JPH10299679A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress and void abnormal abrasion and generation of sludge caused by sliding of a vane leading end with a piston outer periphery without deteriorating characteristics of a compressor by forming a recession with which one end of the vane is engaged on an outer periphery of the piston, and setting a retreating rate of the vane so as not to exceed the depth of the recession. SOLUTION: Under normal operation, a leading end 7a of a vane 7 bites into a bottom of a recession 6a of a piston 6, while a leading end 17a of a vane 17 bites into a bottom of a recession 16a of the piston 16, respectively by the same rate L7. When only the lower side vane 7 is under relief due to liquid compression, etc., a lever 21 retreats through a back surface 7b of the vane and a lower cylindrical surface of the lever. A lever supporter 22 retreates by a rate L22. The lower cylindrical surface can retreat by length twise as that of a moving rate of the lever supporter 22. The retreating rate L22 of the lever supporter 22 is set so as not to exceed half of depth L7 of the recession of the piston. The vane is not dislocated from the piston recession, and autorotation of the piston is restricted. Abnormal abrasion caused by sliding is thus suppressed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used for refrigeration and air conditioning equipment.

[0002]

2. Description of the Related Art FIG. 15 is a longitudinal sectional view of a conventional single-cylinder rotary compressor disclosed in Japanese Utility Model Laid-Open Publication No. 3-50314.
The single-cylinder rotary compressor includes an electric motor stator 2
And a compression mechanism, which is rotatably fitted to a cylinder 5, a shaft 4 which is driven by the motor stator 2 via a motor rotor 3, and a crank of the shaft. A piston 6 revolves along the inner surface of the cylinder 5 as the shaft rotates, a vane 7 reciprocates in a groove formed in the cylinder 5 while one end of the piston comes in contact with the piston, and moves the vane from the back toward the piston. And an upper bearing 9 and a lower bearing 10 into which the shaft 4 is rotatably fitted at both ends of the cylinder 5. This is a refrigerant compressor in which a cylinder is closed by an end surface of an end plate integrated with the lower bearing 10.

Next, the operation of the single cylinder rotary type compressor will be described. A suction pipe 11 having a suction muffler 11a is inserted from the outside into the closed container 1, and the refrigerant gas guided into the cylinder from the suction pipe revolves along the inner circumference of the cylinder 5 with the rotation of the shaft. Piston 6
And one end of the cylinder 5
The compressed refrigerant gas is compressed by the change in volume of the sealed volume formed by the vane 7 reciprocating in the groove formed in the cylinder, and the compressed refrigerant gas is discharged from the cylinder into the closed container 1 through the discharge port. Thereafter, the liquid is sent out from the discharge pipe 13 inserted into the closed container 1 into the refrigeration cycle. Refrigeration oil 14 is sealed in the bottom of the sealed container 1 and supplied to each sliding portion of the compression mechanism.

FIG. 16 shows another conventional example.
It is a longitudinal section of a two-cylinder rotary compressor. In the case of a two-cylinder rotary compressor, the eccentric direction of the lower crank 4a of the shaft 4 and the upper crank 4
The direction of eccentricity of b is 180 degrees opposite direction. For this reason,
The piston 6 inserted into the lower crank portion 4a and the piston 16 inserted into the upper crank portion 4b revolve with a phase difference of 180 degrees, so that the vane housed in the lower cylinder 5 and the upper vane The vanes housed in the cylinder 15 reciprocate with a phase difference of 180 degrees.

[0005]

In the conventional single-cylinder or two-cylinder rotary compressor described above, a piston whose outer periphery is a substantially perfect cylindrical surface is rotatably fitted into a crank portion of a shaft. On the other hand, since the vane is normally pressed against the piston outer periphery by a pressure difference or elastic force,
Depending on the operating conditions, the relative sliding speed between the vane tip and the outer periphery of the piston may increase. In particular, in a refrigerant atmosphere where the molecular structure does not contain chlorine element in the halogen derivative of hydrocarbons, since the extreme pressure effect of chlorine compounds cannot be expected,
Wear progresses at the point of sliding contact between the tip of the vane and the outer periphery of the piston where the lubrication condition has deteriorated, and the so-called mechanochemical reaction in which the worn metal element and the organic matter in the refrigerant / lubricating oil combine becomes remarkable, and a large amount of sludge is generated. Was done. This sludge adheres to each part in the refrigerant cycle, and its function is reduced or stopped, and there is a problem that the life of the refrigeration and air conditioning equipment is remarkably shortened. The present invention has been made to solve the above problems, without impairing the characteristics of conventional compressors such as high performance, high reliability, and low cost.
An object of the present invention is to provide a compressor that suppresses and avoids abnormal wear and sludge generation due to sliding between a vane tip and a piston outer periphery. It is another object of the present invention to obtain a compressor in which the vane does not come off from the recess of the piston even when the vane is relieved during abnormal pressure rise such as liquid compression. Another object is to obtain a compressor with low vibration and low noise. It is another object of the present invention to obtain a low-cost compressor having excellent operation stability, high reliability, and excellent productivity. Another object of the present invention is to obtain a compressor using a refrigerant that is a halogen derivative of a hydrocarbon and does not contain a chlorine element in its molecular structure.

[0006]

According to a first aspect of the present invention, there is provided a rotary compressor including a cylinder, a piston rotating along an inner periphery of the cylinder, and a piston provided on the cylinder while being pressed by the piston. A rotary vane having a vane reciprocating in a groove formed therein and a bearing closing an opening of an end face of the cylinder, a concave portion on one end of the vane is provided on an outer periphery of the piston, and The amount of retraction of the piston with respect to the piston is less than the depth of the recess.

A rotary compressor according to a second aspect of the present invention has two cylinders, two pistons rotating along the inner periphery of each cylinder, and one end of each of the two pistons. Two vanes reciprocating in grooves provided in the two cylinders while in contact with each other;
In a rotary compressor having a partition plate provided between the two cylinders for closing an opening of the cylinder and two bearings for closing the other end opening of the two cylinders, the two pistons are provided. A lever provided with a recess on the outer periphery of the vane, one end of each of the vanes being engaged with the recess, a center portion rotatably supported, and a lever having both ends for pressing the other ends of the two vanes, respectively. And the amount of retreat of the vane with respect to the piston via the lever is set to be equal to or less than the depth of the concave portion.

A rotary compressor according to a third aspect of the present invention is the rotary compressor according to the second aspect, further comprising a member for rotatably supporting a central portion of the lever, and a concave portion provided on an outer peripheral portion of the piston. Is slightly greater than the required relief depth, and the member that rotatably supports the central part of the lever is capable of translationally following the shaft in the radial direction.
Further, the translational retreat amount of the member is less than half of the depth of the concave portion provided on the outer periphery of the piston, and is close to half.

The rotary compressor according to a fourth aspect of the present invention is the rotary compressor according to the second aspect, further comprising a member for rotatably supporting the central portion of the lever, and rotatably supporting the central portion of the lever. The movable member is capable of performing translational movement only in the radial direction of the shaft, and the degree of freedom in other directions is substantially restricted.

A rotary compressor according to a fifth aspect of the present invention is the rotary compressor according to the second aspect, further comprising a member for rotatably supporting a central portion of the lever, and a rotatable central portion of the lever. The supporting member is pressed toward the shaft by an elastic material such as a spring.

Further, in the rotary compressor according to a sixth aspect of the present invention, in the second aspect, the two surfaces at both ends of the lever which can come into contact with the back surface of the vane are each a cylindrical surface. .

The rotary compressor according to a seventh aspect of the present invention is the rotary compressor according to the sixth aspect, wherein two cylindrical surfaces at both ends of the lever which can contact the back surface of the vane have a radius of the two cylindrical surfaces. The center of each cylindrical surface is the same, and the center of rotation corresponds to the center of rotation support of the central portion of the lever.

Further, a rotary compressor according to an eighth aspect of the present invention has two cylinders, two pistons rotating along the inner circumference of each cylinder, and one end of each of the two pistons. Two vanes reciprocating in grooves provided in the two cylinders while in contact with each other;
In a rotary compressor having a partition plate provided between the two cylinders for closing an opening of the cylinder and two bearings for closing the other end opening of the two cylinders, the two pistons are provided. A concave portion with which one end of the vane is provided on the outer periphery of
The other ends of the two vanes are provided with inclined portions facing each other, and wedges having two inclined portions that are in pressure contact with the two inclined portions are arranged, and the amount of retreat of the vanes with respect to the piston through the wedges is determined. The depth is not more than the depth of the concave portion on the outer periphery of the piston.

The rotary compressor according to a ninth aspect of the present invention is the rotary compressor according to the eighth aspect, further comprising a member for supporting a wedge in a radial direction of the shaft, and a depth of a concave portion provided on an outer peripheral portion of the piston. And a member for supporting the wedge in the radial direction of the shaft is configured as a wedge support movable in the shaft radial direction, and the movable amount of the wedge support is reduced. The depth is less than half and near half of the depth of the piston outer peripheral recess.

According to a tenth aspect of the present invention, in the rotary compressor according to the ninth aspect, the member for supporting the wedge in the radial direction of the shaft is capable of performing translational movement only in the radial direction of the shaft. And the degree of freedom in other directions is substantially restricted.

According to an eleventh aspect of the present invention, in the rotary compressor according to the ninth aspect, the member for supporting the wedge in the radial direction of the shaft is pressed toward the center of the shaft by an elastic body such as a spring. Is what is being done.

A rotary compressor according to a twelfth aspect of the present invention includes two cylinders, two pistons rotating along the inner periphery of each cylinder, and one end of each of the two pistons. Two vanes reciprocating in grooves provided in the two cylinders while in contact with each other; a partition plate provided between the two cylinders to close an opening of the cylinder; and the other of the two cylinders In the rotary compressor having two bearings respectively closing the end face openings, a concave portion with which one end of the vane is engaged is provided on the outer periphery of the two pistons, and at the other end of the two vanes, An inclined portion having an inclined angle θv in the facing direction is provided, two wedges each having one inclined portion engaging with each of the inclined portions are arranged, and both wedges are separated in the axial direction during normal operation. Ri amount is smaller than cotθv multiple of the piston outer periphery recess depth.

Further, in a rotary compressor according to a thirteenth aspect of the present invention, in the twelfth aspect, the two wedges are pressed in directions away from each other by an elastic body such as a spring.

The rotary compressor according to a fourteenth aspect of the present invention is the rotary compressor according to the first, second, eighth, or twelfth aspect, wherein the refrigerant is a halogen derivative of a hydrocarbon and does not contain a chlorine element in a molecular structure. Is used.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiment 1 FIG. First, a first embodiment of the present invention will be described with reference to FIGS. The description of the structure and operation common to the conventional example is omitted. FIG. 1 is a perspective view of the piston 6 and the vane 7 used in the present invention, and FIG. 2 is a partial cross-sectional view of the piston 6 and the vane 7. As shown in the figure, the outer periphery of the conventional piston was almost a perfect cylindrical surface, whereas the outer peripheral surface of the piston 6 used in the present invention had the same cross-sectional shape, and was changed from the upper end surface to the lower end surface. A concave portion 6a penetrating through is provided. On the other hand, the vane 7 is not much different from the conventional one. The radius of curvature r6 of the concave portion 6a newly provided in the piston 6 is set to a value larger than the radius of curvature r7 of the tip end 7a of the vane 7 which comes into contact with the outer periphery of the piston of the vane 7. That is, the vane tip 7a has a dimensional relationship that can be fitted into the recess 6a of the piston. During normal operation, the vane 7 is pressed against the piston 6 because the back surface is in a high-pressure atmosphere. In this case, the recess 6 of the piston
The vane tip 7a is fitted to a and a high pressure gas and a low pressure gas are sealed by the two being in line contact. Although the above description has been made for one of the two cylinders, that is, the piston 6 and the vane 7 stored in the lower cylinder 5, the same is true for the other cylinder, that is, the upper cylinder 15. The same is true for the stored piston 16 and vane 17.

FIG. 3 is an explanatory perspective view of another portion characteristic of the present embodiment. The lower cylinder 5
The lower end surface is in pressure contact with the lower bearing 10, and the upper end surface is in pressure contact with the lower end surface of the partition plate 19. The upper cylinder 15 has its upper end surface in pressure contact with the upper bearing 9,
The lower end surface presses the upper end surface of the partition plate 19. The central portion of the lower cylinder 5 is a cylindrical hollow portion 5a in which a piston 6 is stored. A vane space 5b is provided in communication with the hollow cylindrical portion 5a, in which the vane 7 reciprocates in synchronization with the movement of the piston 6. Furthermore, the vane space 5b
And a lever space 5c is provided in which the lower half of the lever 21 oscillates around the center hole 21a of the lever in synchronization with the movement of the vane 7. Note that the pendulum motion of the lever 21 referred to in the present specification is a reciprocating motion in which the one-sided amplitude around the center hole 21a is 90 degrees or less. Similarly, the center of the upper cylinder 15 is a hollow cylindrical portion 15a, in which a piston 16 is stored. A vane space 15b is provided in communication with the cylindrical hollow portion 15a, in which the vane 17 reciprocates in synchronization with the movement of the piston 16. Further, a lever space 15c is provided in communication with the vane space 15b, in which the upper half of the lever 21 performs a pendulum motion around the center hole 21a of the lever in synchronization with the movement of the vane 17.

The lever 21 has an inwardly facing surface 2 of the lever support 22 near its center including the center hole 21a.
2b, a rotary pin 23 penetrating both the center hole 22a provided in the lever support 22 and the center hole 21a provided in the lever is press-fitted into the center hole 22a of the lever support. Since the rotation pin 23 and the center hole 21a of the lever are fitted with a gap, the lever 21 is rotatable with respect to the lever support 22. The lever support 22 is stored in a storage space 19a provided in the partition plate 19. At the same time, a lever spring 24 is inserted between the back surface 22c and the spring surface 19b of the partition plate in a contracted state. ing. A lower cylindrical surface 21c and an upper cylindrical surface 21d are provided at both ends of the lever 21, and are in contact with the back surface 7b of the vane 7 and the back surface 17b of the vane 17 by the force of the lever spring 24, respectively.

In a two-cylinder rotary compressor during normal operation, two pistons rotate 180 degrees out of phase, and in synchronism therewith, the two vanes reciprocate 180 degrees out of phase. Depending on the shapes of the recesses of the pistons 6 and 16 and the shapes of the tips of the vanes 7 and 17, roughly speaking, the vanes 7 and 17 have a simple vibration 180 ° out of phase. 7 and the back surface 17b of the vane 17 have cylindrical surfaces 21c and 21d at both ends thereof.
Although the center of the lever 21 with which the lever 21 is in contact with the strictly following movement during the normal operation is strictly accurate, it can be said that the lever 21 is still.

FIG. 4 is a schematic diagram for explaining the relationship between the depth L7 of the concave portion of the vane 7 or the vane 17 and the maximum retractable amount L22 of the lever support 22. During normal operation, the vane 7
Of the piston 6 is provided at the bottom of the recess 6a of the piston 6,
Of the piston 16 is in a state of being cut into the bottom of the concave portion 16a of the piston 16 by a distance L7. Next, consider a case where only the lower vane 7 is relieved by liquid compression or the like. At this time, the state of the upper half vane 17 and the piston 16 and the state of the lower half piston 6 are the same as those in the normal operation, but the other parts are different from those in the normal operation. That is, the vane 7 which has been relieved by liquid compression or the like is attached to the back 7b of the vane and the lower cylindrical surface 21c of the lever.
The lever 21 is pushed rightward in the figure through the arrow. At this time, the substantially stationary upper cylindrical surface 21d becomes a fulcrum, and the lever 21 slightly rotates counterclockwise in the figure. This minute rotation is completed when the back surface 22c of the lever support 22 collides with the stop surface 19c of the partition plate 19. At this time, the lever support 22 is retracted to the right by a distance L22 in the figure, while the lower cylindrical surface 21c, which is located at a distance approximately twice as long as the lever upper cylindrical surface 21d serving as a fulcrum, is the movement amount of the lever support 22. , Ie, twice the distance L22, can be retracted to the right in the figure. As a result, the vane 7 also retreats to the right in the figure by twice the distance L22, and the amount of the tip 7a of the vane 7 caught by the recess 6a of the piston 6 is (L7) −2 × (L
22).

In this embodiment, since the retreat amount L22 of the lever support 22 is set to be equal to or less than half of the depth L7 of the piston concave portion, the above (L7) -2 × (L2
2) is always a positive value. This means that under no circumstances does the vane fall out of the recess in the piston, which substantially restricts the rotation of the piston. By substantially restricting the rotation of the piston, the sliding distance between the tip of the vane and the outer periphery of the piston is greatly reduced.As a result, abnormal wear and sludge generation due to the sliding between the tip of the vane and the outer periphery of the piston are significantly reduced. Can be suppressed. That is, it is possible to improve the reliability of the mounted refrigeration / air-conditioning equipment and obtain a compressor having high reliability. In addition, since the concave portion of the piston of the present invention is not set deeper than necessary, a low-cost compressor excellent in productivity is realized. That is, the depth L7 of the piston concave portion
Is set to a depth slightly exceeding the required relieving depth.
By making the retreat amount L22 of the support 22 less than half and close to half of the depth L7, the vane does not come off from the recess of the piston without setting the recess of the piston deeper than necessary. Therefore, sliding between the piston and the vane is reliably suppressed, and abnormal wear and sludge generation due to the sliding can be reliably suppressed, and a compressor having excellent productivity can be obtained.

The lever support 22 is connected to the shaft 4
Can be translated only in the radial direction, and the movement in the other five degrees of freedom is restricted. That is, the translational movement in the shaft direction and the rotational movement in the tangential direction of the shaft
And the lower end surface of the cylinder 15 are constrained,
The translational movement in the tangential direction of the shaft, the rotational movement in the radial direction of the shaft, and the rotational movement in the shaft direction are restricted by the side guide surface of the storage space 19 a of the partition plate 19. For this reason,
In the case of micro-following movement during normal operation and relief operation during liquid compression relief, it is possible to avoid situations where the back of the vane cannot be pushed firmly or directly from above due to shifting or tilting back and forth, right and left, that is, operation A highly reliable compressor with excellent stability has been realized.

Further, as described above, the lever support 22 is pressed in the direction of the shaft 4 by the lever spring 24, and the spring force of the lever spring 24 is set to a value sufficient to overcome the pendulum motion inertia force of the lever system. Have been. As a result, during normal operation, the lower cylindrical surface 21c of the lever 21 and the back surface 7b of the vane 7, and the upper cylindrical surface 21d of the lever 22 and the back surface 17b of the vane 17 are always in contact. For this reason, a low-vibration and low-noise compressor is realized, in which the contact surfaces sometimes collide with each other and do not generate large vibration or noise.

Since the lower cylindrical surface 21c and the upper cylindrical surface 21d of the lever 21 used in the present invention are formed as cylindrical names as the name implies, the back surface of the vane accompanying the pendulum movement of the lever 21 during normal operation. In addition to the smooth movement of contacts at the time of liquid compression, the movement of the other contact with one contact as a fulcrum at the time of liquid compression is also smooth, and a highly reliable compressor with excellent operation stability has been realized. .

In addition, in the lever 21 used in the present invention, the radius of curvature of the lower cylindrical surface 21c and the radius of curvature of the upper cylindrical surface 21d are made the same, and at the same time, the center of the lower cylindrical surface 21c and the center of the upper cylindrical surface 21d. The middle point between the two centers is substantially aligned with the lever center hole 21a. This will be described with reference to FIGS. FIG. 5 is a functional explanatory view of the lever shape employed in the embodiment of the present invention.
FIG. 5 is a functional explanatory view of a lever having a different shape from the lever employed in the embodiment of the present invention. 5, the upper diagram (a) illustrates a state in which the lever 21 is in a neutral state, and the lower diagram (b) illustrates a state in which the lever 21 swings by θ, that is, the lever 21 is tilted by θ. . In the above (a) explanatory diagram, point 21
a is the center of the pendulum movement of the lever 21, and points 21c and 21d represent the vane back 7 when the lever 21 is in a neutral state, that is, when the lever 21 is standing vertically.
b, 17b, and points 21e and 21f are:
The horizontal line passing through the points 21c and 21d is the point 2
It is a point that intersects a vertical line passing through 1a. And lever 2
The radius of the cylindrical surface 21c is R21c, the radius of the cylindrical surface 21d is R21d, and the distance between the points 21c and 21e is L2.
1c, the distance between the point 21d and the point 21f is L21d, and
The distance between 1a and point 21e and the distance between point 21a and point 21f are all L21. In the state of FIG. 5A, the lower contact point is L21c from the reference, the upper contact point is L21d from the reference,
In the case of the embodiment of the present invention, since both have the same value,
The sum of both is L21c + L21d = 2 × L21c. On the other hand, in the state shown in the lower (b) of FIG. 5, that is, in the state inclined by θ, the lower contact point is
L21 × sinθ + R21c, the contact point on the top is -L21
× Sin θ + R21d, and the sum of both becomes (L21 × sin θ + R21c) + (− L21 × sin θ + R21d) = R21c + R21d = 2 × R21c = 2 × L21c. The sum of the distances of the contact points from the reference plane is constant. This means that when the two vanes make simple vibrations 180 degrees out of phase, the center point 21a of the pendulum movement of the lever 21 is at a fixed position and does not move.

FIG. 6 is a functional explanatory view of a lever having a different shape from the lever employed in the embodiment of the present invention.
The upper (a) explanatory diagram shows a state in which the lever 21 is neutral, and the lower (b) diagram shows a state in which the lever 21 swings by θ, that is, tilts by θ. The definition of the points and the definition of the length are the same as in FIG. In the state shown in the upper part of FIG. 6A, the lower contact point is L21 from the reference.
c, The upper contact point is L21d from the reference, and when both are set to the same value, the sum of both is L21c + L21d = 2 × L21c. On the other hand, in the state shown in the lower (b) of FIG. 6, that is, in the state tilted by θ, the lower contact point is L21 × sinθ + (L21c−R21c) × cosθ + R
21c, the upper contact point is -L21 × sin θ + (L21
d−R21d) × cos θ + R21d, so that the sum of both is (L21 × sin θ + L21c × cos θ−R21c × cos θ + R21c)
+ (− L21 × sin θ + L21d × cos θ−R21d × cos θ + R2
1d) = 2 × L21c−2 × (1-cos θ) × (L21c−R21
c) In a case different from the embodiment of the present invention, as θ increases, the total distance between the upper and lower contact points from the reference plane decreases. This means that when the two vanes make a simple vibration having a phase difference of 180 degrees, the center point 21 of the pendulum motion of the lever 21 is changed.
a means that the total amplitude oscillates as (1−cos θmax) × (L21c−R21c). From the above comparison, when the embodiment of the present invention is adopted, the small following movement of the lever support during the pendulum movement of the lever during normal operation is relatively small. That is, a highly reliable compressor excellent in operation stability is realized.

Further, in this embodiment, a refrigerant which is a halogen derivative of hydrocarbon and does not contain chlorine element in the molecular structure is used as the refrigerant. Since this refrigerant cannot expect the extreme pressure action of chlorine compounds, it has been liable to cause abnormal wear and sludge generation in the past. However, in the present embodiment, such a problem does not become apparent because the above-described device has been devised. As a result, a highly reliable compressor that does not destroy the ozone layer, yet does not cause abnormal wear and does not generate sludge can be obtained.

Embodiment 2 FIG. Next, a second embodiment of the present invention will be described with reference to FIG. The description of the structure and operation common to the conventional example is omitted. FIG. 7 shows the first embodiment.
FIG. 7 is a schematic diagram when the already-described piston-vane engagement structure and lever structure are applied to a single-cylinder rotary compressor. The lower balancer 25 has a cylindrical outer surface and is eccentrically attached to the shaft 4. The lever 21 is supported by a lever support 22 via a rotating pin 23, and together with a lever spring 24, the lower bearing 1
0. With such a configuration, the same operation and effect as in the case of the two-cylinder described in the first embodiment can be expected even with a single-cylinder rotary compressor. Further, also in the present embodiment, when a refrigerant which is a halogen derivative of hydrocarbon and does not contain chlorine element in the molecular structure is used as the refrigerant, the same operation and effect as in the first embodiment can be expected.

Embodiment 3 A third embodiment of the present invention will be described with reference to FIGS. The description of the structure and operation common to the conventional example is omitted. FIG. 8 is a perspective view of the piston 6 and the vane 7 used in the present invention, and FIG. 2 is a partial cross-sectional view of the piston 6 and the vane 7. While the outer circumference of the conventional piston is almost a perfect cylindrical surface, the outer circumference of the piston 6 used in the present invention has the same cross-sectional shape and a recess 6 penetrating from the upper end face to the lower end face.
a is provided. Newly provided recess 6 in piston 6
The radius of curvature r6 of a is set to a value larger than the radius of curvature r7 of the vane tip 7a abutting on the outer peripheral portion of the piston of the vane 7. That is, the vane tip 7a is located at the recess 6a of the piston.
It has a dimensional relationship that allows it to be fitted into. During normal operation, the vane 7 is pressed against the piston 6 because the back surface is in a high-pressure atmosphere. In this case, the vane tip 7a is fitted into the recess 6a of the piston, and the two are in line contact to seal the high-pressure gas and the low-pressure gas. On the other hand, a part or all of the end face of the vane 7 on the opposite side to the vane tip 7a is provided with a vane back inclined surface 7c which is a plane not parallel to the vane tip 7a. Although the above description has been directed to one of the two cylinders, that is, the piston 6 and the vane 7 housed in the lower cylinder 5, the same is true for the other, that is, the upper cylinder 15
The same applies to the piston 16 and the vane 17 stored in

FIG. 9 is a perspective view for explaining other portions characteristic of the present embodiment, and FIG. 10 is a partial longitudinal sectional view of the present embodiment. In both figures, the lower end of the lower cylinder 5 is in pressure contact with the end face 10 a of the lower bearing 10, and the upper end is in pressure contact with the lower end face of the partition plate 19. The upper cylinder 15 has an upper end surface pressed against the end surface 9 a of the upper bearing 9, and a lower end surface pressed against the upper end surface of the partition plate 19. The central portion of the lower cylinder 5 is a cylindrical hollow portion 5a in which a piston 6 is stored. In addition, the cylindrical hollow portion 5
A vane space 5b is provided in communication with a, in which the vane 7 reciprocates in synchronization with the movement of the piston 6. Further, the wedge space 5d communicates with the vane space 5b.
The lower part of the wedge 31 reciprocates in the direction perpendicular to the direction of movement of the vane in synchronization with the movement of the vane 7. Similarly, the center of the upper cylinder 15 is a hollow cylindrical portion 15a, in which a piston 16 is stored. In addition, the cylindrical hollow portion 1
A vane space 15b is provided in communication with 5a, in which the vane 17 reciprocates in synchronization with the movement of the piston 16. Further, a wedge space 15d is provided in communication with the vane space 15b, in which the upper part of the wedge 31 reciprocates in a direction perpendicular to the direction of movement of the vane in synchronization with the movement of the vane 7.

The wedge 31 has a lower portion in the wedge space 5d of the cylinder 5 and an upper portion in the wedge space 15d of the cylinder 15.
d, and the central part thereof is at both end faces 3
1b, the guide surface 19d of the storage space 19a of the partition plate 19
Is fitted. Further, a lower inclined surface 31c and an upper inclined surface 31d are provided at both ends of the wedge 31, and are in contact with the vane back inclined surface 7c of the vane 7 and the vane back inclined surface 17c of the vane 17, respectively. The wedge support 32 is a wedge 3
1, the lower part of which is the wedge space 5d of the cylinder 5.
The upper part is stored in the wedge space 15d of the cylinder 15, and the center part is both end faces 32b.
The partition plate 19 is fitted to the guide surface 19d of the storage space 19a. The back surface 32c of the wedge support 32 and the cylinder 5
A wedge spring 33 is inserted in a contracted state between the spring surface 5e of the cylinder 15 and another wedge spring 33 between the back surface 32c of the wedge support 32 and the spring surface 15e of the cylinder 15. 33 is inserted in a contracted state. The wedge support 32 pressed toward the center in the radial direction by the wedge spring 33 has a front surface 32a.
, The back surface 31a of the wedge 31 is similarly pressed toward the center in the radial direction. Further, the lower end surface 32d and the upper end surface 32e of the wedge support 32 are engaged with the end surface 10a of the lower bearing 10 and the end surface 9a of the upper bearing 9, respectively.

In a two-cylinder rotary compressor during normal operation, two pistons rotate 180 degrees out of phase, and in synchronism therewith, the two vanes reciprocate 180 degrees out of phase. Depending on the shapes of the recesses of the pistons 6 and 16 and the shapes of the tips of the vanes 7 and 17, roughly speaking, the vanes 7 and 17 have a simple vibration 180 ° out of phase. The wedge 31 in which the inclined surfaces 31c and 31d at both ends thereof are in contact with the vane back inclined surface 7c of the vane 7 and the vane back inclined surface 17c of the vane 17 has a substantially simple vibration in the axial direction of the shaft 4 during normal operation. Strictly speaking, in the right angle direction, that is, in the radial direction, it is strictly following, but it is no doubt that it is still.

FIG. 11 is a schematic diagram for explaining the relationship between the depth L7 of the concave portion of the vane 7 or the vane 17 and the maximum retractable amount L22 of the wedge support 32. In this explanation,
The inclination angle of the vane back inclined surfaces 7c and 17c is defined as θv. First, at the time of normal operation, the tip 7a of the vane 7 enters the bottom of the recess 6a of the piston 6, and the tip 17a of the vane 17 enters the bottom of the recess 16a of the piston 16 for a distance L7, so to speak. Next, consider a case where only the lower vane 7 is relieved by liquid compression or the like. At this time, the state of the vane 17 and the piston 16 and the state of the piston 6 are the same as those in the normal operation, but the states of other parts are different from those in the normal operation. That is, the vane 7 which has been relieved by liquid compression or the like moves rightward in the drawing, and at this time, the vane back inclined surface 7c and the wedge lower inclined surface 31
c slides between the inclined surfaces, and as a result, the wedge 31 moves in the upper right direction in the figure. Then, this movement is performed on the back surface 31a of the wedge 31.
Is the stop surface 19 of the partition plate 19 via the wedge support 32.
This is completed by colliding with c. Now, regarding the amount of movement of the wedge 31 in the upper right direction, assuming that the angle of the inclined surface of the back of the vane is θv, the wedge 31 moves by L22 to the right and L22 × cot θv in the upper direction. Moving. As a result, the vane 7 whose movement is restricted in the vertical direction moves L22 + L22 × cotθv × tanθv = 2 × L22 to the right, and the tip 7a of the vane 7 with respect to the recess 6a of the piston 6 Is (L7) -2 ×
(L22).

In the present embodiment, the retreat amount L of the wedge support 32
Since (22) is set to be equal to or less than half of the depth L7 of the piston concave portion, the above (L7) −2 × (L22)
Is always a positive value. This means that under no circumstances does the vane fall out of the recess in the piston, which substantially restricts the rotation of the piston. By substantially restricting the rotation of the piston, the sliding distance between the tip of the vane and the outer periphery of the piston is greatly reduced.As a result, abnormal wear and sludge generation due to the sliding between the tip of the vane and the outer periphery of the piston are significantly reduced. Can be suppressed. That is, it is possible to improve the reliability of the mounted refrigeration / air-conditioning equipment and obtain a compressor having high reliability.
In addition, since the concave portion of the piston of the present invention is not set deeper than necessary, a low-cost compressor excellent in productivity is realized. That is, the depth L7 of the piston concave portion is set to a depth slightly exceeding the required relieving depth, and the wedge support 32 is used.
By making the retreat amount L22 less than half and close to half of the depth L7, the vane does not come off from the piston recess without setting the piston recess more deeply than necessary. The sliding between the vane and the vane is reliably suppressed, and abnormal wear and sludge generation due to the sliding can be surely suppressed, and a compressor excellent in productivity can be obtained. In addition, the larger the inclination angle θv of the above-described vane back inclined surface, the smaller the axial movement amount of the wedge 31 and the lower the vibration, but on the other hand, the larger the component force for pushing the vane in the axial direction. Have. In consideration of this characteristic, the inclination angle θv is set to an appropriate value.

The wedge support 32 is capable of translating only in the radial direction of the shaft 4, and is restricted from moving in the other five degrees of freedom. That is, the translational movement in the shaft direction and the rotational movement in the tangential direction of the shaft are restrained by the end face 10a of the lower bearing 10 and the end face 9a of the upper bearing 9,
The translational movement in the tangential direction of the shaft, the rotational movement in the radial direction of the shaft, and the rotational movement in the shaft direction are restricted by the side guide surface 19 d of the storage space 19 a of the partition plate 19. For this reason, even in the case of a small follow-up movement during normal operation or a relief operation during liquid compression relief, the wedge is shifted or tilted back and forth, left and right, and it may not be able to firmly contact the inclined back surface of the vane / it can not be pushed. A highly reliable compressor that can be avoided, that is, has excellent operation stability is realized.

As described above, the wedge support 32 is pressed in the direction of the shaft 4 by the wedge spring 33, and the spring force of the wedge spring 33 has a value sufficient to overcome the reciprocating linear motion inertia force of the wedge system. Is set. As a result, during normal operation, the lower inclined surface 31c of the wedge 31 and the back inclined surface 7c of the vane 7, and the upper inclined surface 31d of the wedge 31 and the back inclined surface 17c of the vane 17 are always in contact with each other. For this reason, a low-vibration and low-noise compressor is realized, in which the contact surfaces sometimes collide with each other and do not generate large vibration or noise.

Further, in the present embodiment, the refrigerant used is a halogen derivative of a hydrocarbon which does not contain chlorine element in the molecular structure. Since this refrigerant cannot expect the extreme pressure action of chlorine compounds, it has been liable to cause abnormal wear and sludge generation in the past. However, in the present embodiment, such a problem does not become apparent because the above-described device has been devised. As a result, a highly reliable compressor that does not destroy the ozone layer, yet does not cause abnormal wear and does not generate sludge can be obtained.

Embodiment 4 Next, a second embodiment of the present invention will be described with reference to FIGS. The description of the structure and operation common to the first embodiment of the present invention is omitted. FIG. 12 is a perspective view for explaining a characteristic part of the present embodiment, and FIG. 13 is a partial longitudinal sectional view of the present embodiment. In both figures, the lower end of the lower cylinder 5 is in pressure contact with the end face 10 a of the lower bearing 10, and the upper end is in pressure contact with the lower end face of the partition plate 19. The upper end surface of the upper cylinder 15 is the end surface 9 a of the upper bearing 9.
The lower end surface thereof is in pressure contact with the upper end surface of the partition plate 19. The central portion of the lower cylinder 5 is a cylindrical hollow portion 5a in which a piston 6 is stored. A vane space 5b is provided in communication with the hollow cylindrical portion 5a, in which the vane 7 reciprocates in synchronization with the movement of the piston 6. Further, a wedge space 5d is provided in communication with the vane space 5b, in which the wedge 41 reciprocates in a direction perpendicular to the movement direction of the vane in synchronization with the movement of the vane 7. Similarly, the center of the upper cylinder 15 is a hollow cylindrical portion 15a, in which a piston 16 is stored. A vane space 15b is provided in communication with the cylindrical hollow portion 15a, in which the vane 17 reciprocates in synchronization with the movement of the piston 16. Further, a wedge space 15d is provided in communication with the vane space 15b, in which the wedge 42 reciprocates in a direction perpendicular to the direction of movement of the vane in synchronization with the movement of the vane 7.

The wedge 41 has both end surfaces 41b fitted on side guide surfaces 5f which are parallel inner surfaces of the wedge space 5d of the cylinder 5, and has a front surface 41d and a back surface 4d.
1e is engaged with the front guide surface 19e of the partition plate 19 and the rear guide surface 5g of the cylinder 5, respectively. On the other hand, an inclined surface 41c is provided on the end surface of the wedge 41 on the vane side, and is in contact with the vane back inclined surface 7c of the vane 7. Similarly, the wedge 42 has both end faces 42b
Side guide surface 15 which is a parallel inner surface of wedge space 15d of No. 5
f, and the front surface 42d and the back surface 42e of the
And the rear guide surface 15 g of the cylinder 15. On the other hand, the end surface of the wedge 42 on the vane side has an inclined surface 42.
c is provided, and the vane back inclined surface 1 of the vane 17 is provided.
7c. On the end surfaces of the wedges 41 and 42 that do not contact the vane, opposing end surfaces 41a and 42a are formed in parallel with each other.
A wedge spring 33 is inserted between the two wedges in a contracted state.

FIG. 14 is a schematic diagram for explaining the relationship between the depth L7 of the concave portion of the vane 7 or the vane 17 and the distance between the lower wedge 41 and the upper wedge 42. In this description, the inclination angle of the vane back inclined surfaces 7c and 17c is defined as θv.
First, during normal operation, the tip 7a of the vane 7 is located at the bottom of the recess 6a of the piston 6, and the tip 17a of the vane 17 is located at the bottom of the recess 16a of the piston 16, by a distance L7.
It is in a state of being bitten. Next, consider a case where only the lower vane 7 is relieved by liquid compression or the like. At this time, the state of the vane 17 and the piston 16, the state of the wedge 42 and the state of the piston 6 are the same as those in the normal operation, but the states of other parts are different from those in the normal operation. That is, the vane 7 which has been relieved by liquid compression or the like moves rightward in the drawing. At this time, the vane back inclined surface 7c and the inclined surface 41c of the lower wedge 41 slide between the inclined surfaces, and as a result, the lower wedge 41 Moves upward in the figure. This movement is completed when the opposing end surface 41a of the lower wedge 41 collides with the opposing end surface 42a of the upper wedge 42. Now, regarding the amount of movement of the vane 7 in the right direction, if the angle of the inclined surface of the back of the vane is θv, the lower wedge 41 moves upward by L41, and as a result, Vane 7 whose movement is restricted
Moves only in the right direction by (tan θv) × (L41), and the amount of the tip 7a of the vane 7 caught by the concave portion 6a of the piston 6 is (L7) − (tan θ).
v) × (L41).

In the present embodiment, the normal distance L41 between the lower wedge 41 and the upper wedge 42 is set to be smaller than (cotθv) times the depth L7 of the piston concave portion. ) − (Tan θv) × (L41)> (L7) − (tan
θv) × (cotθv) × (L7) = 0, and the amount of the tip 7a of the vane 7 caught always becomes a positive value. This means that under no circumstances does the vane fall out of the piston recess,
Thereby, the rotation of the piston is substantially restrained. By substantially restricting the rotation of the piston, the sliding distance between the tip of the vane and the outer periphery of the piston is greatly reduced.As a result, abnormal wear and sludge generation due to the sliding between the tip of the vane and the outer periphery of the piston are significantly reduced. Can be suppressed. That is, it is possible to improve the reliability of the mounted refrigeration / air-conditioning equipment and obtain a compressor having high reliability. In addition, since the concave portion of the piston of the present invention is not set deeper than necessary, a low-cost compressor excellent in productivity is realized. In addition, the inclination angle θv of the aforementioned vane back inclined surface
Has the characteristic that the larger the size, the smaller the amount of movement of the wedge 31 in the axial direction and the lower the vibration, but the greater the component force for pushing the vane in the axial direction. In view of this characteristic,
The inclination angle θv is set to an appropriate value.

The lower wedge 41 is capable of translating only in the axial direction of the shaft 4, and is restricted from moving in the other five degrees of freedom. That is, the translational movement in the radial direction and the rotational movement in the tangential direction of the shaft are restricted by the front guide surface 19e of the partition plate 19 and the rear guide surface 5g of the cylinder 5, and the translational movement in the tangential direction of the shaft and the rotational movement in the shaft radial direction are performed. And the rotational movement in the shaft direction are restricted by the side guide surface 5f of the cylinder 5. Similarly,
The upper wedge 42 is capable of translating only in the axial direction of the shaft 4, and is restricted from moving in the other five degrees of freedom. That is, the translational movement in the radial direction and the rotational movement in the tangential direction of the shaft of the shaft are caused by the front guide surface 19e of the partition plate 19.
And the rear guide surface 15 g of the cylinder 15, and the translational movement in the tangential direction of the shaft, the rotational movement in the radial direction of the shaft, and the rotational movement in the shaft direction are restricted by the side guide surface 15 f of the cylinder 15. For this reason, even in the case of a small follow-up movement during normal operation or a relief operation during liquid compression relief, the wedge is shifted or tilted back and forth, left and right, and it may not be able to firmly contact the inclined back surface of the vane / it can not be pushed. A highly reliable compressor that can be avoided, that is, has excellent operation stability is realized.

As described above, the lower wedge 41 and the upper wedge 42 are pressed against the vanes 7 and 17 by the wedge springs 33, respectively, and the spring force of the wedge springs 33 is the reciprocating linear motion inertia force of the wedge system. Is set to a value that is sufficient to overcome. As a result, during normal operation, the inclined surface 41c of the lower wedge 41, the inclined surface 7c of the back of the vane 7, and the upper wedge 4
2 inclined surface 42c and the back inclined surface 17c of the vane 17
Each is always in contact. For this reason, a low-vibration and low-noise compressor is realized, in which the contact surfaces sometimes collide with each other and do not generate large vibration or noise.

Further, in the present embodiment, the refrigerant used is a halogen derivative of a hydrocarbon which does not contain chlorine element in the molecular structure. Since this refrigerant cannot expect the extreme pressure action of chlorine compounds, it has been liable to cause abnormal wear and sludge generation in the past. However, in the present embodiment, such a problem does not become apparent because the above-described device has been devised. As a result, a highly reliable compressor that does not destroy the ozone layer, yet does not cause abnormal wear and does not generate sludge can be obtained. In the third and fourth embodiments, the back of the vane has been described assuming a high-pressure atmosphere. However, a low-pressure atmosphere or an intermediate pressure atmosphere may be used.

[0049]

As described above, the rotary compressor according to the first aspect of the invention reciprocates in a cylinder, a piston rotating along the inner periphery of the cylinder, and a groove provided in the cylinder while being pressed by the piston. In a rotary compressor having a moving vane and a bearing for closing an opening of an end face of a cylinder, a concave portion is provided on an outer periphery of a piston so that one end of the vane is engaged, and a retreat amount of the vane with respect to the piston is reduced by a depth of the concave portion. As a result, the recess of the piston does not come off the vane, and the rotation of the piston is restrained. Therefore, sliding between the piston and the vane is reliably suppressed, and abnormal wear and sludge generation due to the sliding can be reliably suppressed. In addition, when the liquid is compressed, the vane separates from the piston within the range of the concave portion of the piston, and the high-pressure refrigerant that has been abnormally pressurized is released from the high-pressure side space to the low-pressure side space. Is avoided. That is, it is possible to improve the reliability of the mounted refrigeration / air-conditioning equipment and obtain a rotary compressor having high reliability.

The rotary compressor according to the second aspect of the present invention has two cylinders, two pistons rotating along the inner circumference of each cylinder, and one end of each of the two pistons. Two vanes reciprocating in grooves provided in the two cylinders while in contact with each other;
In a rotary compressor having a partition plate provided between the two cylinders for closing an opening of the cylinder and two bearings for closing the other end opening of the two cylinders, the two pistons are provided. A lever provided with a recess on the outer periphery of the vane, one end of each of the vanes being engaged with the recess, a center portion rotatably supported, and a lever having both ends for pressing the other ends of the two vanes, respectively. And the amount of retreat of the vane with respect to the piston via the lever is set to be equal to or less than the depth of the concave portion, so that the rotation of the piston is substantially restrained, and the vane tip and the outer peripheral portion of the piston slide. The moving distance is significantly reduced, and as a result, abnormal wear and sludge generation due to sliding between the vane tip and the outer periphery of the piston can be significantly suppressed. In addition, during liquid compression, the vane separates from the piston within the range of the concave part of the piston, so that the high-pressure refrigerant that has been abnormally pressurized is released from the high-pressure side space to the low-pressure side space, thereby avoiding an increase in bearing load due to abnormally high pressure. Is done. That is, it is possible to obtain a rotary compressor having improved reliability of mounted refrigeration and air-conditioning equipment and having high reliability.

The rotary compressor according to a third aspect of the present invention is the rotary compressor according to the second aspect, further comprising a member for rotatably supporting a central portion of the lever, and a concave portion provided on an outer peripheral portion of the piston. Is slightly greater than the required relief depth, and the member that rotatably supports the central part of the lever is capable of translationally following the shaft in the radial direction.
In addition, since the amount of translation and retreat of the member is less than half of the depth of the concave portion provided on the outer periphery of the piston and is set to nearly half, the concave portion of the piston is set deeper than necessary in addition to the effect of the second invention. Without this, the concave portion of the piston does not come off the vane, so that sliding between the piston and the vane is reliably suppressed, and abnormal wear and sludge generation due to the sliding are surely suppressed. it can. For this reason, a low-cost rotary compressor excellent in productivity can be obtained while increasing the reliability of the mounted refrigeration and air-conditioning equipment and having high reliability.

The rotary compressor according to a fourth aspect of the present invention is the rotary compressor according to the second aspect, further comprising a member for rotatably supporting the central portion of the lever, and rotatably supporting the central portion of the lever. In addition to the effect of the second invention, the member to be moved is capable of performing translational follow-up movement only in the radial direction of the shaft and the degree of freedom in other directions is substantially restricted. The contact point with the back of the vane does not vary and is stable. Therefore, a highly reliable rotary compressor having excellent lever operation stability can be obtained.

A rotary compressor according to a fifth aspect of the present invention is the rotary compressor according to the second aspect, further comprising a member for rotatably supporting a central portion of the lever, and allowing the central portion of the lever to be rotatable. Since the supporting member is pressed in the direction of the shaft by an elastic material such as a spring, both ends of the lever and the back surface of the vane are always in contact. For this reason, a low noise and low vibration rotary compressor which does not generate the collision sound and vibration of the lever can be obtained.

Further, in the rotary compressor according to the sixth aspect of the present invention, in the second aspect, the two surfaces at both ends of the lever which can contact the back surface of the vane are cylindrical surfaces. In addition to the effect of the second aspect, the movement of the contact point with the back surface of the vane accompanying the pendulum movement of the lever becomes smooth. For this reason, a highly reliable rotary compressor excellent in operation stability, in which the contact between the lever and the vane moves smoothly, can be obtained.

The rotary compressor according to a seventh aspect of the present invention is the rotary compressor according to the sixth aspect, wherein the two cylindrical surfaces at both ends of the lever, which can contact the back surface of the vane, have a radius of the two cylindrical surfaces. In addition to being the same, the midpoint of the center of each cylindrical surface coincides with the rotation support center of the central portion of the lever, so that in addition to the effect of the sixth invention, the lever support during the pendulum movement of the lever is added. The small following motion is relatively small. For this reason, a low-cost compressor excellent in productivity without making the piston recess unnecessarily deep can be obtained,
A highly reliable rotary compressor excellent in the operational stability of the lever support can be obtained.

Further, a rotary compressor according to an eighth aspect of the present invention includes two cylinders, two pistons rotating along the inner circumference of each cylinder, and one end of each of the two pistons. Two vanes reciprocating in grooves provided in the two cylinders while in contact with each other;
In a rotary compressor having a partition plate provided between the two cylinders for closing an opening of the cylinder and two bearings for closing the other end opening of the two cylinders, the two pistons are provided. A concave portion with which one end of the vane is provided on the outer periphery of
The other ends of the two vanes are provided with inclined portions facing each other, and wedges having two inclined portions that are in pressure contact with the two inclined portions are arranged, and the amount of retreat of the vanes with respect to the piston through the wedges is determined. Since the depth is not more than the depth of the concave portion on the outer periphery of the piston, the rotation of the piston is substantially restricted. Therefore, the sliding distance between the tip of the vane and the outer periphery of the piston is greatly reduced, and as a result, abnormal wear and sludge generation due to the sliding between the tip of the vane and the outer periphery of the piston can be significantly suppressed. In addition, during liquid compression, the vane separates from the piston within the range of the concave part of the piston, so that the high-pressure refrigerant that has been abnormally pressurized is released from the high-pressure side space to the low-pressure side space, thereby avoiding an increase in bearing load due to abnormally high pressure. Is done. Further, since the newly added sliding member is reciprocal sliding instead of rotational sliding, the occurrence of wear and seizure is avoided. That is, it is possible to obtain a rotary compressor having improved reliability of mounted refrigeration and air-conditioning equipment and having high reliability.

According to a ninth aspect of the present invention, in the rotary compressor according to the eighth aspect, the rotary compressor further comprises a member for supporting a wedge in a radial direction of the shaft, and a depth of a concave portion provided on an outer peripheral portion of the piston. And the member that supports the wedge in the radial direction of the shaft,
The wedge support is configured as a wedge support that can move in the shaft radial direction, and the movable amount of the wedge support is less than half of the depth of the piston outer peripheral portion concave portion, and is close to half. Therefore, in addition to the effects of the eighth invention, The rotation of the piston is substantially restrained without setting the recess of the piston deeper than necessary.
For this reason, a low-cost rotary compressor excellent in productivity can be obtained while increasing the reliability of the mounted refrigeration and air-conditioning equipment and having high reliability.

Further, in the rotary compressor according to the tenth aspect of the present invention, in the ninth aspect, the member for supporting the wedge in the radial direction of the shaft is capable of performing translational movement only in the radial direction of the shaft. And the degree of freedom in other directions is substantially constrained, so that in addition to the effects of the ninth aspect of the invention, the press-contact portion between the inclined portion of the wedge and the inclined portion on the back surface of the vane does not vary and is stable. I do. Therefore, a highly reliable rotary compressor having excellent wedge operation stability can be obtained.

In the rotary compressor according to an eleventh aspect of the present invention, in the ninth aspect, the member for supporting the wedge in the radial direction of the shaft is pressed in the center direction of the shaft by an elastic body such as a spring. As a result, the inclined portion of the wedge and the inclined portion on the back of the vane are constantly pressed against each other. For this reason, a low noise and low vibration rotary compressor which does not generate the collision sound and vibration of the wedge and the vane can be obtained.

A rotary compressor according to a twelfth aspect of the present invention includes two cylinders, two pistons rotating along the inner circumference of each cylinder, and one end of each of the two pistons. Two vanes reciprocating in grooves provided in the two cylinders while in contact with each other; a partition plate provided between the two cylinders to close an opening of the cylinder; and the other of the two cylinders In the rotary compressor having two bearings respectively closing the end face openings, a concave portion with which one end of the vane is engaged is provided on the outer periphery of the two pistons, and at the other end of the two vanes, An inclined portion having an inclined angle θv in the facing direction is provided, two wedges each having one inclined portion engaging with each of the inclined portions are arranged, and both wedges are separated in the axial direction during normal operation. Since the amount Ri is smaller than cotθv multiple of the piston outer periphery recess depth, rotation of the piston is substantially constrained without deeper setting the recess of the piston than necessary. Therefore, the sliding distance between the tip of the vane and the outer periphery of the piston is greatly reduced, and as a result, abnormal wear and sludge generation due to the sliding between the tip of the vane and the outer periphery of the piston can be significantly suppressed. In addition, during liquid compression, the vane moves away from the piston within the range of the recess of the piston, so high-pressure refrigerant that has been abnormally boosted is released from the high-pressure side space to the low-pressure side space. Is done. Furthermore, the newly added sliding member is compact and the number of parts is small.
That is, a low-cost rotary compressor with high productivity can be obtained while increasing the reliability of the mounted refrigeration and air-conditioning equipment and having high reliability.

Further, in the rotary compressor according to the thirteenth aspect of the present invention, in the twelfth aspect, since the two wedges are pressed in directions away from each other by an elastic body such as a spring, the inclination of the wedges is reduced. The part and the inclined part on the back of the vane are always in pressure contact with each other. For this reason, a low noise and low vibration rotary compressor which does not generate the collision sound and vibration of the wedge and the vane can be obtained.

The rotary compressor according to a fourteenth aspect of the present invention is the rotary compressor according to the first, second and eighth aspects, wherein a refrigerant which is a halogen derivative of a hydrocarbon and does not contain a chlorine element in a molecular structure is used. Therefore, in addition to the effects of the first, second, and eighth inventions, a highly reliable rotary compressor that does not destroy the ozone layer, does not cause abnormal wear, and does not generate sludge can be obtained.

[Brief description of the drawings]

FIG. 1 is a perspective view of a piston vane according to a first embodiment of the present invention.

FIG. 2 is a partial cross-sectional view of the piston vane according to the first embodiment of the present invention.

FIG. 3 is a perspective view of main components according to the first embodiment of the present invention.

FIG. 4 is a schematic diagram illustrating setting of a retreat amount of a lever according to the first embodiment of the present invention;

FIG. 5 is a functional explanatory view of a lever shape according to the first embodiment of the present invention.

FIG. 6 is a functional explanatory view of a shape different from the lever shape according to the first embodiment of the invention;

FIG. 7 is a schematic diagram showing a configuration of Embodiment 2 of the present invention.

FIG. 8 is a perspective view of a piston vane according to a third embodiment of the present invention.

FIG. 9 is a perspective view of main parts according to Embodiment 3 of the present invention.

FIG. 10 is a partial longitudinal sectional view of Embodiment 3 of the present invention.

FIG. 11 is a schematic diagram illustrating the setting of the amount of retraction of the wedge according to the third embodiment of the present invention.

FIG. 12 is a perspective view of main components according to a fourth embodiment of the present invention.

FIG. 13 is a partial longitudinal sectional view of Embodiment 4 of the present invention.

FIG. 14 is a schematic diagram illustrating setting of the amount of separation between two wedges according to the fourth embodiment of the invention;

FIG. 15 is a longitudinal sectional view of a conventional single-cylinder rotary compressor.

FIG. 16 is a longitudinal sectional view of a conventional two-cylinder rotary compressor.

[Explanation of symbols]

4 shaft, 5 cylinder, 6 piston, 6a recess, 7 vane, 7a vane tip (one end), 7b vane back (other end), 7c, 17c inclined part, 9 upper bearing,
10 lower bearing, 16 piston, 16a recess, 17
Vane, 17a Vane tip (one end), 17b Vane back (other end), 19 partition plate, 21 lever, 22 lever support, 24 lever spring 31 wedge, 32 supporting member (wedge support), 33 elastic body, 41, 42
Wedge, 41c, 42c Inclined part.

Claims (14)

[Claims] 1. A cylinder, a piston rotating along the inner periphery of the cylinder, a vane reciprocating in a groove provided in the cylinder while being pressed by the piston, and closing an end face opening of the cylinder. In the rotary compressor having a bearing, the recess is provided on the outer periphery of the piston so that one end of the vane is engaged, and the amount of retreat of the vane with respect to the piston is set to be equal to or less than the depth of the recess. Features a rotary compressor. 2. Two cylinders, two pistons rotating along the inner circumference of each cylinder, and a groove provided in the two cylinders while contacting one end of each of the two pistons. A rotary type having two vanes reciprocating, a partition plate provided between the two cylinders for closing the opening of the cylinder, and two bearings for closing the other end opening of the two cylinders, respectively. In the compressor, a concave portion is provided on the outer periphery of the two pistons, one end of each of the vanes is engaged with the concave portion, the center is rotatably supported, and the other end of the two vanes is connected to the concave portion. A rotary pressure, wherein a lever having both ends to press each other is disposed, and a retreat amount of the vane with respect to the piston through the lever is set to be equal to or less than a depth of the concave portion. Contractor. And a member for rotatably supporting a central portion of the lever, wherein a depth of a concave portion provided on an outer peripheral portion of the piston slightly exceeds a required depth of the relief, and a central portion of the lever is provided. The member for rotatably supporting the member is capable of performing translational follow-up movement in the radial direction of the shaft, and the amount of translational retreat of the member is less than half of the depth of the concave portion provided on the outer periphery of the piston, and is near half. The rotary compressor according to claim 2, wherein: 4. A member for rotatably supporting the central portion of the lever, wherein the member for rotatably supporting the central portion of the lever is capable of performing translational movement only in the radial direction of the shaft, and in other directions. 3. The rotary compressor according to claim 2, wherein the degree of freedom of the rotary compressor is substantially restricted. 5. A member for rotatably supporting the central portion of the lever, wherein the member for rotatably supporting the central portion of the lever is pressed toward the shaft by an elastic material such as a spring. The rotary compressor according to claim 2, wherein 6. The rotary compressor according to claim 2, wherein the two surfaces at both ends of the lever which can contact the back surface of the vane are cylindrical surfaces. 7. The two cylindrical surfaces at both ends of the lever, which can contact the back surface of the vane, have the same radius of the two cylindrical surfaces, and the midpoint of the center of each cylindrical surface is the center of the lever. 7. The rotary compressor according to claim 6, wherein the rotary compressor coincides with the rotation support center. 8. Two cylinders, two pistons rotating along the inner circumference of each cylinder, and a groove provided in each of the two cylinders while contacting one end of each of the two pistons. A rotary type having two vanes reciprocating, a partition plate provided between the two cylinders for closing the opening of the cylinder, and two bearings for closing the other end opening of the two cylinders, respectively. In the compressor, a concave portion with which one end of the vane is engaged is provided on the outer periphery of the two pistons, and an inclined portion is provided at the other end of the two vanes in a direction facing each other, and is pressed against both inclined portions. A wedge having two inclined portions, and a retreat amount of the vane with respect to the piston through the wedge is set to be equal to or less than a depth of a concave portion on an outer periphery of the piston. Rotary compressor. 9. A member for supporting a wedge in a radial direction of the shaft, wherein a depth of a concave portion provided on an outer peripheral portion of the piston slightly exceeds a required depth of the relief, and the wedge is formed in a radial direction of the shaft. The wedge support is configured as a wedge support movable in the radial direction of the shaft, and the movable amount of the wedge support is less than half and near half of the depth of the piston outer peripheral recess. A rotary compressor according to claim 8. 10. A member for supporting a wedge in a radial direction of a shaft, wherein the member is capable of performing translational movement only in the radial direction of the shaft, and the degree of freedom in other directions is substantially restricted. The rotary compressor according to claim 9, wherein 11. The rotary compressor according to claim 9, wherein a member that supports the wedge in a radial direction of the shaft is pressed toward a center of the shaft by an elastic body such as a spring. 12. Two cylinders, two pistons rotating along the inner circumference of each cylinder, and one end of each of the two pistons being brought into contact with a groove provided in the two cylinders. A rotary type having two vanes reciprocating, a partition plate provided between the two cylinders for closing the opening of the cylinder, and two bearings for closing the other end opening of the two cylinders, respectively. In the compressor, a concave portion with one end of the vane is provided on the outer periphery of the two pistons, and an inclined portion having an inclination angle θv in a direction facing each other is provided on the other end of the two vanes. Two wedges each having one inclined portion that engages with the inclined portion are arranged, and the amount of axial separation between both wedges during normal operation is cotθv times the depth of the piston outer peripheral concave portion. Rotary compressor, characterized in that small. 13. The rotary compressor according to claim 12, wherein the two wedges are pressed in a direction away from each other by an elastic body such as a spring. 14. The rotary compressor according to claim 1, wherein a refrigerant which is a halogen derivative of a hydrocarbon and does not contain a chlorine element in a molecular structure is used.