JPH0814175A - Rotary compressor - Google Patents

Abstract

(57) [Summary] [Purpose] To improve the efficiency of a rotary compressor by preventing lubrication failure (that is, seizure or abnormal wear) at the tip of the vane and reducing friction loss. [Structure] A roller 2 mounted on an eccentric shaft 1, a cylinder 3 accommodating the roller 2 rollably, and a cylinder 3
In a rotary compressor provided with a vane 4 which is capable of moving forward and backward with respect to the outer surface of the roller 2 in a biased state, and a contact state between the vane 4 and the roller 2 is a cylindrical side surface. The inscribed surface contact.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION The present invention is disclosed in Japanese Patent Application No. 6-9025.
The invention relates to a patent application based on the provisions of Article 42-2, paragraph 1 of the Patent Act, which filed No. 6 as an earlier application, and, like the invention of the earlier application, relates to a rotary compressor, more specifically, an alternative refrigerant. The present invention relates to a rotary compressor capable of maintaining sufficient lubrication characteristics even when used.

[0002]

2. Description of the Related Art For example, as shown in FIG.
A roller 2 mounted on the upper side, a cylinder 3 for accommodating the roller 2 so as to be rollable, a cylinder 3 which is movable forward and backward with respect to the cylinder 3, and slidably contacts an outer surface of the roller 2 in a biased state. Moreover, the rotary compressor provided with the vane 4 having the convex curved surface portion 4a at the tip has been widely used conventionally for compressing the refrigerant in the refrigerating apparatus. In FIG. 24, reference numeral 5 is a casing, 6 is a suction passage, 7 is a discharge passage, 8 is an urging means (for example, a spring) for urging the vane 4, and 9 is a high pressure for exerting a back pressure on the back surface of the vane 4. A high pressure gas chamber 10 into which a gas refrigerant (for example, a discharge gas refrigerant) is introduced is a guide groove for guiding the vane 4.

By the way, due to restrictions on CFC / HCFC-based CFCs (prohibition of production / use), which is said to be the cause of ozone layer depletion, HFC-based CFCs, which are a substitute for CFC / HCFC-based CFCs, will be used as refrigerants for refrigeration equipment in the future. The current CFC / HCFC
While CFC-based CFCs have some lubricity themselves and are compatible with lubricating oils with excellent lubricity (for example, mineral oil), HFC CFCs, which are alternative refrigerants, have almost lubricity. Do not do, and a lubricating oil with excellent lubricity
(For example, mineral oil, etc.) is incompatible, so in a refrigeration system that uses HFC-based CFCs as a circulating refrigerant, a lubricating oil that is inferior in lubricity but compatible (for example, ester oil) must be used. There is a fact that must be.

Therefore, when HFC-based CFC, which is an alternative refrigerant, is used as a circulating refrigerant, the lubrication characteristics of the sliding parts of the compressor are deteriorated, and especially the lubrication conditions at the tip of the vane in the rotary compressor are severe and seizure occurs. However, poor lubrication such as abnormal wear is becoming a problem, and the solution is an urgent task.

In order to prevent the above-mentioned poor lubrication, a method of lowering the contact surface pressure between the vane and the roller or a method of improving the lubricating characteristic by devising the material of the tip of the vane can be considered. .

For example, as disclosed in Japanese Utility Model Laid-Open No. 57-3892, the contact between the vane and the roller is made by increasing the radius of curvature of the convex curved surface of the vane tip and reducing the back pressure receiving area of the vane. It is considered that the surface pressure is lowered, and as disclosed in JP-A-5-321168, the vane is made of an alloy steel containing chromium and subjected to a nitriding treatment, and the tip portion thereof is formed. It has been considered to improve the lubrication characteristics of the vane tip by applying a ceramic coating of titanium nitride.

[0007]

In the former case of the above-mentioned known example, only by increasing the radius of curvature of the convex curved surface portion of the tip of the vane, the vane and the roller are in a state of external contact with the outer peripheral surface of the cylinder. However, the range in which the contact surface pressure can be reduced is limited. That is, in the case of external contact, the curve X
As shown in FIG. 19 (see FIG. 19), even if the radius of curvature r of the convex curved surface portion 4a (see FIG. 24) becomes large, there is a limit to the reduction of the contact surface pressure.

On the other hand, in the case of the latter of the above-mentioned known examples, since the ceramic coating of titanium nitride is a material having a high attacking property against the other member, abnormal wear of the roller may occur, and the material of the roller is special. As a result, it becomes necessary to respond.

The present invention has been made in view of the above points, and it is possible to prevent a lubrication failure (that is, seizure or abnormal wear) at the tip of the vane and to reduce the friction loss to improve the performance of the rotary compressor. The purpose is to improve efficiency.

[0010]

According to the first basic constitution of the present invention, a roller mounted on an eccentric shaft, a cylinder for rotatably accommodating the roller, and a cylinder which can move forward and backward with respect to the cylinder. A rotary compressor provided with a vane that is provided and is in sliding contact with the outer surface of the roller in a biased state,
The contact state between the vane and the roller is the inscribed surface contact of the cylindrical side surface.

The preferred embodiment of the first basic configuration of the present invention is as follows.

A concave curved surface portion is formed at the tip of the vane so that the outer peripheral surface of the roller is inscribed, and the vane tip width is set so that the contact point between the vane and the roller is always on the concave curved surface portion at all rotation angles of the roller. It is preferable to be able to exist, and in this case, it is more preferable to reduce the area of the back pressure acting side end surface of the vane.

In some cases, it may be preferable to provide a tilting pad-shaped sliding contact portion, which is in contact with the outer peripheral surface of the roller, on the tip end of the vane.

A concave curved surface portion is formed at the tip of the vane, and a convex curved surface portion that engages with the concave curved surface portion in an inscribed surface contact state is provided on the outer peripheral surface of the roller, or a convex curved surface portion is formed at the tip of the vane. And a concave curved surface portion that engages with the convex curved surface portion in an inscribed surface contact state is provided on the outer peripheral surface of the roller, or has convex curved surface portions at both ends between the vane and the roller. It is preferable to interpose a pivot-shaped bearing, and to provide the vane tip and the roller outer peripheral surface with concave curved surface portions that engage with the convex convex curved surface portions in an inscribed surface contact state, respectively. In these cases, It is more preferable that a sliding contact member that reduces the relative rotation speed between the eccentric shaft and the roller is interposed between the eccentric shaft and the roller. The sliding contact member is
It may be a rotating ring, but is preferably a floating pad.

In the second basic configuration of the present invention, a flat surface portion is formed at the tip of the vane, and the tip width of the vane is such that the contact point between the vane and the roller is the concave curved surface portion at all rotation angles of the roller. The back pressure acting side end surface of the vane is preferably reduced in this case.

According to the third basic constitution of the present invention, the base metal of the vane is subjected to a surface treatment such as alloy steel having a surface hardness of 600 Hv to 800 Hv or nitriding to obtain a surface hardness of 800 Hv to 1
It is made of alloy steel adjusted to 200 Hv, and the surface of the tip of the vane is coated with chromium nitride ceramic coating. In this case, the shape of the tip of the vane and the shape of the roller are not limited, but it is more preferable to use together with the above-mentioned first and second basic configurations of the present invention.

In the first, second and third basic configurations of the present invention, the roller has a surface hardness of 400 Hv-60.
Alloy cast iron adjusted to 0 Hv or surface hardness 600 Hv ~
It is more preferable to use die steel adjusted to 800 Hv.

In the third basic structure of the present invention, a convex curved surface portion is formed at the tip of the vane, the radius of curvature of the convex curved surface portion is r, the vane tip width is b, the roller radius is R, and the roller radius is R. Letting the revolution radius be e and the non-contact width at the edge of the vane be α, r = (b-2α) / (2e-b +
2α), and α = 0.1-0.8m
It is preferably m.

The basic configuration and preferred embodiments of the present invention described above (that is, claims 1 to 17)
The invention described in 1) is disclosed in the specification and drawings of the previous application.

Further, the rotary compressor according to the present invention has a newly added basic structure and preferred embodiments described below (that is, claims 18 to 21).
The invention described in 1).

In the fourth basic structure of the present invention, the flat portion is formed at the tip of the vane, and the flat portion at the tip of the vane is formed in sliding contact with the roller at all rotation angles of the roller. However, in this case, it is preferable to reduce the area of the back pressure acting side end surface of the vane. The base material of the vane has a surface hardness of 600 Hv.
.About.800 Hv alloy steel or alloy steel whose surface hardness is adjusted to 800 Hv to 1200 Hv by surface treatment such as nitriding, and the surface of the vane tip is coated with chromium nitride ceramic, and the roller has a surface hardness of 40.
It is more preferable to use alloy cast iron adjusted to 0 Hv to 600 Hv or die steel adjusted to surface hardness 600 Hv to 800 Hv.

[0022]

In the first basic structure of the present invention, the contact state between the tip of the vane and the roller is the inscribed surface contact of the outer peripheral surface of the cylinder (that is,
Inscribed surface contact between the concave curved surface of the vane tip and the roller outer peripheral surface,
Inner surface contact between the tilting pad-shaped sliding contact part of the vane tip and the roller outer peripheral surface, inward contact surface between the concave curved surface part of the vane tip and the convex curved surface part of the roller outer periphery, convex curved surface part of the vane tip and the roller outer circumference Inner surface contact with the concave curved surface part, and convex surface curved surface parts at both ends of the pivot-shaped bearing interposed between the vane and the roller, and the inner surface contact surface of the vane tip and the concave curved surface part on the outer circumference of the roller)
Therefore, the contact area between the two can be increased, and the contact surface pressure is significantly reduced. The curve Y in FIG.
As shown in, the radius of curvature of the concave curved surface in the inscribed surface contact
Considering that the smaller the r, the smaller the contact surface pressure,
Inner surface contact between the concave curved surface at the tip of the vane and the convex curved surface at the outer periphery of the roller, internal contact between the convex curved surface at the tip of the vane and concave curved surface at the outer periphery of the roller, and between the vane and the roller When the convex curved surfaces at both ends of the pivot-shaped bearing are in contact with the vane tip and the concave curved surface at the outer circumference of the roller, the contact surface pressure is significantly reduced. In addition, when the inclining surface contact between the tilting pad-shaped sliding contact part at the tip of the vane and the roller outer peripheral surface is made, the sliding contact part and the roller outer peripheral surface can come into full contact, and the full rotation of the roller can be achieved without increasing the vane width. A large reduction in contact surface pressure is obtained in the area. In this case, since the lubricating oil film is interposed between the sliding contact portion and the outer circumference of the roller, sliding resistance is further reduced.

In the case where the concave curved surface at the tip of the vane and the outer peripheral surface of the roller are in contact with each other on the inscribed surface, if the area of the end surface on the back pressure acting side of the vane is reduced, the back pressure acting on the vane is reduced and the contact is reduced. The surface pressure is further reduced.

Inward surface contact between the concave curved surface portion of the vane tip and the convex curved surface portion of the roller outer periphery, inward surface contact between the convex curved surface portion of the vane tip and the concave curved surface portion of the roller outer periphery, and between the vane and the roller When the convex curved surfaces at both ends of the pivot bearing installed on the inner surface of the vane tip and the concave curved surface of the roller outer circumference make inscribed surface contact, the roller cannot rotate due to the engagement with the vane tip. Although the relative rotation speed between the eccentric shaft and the roller increases, if a sliding contact member that reduces the relative rotation speed between the eccentric shaft and the roller is interposed between the eccentric shaft and the roller, the relative rotation between the eccentric shaft and the sliding contact member is increased. And the relative rotation also occurs between the sliding contact member and the roller, and the relative rotation speed between the respective members is significantly reduced. In this case, the sliding contact member may be a rotating ring, but if a floating pad is used,
Since a sufficient amount of lubricating oil can be supplied to the sliding portions of each member, a friction reducing effect and a cooling effect can be obtained.

In the second basic configuration of the present invention, the contact surface pressure is reduced as compared with the conventional external contact surface contact due to the contact between the flat surface portion of the vane tip and the roller outer peripheral surface. In the case of surface contact between the flat surface of the vane tip and the roller outer peripheral surface,
As indicated by the straight line Z in FIG. 9, the contact surface pressure is higher than that in the case of internal contact (curve Y), but the contact surface pressure is lower than that in the case of external contact (curve X). In this case,
When the area of the back pressure acting side end surface of the vane is reduced, the back pressure acting on the vane is reduced and the contact surface pressure is further reduced.

According to the third basic constitution of the present invention, the wear resistance is improved by appropriately increasing the hardness of the surface of the vane base material, and the seizure resistance, self-lubricating property and wear resistance are excellent, and the attack on the mating member is achieved. The presence of the less aggressive chromium nitride ceramic coating results in a significant improvement in the lubrication properties between the vane tip and the roller. The first and second aspects of the present invention
Further improvement in lubrication characteristics can be obtained when used in combination with the basic constitution of. Moreover, the roller has a surface hardness of 400H.
Alloy cast iron adjusted to v to 600 Hv or surface hardness 60
If the die steel is adjusted to 0 Hv to 800 Hv, wear resistance and seizure resistance on the roller side are also improved.

Since the tip of the vane in the third basic structure of the present invention is excellent in self-lubricating property and wear resistance, even when the tip of the vane is formed into a convex curved surface, the shape of the vane is substantially deformed due to wear. Therefore, when the radius of curvature of the convex curved surface portion is r, the vane tip width is b, the roller radius is R, the roller revolution radius is e, and the non-contact width at the vane tip edge is α, r = ( b-2α) / (2e-
b + 2α) (that is, the radius of curvature r is set to the maximum value), and α = 0.1 to 0.8 mm, there is no risk of contact between the vane tip edge and the roller outer peripheral surface. As a result, the contact surface pressure between the vane tip and the roller can be reduced.

The operation of the present invention described above (that is, the invention described in claims 1 to 17) is disclosed in the specification and drawings of the previous application.

Furthermore, the rotary compressor according to the present invention (that is, the invention described in claims 18 to 21) has the following newly added actions.

In the fourth basic configuration of the present invention, the contact surface pressure is significantly reduced by contact between the flat surface portion of the tip of the vane and the flat surface portion of the roller as compared with the conventional external contact surface contact.
In the case of surface contact between the flat surface portion of the vane tip and the flat surface portion of the roller, the contact surface pressure is close to that of the inward contact surface, which is significantly lower than that of the conventional outer contact surface. In this case, if the area of the back pressure acting side end surface of the vane is reduced, the back pressure acting on the vane is reduced and the contact surface pressure is further reduced. Further, in this case, the base metal of the vane is subjected to a surface treatment such as alloy steel having a surface hardness of 600 Hv to 800 Hv or nitriding to obtain a surface hardness of 800 Hv to 1200 Hv.
Made of alloy steel adjusted to, and the surface of the vane tip is coated with chromium nitride ceramic, improving the wear resistance by moderately increasing the hardness of the vane base metal surface,
The presence of the ceramic coating of chromium nitride, which has excellent seizure resistance, self-lubricating property, and wear resistance, and has low attack on the mating member, provides a significant improvement in the lubrication property between the vane tip and the roller. In that case, if the roller is made of alloy cast iron whose surface hardness is adjusted to 400 Hv to 600 Hv or die steel whose surface hardness is adjusted to 600 Hv to 800 Hv, abrasion resistance and seizure resistance on the roller side are also improved. It will be.

[0031]

According to the first basic configuration of the present invention, the contact state between the vane tip and the roller is such that the vane tip is in contact with the inner peripheral surface of the cylinder (that is, the concave curved portion of the vane tip and the roller outer peripheral surface are in contact with each other). Surface contact, inward surface contact between the tilting pad-shaped sliding contact part of the vane tip and the roller outer peripheral surface, inward surface contact between the concave curved surface part of the vane and the convex curved surface part of the roller outer periphery, convex curved surface of the vane tip Surface contact with the concave curved surface of the roller outer periphery, and convex surface curved surfaces at both ends of the pivot-shaped bearing interposed between the vane and the roller with the inner surface of the vane tip and the concave curved surface of the roller outer periphery ), The contact surface pressure is greatly reduced because the contact area between the two can be increased, improving reliability and preventing friction loss by preventing seizure and abnormal wear of the vane tip. Excellent effect that high efficiency can be achieved by reducing A. Further, even when the tip of the vane is ceramic-coated, it is possible to improve the reliability such as the peeling resistance of the ceramic coating against the impact force when the vane is jumped.

Further, in the case where the tilting pad-like sliding contact portion at the tip of the vane and the outer peripheral surface of the roller are in contact with each other, the sliding contact portion and the outer circumference of the roller can be entirely in contact with each other, and the vane width can be increased. The contact surface pressure is significantly reduced in the entire rotation region of the roller, and the above-mentioned lubrication characteristics are significantly improved. In this case, since the lubricating oil film is interposed between the sliding contact portion and the roller outer periphery, sliding resistance is further reduced, which greatly contributes to high efficiency.

In the case where the concave curved surface portion of the vane tip and the roller outer peripheral surface are in contact with each other on the inscribed surface, when the area on the back pressure acting side of the vane is reduced, the back pressure acting on the vane is reduced and the contact is reduced. The surface pressure is further reduced, and the above-mentioned lubrication characteristics can be further improved.

Inward surface contact between the concave curved surface portion of the vane tip and the convex curved surface portion of the roller outer periphery, inward surface contact between the convex curved surface portion of the vane tip and the concave curved surface portion of the roller outer periphery, and between the vane and the roller When the inner curved surface contact between the convex curved surface portions at both ends of the pivot-shaped bearing and the vane tip and the concave curved surface portion on the outer circumference of the roller is provided, there is an advantage that the inner surface contact can be obtained without expanding the vane width. . In this case, since the roller cannot rotate on its own due to the engagement with the tip of the vane, the relative rotation speed between the eccentric shaft and the roller increases, but between the eccentric shaft and the roller,
By interposing a sliding contact member that reduces the relative rotation speed of both,
Relative rotation occurs between the eccentric shaft and the sliding contact member,
Relative rotation will also occur between the sliding contact member and the roller, and the relative rotation speed between each member will be significantly reduced,
The effect that the reliability is remarkably improved is obtained. In this case, the sliding contact member may be a rotating ring, but if a floating pad is used, lubricating oil can be sufficiently supplied to the sliding portion of each member, so that a friction reducing effect and a cooling effect can be obtained, and reliability is further improved. The property is improved.

According to the second basic configuration of the present invention, since the flat portion at the tip of the vane is brought into surface contact with the roller outer peripheral surface, the contact surface pressure is lower than that in the conventional external contact surface contact. Therefore, there is an excellent effect that reliability can be improved with a simple structure. Also in this case, if the area of the vane on the back pressure acting side is reduced, the back pressure acting on the vane is reduced, the contact surface pressure is further reduced, and it greatly contributes to the improvement of the lubricating characteristic.

According to the third basic constitution of the present invention, the wear resistance is improved by appropriately increasing the hardness of the surface of the vane base material, and the seizure resistance, self-lubrication property and wear resistance are excellent, and the mating member The presence of the less aggressive chromium nitride ceramic coating provides a significant improvement in the lubrication properties between the vane tip and the roller, which has the excellent effect of ensuring a high degree of reliability. It should be noted that when used in combination with the first and second basic configurations of the present invention, further improvement in lubrication characteristics can be obtained. Moreover, the roller has a surface hardness of 400 Hv.
~ 60 Hv alloy cast iron or surface hardness 60
If the die steel is adjusted to 0 Hv to 800 Hv, the wear resistance and seizure resistance on the roller side are also improved, and the reliability is further improved.

Since the tip of the vane in the third basic structure of the present invention is excellent in self-lubricating property and wear resistance, even when the tip of the vane is a convex curved surface, the shape of the vane is substantially deformed due to wear. Therefore, when the radius of curvature of the convex curved surface portion is r, the vane tip width is b, the roller radius is R, the roller revolution radius is e, and the non-contact width at the vane tip edge is α, r = ( b-2α) / (2e-
b + 2α) (that is, the radius of curvature r is set to the maximum value), and α = 0.1 to 0.8 mm, there is no risk of contact between the vane tip edge and the roller outer peripheral surface. As a result, the contact surface pressure between the tip of the vane and the roller can be reduced, and it is possible to improve the reliability by preventing seizure and abnormal wear of the tip of the vane and reduce the friction loss, resulting in higher efficiency. .

The effects of the invention of the present application described above (that is, the invention described in claims 1 to 17) are disclosed in the specification and drawings of the previous application.

Further, the rotary compressor according to the present invention (that is, the invention described in claims 18 to 21) has the following newly added effects.

According to the fourth basic structure of the present invention, the contact surface pressure is significantly reduced as compared with the conventional external contact surface contact, and the excellent effect that the reliability is improved with a simple structure can be achieved. There is. Also in this case, if the area of the vane on the back pressure acting side is reduced, the back pressure acting on the vane is reduced, the contact surface pressure is further reduced, and it greatly contributes to the improvement of the lubricating characteristic.

[0041]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some preferred embodiments of the present invention will be described below with reference to the accompanying drawings.

Embodiment 1 FIG. 1 shows a rotary compressor according to Embodiment 1 of the present invention.

The rotary compressor of this embodiment has almost the same structure as that described in the section of the prior art (that shown in FIG. 24), and only the vanes 4 have different shapes. Therefore, common members are denoted by the same reference numerals, and description thereof will be omitted.

In the case of this embodiment, a concave curved surface portion 4b is formed at the tip of the vane 4 so as to make an inscribed contact with the outer peripheral surface of the roller 2. The width b of the vane 4 is made larger than that of the conventional one (shown in FIG. 24) so that the contact point between the vane 4 and the roller 2 can exist on the concave curved surface portion 4b at all rotation angles of the roller 2. ing. This makes vane 4
It is prevented that the edge portion of and the outer peripheral surface of the roller 2 come into contact with each other.

In this rotary compressor, as shown in FIG.
As shown in (a) to (d), the roller 2 rolls along the inner peripheral surface of the cylinder 3 as the eccentric shaft 1 rotates, and the suction passage 6
The fluid (that is, the gas refrigerant) sucked in from is compressed and discharged from the discharge passage 7. In this process, the contact point between the tip of the vane 4 and the outer peripheral surface of the roller 2 is always present on the concave curved surface portion 4b.

With the above construction, the contact state between the tip of the vane 4 and the roller 2 is in contact with the inner surface of the outer peripheral surface of the cylinder (that is, the concave curved surface portion 4b at the tip of the vane 4 and the outer peripheral surface of the roller 2). (Contact surface contact), the contact area between the two can be increased, and the contact surface pressure is significantly reduced. Therefore, it is possible to improve reliability by preventing seizure and abnormal wear of the tip of the vane 4 and to improve efficiency by reducing friction loss. Further, even when the tip of the vane 4 is ceramic-coated, it is possible to improve the reliability such as the peeling resistance of the ceramic coating against the impact force when the vane 4 is jumped.

FIG. 19 shows the results obtained by calculating the average contact surface pressure according to Hertz's elastic contact theory for the outer contact surface (curve X), the inner contact surface (curve Y) and the plane contact (curve Z). There is. According to this, the contact surface pressure is lower in the case of the inner surface contact than in the case of the outer surface contact, regardless of the radius of curvature.

Further, in FIG. 20, the minimum oil film thickness (μm) with respect to the rotation angle (deg) of the roller 2 due to the tip shape of the vane 4 is shown.
According to this, the concave curved surface vane of this embodiment is compared with the conventional convex curved surface vane (shown by the curve X).
It can be seen that the minimum oil film thickness (indicated by curve Y) is significantly increased.

Further, FIG. 21 shows the change of the friction coefficient with respect to the rotation angle (deg) of the roller 2 depending on the tip shape of the vane 4. According to this, the conventional convex curved surface vane is shown.
It can be seen that the friction coefficient of the concave curved surface vane (shown by the curve Y) of the present embodiment is significantly reduced as compared with (shown by the curve X).

By the way, the vane 4 and the roller 2 in the rotary compressor according to the present embodiment are sufficiently effective even if they are made of the same material as the conventional product. The effect of improving the lubrication characteristics is further promoted.

That is, the base material of the vane 4 has a surface hardness of 600.
Hv to 800 Hv alloy steel or alloy steel whose surface hardness is adjusted to 800 Hv to 1200 Hv by surface treatment such as nitriding. The tip surface of the vane 4 is coated with chromium nitride ceramic and the surface hardness of the roller is It is composed of alloy cast iron adjusted to 400 Hv to 600 Hv or die steel adjusted to surface hardness of 600 Hv to 800 Hv.

In this way, chromium nitride is improved in wear resistance due to moderately high hardness of the surface of the vane base material, and is excellent in seizure resistance, self-lubricating property and wear resistance, and is low in aggressiveness to the mating member. The presence of the ceramic coating significantly improves the lubrication characteristics between the tip of the vane 4 and the roller 2, and ensures a high degree of reliability.

Moreover, in the case of this embodiment, the abrasion resistance and the seizure resistance on the roller 2 side are also improved, and the reliability is further improved.

FIG. 22 shows a comparison of the seizure load between the current material and various ceramic coating materials. According to this, the chromium nitride ceramic coating of the present embodiment is the same as the current material. The seizure resistance is significantly improved compared to that of, and seizure resistance equivalent to that of other ceramic coatings (that is, titanium nitride, titanium carbonitride or vanadium carbide ceramic coatings) is exhibited.

FIG. 23 shows the self-wearing characteristics of the chromium nitride ceramic coating material and the titanium nitride ceramic coating material and the aggressiveness to the mating member when ester oil is used as the lubricating oil. According to the present invention, the ceramic coating of chromium nitride and the ceramic coating of titanium nitride according to the present example are almost equivalent to the ceramic coating of titanium nitride in self-wear property, but nitride in the attacking property against the counterpart member. It can be seen that the titanium ceramic coating material is much higher. It should be noted that, as the counterpart member of the ceramic coating material of chromium nitride, it is understood that high hardness alloy cast iron or die steel is preferable to monichrome cast iron.

In summary of the above facts, it can be seen that the vane 4 having the ceramic coating of chromium nitride applied to the tip thereof is extremely effective in improving the lubrication characteristics.

By the way, when an alloy steel (for example, high speed tool steel or die steel) is used as the vane base material, its surface hardness is 600 Hv to 800 Hv, but 750 Hv to
A surface hardness of 800 Hv is desirable. When the vane base material is the alloy steel that has undergone a surface treatment such as nitriding, the surface hardness is 800 Hv to 1
The hardness is 200 Hv, but the surface hardness is preferably 1100 Hv to 1200 Hv.

On the other hand, when alloy cast iron is used as the roller material, its surface hardness is set to 400 Hv to 600 HV, but it is desirable to set it to 550 Hv to 600 Hv. When die steel is used as the roller material, the surface hardness is 600 Hv to 800 HV.
A surface hardness of Hv to 800 Hv is desirable.

Embodiment 2 FIG. 3 shows a rotary compressor according to Embodiment 2 of the present invention.

In the case of the present embodiment, the back pressure acting side area of the vane 4 in the first embodiment (that is, the area of the vane end surface 4c facing the high pressure gas chamber 9) is reduced. By doing so, the pressing force of the vane 4 against the roller 2 is reduced, and the contact surface pressure can be further reduced. Other configurations, functions, and effects are the same as those in the first embodiment, and the description thereof will be omitted to avoid duplication.

Embodiment 3 FIG. 4 shows a rotary compressor according to Embodiment 3 of the present invention.

In the case of this embodiment, the tip of the vane 4 is provided with a sliding contact portion 11 in the form of a tilting pad which comes into inward contact with the outer peripheral surface of the roller 2. In this case, since the radius of curvature of the sliding contact surface of the sliding contact portion 11 and the radius of curvature of the outer peripheral surface of the roller 2 can be made equal, the sliding contact portion 11 and the roller 2 do not have to be widened. The entire surface can be brought into contact with the outer peripheral surface, the contact surface pressure is significantly reduced in the entire rotation region of the roller 2, and the above-mentioned lubrication characteristics are significantly improved. In this case, since the lubricating oil film is interposed between the sliding contact portion 11 and the outer peripheral surface of the roller 2, sliding resistance is further reduced, which greatly contributes to high efficiency. In this embodiment, the vane 4 and the roller 2 do not come into direct contact with each other, so that it is not always necessary to specify the material as in the first embodiment. Other configurations, functions, and effects are the same as those in the first embodiment, and the description thereof will be omitted to avoid duplication.

Embodiment 4 FIG. 5 shows a rotary compressor according to Embodiment 4 of the present invention.

In the case of the present embodiment, the concave curved surface portion 4b is formed at the tip of the vane 4, and the convex curved surface portion which engages with the outer peripheral surface of the roller 2 in the inner surface contact state with the concave curved surface portion 4b. 2a is provided. In this case, since the radius of curvature of the convex curved surface portion 2a can be reduced, it is not necessary to increase the width of the vane 4. Further, in this case, since the roller 2 is constrained by the engagement of the concave curved surface portion 4b at the tip of the vane 4 and the convex curved surface portion 2a at the outer periphery of the roller 2, the roller 2 revolves with the rotation of the eccentric shaft 1, but rotates on its axis. I can't.

In the case of the present embodiment, the concave curved surface portion 4b having a small radius of curvature and the convex curved surface portion 2a having a small radius of curvature make an inscribed surface contact, so that the contact surface pressure reducing effect becomes large (curve Y in FIG. 19). reference). Other configurations, functions, and effects are the same as those in the first embodiment, and the description thereof will be omitted to avoid duplication.

Embodiment 5 FIG. 6 shows a rotary compressor according to Embodiment 6 of the present invention.

In the case of the present embodiment, the convex curved surface portion 4a is formed at the tip of the vane 4, and the concave curved surface portion 2b which engages with the convex curved surface portion 4a in an inward contact surface contact state is formed on the outer peripheral surface of the roller 2. It is provided. In this case, since the radius of curvature of the concave curved surface portion 2b can be reduced, it is not necessary to increase the width of the vane 4. Further, in this case, the roller 2 has the convex curved surface portion 4a at the tip of the vane 4.
Since it is constrained by the engagement with the concave curved surface portion 2b on the outer periphery of the roller 2, it revolves along with the rotation of the eccentric shaft 1, but cannot rotate.

In the case of this embodiment, since the inner curved surface contact between the concave curved surface portion 4b having a small radius of curvature and the convex curved surface portion 2a having a small radius of curvature, the contact surface pressure reducing effect becomes large (curve Y in FIG. 19). reference). Other configurations, functions, and effects are the same as those in the first embodiment, and the description thereof will be omitted to avoid duplication.

Embodiment 6 FIG. 7 shows a rotary compressor according to Embodiment 6 of the present invention.

In the case of this embodiment, a pivot bearing 12 having convex curved surface portions 12a, 12a at both ends is provided between the vane 4 and the roller 2, and the tip of the vane 4 and the outer peripheral surface of the roller 2 are provided. In addition, concave curved surface portions 4b and 2b that engage with the convex surface portions 12a and 12a respectively in an inscribed surface contact state are provided. In this case, since the radius of curvature of the convex curved surface portion 12a of the pivot-shaped bearing 12 can be reduced, the vane 4
There is no need to increase the width of. In this case, the roller 2
Is constrained by the engagement between the convex curved surface portion 12a of the pivot bearing 12 and the concave and convex curved surface portion 2b on the outer circumference of the roller 2, so that it revolves as the eccentric shaft 1 rotates, but cannot rotate.

In the case of this embodiment, the pivot bearing convex curved surface portions 12a, 12a having a small radius of curvature are in contact with the vane concave curved surface portion 4b and the roller concave curved surface portion 2b having a small radius of curvature. The pressure reducing effect is increased (see the curve Y in FIG. 19). Other configurations and operational effects are described in the first embodiment.
Since it is similar to the case of 1, the description is omitted by avoiding duplication.

Embodiment 7 FIG. 8 shows a rotary compressor according to Embodiment 7 of the present invention.

In the case of this embodiment, as in the case of the fourth embodiment, the concave curved surface portion 4b is formed at the tip of the vane 4, and the outer peripheral surface of the roller 2 is in contact with the concave curved surface portion 4b on the inner surface. Although the convex curved surface portion 2a that is engaged with is provided, a rotary ring 13 that acts as a sliding contact member that reduces the relative rotational speed between the eccentric shaft 1 and the roller 2 is provided between the eccentric shaft 1 and the roller 2.

By virtue of such construction, the roller 2
Even if the rotation of the eccentric shaft 1 and the rotating ring 13 is relatively rotated even if the rotation of the rotating ring 13 and the roller 2 is restricted because the rotation of the rotating ring 13 and the rotation ring 13 is restricted. The relative rotation speed between them will be reduced. Therefore, it is possible to prevent wear of the eccentric shaft 1 or the roller 2 due to rotational friction and reduce frictional heat. Other configurations, functions and effects are the same as those in the fourth embodiment, and thus the description thereof will be omitted to avoid duplication.

Embodiment 8 FIG. 9 shows a rotary compressor according to Embodiment 8 of the present invention.

In the case of the present embodiment, as in the case of the fourth embodiment, the concave curved surface portion 4b is formed at the tip of the vane 4, and the outer peripheral surface of the roller 2 is in contact with the concave curved surface portion 4b on the inner surface. Although the convex curved surface portion 2a which is engaged with is provided, the floating pad 14 that acts as a sliding contact member that reduces the relative rotation speed of the eccentric shaft 1 and the roller 2 is provided between the eccentric shaft 1 and the roller 2. The floating pad 14 slides along with the rotation of the eccentric shaft 1, and is made of a material such as sintered alloy, alloy cast iron, bearing steel, and nitriding stainless.

By virtue of this construction, the roller 2
Even if the structure is constrained so that it cannot rotate, relative rotation occurs between the eccentric shaft 1 and the floating pad 14, and relative rotation also occurs between the floating pad 14 and the roller 2. The relative rotation speed between them will be reduced. Therefore, it is possible to prevent wear of the eccentric shaft 1 or the roller 2 due to rotational friction and reduce frictional heat. Moreover, since the lubricating oil can be sufficiently supplied to the sliding parts of the respective members, the friction reducing effect and the cooling effect can be obtained.
Other configurations, functions and effects are the same as those in the fourth embodiment, and thus the description thereof will be omitted to avoid duplication.

Embodiment 9 FIG. 10 shows a rotary compressor according to Embodiment 9 of the present invention.

In the case of this embodiment, as in the case of the fifth embodiment, the convex curved surface portion 4a is formed at the tip of the vane 4, and the outer peripheral surface of the roller 2 is engaged with the convex curved surface portion 4a in an inscribed surface contact state. Although the concave curved surface portion 2b is provided, the rotating ring 13 that acts as a sliding contact member that reduces the relative rotation speed between the eccentric shaft 1 and the roller 2 is provided between the eccentric shaft 1 and the roller 2.

By virtue of such construction, the roller 2
Even if the rotation of the eccentric shaft 1 and the rotating ring 13 is relatively rotated even if the rotation of the rotating ring 13 and the roller 2 is restricted because the rotation of the rotating ring 13 and the rotation ring 13 is restricted. The relative rotation speed between them will be reduced. Therefore, it is possible to prevent wear of the eccentric shaft 1 or the roller 2 due to rotational friction and reduce frictional heat. Other configurations, functions and effects are the same as those of the fifth embodiment, and the description will be omitted to avoid duplication.

Embodiment 10 FIG. 11 shows a rotary compressor according to Embodiment 10 of the present invention.

In the case of the present embodiment, as in the case of the fifth embodiment, the convex curved surface portion 4a is formed at the tip of the vane 4, and the outer peripheral surface of the roller 2 is engaged with the convex curved surface portion 4a in an inscribed surface contact state. Although a concave curved surface portion 2b is provided, a floating pad 14 that acts as a sliding contact member that reduces the relative rotation speed of the eccentric shaft 1 and the roller 2 is provided between the eccentric shaft 1 and the roller 2. The floating pad 14 slides along with the rotation of the eccentric shaft 1, and is made of a material such as sintered alloy, alloy cast iron, bearing steel, and nitriding stainless.

By virtue of such construction, the roller 2
Even if the rotation of the eccentric shaft 1 and the rotating ring 13 is relatively rotated even if the rotation of the rotating ring 13 and the roller 2 is restricted because the rotation of the rotating ring 13 and the rotation ring 13 is restricted. The relative rotation speed between them will be reduced. Therefore, it is possible to prevent wear of the eccentric shaft 1 or the roller 2 due to rotational friction and reduce frictional heat. Moreover, since the lubricating oil can be sufficiently supplied to the sliding parts of the respective members, the friction reducing effect and the cooling effect can be obtained.
Other configurations, functions and effects are the same as those of the fifth embodiment, and the description will be omitted to avoid duplication.

Embodiment 11 FIG. 12 shows a rotary compressor according to Embodiment 11 of the present invention.

In the case of this embodiment, similarly to the sixth embodiment, between the vane 4 and the roller 2, the convex curved surface portions 12 are provided at both ends.
A concave curved surface portion 4b is provided which is provided with a pivot bearing 12 having a and 12a, and which engages with the tip end of the vane 4 and the outer peripheral surface of the roller 2 with the biconvex curved surface portions 12a and 12a in an inscribed surface contact state. , 2b are provided respectively, but a rotary ring 13 acting as a sliding contact member for reducing the relative rotational speed between the eccentric shaft 1 and the roller 2 is provided between the eccentric shaft 1 and the roller 2.

By virtue of such construction, the roller 2
Even if the rotation of the eccentric shaft 1 and the rotating ring 13 is relatively rotated even if the rotation of the rotating ring 13 and the roller 2 is restricted because the rotation of the rotating ring 13 and the rotation ring 13 is restricted. The relative rotation speed between them will be reduced. Therefore, it is possible to prevent wear of the eccentric shaft 1 or the roller 2 due to rotational friction and reduce frictional heat. Other configurations, functions and effects are the same as those of the sixth embodiment, and the description will be omitted to avoid duplication.

Embodiment 12 FIG. 13 shows a rotary compressor according to Embodiment 12 of the present invention.

In the case of this embodiment, similarly to the sixth embodiment, between the vane 4 and the roller 2, the convex curved surface portions 12 are provided at both ends.
A concave curved surface portion 4b is provided which is provided with a pivot bearing 12 having a and 12a, and which engages with the tip end of the vane 4 and the outer peripheral surface of the roller 2 with the biconvex curved surface portions 12a and 12a in an inscribed surface contact state. , 2b are respectively provided, but a floating pad 14 acting as a sliding contact member for reducing the relative rotation speed between the eccentric shaft 1 and the roller 2 is interposed between the eccentric shaft 1 and the roller 2. The floating pad 14 slides along with the rotation of the eccentric shaft 1, and is made of a material such as sintered alloy, alloy cast iron, bearing steel, and nitriding stainless.

By virtue of such construction, the roller 2
Even if the rotation of the eccentric shaft 1 and the rotating ring 13 is relatively rotated even if the rotation of the rotating ring 13 and the roller 2 is restricted because the rotation of the rotating ring 13 and the rotation ring 13 is restricted. The relative rotation speed between them will be reduced. Therefore, it is possible to prevent wear of the eccentric shaft 1 or the roller 2 due to rotational friction and reduce frictional heat. Moreover, since the lubricating oil can be sufficiently supplied to the sliding parts of the respective members, the friction reducing effect and the cooling effect can be obtained.
Other configurations, functions and effects are the same as those of the sixth embodiment, and the description will be omitted to avoid duplication.

Embodiment 13 FIG. 14 shows a rotary compressor according to Embodiment 13 of the present invention.

In this embodiment, the flat portion 4d is formed at the tip of the vane 4, and the tip width of the vane 4 is set so that the contact point between the vane 4 and the roller 2 is above the flat portion 4d at all rotation angles of the roller 2. Always exist.

In the case of a plane contact between the flat portion 4d at the tip of the vane 4 and the outer peripheral surface of the roller 2, as shown by a straight line Z in FIG.
Although the contact surface pressure is higher than that in the case of inscribed surface contact (curve Y), the contact surface pressure is lower than that in the case of conventional circumscribed surface contact (curve X).

The vane width at which the contact point between the vane 4 and the roller 2 always exists on the plane portion 4d at all rotation angles of the roller 2 is as shown in FIG. The revolution radius of the roller 2 is e, and the width of the non-contact portion at the tip edge of the vane 4 is α (usually 0.1 to 0.8 mm
Is required), b ≧ 2 (e−α) is set. Since other configurations are the same as those in the first embodiment, the description will be omitted to avoid duplication.

Embodiment 14 FIG. 16 shows a rotary compressor according to Embodiment 14 of the present invention.

In the case of this embodiment, the back pressure acting side area of the vane 4 in the embodiment 13 (that is, the area of the vane end surface 4c facing the high pressure gas chamber 9) is reduced. As a result, the pressing force of the vane 4 against the roller 2 is reduced, and the contact surface pressure is further reduced. Other configurations, functions and effects are the same as those of the thirteenth embodiment, and the description thereof will be omitted to avoid duplication.

Embodiment 15 FIG. 17 shows a main part of a rotary compressor according to Embodiment 15 of the present invention.

In the case of this embodiment, the convex curved surface portion 4a is formed at the tip of the vane 4, and the materials of the vane 4 and the roller 2 are defined as follows.

As in Example 1, the base material of the vane 4 is made of alloy steel having a surface hardness of 600 Hv to 800 Hv or alloy steel adjusted to have a surface hardness of 800 Hv to 1200 Hv by surface treatment such as nitriding. On the tip surface,
While applying a ceramic coating of chromium nitride, the roller 2 is made of alloy cast iron whose surface hardness is adjusted to 400 Hv to 600 Hv or die steel whose surface hardness is adjusted to 600 Hv to 800 Hv.

By the way, the tip of the vane 4 is fixed to the convex curved surface portion 4a.
If the radius of curvature r of the convex curved surface portion 4a is b, the vane tip width is b, the roller radius is R, the roller revolution radius is e, and the non-contact width at the edge of the vane tip is α, then r = ( b
-2α) / (2e−b + 2α), but
The wear of the vane 4 progresses, the contact portion expands, and α
When = 0, the edge portion of the vane 4 and the outer peripheral surface of the roller 2 come into contact with each other, causing poor lubrication. Therefore, in the conventional vane, the width α of the non-contact part is increased considering the wear allowance.
(For example, α = 0.9 to 1.0 mm). Therefore, it becomes difficult to increase the radius of curvature r of the convex curved surface portion 4a,
There was also a limit to the reduction of contact surface pressure.

However, in the case of the present embodiment, the wear resistance is remarkably improved as described in the first embodiment by the above-mentioned constitution, and therefore the wear of the tip of the vane 4 can be made 0.01 mm or less during the guaranteed life. Therefore, even if the width α of the non-contact portion is reduced to 0.1 to 0.8 mm, the edge portion of the vane 4 and the outer peripheral surface of the roller 2 do not come into contact with each other even at the wear limit. That is, since the width α of the non-contact portion can be reduced, the radius of curvature r of the convex curved surface portion 4a can be increased, and the contact surface pressure can be reduced (FIG. 19).
Curve X).

The embodiments described above (that is, the embodiments according to claims 1 to 17) are disclosed in the specification and drawings of the previous application.

In the following, the newly added embodiment (ie,
Embodiments according to claims 18 to 21 will be described.

Embodiment 16 FIG. 18 shows a main part of a rotary compressor according to Embodiment 16 of the present invention.

In this embodiment, the flat portion 4d is formed at the tip of the vane 4, and the vane 4 is formed on the roller 2.
A flat surface portion 4d at the tip and a flat surface portion 2c in sliding contact at all rotation angles of the roller 2 are formed. As a result, the vane 4 and the roller 2 come into contact with each other on their flat surfaces, and the contact surface pressure per unit contact area is significantly reduced. Then, the area of the back pressure acting side end surface 4c of the vane 4 is reduced to reduce the pressing force of the vane 4 against the roller 2, and the contact surface pressure between the both is further reduced.

Further, in the case of the present embodiment, the surface hardness of the base material of the vane 4 is 600 Hv to 80 Hv as in the case of the first embodiment.
0Hv alloy steel or alloy steel whose surface hardness is adjusted to 800Hv to 1200Hv by surface treatment such as nitriding, and the surface of the tip of the vane 4 is coated with chromium nitride ceramic while the roller 2 is covered with surface hardness 4
It is made of alloy cast iron adjusted to 00 Hv to 600 Hv or die steel adjusted to surface hardness of 600 Hv to 800 Hv. As a result, the same effect as that of the first embodiment can be expected.

Incidentally, the eccentricity e of the roller 2 is 5 mm,
The vane 4 has a length Hb of 25 mm and a bearing radius Rj of 16 m.
m, the radius Rr of the roller 2 is 23 mm, the radius Rs of the cylinder 3 is 28 mm, and the width Rw of the flat surface portion 2c of the roller 2 is 2.
3.5 mm, vane 4 width Wb is 4.5 mm, vane 4
When tested by a rotary compressor in which the width Wbt of the flat surface portion 4a of 1 is 13.5 mm, the contact area is 0.6 M.
p, friction loss was 1 W, and EER was 2.44. These are conventionally known external contact type (that is, contact surface pressure: 206 Mp, friction loss: 30 W, EER: 2.4).
This is a significantly improved value compared to 0).

That is, in the rotary compressor of the present embodiment, the contact surface pressure between the vane 4 and the roller 2 is significantly reduced, and as a result, the lubrication state is significantly improved and the friction loss is reduced to improve the mechanical efficiency. It is possible to improve reliability by improving wear resistance and seizure resistance.

The invention of the present application is not limited to the configuration of each of the above-described embodiments, and it goes without saying that the design can be appropriately changed without departing from the scope of the invention.

[Brief description of drawings]

FIG. 1 is a cross-sectional plan view of a rotary compressor according to a first embodiment of the present invention.

FIG. 2 is an operation state explanatory diagram for explaining an operation state of the rotary compressor according to the first embodiment of the present invention.

FIG. 3 is a cross-sectional plan view of a rotary compressor according to a second embodiment of the present invention.

FIG. 4 is a cross-sectional plan view of a rotary compressor according to a third embodiment of the present invention.

FIG. 5 is a cross-sectional plan view of a rotary compressor according to a fourth embodiment of the present invention.

FIG. 6 is a cross-sectional plan view of a rotary compressor according to a fifth embodiment of the present invention.

FIG. 7 is a cross-sectional plan view of a rotary compressor according to a sixth embodiment of the present invention.

FIG. 8 is a cross-sectional plan view of a rotary compressor according to a seventh embodiment of the present invention.

FIG. 9 is a cross-sectional plan view of a rotary compressor according to Embodiment 8 of the present invention.

FIG. 10 is a cross-sectional plan view of a rotary compressor according to a ninth embodiment of the present invention.

FIG. 11 is a cross-sectional plan view of a rotary compressor according to Embodiment 10 of the present invention.

FIG. 12 is a cross-sectional plan view of a rotary compressor according to Embodiment 11 of the present invention.

FIG. 13 is a cross-sectional plan view of a rotary compressor according to Embodiment 12 of the present invention.

FIG. 14 is a cross-sectional plan view of a rotary compressor according to Embodiment 13 of the present invention.

FIG. 15 is an enlarged sectional view of essential parts of a rotary compressor according to embodiment 13 of the present invention.

FIG. 16 is a cross-sectional plan view of a rotary compressor according to Embodiment 14 of the present invention.

FIG. 17 is an enlarged cross-sectional view of a main part of a rotary compressor according to Embodiment 15 of the present invention.

FIG. 18 is a cross-sectional view showing the main parts of a rotary compressor according to Embodiment 16 of the present invention.

FIG. 19 is a characteristic diagram showing a change in contact surface pressure with respect to the radius of curvature of the tip of the vane.

FIG. 20 is a characteristic diagram showing a change in minimum oil film thickness with respect to a rotation angle of a roller.

FIG. 21 is a characteristic diagram showing a change in friction coefficient with respect to a rotation angle of a roller.

FIG. 22 is a characteristic diagram showing a seizure load on a conventional product and various ceramic coating materials.

FIG. 23 is a characteristic diagram showing the self-wearing characteristics and the aggression with respect to the mating member of the ceramic coating material of chromium nitride and the ceramic coating material of titanium nitride.

FIG. 24 is a cross-sectional plan view of a conventionally known rotary compressor.

[Explanation of symbols]

1 is an eccentric shaft, 2 is a roller, 2a is a convex curved surface portion, 2b is a concave curved surface portion, 2c is a flat surface portion, 3 is a cylinder, 4 is a vane, 4a is a convex curved surface portion, 4b is a concave curved surface portion, 4c is a back pressure. Working end face, 4d
Is a flat surface portion, 9 is a high pressure gas chamber, 11 is a sliding contact portion, 12 is a pivot bearing, 12a is a convex curved surface portion, 13 is a sliding contact member (rotating ring), and 14 is a sliding contact member (floating pad).

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Kazumasa Ochiai 1304 Kanaoka-machi, Sakai City, Osaka Prefecture Daikin Industry Co., Ltd. Kanaoka Plant, Sakai Factory (72) Inventor, Ryo Kamino, 1304 Kanaoka-machi, Sakai City, Osaka Prefecture Daikin Industries, Ltd. Sakai Plant Kanaoka Factory

Claims (21)

[Claims] 1. A roller mounted on an eccentric shaft, a cylinder for accommodating the roller in a rollable manner, a cylinder provided so as to be movable back and forth with respect to the cylinder, and slid on an outer surface of the roller in a biased state. A rotary compressor provided with a vane in contact with the vane, wherein a contact state between the vane and the roller is an inscribed surface contact of a cylindrical side surface. 2. A concave curved surface portion is formed at the tip of the vane so that the outer peripheral surface of the roller is inscribed, and the vane tip width is such that the contact point between the vane and the roller is the concave curved surface portion at all rotation angles of the roller. A rotary compressor according to claim 1, characterized in that it can always be present above. 3. The rotary compressor according to claim 2, wherein the area of the end surface on the back pressure acting side of the vane is reduced. 4. The rotary compressor according to claim 1, wherein the tip of the vane is provided with a tilting pad-shaped sliding contact portion that comes into inward contact with the outer peripheral surface of the roller. 5. A concave curved surface portion is formed at the tip of the vane, and a convex curved surface portion that engages with the concave curved surface portion in an inscribed surface contact state is provided on the outer peripheral surface of the roller. The rotary compressor according to claim 1, wherein: 6. A convex curved surface portion is formed at the tip of the vane, and a concave curved surface portion that engages with the convex curved surface portion in an inscribed surface contact state is provided on the outer peripheral surface of the roller. The rotary compressor according to claim 1. 7. A roller mounted on an eccentric shaft, a cylinder rotatably accommodating the roller, a cylinder provided so as to be movable back and forth with respect to the cylinder, and slid on an outer surface of the roller in a biased state. A rotary compressor having a vane in contact with the vane, and between the vane and the roller, pivot bearings having convex curved portions at both ends are provided, and the vane tip and the roller outer peripheral surface are provided. The rotary compressor is provided with a concave curved surface portion that engages with each of the convex curved surface portions in a state of inscribed surface contact. 8. The sliding contact member for reducing the relative rotation speed between the eccentric shaft and the roller is interposed between the eccentric shaft and the roller, and the roller is placed in the sliding contact member. Rotary compressor. 9. The rotary compressor according to claim 8, wherein the sliding contact member is a rotating ring. 10. The rotary compressor according to claim 8, wherein the sliding contact member is a floating pad. 11. A roller mounted on an eccentric shaft, a cylinder rotatably accommodating the roller, a cylinder provided so as to be movable back and forth with respect to the cylinder, and slid on an outer surface of the roller in a biased state. A rotary compressor provided with a vane in contact with the vane, wherein a flat portion is formed at the tip of the vane, and the tip width of the vane is set so that the contact point between the vane and the roller is at the entire rotation angle of the roller. A rotary compressor characterized in that it can always exist on a flat surface. 12. The rotary compressor according to claim 11, wherein an area of a back pressure acting side end surface of the vane is reduced. 13. The surface hardness of the base material of the vane is 600.
The alloy steel of Hv to 800 Hv or alloy steel whose surface hardness is adjusted to 800 Hv to 1200 Hv by surface treatment such as nitriding, and the surface of the tip of the vane is coated with chromium nitride ceramic coating. The rotary compressor according to any one of claims 1 to 12. 14. The roller has a surface hardness of 400 Hv.
Alloy cast iron adjusted to 600 Hv or surface hardness 600
The rotary compressor according to claim 13, wherein the rotary compressor is made of die steel adjusted to Hv to 800 Hv. 15. A roller mounted on an eccentric shaft, a cylinder rotatably accommodating the roller, a cylinder provided so as to be movable back and forth with respect to the cylinder, and slid on an outer surface of the roller in a biased state. A rotary compressor having a vane in contact with the base material of the vane, the surface hardness of which is 600 Hv to 8
A rotary compressor comprising an alloy steel of 00 Hv or an alloy steel whose surface hardness is adjusted to 800 Hv to 1200 Hv by surface treatment such as nitriding, and the surface of the tip of the vane is coated with chromium nitride ceramic. 16. The roller has a surface hardness of 400 Hv-
Alloy cast iron adjusted to 600 Hv or surface hardness 600
The rotary compressor according to claim 15, wherein the rotary compressor is made of die steel adjusted to Hv to 800 Hv. 17. A convex curved surface portion is formed at the tip of the vane, the radius of curvature of the convex curved surface portion is r, the vane tip width is b, the roller radius is R, the roller revolution radius is e, and the vane tip is Let α be the non-contact width at the edge of r =
The rotary compression according to any one of claims 15 and 16, wherein the setting is (b-2α) / (2e-b + 2α), and α = 0.1 to 0.8 mm. Machine. 18. A roller mounted on an eccentric shaft, a cylinder rotatably accommodating the roller, a cylinder provided so as to be movable back and forth with respect to the cylinder, and slid on an outer surface of the roller in a biased state. A rotary compressor provided with a vane in contact with the vane, wherein a flat portion is formed at a tip of the vane, and a flat surface which is in sliding contact with the roller at the flat portion of the vane at all rotation angles of the roller. A rotary compressor characterized in that a part is formed. 19. The rotary compressor according to claim 18, wherein the area of the back pressure acting side end surface of the vane is reduced. 20. A surface hardness of the base material of the vane is 600.
The alloy steel of Hv to 800 Hv or the alloy steel whose surface hardness is adjusted to 800 Hv to 1200 Hv by surface treatment such as nitriding, and the surface of the tip of the vane is coated with chromium nitride ceramic coating. The rotary compressor according to any one of 18 and 19. 21. The roller has a surface hardness of 400 Hv-
Alloy cast iron adjusted to 600 Hv or surface hardness 600
The rotary compressor according to claim 20, wherein the rotary compressor is made of die steel adjusted to Hv to 800 Hv.