cylinder 10, the main bearing 50 and the main muffler 52 are fixed by four screws 38. The main bearing air hole 51 is opened in the high pressure chamber 14 and the U groove 14a, and therefore, the high pressure gas in the high pressure chamber 14 is discharged into the main muffler 52, and thereafter, is discharged into the housing 2 from the muffler discharge hole 52 a. According to fig. 6, the main bearing 40 has not conventionally been provided with an exhaust hole, an exhaust valve, and a valve accommodating groove. As a result, the rigidity of the main bearing 40 can be greatly improved.

Further, springs for pressing the first vane 20 and the second vane 30 to the piston side are provided, and the spring of the first vane 20 is larger than the spring of the second vane 30. Thus, the elastic force of the spring of the first slide plate 20 is greater than that of the spring of the second slide plate 30, and the first slide plate 20 can be driven to reciprocate better.

Embodiment 2

As shown in fig. 7, since the rotary compressor of embodiment 2 has a larger discharge capacity than that of embodiment 1 and the vane height increases, two sets of the discharge holes 25 and the discharge valves 23 are arranged in parallel in the first vane 60, the two sets of the discharge holes 25 are spaced apart in the height direction of the first vane 20, and the two discharge valves 23 correspond to the two discharge holes 25 one by one, respectively. . After the compression element 8 is assembled by using the first vane 60, the rotary compressor 101 shown in fig. 8 is completed.

in embodiment 2, a sub-bearing air hole 56 is added in addition to the main bearing air hole 51. Therefore, the high-pressure gas discharged from the sub-bearing gas hole 56 is discharged to the main muffler 52 through the sub-muffler 57 and the cylinder through hole 19, and thereafter, is mixed with the gas discharged from the main bearing gas hole 51, and is discharged from the muffler gas discharge hole 52 a.

Embodiment 3

Embodiment 3 shown in fig. 9 is a design in which the first vane 20 disclosed in embodiment 1 is applied to a swing type rotary compressor. Fig. 9 corresponds to the X-X section of fig. 1. The first vane 70 is integrated with the piston 35 because of the rocking type. The second vane 80 corresponds to the second vane 30 of embodiment 1. As in embodiment 1, the second vane 80 having the exhaust port 25 and the exhaust valve 23 may be disposed at the position of the first vane 70, or the general oscillating vane 70 may be disposed at the position of the second vane 80. That is, any one of the first and second vanes 70 and 80 may be a swing vane.

The rotary compressor according to the present invention is mounted on an air conditioner, a refrigeration equipment, a water heater, or the like. And, it can be applied to a swing type rotary compressor, a horizontal type rotary compressor or a shell low pressure type rotary compressor in which a piston and a vane are integrated. Manufacturing can of course also be achieved using existing equipment.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

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

Claims

1. A rotary compressor, comprising: the compressor comprises a piston, a first slide sheet and a second slide sheet, wherein the piston revolves in a cylindrical compression cavity formed by a cylinder, and the first slide sheet and the second slide sheet are arranged in a first slide sheet groove and a second slide sheet groove of the cylinder, and the first slide sheet and the second slide sheet respectively reciprocate through the piston;

At least one vent hole in said first slide opening to said compression chamber;

An exhaust valve for opening and closing the exhaust hole is arranged on the side surface of the first sliding sheet;

and high-pressure gas passing through the exhaust hole is exhausted to a high-pressure cavity enclosed among the first sliding sheet, the second sliding sheet and the periphery of the piston.

2. The rotary compressor according to claim 1, wherein a curved surface that enlarges an opening degree of the discharge valve is provided on a side of the first vane groove opening end.

3. The rotary compressor according to claim 1, wherein a notch groove opened to the discharge hole is provided in an opening end wall of the first vane groove.

4. the rotary compressor of claim 1, wherein a high pressure chamber between the first vane and the second vane communicates with a muffler disposed on a bearing sealing an open end of the compression chamber.

5. The rotary compressor of claim 1, wherein a cutout is provided to enlarge the volume of the high pressure chamber.

6. The rotary compressor of claim 1, wherein any one of the first vane and the second vane is a wobble vane.

7. The rotary compressor according to claim 1, wherein springs for pressing the first vane and the second vane to the piston side are provided, and the spring of the first vane is larger than the spring of the second vane.

8. The rotary compressor of claim 1, wherein the first vane and the second vane are located on a same side of a suction hole of the cylinder and the second vane is located close to the suction hole with respect to the first vane.

9. The rotary compressor of claim 1, wherein the discharge valve is integrated on the first vane, the rotary compressor further comprising: and the fixed valve is fixed at the fixed end part of the exhaust valve.

10. The rotary compressor of claim 1, wherein the discharge holes are two and spaced apart in a height direction of the first vane, and the discharge valves are two and correspond to the two discharge holes, respectively.