JPH05202874A - Rotary compressor - Google Patents

Abstract

PURPOSE:To improve volumetric efficiency and indication efficiency by eliminating relative displacement between a blade and a roller to minimum friction loss and power, and reducing gas leakage from a compression chamber to a suction chamber to eliminate gas leakage from the back surface chamber of the blade to the suction chamber and the compression chamber CONSTITUTION:A blade for defining the cylinder chamber 41 of a cylinder 4 into a compression chamber X and a suction chamber Y is provided at a roller 7 so as to be protruded outward in the diametrical direction of the roller 7, and a supporting element 11 which is provided with a receiving groove 11a for receiving the protruding side top end part of the blade 8 at the cylinder 4, and the roller 7 relatively-rotated to the eccentric shaft part of the drive shaft where the roller 7 is engaged and lubricating oil is fed constantly to reduce friction loss and power force loss. Besides, the pressure of the blade 7 is eliminated, and the the leakage of the back pressure to the suction chamber Y and the compression chamber X is eliminated to improve volumetric efficiency and indication efficiency, thus reducing the leakage from the compression chamber X to the suction chamber Y.

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art Conventionally, a rotary compressor is described in, for example, Japanese Utility Model Laid-Open No. 61-114082. As shown in FIGS. 16 and 17, in this conventional compressor, a compression element A driven by a motor is arranged in a closed casing, and the compression element A has a cylinder C having a cylinder chamber B. And a roller E which is inserted into an eccentric shaft portion of a drive shaft D extending from the motor and revolves in the cylinder chamber B by the rotation of the drive shaft D, and an intake port F provided in the cylinder C.
And a discharge port G, and a blade H disposed so as to be movable back and forth at an intermediate position between the discharge port and the discharge port G. The blade H has a back surface side on which a part of the high-pressure gas discharged from the discharge port G is placed. The cylinder chamber B is partitioned into a compression chamber X and a suction chamber Y by causing the tip portion of the blade H to constantly contact the outer peripheral surface of the roller E by this back pressure. There is. Further, the discharge port G is provided with a plate-shaped valve body I that opens and closes the discharge port G by abutting a valve seat surface formed around the outlet port.

Then, while the roller E is revolved in the cylinder chamber B by the rotation of the drive shaft D, the gas is compressed in the compression chamber X in the cylinder chamber B defined by the blade H, and this compression stroke is performed. When the process is completed and the process moves to the discharge process, the compressed high-pressure gas is discharged from the discharge port G into the casing by the opening operation of the valve body I, and the discharge process is completed and the process proceeds to the intake process. At this time, the valve body I is closed to close the discharge port G, and the suction chamber Y defined by the blade H in the cylinder chamber B from the suction port F is closed.
The low-pressure gas is sucked in and the compression stroke and the discharge stroke are repeated.

[0004]

[Problems to be Solved by the Invention] However, as described above,
When the blade H is supported in the cylinder C so as to be movable back and forth and a back pressure is applied to bring the tip of the blade H into contact with the outer peripheral surface of the roller E, so that the blade H and the roller E are relatively moved. , Back pressure is applied to the blade H to press the tip of the blade H against the outer peripheral surface of the roller,
It is necessary to bring the blades H into contact with each other, and the contact of the blade H with the outer circumferential surface of the roller H is a metal contact without interposing oil.
There is a problem that friction loss due to sliding between the blade H and the outer peripheral surface of the roller is large and power loss is large. In addition, a back pressure of the high-pressure gas discharged from the discharge port G is applied to the back surface of the blade H to bring the tip end of the blade H into contact with the outer peripheral surface of the roller E. The high pressure gas in the back chamber is as shown by the arrow a in FIG.
There is a problem of leakage into the suction chamber Y via the side surface of the blade H and the blade sliding groove, resulting in a decrease in volumetric efficiency, and the compression chamber X fluctuates from low pressure to high pressure. When the internal pressure of the compression chamber X is lower than the back pressure,
There is also a problem that the high-pressure gas acting on the back chamber leaks into the compression chamber X via the side surface of the blade H and the blade sliding groove, which lowers the indicating efficiency. Further, the high pressure gas compressed in the compression chamber X may leak from the contact portion between the tip of the blade H and the roller E to the suction chamber Y as shown by an arrow b in FIG. Along with the leakage from the side surface of the blade H, there was a problem that the volumetric efficiency was further reduced.

The present invention has been made in view of the above problems, and an object thereof is to eliminate the relative movement of the blade with respect to the roller to reduce friction loss and power loss, and moreover, suction from the blade rear chamber or compression chamber. The point is to reduce gas leakage into the chamber and improve volumetric efficiency and indicator efficiency.

[0006]

In order to achieve the above object, the present invention, as clearly shown in FIG.
And a cylinder 4 having a
A compression element 3 having a roller 7 that revolves in the cylinder chamber 41 and a blade 8 that divides the cylinder chamber 41 into a compression chamber X and a suction chamber Y, and compresses a gas fluid sucked from a suction port 3a. In the rotary compressor configured to discharge from the discharge port 3b, the blade 8 is integrally provided on the roller 7 so as to project outward in the radial direction of the roller 7, and the cylinder 4 It is characterized in that a support 11 having a receiving groove 11a for receiving the tip end of the blade 8 on the protruding side is rotatably provided.

Further, as shown in FIG. 1, the roller 7
It is preferable to provide a projection 75, which projects toward the discharge port 3b and is capable of entering the discharge port 3b, at a portion facing the discharge port 3b on the outer peripheral portion of the above.

Further, as shown in FIG. 14 or FIG. 15, the height of the roller 7 is set low at the high temperature side wall portion 7a in contact with the compression chamber X side and high at the low temperature side wall portion 7b in contact with the suction chamber Y side. Is also preferable.

[0009]

In the above rotary compressor, the roller 7
And the roller 7 is fitted to the roller 7 and relatively rotated between the roller 7 and the eccentric shaft portion of the drive shaft to which the lubricating oil is supplied, thereby eliminating the relative movement between the blade and the roller as in the conventional example. Therefore, the friction loss and the power loss can be reduced as compared with the conventional example in which the blade and the roller are relatively moved. That is, the eccentric shaft portion of the drive shaft into which the roller 7 is fitted is constantly supplied with lubricating oil from the oil supply passage of the drive shaft and is in fluid contact with the eccentric shaft portion. The frictional resistance can be reduced, so that the friction loss can be reduced and the power loss can also be reduced as compared with the case where the back pressure is applied to the blade 8 to relatively move the blade and the roller. Moreover, since the blade 8 is provided on the roller 7 so that it is not necessary to apply back pressure to the blade 8, gas leakage from the back chamber of the blade to the suction chamber Y and the compression chamber X can be eliminated. Therefore, the volumetric efficiency and the indicating efficiency can be improved. Further, since the blade 8 is provided on the roller 7, the gas leakage from the compression chamber X to the suction chamber Y can be reduced, and the gas leakage from the back chamber does not occur. Together with this, the volumetric efficiency can be further enhanced.

Further, by providing a projection 75 projecting toward the discharge port 3b and capable of entering the discharge port 3b at a portion of the outer peripheral portion of the roller 7 facing the discharge port 3b, a compression stroke to a discharge stroke is formed. When transitioning to, the protrusion 75 provided on the roller 7 can be gradually rushed into the discharge port 3b from a position distant from the discharge port 3b, and at the time of this rush, the compressed gas in the discharge port 3b is compressed. Since it can be rushed to be pushed out to the outside, the top clearance can be reduced, and when the low pressure gas is sucked into the suction chamber Y after shifting to the suction stroke after the end of the discharge stroke, the discharge port 3b is discharged. It is possible to reduce the reverse flow rate of the high-pressure gas remaining inside to the suction chamber Y side. As a result, compression loss, overheating and pulsation of the suction gas in the suction chamber Y can be prevented, and at the start of the above discharge stroke, that is, at the beginning of the discharge stroke where the discharge amount increases, the protrusion 75 Since it does not rush into the discharge port 3b, a sufficient gas discharge passage can be secured, so that the gas discharge resistance can be reduced, overcompression of gas can be prevented, and power loss due to this overcompression can be eliminated. You can do it.

Further, by setting the height of the roller 7 low at the high temperature side wall portion 7a in contact with the compression chamber X side and high at the low temperature side wall portion 7b in contact with the suction chamber Y side, the roller 7 becomes non-rotating. At the time of operation, the disadvantage caused by the difference in the thermal expansion amount in the height direction of the roller 7 due to the temperature difference generated along the circumference of the roller 7 can be eliminated. That is, in the conventional blade reciprocating type shown in FIG. 16, the roller E can be rotated by being rotated by the rotation of the drive shaft D, so that the outer surfaces thereof become a low temperature suction chamber Y and a high temperature compression chamber X. The rollers E may come into contact with each other alternately and have a substantially uniform temperature along the circumference thereof, but when the roller 7 is a non-rotating type, the wall portion contacting the low temperature suction chamber Y and the high temperature compression chamber X is Since it is fixedly determined on the circumference, the wall temperature of the roller 7 changes as shown in FIG. 12 when the protrusion of the blade 8 is set as a base point of 0 degrees and an angle is formed in the clockwise direction as shown in FIG. , The peak of high temperature is around 270 degrees, and the peak of low temperature is 9
It will be near 0 degrees. Therefore, 270
The thermal expansion is large in the high temperature side wall portion 7a which is in contact with the compression chamber X side with a peak near 90 degrees, and is small in the low temperature side wall portion 7b which is in contact with the suction chamber Y side with a valley near 90 degrees and is small. The heights of the rollers 7 are different from each other by several tens of microns as shown by the imaginary line in FIG. On the other hand, since the cylinder 4 is placed in the casing filled with high-pressure discharge gas, its thermal expansion can be considered to be substantially uniform along the circumference of the cylinder chamber 41. Since the height is set in consideration of the maximum amount of thermal expansion, it eventually comes into contact with the suction chamber Y side, and a large gap is formed on the upper and lower end surfaces of the low temperature side wall portion 7b having a small amount of thermal expansion. As a result, leakage occurs, which causes a disadvantage that the intake gas is heated and volumetric efficiency is reduced. Therefore, as shown in FIG. 14 or FIG.
Of the high temperature side wall portion 7a in contact with the compression chamber X side,
By setting the low temperature side wall portion 7b in contact with the suction chamber Y side to be high, the difference in thermal expansion is positively utilized during operation, and the high temperature side wall portion 7b can be used as indicated by the imaginary line in each figure.
By making the heights of a and the low temperature side wall portion 7b uniform, the leakage due to the imbalance of the height of the roller 7 is eliminated.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The rotary compressor shown in FIG. 10 includes a hermetic casing 1 having a motor 2 disposed in the upper upper portion thereof, and a compression element 3 disposed at the lower portion of the motor 2 so that An extending drive shaft 21 is operatively connected to the compression element 3. The compression element 3 includes a cylinder 4 having a cylinder chamber 41 therein, a front head 5 and a rear head 6 facing the upper and lower open portions of the cylinder 4, and a roller revolvably installed in the cylinder chamber 41. 7 and
The lower portion of the drive shaft 21 is supported by bearings provided on the heads 5 and 6, and the roller 7 is rotatably inserted into the eccentric shaft portion 22 of the drive shaft 21 to form the drive shaft. With the rotation of 21, the roller 7 is rotated while slidingly contacting the eccentric shaft portion 22. Further, an oil supply passage 23 that opens to the bottom oil sump 1b of the casing 1 is provided on the center side of the drive shaft 21, a pump element 24 is attached to the inlet of the oil supply passage 23, and an intermediate outlet of the oil supply passage 23. The roller 7 and the eccentric shaft portion 2
The lubricating oil pumped up from the oil sump 1a by the pump element 24 is supplied to the sliding contact surface from the oil supply passage 23 by opening the sliding contact surface with the sliding contact surface.

Further, the compression element 3 has a suction port 3 for suction gas fluid which opens into a cylinder chamber 41 of the cylinder 4.
a and a discharge port 3b of the compressed gas fluid, which also opens in the cylinder chamber 41, are formed. For example, as is apparent from FIG. 1, a suction port 3a opening to the cylinder chamber 41 is formed in a side wall of the cylinder 4, and a cylinder chamber 41 is opened in a side wall of the cylinder 4 near the suction port 3a. The discharge ports 3b are respectively formed, and the suction ports 3 are formed.
A blade 8 which defines the inside of the cylinder chamber 41 into a compression chamber X and a suction chamber Y is provided at an intermediate portion between a and the discharge port 3b, and a valve formed around the outlet of the discharge port 3b. A plate-shaped valve body 9 that abuts the seat surface and opens and closes the discharge port 3b is provided. In FIG. 1, 10 is the valve body 9
In FIG. 10, 1a is an external discharge pipe connected to the upper side of the casing 1.

In the above rotary compressor, however, the blade 8 is provided on a part of the outer periphery of the roller 7 so as to project outward in the radial direction of the roller 7, as shown in FIG. At the same time, a circular holding hole 42 having a cylindrical shape, a spherical shape, or the like is provided in an intermediate inner portion of the cylinder 4 between the suction port 3a and the discharge port 3b.
And a receiving groove 1 whose one end is opened to the cylinder chamber 41 side.
The support 11 having 1a is rotatably held, and the tip end of the blade 8 on the protruding side is slidably inserted into the receiving groove 11a of the support 11.

The blade 8 is provided on a part of the outer periphery of the roller 7.
When the blade 8 is provided, for example, as shown in FIG. 1, a mounting groove 71 into which a part of the base end of the blade 8 can be inserted is formed on the roller 7 side, and the base of the blade 8 is formed in the mounting groove 71. The end portions are inserted and bonded together with an adhesive, or they are integrated by brazing. Alternatively, as shown in FIGS. 2 and 3, on the outer circumference in the radial direction of the roller 7, a deep groove 72a is formed at the central portion in the axial direction and shallow grooves 72 are formed at both ends.
The stepped groove 72 of b and the fitting hole 73 penetrating axially outward from both end surfaces of the deep groove portion of the stepped groove 72 are provided, and the base end of the blade 8 is provided with the stepped groove 72 of the stepped groove 72. A fitting portion 81 having a fitting protrusion 81a for fitting in the deep groove portion is provided, a fitting hole 82 is provided in the fitting protrusion 81a, and the fitting portion 81 of the blade 8 is fitted in the stepped groove 72. At the same time, the blade 8 is fixed to the roller 7 by inserting one pin 83 into each of the fitting holes 73 and 82.
In this case, it is preferable that an adhesive agent is auxiliary attached to the fitting portion of the fitting portion 81 into the stepped groove 72. Also, FIG.
As shown in FIG. 7, a protrusion 74 is provided on a part of the outer periphery of the roller 7, and a groove 84 that can enter the protrusion 74 is provided on the side of the blade 8 so that the protrusion 74 is intervened in the groove 84. Pin 85 on the protrusion 74 and the blade 8 while
It is also possible to fix the blade 8 to the roller 7 by penetrating it and filling an adhesive between the opposing surfaces of the blade 8 and the roller 7.

The blade 8 provided on the roller 7 is driven into and out of the receiving groove 11a of the support 11 by the drive of the drive shaft 21, and the support 11 is rotated. Accordingly, the inside of the cylinder chamber 41 is moved inside the compression chamber X by moving back and forth in the radial direction while swinging.
And a suction chamber Y. With the above configuration, the roller 7 is rotated relative to the eccentric shaft portion 22, and the tip portion of the blade 8 comes into contact with the outer peripheral surface of the roller 7 as in the conventional case, so that the blade 8 and the roller 7 Since and do not move relative to each other, wear due to friction between the blade 8 and the roller 7 and power loss due to the friction can be eliminated. That is, the blade 8 and the roller 7 do not move relative to each other, but the roller 7 and the eccentric shaft portion 2 do not move.
2 will rotate relative to each other, but the eccentric shaft portion 22 of the drive shaft 21 into which the roller 7 is fitted has the drive shaft 2
Since the lubricating oil is constantly supplied from the first oil supply passage 23 and is in fluid contact, the frictional resistance can be reduced,
The friction loss can be reduced and the power loss can be reduced as compared with the case where the back pressure is applied to the blade 8 and the blade 8 is brought into contact with the roller 7 and moved relatively.

Further, since the blade 8 is provided on the roller 7, it is not necessary to apply back pressure as in the conventional case. Therefore, unlike the conventional example, the back chamber of the blade is used to the suction chamber Y and the compression chamber. Gas leakage to the chamber X is eliminated, and volumetric efficiency and indicating efficiency can be increased. Further, gas leakage from the compression chamber X to the suction chamber Y is reduced, and the volumetric efficiency can be further increased. That is, the gas fluid in the compression chamber X may leak to the suction chamber Y side from between both side wall surfaces of the blade 8 and the receiving groove 11a of the support body 11 into which the blade 8 is inserted. Since the gas in the compression chamber X fluctuates from low pressure to high pressure, when the pressure difference between the gas fluid pressure in the compression chamber X and the gas fluid pressure in the suction chamber Y becomes a predetermined pressure or more. Only the gas leakage is caused, and the gas leakage does not occur other than that, so that the gas leakage amount from the compression chamber X to the suction chamber Y can be significantly reduced as compared with the conventional one.

Further, a substantially cylindrical projection 75 having a smaller diameter than the discharge port 3b is provided at a portion of the outer peripheral portion of the roller 7 facing the discharge port 3b, and a discharge process in which the discharge amount is increased. At the time of start, the projection 75 is in a position where it does not enter the ejection port 3b, and the projection 75 gradually enters the ejection port 3b as the ejection process progresses and the ejection amount decreases. The compressed gas in the discharge port 3b is pushed out by the rush.

Next, the operation of the rotary compressor having the above structure will be described. First, as shown in FIG.
When attempting to start the suction and compression strokes when the revolution angle of the roller 7 is 0 degree, the blade 8 is in a state of being inserted into the inside of the receiving groove 11a in the support body 11, and At times, the projection 75 provided on the roller 7 is in a state of being projected into the discharge port 3b. Then, when the roller 7 revolves 90 degrees from the above state, as shown in FIG. 6, the protrusion 75 is separated from the discharge port 3b, and the blade 8 rotates the support body 11. While swinging, the receiving groove 11a
Is slid to the outer side, the gas fluid is compressed in the compression chamber X in the cylinder chamber 41 defined by the blade 8 as the roller 7 revolves, and the suction chamber Y is also compressed. On the side, the gas fluid is sucked from the suction port 3a.

Further, as shown in FIG. 7, the roller 7
When the revolution angle of 180 degrees becomes 180 degrees, the compression chamber X
The compression of the gas fluid in the suction chamber Y and the suction of the gas fluid in the suction chamber Y are continued, and at this time, the blade 8 is moved by the support 1
The maximum amount is pulled out from the first receiving groove 11a.
Further, as shown in FIG. 8, when the revolution angle of the roller 7 reaches 270 degrees and the discharge stroke is reached, the blade 8 provided on the roller 7 gradually inwardly moves along with the revolution of the roller 7. While sliding to the side, the gas fluid compressed in the compression chamber X is discharged from the discharge port 3b to the outside, and at this time, the protrusion 75 starts to rush into the discharge port 3b. Then, as shown in FIG. 9, when the roller 7 revolves from 315 degrees to 360 degrees (FIG. 1), the discharge of the gas fluid compressed in the compression chamber X from the discharge port 3b ends. At this time, the protrusion 75
Is rushed into the discharge port 3b, the top clearance of the discharge port 3b is made small, and the amount of residual gas in the discharge port 3b can be reduced, and this residual gas flows back to the suction chamber of FIG. Reduction in volumetric efficiency can be reduced.

As described above, when shifting to the discharge stroke, the protrusion 75 provided on the roller 7 is located at a position apart from the discharge port 3b and corresponds to the swing angle of the roller 7 as described above. The projection 75 gradually enters the discharge port 3b, and at the time of this projection, the compressed gas in the discharge port 3b protrudes to the outside. Therefore, when the top clearance can be reduced, and when the low pressure gas is sucked into the suction chamber Y after the discharge stroke is completed and the low pressure gas is sucked into the suction chamber Y, the high pressure gas remaining in the discharge port 3b is located on the suction chamber Y side. It is possible to reduce the reverse flow rate to the. As a result, compression loss, overheating and pulsation of the suction gas in the suction chamber Y can be prevented, and at the start of the above discharge stroke, that is, at the beginning of the discharge stroke where the discharge amount increases, the protrusion 75
Since it does not rush into the discharge port 3b, a sufficient gas discharge passage can be secured, so that the gas discharge resistance can be reduced, overcompression of gas can be prevented, and power loss due to this overcompression can be eliminated. You can do it.

By the way, as shown in FIG. 14, the height of the roller 7 reaches the maximum temperature at the angle formed by the upper and lower end surfaces of the roller 7 in the clockwise direction with the blade protrusion as the base point.
By forming the inclined surfaces 701 and 702 having the lowest temperature near 0 degrees and the highest temperature near 90 degrees, which is the lowest temperature, the low temperature side wall 7a that is in contact with the compression chamber X side is low, and the low temperature side wall is in contact with the suction chamber Y side. It is preferable to set it high in the portion 7b. In this case, during operation, the high temperature side wall portion 7a is originally low in height.
However, the thermal expansion is larger than that of the low temperature side wall portion 7b which is originally high, and as shown by the imaginary line in the figure, the high temperature side wall portion 7a and the low temperature side wall portion 7b have a uniform height, and the roller 7 Along the circumference, the gaps between the upper and lower end face portions of the roller 7 can be kept evenly small, leakage through the upper and lower end face portions of the roller 7 can be reduced, and heating of the suction gas can be further reduced. Therefore, the volumetric efficiency can be further improved.
The roller 7 is made of molybdenum-nickel-chromium alloy or the like, and the height difference between the high temperature side wall portion 7a and the low temperature side wall portion 7b is set to about several tens of microns.

Further, as shown in FIG. 15, the roller 7 is in contact with the compression chamber X side and the height of the high temperature side wall portion 7a consisting of a semi-cylindrical portion having an angle of 180 to 360 degrees is uniformly low. The low temperature side wall portion 7b which is in contact with the Y side and is formed of a semicircle or the like having an angle of 0 to 180 degrees may be uniformly raised, and the upper and lower end surfaces thereof may be shaped to have steps 703 and 704. In this case, , There is some unevenness on the end surface at the step, but
Processing can be simplified compared to the one shown in FIG. 14, and the end faces of the high temperature side wall surface 7a and the low temperature side wall surface 7b during operation can be substantially aligned compared to those formed with a single height cylinder. Therefore, it is possible to reduce the leakage through the end face portion.

[0024]

As described above, in the rotary compressor of the present invention, the cylinder chamber 41 of the cylinder 4 is replaced by the compression chamber X.
And a suction chamber Y defining a blade 8 integrally provided on the roller 7 so as to project outward in the radial direction of the roller 7, and a receiving portion for receiving the protruding end portion of the blade 8 in the cylinder 4. A support 11 having a groove 11a is rotatably provided so that the roller 7 and the eccentric shaft portion of the drive shaft to which the roller 7 is fitted and which is supplied with lubricating oil are relatively rotated. Since the relative movement of the blade and the roller is eliminated as in the conventional example, the friction loss and the power loss can be reduced as compared with the conventional example in which the blade and the roller are relatively moved. That is, the roller 7
The eccentric shaft part of the drive shaft that is fitted with is constantly in contact with the lubricating oil from the oil supply passage of the drive shaft and is in fluid contact. The friction loss can be reduced and the power loss can also be reduced as compared with the case where the back pressure is applied to the blade 8 to relatively move the blade and the roller. Moreover, since the blade 8 is provided on the roller 7 so that it is not necessary to apply back pressure to the blade 8, gas leakage from the back chamber of the blade to the suction chamber Y and the compression chamber X can be eliminated. Volume efficiency and indicating efficiency can be improved.
Since the gas leakage from the compression chamber X to the suction chamber Y can be prevented, the volume efficiency can be further improved in combination with the absence of gas leakage from the back chamber.

Further, by providing a projection 75 projecting toward the discharge port 3b and capable of entering the discharge port 3b at a portion of the outer peripheral portion of the roller 7 facing the discharge port 3b, the compression stroke to the discharge stroke can be performed. When transitioning to, the protrusion 75 provided on the roller 7 can be gradually rushed into the discharge port 3b from a position distant from the discharge port 3b, and at the time of this rush, compression in the discharge port 3b is performed. Since the gas can be rushed to be pushed out to the outside, the top clearance can be reduced, and when the low pressure gas is sucked into the suction chamber Y by shifting to the suction stroke after the end of the discharge stroke,
The reverse flow rate of the high-pressure gas remaining in the discharge port 3b to the suction chamber Y side can be reduced. As a result, compression loss, overheating and pulsation of the suction gas in the suction chamber Y can be prevented, and at the start of the above discharge stroke, that is, at the beginning of the discharge stroke where the discharge amount increases, the protrusion 75 Does not penetrate into the discharge port 3b, so that a sufficient gas discharge passage can be secured, so that the gas discharge resistance can be reduced,
It is possible to prevent overcompression of the gas and eliminate power loss due to this overcompression.

Further, by setting the height of the roller 7 low at the high temperature side wall portion 7a in contact with the compression chamber X side and high at the low temperature side wall portion 7b in contact with the suction chamber Y side, the roller 7 is in operation.
The difference in thermal expansion caused by the temperature difference along the circumference of the roller can be positively utilized, and the heights of the high temperature side wall portion 7a and the low temperature side wall portion 7b can be made uniform, so that the roller height imbalance is unbalanced. Therefore, it is possible to reduce the leakage caused by the above, further reduce the heating of the suction gas, and further improve the volumetric efficiency.

[Brief description of drawings]

FIG. 1 is a plan sectional view showing a main part of a cylinder provided in a rotary compressor of the present invention.

FIG. 2 is a sectional view showing an example of a blade mounting structure.

FIG. 3 is a central vertical sectional view of FIG.

FIG. 4 is a cross-sectional view showing another example of the mounting structure of the blade.

FIG. 5 is a plan sectional view showing a case where the revolution angle of the roller is 0 degree.

FIG. 6 is a plan sectional view showing a case where the revolving angle of the roller is 90 degrees.

FIG. 7 is a plan sectional view showing a case where the revolution angle of the roller is 180 degrees.

FIG. 8 is a plan sectional view showing a case where the revolution angle of the roller is 270 degrees.

FIG. 9 is a plan sectional view showing a case where the revolution angle of the roller is 315 degrees.

FIG. 10 is a vertical sectional view showing the overall structure of a rotary compressor.

FIG. 11 is a plan sectional view showing a main part of a cylinder for explaining another embodiment.

FIG. 12 is a diagram showing a wall temperature with respect to a roller angle for explaining the other embodiment.

FIG. 13 is a vertical sectional view showing a main part of a cylinder for explaining the other embodiment.

FIG. 14 is a cross-sectional view showing an example of a specific shape of a roller in the other embodiment.

FIG. 15 is a sectional view showing a modification of the specific shape of the roller.

FIG. 16 is a plan sectional view showing a compression element of a conventional rotary compressor.

FIG. 17 is a partial cross-sectional view of the conventional rotary compressor.

[Explanation of symbols]

 3 Compression Element 3a Suction Port 3b Discharge Port 4 Cylinder 41 Cylinder Chamber 7 Roller 7a High Temperature Sidewall 7b Low Temperature Sidewall 75 Protrusion 8 Blade 11 Support 11a Receiving Groove

Claims (3)

[Claims] 1. A cylinder 4 having a cylinder chamber 41, a roller 7 which is installed in the cylinder chamber 41 and revolves in the cylinder chamber 41, and the cylinder chamber 41 is divided into a compression chamber X and a suction chamber Y. Compression element 3 with blade 8
In the rotary compressor which has the gas fluid sucked from the suction port 3a and is discharged from the discharge port 3b, the blade 8 is projected to the roller 7 in the radial direction of the roller 7. The rotary compressor is characterized in that it is integrally provided on the cylinder 4, and that the cylinder 4 is rotatably provided with a support 11 having a receiving groove 11a for receiving the tip end of the protruding side of the blade 8. 2. The discharge port 3 is formed by projecting toward the discharge port 3b at a portion of the roller 7 facing the discharge port 3b.
The rotary compressor according to claim 1, further comprising a protrusion 75 that can be inserted into b. 3. The height of the roller 7 is low at the high temperature side wall portion 7a in contact with the compression chamber X side and low at the low temperature side wall portion 7 in contact with the suction chamber Y side.
The rotary compressor according to claim 1 or 2, wherein the value is set high in b.