JPWO2020170361A1 - Rolling piston type compressor and refrigeration cycle equipment - Google Patents

Abstract

The rolling piston type compressor is a rolling piston type compressor having a compression mechanism portion in a closed container, and the compression mechanism portion has a cylinder, an upper bearing, and a lower bearing, and has a suction connecting path and a suction path. In the middle of the suction path of the cylinder, on the side opposite to the connection side of the suction communication path, a step is formed that projects toward the compression chamber side to receive the refrigerant, and the circumferential direction between the suction path of the cylinder and the vane groove. A protrusion is formed between the protrusions, a first gap is formed between the upper end of the protrusion and the upper bearing, and a second gap is formed between the lower end of the protrusion and the lower bearing. The protrusion has the flexibility to flex elastically in the pressing direction due to the compressive load when a compressive load is applied to the vane by the refrigerant in the compression chamber.

Description

The present invention relates to a rolling piston type compressor and a refrigeration cycle device having a compression mechanism in a closed container.

As a conventional rolling piston type compressor, there is one described in Patent Document 1. In the technique of Patent Document 1, the crankshaft has an eccentric portion. A cylinder is provided on the outer peripheral side of the eccentric portion and is formed in a cylindrical shape. The piston rotates following the eccentric portion, and a compression chamber is formed between the eccentric portion and the cylinder. The upper bearing and the lower bearing block both end faces of the cylinder. Further, the cylinder is formed with a suction passage extending from the outer peripheral surface to the cylinder chamber.

Here, since the refrigerant pressure of the carbon dioxide refrigerant is higher than the refrigerant pressure of the freon-based refrigerant, the load on the bearing is large, the differential pressure is large, and the adverse effect due to the refrigerant leakage is large. Therefore, in order to reduce the bearing load and improve the efficiency of the compressor, it is effective that the cylinder has a thinner thickness when the carbon dioxide refrigerant is used as compared with the compressor using a refrigerant other than the carbon dioxide refrigerant.

If the thickness of the cylinder is thin, a sufficient passage cross-sectional area cannot be secured when a suction passage is formed in the cylinder. Therefore, the pressure loss of the intake refrigerant is increased, which causes a decrease in efficiency.

Therefore, suction connecting paths connecting to the suction passages are formed in the upper and lower bearings and lower bearings that block the cylinders, so that the cross-sectional area of the passages is sufficiently secured and the pressure loss of the suction refrigerant is reduced. (See, for example, Patent Document 2).

Japanese Unexamined Patent Publication No. 2006-200504 Japanese Unexamined Patent Publication No. 2001-82369

In the conventional closed type compressor of this kind, the high pressure chamber and the low pressure chamber are separated by a vane at the time of driving. Therefore, the high-pressure refrigerant gas in the high-pressure chamber presses the vane against the vane groove. As a result, there is a problem that one-sided contact occurs between the radial inner end of the cylinder and the side surface of the vane in the vane groove, the local surface pressure increases, and the wear increases.

Further, in the conventional rotary compressor having a suction connecting path in the upper bearing or the lower bearing, when the refrigerant flows into the compression chamber formed by the cylinder and the piston from the suction connecting path provided in the bearing, the refrigerant flow path The cross-sectional area of is narrowed. Therefore, even if a suction connecting path having an opening diameter similar to that of the conventional one is formed, the pressure loss of the suction refrigerant cannot be substantially reduced.

The present invention is for solving the above problems, and when driving the compressor, one-sided contact between the vane and the cylinder is prevented, the lubricity of the vane is improved, and when the refrigerant is guided from the suction pipe to the compression chamber. It is an object of the present invention to obtain a rolling piston type compressor and a refrigeration cycle device in which a sufficient cross-sectional area of the refrigerant flow path is secured and the pressure loss of the inflowing refrigerant can be reduced.

The rolling piston type compressor according to the present invention is a rolling piston type compressor having a compression mechanism portion in a closed container, and the compression mechanism portion has a vane groove in which a compression chamber is formed and vanes are arranged. It has a formed cylinder, an upper bearing that covers the upper end surface of the cylinder, and a lower bearing that covers the lower end surface of the cylinder, and sucks the refrigerant through a suction hole formed in either the upper bearing or the lower bearing. A suction connecting path to be provided and a suction path for flowing a refrigerant from the suction connecting path to the compression chamber are provided on the radial side of the compression chamber of the cylinder, and in the middle of the suction path of the cylinder. On the side opposite to the connection side of the suction communication path, a step is formed so as to project toward the compression chamber side to receive the refrigerant, and the circumferential direction between the suction path of the cylinder and the vane groove is described as described above. A protrusion protruding toward the compression chamber is formed, a first gap is formed between the upper end of the protrusion and the upper bearing, and a first gap is formed between the lower end of the protrusion and the lower bearing. A second gap is formed, and the protrusion has the flexibility to flex elastically in the pressing direction due to the compressive load when a compressive load is applied to the vane by the refrigerant in the compressor chamber. ..

The refrigeration cycle apparatus according to the present invention includes the above-mentioned rolling piston type compressor.

According to the rolling piston type compressor and the refrigeration cycle apparatus according to the present invention, when a compressive load is applied to the vane by the refrigerant in the compression chamber, the protrusions are elastically flexed in the pressing direction due to the compressive load. Has. As a result, it is possible to prevent one-sided contact between the vane and the cylinder when the compressor is driven. In the middle of the suction path, a step is formed on the side opposite to the connection side of the suction communication path, which protrudes toward the compression chamber and receives the refrigerant. As a result, in the suction path, a sufficient cross-sectional area of the medium flow path can be secured when guiding the refrigerant from the suction pipe to the compression chamber. Therefore, one-sided contact between the vane and the cylinder is prevented when the compressor is driven, the lubricity of the vane is improved, and a sufficient cross-sectional area of the refrigerant flow path is secured when guiding the refrigerant from the suction pipe to the compression chamber. The pressure loss of the inflow refrigerant can be reduced.

It is explanatory drawing which shows the rolling piston type compressor which concerns on Embodiment 1 of this invention in the vertical cross section. It is explanatory drawing which shows the compression mechanism part which concerns on Embodiment 1 of this invention in the cross section. It is explanatory drawing which shows the suction connecting path and the suction path which concerns on Embodiment 1 of this invention in the vertical cross section of the line AA of FIG. It is explanatory drawing which shows the protrusion | protrusion which concerns on Embodiment 1 of this invention in the vertical cross section of line BB of FIG. It is explanatory drawing which shows the cutting process of the suction path which concerns on Embodiment 1 of this invention. It is a flowchart which shows the cutting process of the suction path which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the suction connecting path and the suction path of the comparative example 1 in a vertical cross section. It is explanatory drawing which shows the suction connecting path and the suction path of the comparative example 2 in the vertical cross section. It is a refrigerant circuit diagram which shows the refrigerating cycle apparatus which applied the rolling piston type compressor which concerns on Embodiment 2 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each figure, those having the same reference numerals are the same or equivalent thereof, and they are common in the entire text of the specification. Further, in the cross-sectional view, hatching is appropriately omitted in view of visibility. Furthermore, the forms of the components shown in the full text of the specification are merely examples and are not limited to these descriptions.

Embodiment 1.
FIG. 1 is an explanatory view showing a compressor 100, which is a rolling piston type compressor according to the first embodiment of the present invention, in a vertical cross section. FIG. 2 is an explanatory view showing a compression element 5 which is a compression mechanism portion according to the first embodiment of the present invention in a cross section. As shown in FIG. 1, the compressor 100 is connected to, for example, the evaporator 104 of the refrigeration cycle device 101 shown with reference to FIG. 9 by the suction pipe 7a, and the condenser 102 of the refrigeration cycle device 101 by the discharge pipe 7b. Connected and used.

The closed container 2 that constitutes the appearance of the compressor 100 is composed of a substantially cylindrical body portion 21, a substantially hemispherical upper lid portion 22, and a lower lid portion 23. The upper lid portion 22 is welded to the upper portion of the body portion 21, and the lower lid portion 23 is welded to the lower portion of the body portion 21. The closed container 2 is provided on the pedestal 3. The lower lid portion 23 and the pedestal 3 are fixed. In the compressor 100, the pedestal 3 is fixed to the installation location by bolts or the like in the normal installation state.

Inside the closed container 2, an electric element 4 constituting a drive unit and a compression element 5 constituting a compression mechanism unit are housed.

The electric element 4 is composed of a stator 41 fixed to the inner peripheral surface of the body 21 of the closed container 2 and a rotor 42 arranged with a slight gap inside the stator 41. The stator 41 and the body portion 21 are fixed by spot welding or shrink fitting. The electric element 4 is connected to a terminal 6a attached to the central portion of the upper lid portion 22 via a lead wire 6b. Electric power is supplied from the terminal 6a to the electric element 4 via the lead wire 6b.

The compression element 5 is composed of a crankshaft 51, a cylinder 52, an upper bearing 53, a lower bearing 54, a roller 55, and a vane 56. The body portion 21 and the upper bearing 53 are fixed by spot welding. The crankshaft 51 has a roller 55 on the outer peripheral portion of the eccentric portion 51a eccentric in one direction, and is inserted and fixed to the central portion of the rotor 42 of the electric element 4. The cylinder 52 is a tubular member and forms a compression chamber 52a concentric with the crankshaft 51 inside. The cylinder 52 is formed with a vane groove 52e for arranging the vane 56. The upper bearing 53 and the lower bearing 54 support the crankshaft 51. An upper bearing 53 is arranged at the upper end of the cylinder 52 to cover the upper end surface of the cylinder 52. A lower bearing 54 is arranged at the lower end of the cylinder 52 to cover the lower end surface of the cylinder 52. The roller 55 is mounted in the cylinder 52 as an eccentric portion 51a of the crankshaft 51. The vane 56 is inserted into a vane groove 52e provided in the cylinder 52, and divides the compression chamber 52a into a low pressure chamber 52g and a high pressure chamber 52h.

The body portion 21 is provided with a through hole. The suction pipe 7a is connected to the through hole. The tip of the suction pipe 7a is inserted into a suction hole 53a provided in the upper bearing 53. The suction hole 53a is connected to the suction communication path 53b processed horizontally with the crankshaft 51 from the lower end surface of the upper bearing 53. The suction connecting path 53b sucks the refrigerant gas through the suction holes 53a formed in the upper bearing 53.

The suction connecting path 53b of the upper bearing 53 is provided on the outer peripheral side of the compression chamber 52a of the cylinder 52 and is connected to the suction path 52b having the stepped 52c. The suction path 52b allows the refrigerant to flow from the suction connecting path 53b to the compression chamber 52a on the outer side in the radial direction from the compression chamber 52a of the cylinder 52.

The cylinder 52 is formed with a vane groove 52e extending in the radial direction from between the suction path 52b and the discharge port 52d. The vane groove 52e extends from the compression chamber 52a outward in the radial direction of the cylinder 52 and penetrates both the upper and lower surfaces of the cylinder 52. The outer peripheral side of the vane groove 52e is also connected to the outer peripheral hole 52f that penetrates both the upper and lower surfaces. A vane 56 that separates the compression chamber 52a into a low-pressure chamber 52g on the low-pressure side and a high-pressure chamber 52h on the high-pressure side is inserted into the vane groove 52e. In the vane 56, the tip of the vane 56 on the inner side in the radial direction is in contact with the outer peripheral surface of the roller 55 by a spring 57 housed in a hole 52f which is a back portion on the outer side in the radial direction. A discharge port 52d is provided on the high pressure chamber 52h side near the vane 56. The discharge port 52d communicates with an opening that opens in the internal space of the closed container 2.

The cylinder 52 is formed with an elastically deformable protrusion 52j between the suction path 52b having the width a1 and the vane groove 52e. The protrusion 52j projects toward the compression chamber 52a between the suction path 52b of the cylinder 52 and the vane groove 52e in the circumferential direction. The protrusion 52j has the flexibility to elastically bend the vane 56 in the pressing direction due to the compressive load when a compressive load is applied by the refrigerant gas in the compression chamber 52a.

FIG. 3 is an explanatory view showing the suction connecting path 53b and the suction path 52b according to the first embodiment of the present invention in a vertical cross section of the line AA of FIG. As shown in FIG. 3, in the middle of the suction path 52b of the cylinder 52, a stepped 52c is formed on the side opposite to the connection side of the suction communication path 53b, protruding toward the compression chamber 52a and receiving the refrigerant gas. There is. The stepped 52c is a one-step stepped portion. The stepped 52c is a flat plate having a flat surface on the connecting side of the suction connecting path 53b, which is bent at a right angle from the vertical wall surface of the space portion forming the suction path 52b. When forming the stepped 52c, a space portion formed by cutting in the vertical direction with the tool 10 shown in reference to FIG. 5 from the connection side of the suction connecting path 53b and hollowing out in the vertical direction forms the suction path 52b. It is formed. Then, from the position where the space portion where the suction path 52b is formed is formed, the space portion where the suction path 52b is formed is expanded by cutting to the compression chamber 52a side by the tool 10, and the space portion is flat facing upward of the stepped 52c. A surface is formed. After that, the space portion forming the suction path 52b by cutting on the side opposite to the connection side of the suction communication path 53b by the tool 10 penetrates in the vertical direction, and the tip portion 52c1 on the compression chamber 52a side of the stepped 52c penetrates. It is formed. As a result, a flat plate-shaped one-step stepped 52c is formed. The stepped 52c has a width a2 on the lower surface on the outer peripheral side and a length a3 protruding toward the compression chamber 52a in the suction path 52b of the cylinder 52. The space portion forming the suction path 52b on the inner peripheral side of the stepped 52c penetrates both the upper and lower surfaces and communicates with the compression chamber 52a.

FIG. 4 is an explanatory view showing the protrusion 52j according to the first embodiment of the present invention in a vertical cross section of the line BB of FIG. As shown in FIG. 4, a first gap 60a is formed between the upper end portion of the protrusion 52j and the upper bearing 53. A second gap 60b is formed between the lower end of the protrusion 52j and the lower bearing 54. The first gap 60a and the second gap 60b secure a gap so as not to come into contact with the upper bearing 53 and the lower bearing 54 attached to the cylinder 52 on the upper and lower end surfaces of the protrusion 52j, respectively. In the first gap 60a and the second gap 60b, for example, the depth of the gap, that is, the gap to be formed is set to 0.1 to 0.15 mm.

<Cutting process of stepped 52c>
FIG. 5 is an explanatory view showing a cutting process of the suction path 52b according to the first embodiment of the present invention. FIG. 6 is a flowchart showing a cutting process of the suction path 52b according to the first embodiment of the present invention.

As shown in FIG. 5, the stepped 52c is machined through a continuous cutting process by a tool 10 such as an end mill. The tool 10 communicates with the control unit 11 via a wired or wireless communication line 12 to control the cutting process. The control unit 11 is hardware that executes so-called cutting software processing.

As shown in FIGS. 5 and 6, in step S1, the control unit 11 cuts downward from the connection side of the suction connecting path 53b by the tool 10 and cuts the surface of the stepped 52c in the vertical direction. A space portion that serves as an inhalation route 52b up to is formed.

In step S2, the control unit 11 cuts and sucks from the position where the space portion serving as the suction path 52b to the surface of the stepped 52c is formed by the tool 10 to the center side of the cylinder 52 on the compression chamber 52a side. A flat surface of the stepped 52c is formed while expanding the space portion serving as the path 52b toward the compression chamber 52a.

In step S3, the control unit 11 is machined by the tool 10 on the side opposite to the connection side of the suction communication path 53b to penetrate the space portion to be the suction path 52b in the vertical direction in the radial direction of the stepped 52c. The inner tip portion 52c1 is formed. As a result, the stepped 52c is formed in the shape of a one-step flat plate.

<Operation of compressor 100>
When power is supplied through the terminal 6a, the crankshaft 51 fixed to the rotor 42 rotates about the crankshaft 51. As a result, the refrigerant gas is sucked into the compression chamber 52a from the refrigeration cycle device 101 through the suction pipe 7a and the suction path 52b, and is compressed by the eccentric movement of the roller 55 in the compression chamber 52a. The compressed high-pressure refrigerant gas is released into the closed container 2, and the inside of the closed container 2 is in a high-pressure state. The high-pressure refrigerant gas in the closed container 2 is discharged to the refrigeration cycle device 101 by the discharge pipe 7b. The crankshaft 51 exists on the center line of the body portion 21.

Then, in the compression process, the vane 56 that protrudes into the compression chamber 52a and separates the low pressure chamber 52g and the high pressure chamber 52h while abutting against the roller 55 is pressed in the direction of the vane groove 52e by the compression load of the high pressure refrigerant. That is, the compression load pushes the compression chamber 52a side of the vane 56 in the pressing direction of the compression load. At this time, the protrusion 52j elastically bends in the pressing direction due to the pressing of the vane 56. As a result, one-sided contact between the vane 56 and the vane groove 52e can be prevented, wear due to one-sided contact can be prevented, and the vane 56 can be easily moved.

Further, when the protrusion 52j is bent, the protrusion 52j is attached to the cylinder 52 with the upper bearing 53 and the lower bearing 54 by the first gap 60a and the second gap 60b formed on the upper and lower end surfaces of the protrusion 52j, respectively. Does not touch. As a result, the protrusion 52j does not come into sliding contact with each of the upper bearing 53 and the lower bearing 54, so that the protrusion 52j, the upper bearing 53, and the lower bearing 54 can be prevented from being worn, and an increase in mechanical loss can be prevented.

The stepped 52c provided in the suction path 52b when the compressive load is applied supports the root of the protrusion 52j. As a result, the strength of the protrusion 52j against a compressive load can be improved, and the occurrence of deformation or breakage due to insufficient strength of the protrusion 52j is suppressed. In particular, when the vertical height a4 of the cylinder 52 is reduced in order to reduce the loss due to refrigerant leakage, the strength of the protrusion 52j is reduced. Therefore, this effect is more effective when the cylinder 52 is thinned. However, when the width a1, the width a2, and the protruding length a3 of the stepped 52c become large, the effect of preventing wear due to the bending of the protrusion 52j described above becomes small, and the refrigerant flow path is reduced, so that the pressure loss of the refrigerant is reduced. To increase.

In order to prevent an increase in the pressure loss of the refrigerant, it is necessary not to make a portion of the refrigerant flow path from the suction hole 53a whose cross-sectional area is narrower than that of the suction hole 53a. That is, it is necessary to set the width a1, the width a2, and the protrusion length a3 of the stepped 52c so that the width a6 that minimizes the space distance in the suction path 52b and the diameter a5 of the suction hole 53a have a relationship of a6> a5. be.

By having the stepped 52c in the suction path 52b of the cylinder 52, the increase in the bending width of the refrigerant gas path becomes gradual, and the increasing width in one bending can be reduced. Therefore, it becomes difficult to form a vortex that becomes a turbulent flow of the refrigerant gas. Therefore, the pressure loss of the inflowing refrigerant is reduced. In order to prevent the formation of a vortex of the refrigerant gas and reduce the pressure loss of the refrigerant gas, the vertical height a4 of the cylinder 52 and the vertical height a2 of the stepped 52c have a relationship of a4 / a2 = 2-5. It is effective to make it.

Further, the compressor 100 is particularly effective when the refrigerant used is compressed with a high differential pressure such as carbon dioxide.

<Comparative example 1>
FIG. 7 is an explanatory view showing the suction connecting path 53b and the suction path 52b of Comparative Example 1 in a vertical cross section. In Comparative Example 1 for comparison with the first embodiment shown in FIG. 7, instead of the stepped 52c, the slope 52c2 maintaining the width a6 that minimizes the spatial distance in the suction path 52b was formed. Then, when the effect of reducing the pressure loss of the refrigerant gas was compared between the compressor 100 of the first embodiment and the compressor 100 of the comparative example 1, the refrigerant gas of the compressor 100 of the first embodiment was compared with the compressor 100 of the comparative example 1. However, the effect of reducing the pressure loss by 4.6% was exhibited. As a result, the superiority of the compressor 100 of the first embodiment has been clarified.

<Comparative example 2>
FIG. 8 is an explanatory view showing the suction connecting path 53b and the suction path 52b of Comparative Example 2 in a vertical cross section. In Comparative Example 2 for comparison with the first embodiment shown in FIG. 8, the stepped 52c is not formed. In the case of Comparative Example 2, although the effect of reducing the pressure loss of the refrigerant gas in the suction path 52b is excellent, the amount of bending of the protrusion 52j becomes large due to the absence of the stepped 52c supporting the protrusion 52j, and the protrusion 52j becomes large. Machine loss of 52j was likely to occur. Further, since the protrusion 52j is excessively bent, the vane 56 is tilted with respect to the vane groove 52e and becomes difficult to move in the radial direction, and the lubricity of the vane 56 is deteriorated. As a result, the superiority of the compressor 100 of the first embodiment has been clarified.

<Effect of Embodiment 1>
According to the first embodiment, the compressor 100, which is a rolling piston type compressor, includes a compression element 5 which is a compression mechanism unit and an electric element 4 which is a drive unit in a closed container 2. The compression element 5 has a cylinder 52 in which a compression chamber 52a is formed and a vane groove 52e in which the vane 56 is arranged is formed. The compression element 5 has an upper bearing 53 that covers the upper end surface of the cylinder 52 and a lower bearing 54 that covers the lower end surface of the cylinder 52. A suction connecting path 53b for sucking the refrigerant is provided by the suction hole 53a formed in the upper bearing 53 of the upper bearing 53 or the lower bearing 54. A suction path 52b for flowing a refrigerant from the suction connecting path 53b to the compression chamber 52a is provided on the outer side of the compression chamber 52a of the cylinder 52 in the radial direction. In the middle of the suction path 52b of the cylinder 52, a stepped 52c is formed on the side opposite to the connection side of the suction communication path 53b, which projects toward the compression chamber 52a and receives the refrigerant. A protrusion 52j protruding toward the compression chamber 52a is formed between the suction path 52b of the cylinder 52 and the vane groove 52e in the circumferential direction. A first gap 60a is formed between the upper end of the protrusion 52j and the upper bearing 53. A second gap 60b is formed between the lower end of the protrusion 52j and the lower bearing 54. The protrusion 52j has the flexibility to elastically bend in the pressing direction due to the compressive load when a compressive load is applied to the vane 56 by the refrigerant in the compression chamber 52a.

According to this configuration, when a compressive load is applied to the vane 56 by the refrigerant in the compression chamber 52a, the flexible protrusion 52j elastically bends in the pressing direction due to the compressive load. As a result, one-sided contact between the vane 56 and the cylinder 52 can be prevented when the compressor 100 is driven, the surface pressure of the contact portion is reduced, wear of the contact portion can be prevented, and the lubricity of the vane 56 can be improved. Further, since the upper bearing 53 and the lower bearing 54 and the cylinder 52 are separated from each other by the first gap 60a and the second gap 60b formed above and below the protrusion 52j, the protrusion 52j and the cylinder are separated from each other even if the protrusion 52j is bent. The upper bearing 53 and the lower bearing 54 attached to the upper and lower sides of the 52 do not wear. By providing the suction path 52b on the radial outer side of the compression chamber 52a of the cylinder 52, the cross-sectional area of the refrigerant flow path in the suction path 52b can be formed to be larger than the cross-sectional area of the suction hole 53a, and the refrigerant gas flowing into the suction hole 53a can be formed. The refrigerant gas reaches the compression chamber 52a without narrowing the cross-sectional area in the flow direction on the way. In the middle of the suction path 52b, a stepped 52c is formed on the side opposite to the connection side of the suction communication path 53b, which projects toward the compression chamber 52a and receives the refrigerant. As a result, in the suction path 52b, a sufficient cross-sectional area of the refrigerant flow path can be secured when guiding the refrigerant from the suction pipe 7a to the compression chamber 52a, and the pressure loss of the inflowing refrigerant is reduced. Further, the stepped 52c can reduce the width of curving the flow of the refrigerant gas in the suction path 52b, making it difficult to form a vortex that becomes a turbulent flow of the refrigerant gas, and reducing the pressure loss of the inflowing refrigerant. Therefore, one-sided contact between the vane 56 and the cylinder 52 is prevented when the compressor 100 is driven, the lubricity of the vane 56 is improved, and the refrigerant flow path is interrupted when the refrigerant is guided from the suction pipe 7a to the compression chamber 52a. A sufficient area is secured, and the pressure loss of the inflowing refrigerant can be reduced. Further, by providing the stepped 52c in the suction path 52b of the cylinder 52, the strength of the protrusion 52j formed between the suction path 52b of the cylinder 52 and the vane groove 52e can be improved. As a result, when the cylinder 52 is thinned and the vane 56 is pressed in the direction of the vane groove 52e by the high-pressure refrigerant, it is possible to suppress the occurrence of deformation or breakage due to insufficient strength at the protrusion 52j.

According to the first embodiment, the suction connecting path 53b is formed in the upper bearing 53.

According to this configuration, when guiding the refrigerant from the suction pipe 7a to the compression chamber 52a, the cross-sectional area of the refrigerant flow path can be sufficiently secured along the direction of gravity, and the pressure loss of the inflowing refrigerant can be further reduced.

According to the first embodiment, the stepped 52c is a stepped portion.

According to this configuration, the pressure loss of the inflowing refrigerant is reduced by 4.6% as compared with Comparative Example 1 of the slope 52c2 without the stepped 52c.

According to the first embodiment, the stepped 52c is a flat plate having a flat surface on the connecting side of the suction connecting path 53b.

According to this configuration, when guiding the refrigerant from the suction pipe 7a to the compression chamber 52a, the cross-sectional area of the refrigerant flow path can be sufficiently secured without generating vortices such as turbulent flow, and the pressure loss of the inflowing refrigerant is further reduced. NS.

According to the first embodiment, the stepped 52c forms a space from the connecting side of the suction connecting path 53b to the surface of the stepped 52c hollowed out in the vertical direction by cutting downward with the tool 10. From that position, the tool 10 is used to cut the space toward the compression chamber 52a to form a flat surface of the stepped 52c while expanding the space toward the compression chamber 52a, and then the tool 10 is used to connect the suction connecting path 53b to the connection side. Is a flat plate shape in which the tip portion 52c1 of the stepped 52c is formed while cutting the space portion in the vertical direction by cutting on the opposite side.

According to this configuration, the stepped 52c can be formed by a simple continuous cutting process by the tool 10.

According to the first embodiment, the carbon dioxide refrigerant is compressed.

According to this configuration, even if a carbon dioxide refrigerant having a higher refrigerant pressure than a chlorofluorocarbon-based refrigerant is used, the cylinder 52 has a thin thickness, and the bearing load can be reduced and the compressor efficiency can be improved.

According to the first embodiment, when the vertical height of the cylinder 52 is a4 and the height of the stepped 52c is a2, the relationship of 2 ≦ a4 / a2 ≦ 5 is satisfied.

According to this configuration, by forming the stepped 52c, the formation of a vortex that becomes a turbulent flow of the refrigerant gas can be prevented, and the pressure loss of the inflowing refrigerant can be reduced.

Embodiment 2.
<Refrigeration cycle device 101>
FIG. 9 is a refrigerant circuit diagram showing a refrigerating cycle device 101 to which the compressor 100, which is a rolling piston type compressor according to the second embodiment of the present invention, is applied.

As shown in FIG. 9, the refrigeration cycle device 101 includes a compressor 100, a condenser 102, an expansion valve 103, and an evaporator 104. The compressor 100, the condenser 102, the expansion valve 103, and the evaporator 104 are connected by a refrigerant pipe to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 104 is sucked into the compressor 100 and becomes high temperature and high pressure. The high temperature and high pressure refrigerant is condensed in the condenser 102 to become a liquid. The liquid refrigerant is decompressed and expanded by the expansion valve 103 to become a low-temperature low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 104.

The compressor 100 of the first embodiment can be applied to such a refrigeration cycle device 101. Examples of the refrigeration cycle device 101 include an air conditioner, a refrigeration device, a water heater, and the like.

<Effect of Embodiment 2>
According to the second embodiment, the refrigeration cycle device 101 includes the compressor 100, which is the rolling piston type compressor described above.

According to this configuration, since the refrigeration cycle device 101 includes the compressor 100, one-sided contact between the vane 56 and the cylinder 52 is prevented when the compressor 100 is driven, the lubricity of the vane 56 is improved, and suction is performed. When guiding the refrigerant from the pipe 7a to the compression chamber 52a, a sufficient cross-sectional area of the refrigerant flow path is secured, and the pressure loss of the inflowing refrigerant can be reduced.

2 Airtight container, 3 pedestal, 4 electric element, 5 compression element, 6a terminal, 6b lead wire, 7a suction pipe, 7b discharge pipe, 10 tools, 11 control unit, 12 communication line, 21 body, 22 top lid, 23 Lower lid, 41 stator, 42 rotor, 51 crankshaft, 51a eccentric part, 52 cylinder, 52a compression chamber, 52b suction path, 52c stepped, 52c1 tip, 52c2 slope, 52d discharge port, 52e vane groove , 52f hole, 52g low pressure chamber, 52h high pressure chamber, 52j protrusion, 53 upper bearing, 53a suction hole, 53b suction connecting path, 54 lower bearing, 55 roller, 56 vane, 57 spring, 60a first gap, 60b second Gap, 100 compressor, 101 refrigeration cycle device, 102 condenser, 103 expansion valve, 104 evaporator.

Claims (8)

A rolling piston type compressor equipped with a compression mechanism inside a closed container.
The compression mechanism portion has a cylinder in which a compression chamber is formed and a vane groove in which vanes are arranged, an upper bearing that covers the upper end surface of the cylinder, and a lower bearing that covers the lower end surface of the cylinder.
A suction connecting path for sucking the refrigerant through a suction hole formed in either the upper bearing or the lower bearing.
A suction path for flowing a refrigerant from the suction connecting path to the compression chamber on the radial side of the compression chamber of the cylinder.
Provided
In the middle of the suction path of the cylinder, a step is formed on the side opposite to the connection side of the suction communication path, which projects toward the compression chamber side and receives the refrigerant.
A protrusion protruding toward the compression chamber is formed between the suction path of the cylinder and the vane groove in the circumferential direction.
A first gap is formed between the upper end of the protrusion and the upper bearing.
A second gap is formed between the lower end of the protrusion and the lower bearing.
The protrusion is a rolling piston type compressor having flexibility that elastically bends in the pressing direction due to the compressive load when a compressive load is applied to the vane by the refrigerant in the compression chamber. The rolling piston type compressor according to claim 1, wherein the suction connecting path is formed on the upper bearing. The rolling piston type compressor according to claim 1 or 2, wherein the stepped portion is a stepped portion. The rolling piston type compressor according to any one of claims 1 to 3, wherein the stepped shape is a flat plate having a flat surface formed on the connecting side of the suction connecting path. The stepped structure is formed by cutting in the vertical direction with a tool from the connection side of the suction connecting path to form a space portion hollowed out in the vertical direction, and cutting from that position to the compression chamber side with the tool. The stepped flat surface is formed while expanding the space, and then the tool is used to cut the suction communication path on the opposite side to the connecting side to penetrate the space in the vertical direction. The rolling piston type compressor according to claim 4, which has a flat plate shape having a tip portion formed therein. The rolling piston type compressor according to any one of claims 1 to 5, which compresses a carbon dioxide refrigerant. The invention according to any one of claims 1 to 6, wherein when the vertical height of the cylinder is a4 and the stepped height is a2, the relationship of 2 ≦ a4 / a2 ≦ 5 is satisfied. Rolling piston type compressor. A refrigeration cycle apparatus including the rolling piston type compressor according to any one of claims 1 to 7.

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