JP3178559B2 - Rotary compressor - Google Patents

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 a refrigeration system.

[0002]

2. Description of the Related Art Conventionally, a rotary compressor has been described in, for example, Japanese Utility Model Laid-Open Publication No. 61-11408. In this conventional compressor, as shown in FIGS. 16 and 17, a compression element A driven by a motor is disposed in a closed casing, and the compression element A is a cylinder C having a cylinder chamber B. A roller E inserted in an eccentric shaft portion of a drive shaft D extending from the motor and revolving in the cylinder chamber B by rotation of the drive shaft D; and a suction port F provided in the cylinder C.
And a blade H disposed at an intermediate position between the discharge port G and the discharge port G. The blade H has a back side on which a part of the high-pressure gas discharged from the discharge port G is placed. The cylinder chamber B is divided into a compression chamber X and a suction chamber Y by allowing the tip of the blade H to always contact a part of the outer peripheral surface of the roller E by the back pressure. I have. Further, the discharge port G is provided with a plate-shaped valve element I which opens and closes the discharge port G by abutting against a valve seat surface formed around the outlet.

The gas is compressed in a compression chamber X in the cylinder chamber B defined by the blades H while the roller E revolves in the cylinder chamber B by the rotation of the drive shaft D. Is completed and the process shifts to the discharge stroke, the compressed high-pressure gas is discharged from the discharge port G into the casing by the opening operation of the valve element I, and the discharge stroke ends and shifts to the suction stroke. 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.
Then, the compression stroke and the discharge stroke are repeated.

[0004]

However, as mentioned above,
When the blade H is supported on the cylinder C so as to be able to move forward and backward, 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. , By applying a back pressure to the blade H to press the tip of the blade H against the outer peripheral surface of the roller,
It is necessary to make contact with the outer peripheral surface of the roller of the blade H. Since the oil is not interposed between the blade H and the metal, the blade H comes into metallic contact.
Friction loss due to sliding between the blade H and the outer peripheral surface of the roller is large, and power loss is also 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 so that the tip end of the blade H is in contact with the outer peripheral surface of the roller E. As shown by the arrow a in FIG.
Leakage into the suction chamber Y through the gap between the side surface of the blade H and the blade sliding groove causes a problem that the volumetric efficiency is reduced, and the compression chamber X varies from a low pressure to a high pressure. When the internal pressure of the compression chamber X is lower than the back pressure,
The high-pressure gas acting on the rear chamber leaks into the compression chamber X through the space between the side surface of the blade H and the blade sliding groove, and there is also a problem that the indicating efficiency is reduced. Further, as shown by an arrow b in FIG. 16, the high-pressure gas compressed in the compression chamber X may leak into the suction chamber Y from the contact portion between the tip end of the blade H and the roller E, as described with reference to FIG. There is a problem that the volumetric efficiency is further reduced in combination with the leakage from the side surface of the blade H.

The present invention has been made in view of the above problems, and an object of the present invention is to eliminate the relative movement of the blade with the rollers, thereby reducing the friction loss and the power loss, and furthermore, the suction from the rear chamber or the compression chamber of the blade. Another object of the present invention is to improve the volumetric efficiency and the indicating efficiency by reducing gas leakage into the chamber.

[0006]

As shown in FIG. 1, a rotary compressor according to one aspect of the present invention comprises a cylinder 4 having a cylinder chamber 41, and a front head provided opposite an open portion of the cylinder 4. 5, a compression element 3 having a rear head 6, a roller 7 revolving inside the cylinder chamber 41 and revolving in the cylinder chamber 41, and a blade 8 dividing the cylinder chamber 41 into a compression chamber X and a suction chamber Y, In the rotary compressor configured to compress the gas fluid sucked from the suction port 3a and discharge it from the discharge port 3b, the blade 8
Is provided integrally with the roller 7 so as to protrude outward in the radial direction of the roller 7, and the cylinder 4 has a receiving groove 11 a for receiving the tip of the protruding side of the blade 8.
1 is rotatably provided, and a roller 7 is fitted into an eccentric shaft portion 22 of a drive shaft 21 which is supported by bearings provided in bearings provided in each of the heads 5 and 6, and a sliding contact between the roller 7 and the eccentric shaft portion 22 is performed. An oil supply passage 23 for supplying lubricating oil from both sides to the heads 5 and 6 is opened to the eccentric shaft portion 22.

As shown in FIG. 1, a rotary compressor according to another aspect of the present invention includes a cylinder 4 having a cylinder chamber 41, a roller 7 provided in the cylinder chamber 41 and revolving in the cylinder chamber 41, and a cylinder 7. Compression element 3 having blades 8 that partition chamber 41 into compression chamber X and suction chamber Y
In the rotary compressor, which compresses the gas fluid sucked from the suction port 3a and discharges the gas fluid from the discharge port 3b, the blade 8 is integrated with the roller 7 so as to protrude radially outward of the roller 7. And cylinder 4
Receiving groove 11a for receiving the tip of the protruding side of the blade 8
A support 75 is provided rotatably, and has a projection 75 protruding toward the discharge port 3b at a position facing the discharge port 3b on the outer peripheral portion of the roller 7 so as to be able to enter the discharge port 3b.
Is provided.

As shown in FIGS. 1, 14 and 15, a rotary compressor according to still another aspect of the present invention is provided with a cylinder 4 having a cylinder chamber 41, and is provided inside the cylinder chamber 41 and revolves in the cylinder chamber 41. And a compression element 3 having a blade 8 for partitioning a cylinder chamber 41 into a compression chamber X and a suction chamber Y, so that the gas fluid sucked from the suction port 3a is compressed and discharged from the discharge port 3b. In the rotary compressor shown in FIG.
A support 11 having a receiving groove 11a for receiving the tip of the protruding side of the blade 8 is rotatably provided in the cylinder 4 while being integrally provided so as to protrude radially outward of the roller 7. 7 is low at the high temperature side wall portion 7a contacting the compression chamber X side, and is low at the low temperature side wall portion 7b contacting the suction chamber Y side.
Is set high.

[0009]

In the rotary compressor according to one aspect of the present invention, the blade is rotated by relative rotation between a roller and an eccentric shaft portion of a drive shaft to which the roller is fitted and to which lubricating oil is supplied. The friction loss and the power loss can be reduced as compared with the case where the and the rollers relatively move. That is, the roller is in fluid contact with the eccentric shaft portion because the lubricating oil is constantly supplied from the oil supply passage of the drive shaft to the eccentric shaft portion of the drive shaft to which the roller is fitted. Further, since the lubricating oil flows from the sliding contact surface between the roller and the eccentric shaft toward the front head or the rear head, the roller is also in fluid contact with each head. As a result, the sliding characteristics of the roller are improved, the friction loss in the relative rotation of the roller and the eccentric shaft and the frictional resistance between the roller and each head are reduced, and a back pressure is applied to the blade to separate the blade and the roller. Friction loss and power loss can be reduced as compared with the case of relative movement. Further, since the blade is provided on the roller so that the back pressure does not act on the blade, gas leakage from the rear chamber of the blade to the suction chamber and the compression chamber can be eliminated, and the volume efficiency and the pointing efficiency can be improved. be able to. Further, by providing the blade 8 on the roller, gas leakage from the compression chamber to the suction chamber can be reduced, and the volume efficiency can be further improved in combination with no gas leakage from the rear chamber.

In the rotary compressor according to another aspect of the present invention, the roller 7 is relatively rotated between the roller 7 and the eccentric shaft portion of the drive shaft to which the roller 7 is fitted and to which lubricating oil is supplied. Since the relative movement between the blade and the roller is eliminated as in the example, the friction loss and the power loss can be reduced as compared with the conventional example in which the blade and the roller relatively move. That is, the lubricating oil is constantly supplied from the oil supply passage of the drive shaft to the eccentric shaft portion of the drive shaft to which the roller 7 is fitted, and is in fluid contact with the eccentric shaft portion. Since the frictional resistance can be reduced, the friction loss and the power loss can be reduced as compared with the case where the back pressure is applied to the blade 8 to move the blade and the roller relatively. In addition, 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 rear chamber of the blade to the suction chamber Y and the compression chamber X can be eliminated. , Volume efficiency and pointing efficiency, and the blade 8
, The gas leakage from the compression chamber X to the suction chamber Y can be reduced, and the volume efficiency can be further increased in combination with no gas leakage from the rear chamber. Further, a discharge port 3 is provided at a portion of the outer peripheral portion of the roller facing the discharge port 3b.
b, the projection 75 provided on the roller 7 is located at a position away from the discharge port 3b when a transition is made from the compression stroke to the discharge stroke by providing a projection 75 that can enter the discharge port 3b. From the discharge port 3b, and at this time, the compressed gas in the discharge port 3b can be pushed out so as to be pushed out, so that the top clearance can be reduced and the discharge stroke ends. When the low-pressure gas is sucked into the suction chamber Y by shifting to the suction stroke later, 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 and 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 when the discharge amount increases, the protrusion 75 3b
, The gas discharge passage can be sufficiently secured, so that the gas discharge resistance can be reduced, the gas can be prevented from being over-compressed, and the power loss due to the over-compression can be reduced.

[0011] In a rotary compressor according to still another aspect of the present invention, the roller 7 is fitted with the roller 7, and
Since the relative rotation between the eccentric shaft portion of the drive shaft to which the lubricating oil is supplied and the relative movement between the blade and the roller is eliminated as in the conventional example, the blade and the roller are moved relative to each other. The friction loss and the power loss can be reduced as compared with the conventional example. That is, the lubricating oil is constantly supplied from the oil supply passage of the drive shaft to the eccentric shaft portion of the drive shaft to which the roller 7 is fitted, and is in fluid contact with the eccentric shaft portion. Since the frictional resistance can be reduced, the friction loss and the power loss can be reduced as compared with the case where the back pressure is applied to the blade 8 to move the blade and the roller relatively. In addition, since the blade 8 is provided on the roller 7 so that it is not necessary to apply a back pressure to the blade 8, the suction chamber Y and the compression chamber X are arranged from the rear chamber of the blade.
Gas leakage from the compression chamber X to the suction chamber Y can be reduced because the blades 8 are provided on the rollers 7. The volume efficiency can be further improved in combination with no gas leakage from the rear chamber. Also, by setting the height of the roller 7 low at the high-temperature side wall 7a contacting the compression chamber X side and high at the low-temperature side wall part 7b contacting the suction chamber Y side, the roller 7 becomes a non-rotating type. The disadvantage caused by the difference in the amount of thermal expansion in the height direction of the roller 7 due to the temperature difference generated along the circumference of the roller 7 can also be eliminated. That is, FIG.
In the conventional blade reciprocating type shown in FIG.
Can rotate by being dragged by the rotation of the drive shaft D, so that the outer surface thereof alternately contacts the low-temperature suction chamber Y and the high-temperature compression chamber X, and the roller E is substantially uniformly heated along its circumference. However, when the roller 7 is a non-rotating type, the low temperature suction chamber Y
And the wall portion in contact with the high temperature compression chamber X is fixedly determined on the circumference. Therefore, as shown in FIG. The wall temperature of 7 changes as shown in FIG. 12, and a high-temperature peak is formed around 270 degrees and a low-temperature peak is formed near 90 degrees. For this reason, thermal expansion is large in the high temperature side wall portion 7a contacting the compression chamber X side with a peak near 270 degrees, and small in the low temperature side wall portion 7b contacting the suction chamber Y side with a valley near 90 degrees. Due to the difference in expansion, the height of the roller 7 will be different on the order of several tens of microns as extremely shown by the imaginary line in FIG. On the other hand, since the cylinder 4 is placed in a casing filled with a high-pressure discharge gas, its thermal expansion can be regarded as substantially uniform along the circumference of the cylinder chamber 41,
In addition, since the height of the cylinder 4 is set in consideration of the maximum thermal expansion amount, a large gap is formed at the upper and lower end surfaces of the low-temperature side wall portion 7b which is in contact with the suction chamber Y and has a small thermal expansion amount. Leakage indicated by an arrow e in FIG. 13 occurs, which disadvantageously reduces the volumetric efficiency by heating the suction gas. Therefore, 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 contacting the compression chamber X side and high at the low-temperature side wall portion 7b contacting the suction chamber Y side. Occasionally, the difference between the thermal expansions is positively utilized, and as shown by the imaginary lines in the figures, the heights of the high-temperature side wall 7a and the low-temperature side wall 7b are made uniform, and the height of the roller 7 is adjusted. Leakage due to balance can be eliminated.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the rotary compressor shown in FIG. 10, a motor 2 is provided in an upper part inside a closed casing 1 and a compression element 3 is provided in a lower part of the motor 2 so that the motor 2 The extending drive shaft 21 is linked 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 opposed to the upper and lower open portions of the cylinder 4, and a roller revolving inside the cylinder chamber 41. 7 and
The lower portion of the drive shaft 21 is supported by bearings provided in the heads 5 and 6, and the roller 7 is rotatably inserted into the eccentric shaft portion 22 of the drive shaft 21, thereby forming the drive shaft 21. With the rotation of 21, the roller 7 is rotated while sliding on the eccentric shaft 22. An oil supply passage 23 is provided at the center of the drive shaft 21 so as to open to the bottom oil reservoir 1b of the casing 1. A pump element 24 is attached to an inlet of the oil supply passage 23, and an intermediate outlet of the oil supply passage 23 is provided. And the roller 7 and the eccentric shaft 2
The lubricating oil pumped from the oil reservoir 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 surface 2.

The compression element 3 has a suction port 3 for a suction gas fluid that opens into a cylinder chamber 41 of the cylinder 4.
a and a discharge port 3b for the compressed gas fluid which is also open to the cylinder chamber 41. For example, as apparent from FIG. 1, a suction port 3a opening to the cylinder chamber 41 is formed on a side wall of the cylinder 4, and a cylinder chamber 41 is formed on a side wall of the cylinder 4 near the suction port 3a. The discharge ports 3b are formed respectively, and these suction ports 3b are formed.
A blade 8 that 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 the discharge port 3a and the discharge port 3b. A plate-shaped valve element 9 for opening and closing the discharge port 3b in contact with the seat surface is provided. In FIG. 1, reference numeral 10 denotes the valve 9
In FIG. 10, reference numeral 1a denotes an external discharge pipe connected to the upper side of the casing 1.

In the rotary compressor described above, the blade 8 is provided on a part of the outer periphery of the roller 7 so as to protrude outward in the radial direction of the roller 7 as clarified in FIG. In addition, a circular holding hole 42 such as a cylinder or a sphere is provided in the cylinder 4 at an intermediate portion between the suction port 3a and the discharge port 3b.
And a receiving groove 1 having one end opened to the cylinder chamber 41 side.
The support 11 having the support 1a is rotatably held, and the protruding end of the blade 8 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.
For example, as shown in FIG. 1, as shown in FIG. 1, a mounting groove 71 is formed on the roller 7 side so as to allow a part of the base end of the blade 8 to be inserted therein. One end is inserted and integrated with an adhesive or integrated by brazing. Alternatively, as shown in FIGS. 2 and 3, a radially outer periphery of the roller 7 has a deep groove 72a at the axial center and a shallow groove 72 at both ends.
b, and a fitting hole 73 penetrating axially outward from both end surfaces of the deep groove portion of the stepped groove 72, and the base end of the blade 8 is provided with the stepped groove 72. A fitting portion 81 having a fitting protrusion 81a fitted 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 is additionally attached to the fitting portion of the fitting portion 81 to the stepped groove 72. Also, FIG.
As shown in the figure, a projection 74 is provided on a part of the outer periphery of the roller 7, and a groove 84 that can enter the projection 74 is provided on the blade 8 side, and the projection 74 is interposed in the groove 84. In this state, a pin 85 is
And the blade 8 may be fixed to the roller 7 by loading an adhesive between the opposing surfaces of the blade 8 and the roller 7.

When the drive shaft 21 is driven, the blade 8 provided on the roller 7 has its protruding tip end moved into and out of the receiving groove 11a of the support 11, and the support 11 rotates. By moving the cylinder chamber 41 radially while swinging, the inside of the cylinder chamber 41 is compressed by the compression chamber X.
And the suction chamber Y. With the above configuration, the roller 7 is relatively rotated with respect to the eccentric shaft 22, and the tip of the blade 8 contacts the outer peripheral surface of the roller 7 as in the related art, and the blade 8 and the roller 7 are rotated. Since the blades 8 and the roller 7 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, instead of the blade 8 and the roller 7 not moving relatively, the roller 7 and the eccentric shaft 2
2 are rotated relative to each other, but the eccentric shaft portion 22 of the drive shaft 21 in which the roller 7 is fitted is provided with the drive shaft 2.
Since the lubricating oil is always supplied from the first oil supply passage 23 and is in fluid contact, the frictional resistance can be reduced.
The friction loss and the power loss can be reduced as compared with a case where a back pressure is applied to the blade 8 and the blade 8 is brought into contact with the roller 7 and relatively moved.

Further, since the blade 8 is provided on the roller 7, it is not necessary to apply a back pressure as in the prior art. Therefore, unlike the conventional example, the blade 8 is moved from the rear chamber of the blade to the suction chamber Y or the compression chamber. Gas leakage into the chamber X is eliminated, and volumetric efficiency and pointing 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 the side walls 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 a low pressure to a 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. Since only gas leakage occurs and no other gas leakage occurs, the amount of gas leakage from the compression chamber X to the suction chamber Y can be significantly reduced as compared with the conventional case.

A substantially cylindrical projection 75 having a diameter smaller than that of the discharge port 3b is provided in a portion of the outer periphery of the roller 7 facing the discharge port 3b, so that the discharge stroke increases the discharge amount. At the start, the projection 75 is at a position where it does not enter the discharge port 3b, and the projection 75 gradually enters the discharge port 3b as the discharge stroke progresses and the discharge amount decreases. The intrusion pushes the compressed gas in the discharge port 3b to the outside.

Next, the operation of the rotary compressor having the above configuration will be described. First, as shown in FIG.
When the suction and compression strokes are to be started when the revolving angle of the roller 7 is 0 degrees, the blade 8 is in a state of being inserted into the inside of the receiving groove 11a in the support body 11, and Sometimes, the projection 75 provided on the roller 7 is in a state of being protruded into the discharge port 3b. Then, when the roller 7 revolves 90 degrees from the above state, the protrusion 75 is separated from the discharge port 3b, and the blade 8 rotates the support 11 as shown in FIG. Swinging while receiving, the receiving groove 11a
, The gas fluid is compressed in the compression chamber X in the cylinder chamber 41 defined by the blade 8 with the revolution of the roller 7, and the suction chamber Y On the side, the gas fluid is sucked from the suction port 3a.

Further, as shown in FIG.
When the revolution angle of the compression chamber X 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.
It is in a state where it has been pulled out from the receiving groove 11a by the maximum amount.
Further, as shown in FIG. 8, when the revolving angle of the roller 7 reaches 270 degrees and the discharge stroke is reached, the blade 8 provided on the roller 7 gradually moves inward as the roller 7 revolves. While sliding to the side, the gas fluid compressed in the compression chamber X is externally discharged from the discharge port 3b, and at this time, the projection 75 starts to enter 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 protruded into the discharge port 3b, the top clearance of the discharge port 3b is reduced, and the amount of residual gas in the discharge port 3b can be reduced. This residual gas flows back to the suction chamber in FIG. A decrease in volumetric efficiency can be reduced.

As described above, when the process shifts to the discharge stroke, the protrusion 75 provided on the roller 7 is located at a position away from the discharge port 3b. The protrusion 75 gradually enters the discharge port 3b, and at the time of the protrusion, the compressed gas in the discharge port 3b is pushed out to the outside. Accordingly, the top clearance can be reduced, and when the process shifts to the suction stroke after the end of the discharge stroke and the low-pressure gas is sucked into the suction chamber Y, the high-pressure gas remaining in the discharge port 3b is removed from the suction chamber Y side. The backflow to the can be reduced. As a result, compression loss and overheating and pulsation of the suction gas in the suction chamber Y can be prevented, and at the start of the discharge stroke, that is, at the beginning of the discharge stroke when the discharge amount increases, the protrusion 75
Does not protrude into the discharge port 3b, so that the gas discharge passage can be sufficiently secured, so that the gas discharge resistance can be reduced, the gas can be prevented from being over-compressed, and the power loss due to the over-compression can be eliminated. You can.

By the way, as shown in FIG. 14, the height of the roller 7 reaches its maximum when the upper and lower end surfaces of the roller 7 are clockwise with respect to the blade protrusion.
By forming the inclined surfaces 701 and 702 having the lowest temperature near 0 ° and the highest temperature near 90 ° where the temperature is lowest, the low temperature side wall 7a is low at the high temperature side wall portion 7a in contact with the compression chamber X side and low temperature side wall is in contact with the suction chamber Y side. It is preferable to set high in the part 7b. In this case, during operation, the high-temperature side wall portion 7a originally having a low height is used.
However, as shown by the imaginary line in the figure, the height of the high-temperature side wall portion 7a and the low-temperature side wall portion 7b are made uniform, and the height of the roller 7 is increased. Along the circumference, the gap between the upper and lower end surfaces can be kept at a uniform small gap, the leakage through the upper and lower end surfaces of the roller 7 can be reduced, and the heating of the suction gas can be further reduced. Thus, the volumetric efficiency can be further improved.
The roller 7 is made of a molybdenum-nickel-chromium alloy or the like, and the difference in height between the high-temperature side wall 7a and the low-temperature side wall 7b is set to about several tens of microns.

As shown in FIG. 15, the height of the roller 7 is in contact with the compression chamber X side and the height of the high-temperature side wall portion 7a composed 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 composed of a semicircular portion having an angle of 0 to 180 degrees, may be uniformly increased, and its upper and lower end surfaces may have steps 703 and 704. In this case, , There is some unevenness on the end face at the step,
Processing can be simplified as compared with that shown in FIG. 14, and the end surfaces of the high-temperature side wall surface 7a and the low-temperature side wall surface 7b during operation can be substantially aligned as compared with those formed by a single-height cylinder. Thus, leakage through the end face can be reduced.

[0024]

According to the rotary compressor of one aspect of the present invention, the roller is relatively rotated between the roller and the eccentric shaft, and the lubricating oil is supplied to improve the sliding characteristics of the roller, thereby improving the friction. Loss and power loss can be reduced. In addition, by providing the blade with the roller, gas leakage from the rear chamber of the blade to the suction chamber and the compression chamber can be eliminated, gas leakage from the compression chamber to the suction chamber can be reduced, and the volumetric efficiency can be further improved. .

According to the rotary compressor in another aspect of the present invention, in addition to the effects of reducing the friction loss and the power loss and improving the volumetric efficiency, in particular, by providing a projection on the outer peripheral portion of the roller, the discharge stroke is improved. Heating and pulsation of the suction gas can be prevented when the process shifts from the suction stroke to the suction stroke. Further, in the early stage of the discharge stroke, the gas discharge resistance can be reduced, and the gas can be prevented from being over-compressed, so that the power loss can be further reduced.

According to the rotary compressor in still another aspect of the present invention, in addition to the effects of reducing frictional loss and power loss and improving volumetric efficiency, particularly, the height of the roller is set at a high temperature in contact with the compression chamber. By setting it low on the side wall and high on the low-temperature side wall that is in contact with the suction chamber side, it is possible to reduce leakage due to unbalance of the height of the rollers, so that the heating of the suction gas can be further reduced and the volume efficiency can be reduced. Can be further improved.

[Brief description of the 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 mounting structure of a blade.

FIG. 3 is a central longitudinal sectional view of FIG. 2;

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

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

FIG. 6 is a plan sectional view showing a case where the revolution 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 longitudinal sectional view showing the entire structure of the 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 illustrating a wall temperature with respect to an angle of a roller for explaining another embodiment.

FIG. 13 is a longitudinal sectional view showing a main part of a cylinder for explaining another embodiment.

FIG. 14 is a cross-sectional view illustrating an example of a specific shape of a roller according to another 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 sectional view of the conventional rotary compressor.

[Explanation of symbols]

 Reference Signs List 3 Compression element 3a Suction port 3b Discharge port 4 Cylinder 41 Cylinder chamber 7 Roller 7a High temperature side wall 7b Low temperature side wall 75 Projection 8 Blade 11 Support 11a Receiving groove

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Takahiro Uematsu 3-12 Chikushinmachi, Sakai-shi, Osaka Daikin Industry Co., Ltd.

Claims (3)

(57) [Claims] A cylinder (4) having a cylinder chamber (41), a front head (5) and a rear head (6) opposed to an open portion of the cylinder (4), and a cylinder chamber (41). The cylinder chamber (41)
A roller (7) revolving inside the cylinder and the cylinder chamber (41)
A compression element (3) having a blade (8) for partitioning the suction chamber into a compression chamber (X) and a suction chamber (Y).
In a rotary compressor configured to compress a gas fluid sucked from a) and discharge the compressed gas fluid from a discharge port (3b), the blade (8) is attached to the roller (7) in a radially outward direction of the roller (7). A support (11) having a receiving groove (11a) for receiving the tip of the protruding side of the blade (8) is rotatably provided in the cylinder (4). The roller (7) is fitted to an eccentric shaft portion (22) of a drive shaft (21) which is supported by bearings provided in the heads (5) and (6), and the roller (7) and the eccentric shaft are fitted. An oil supply passage (23) for supplying lubricating oil from the sliding contact surface with the part (22) toward the heads (5) and (6) is opened to the eccentric shaft part (22). Rotary compressor. 2. A cylinder (4) having a cylinder chamber (41), a roller (7) provided in the cylinder chamber (41) and revolving in the cylinder chamber (41), and the cylinder chamber (41). Is provided with a compression element (3) having a blade (8) for dividing the gas fluid into a compression chamber (X) and a suction chamber (Y), and compresses a gas fluid sucked from a suction port (3a) to a discharge port (3b). And a blade (8) provided integrally with the roller (7) so as to protrude radially outward of the roller (7) and the cylinder (4). A rotatable support (11) having a receiving groove (11a) for receiving the tip of the protruding side of the blade (8), facing the discharge port (3b) at the outer peripheral portion of the roller (7). To the discharge port (3b) Te protrude, characterized in that provided inrush possible and the projection (75) to said discharge opening (3b), rotary compressor. 3. A cylinder (4) having a cylinder chamber (41), a roller (7) installed in the cylinder chamber (41) and revolving in the cylinder chamber (41), and the cylinder chamber (41). Is provided with a compression element (3) having a blade (8) for dividing the gas fluid into a compression chamber (X) and a suction chamber (Y), and compresses a gas fluid sucked from a suction port (3a) to a discharge port (3b). And a blade (8) provided integrally with the roller (7) so as to protrude radially outward of the roller (7) and the cylinder (4). A rotatable support (11) having a receiving groove (11a) for receiving the tip of the protruding side of the blade (8). The height of the roller (7) is adjusted to the compression chamber (X) side. Low at the high temperature side wall (7a) in contact with the suction chamber ( Characterized in that it is set to be higher at low temperatures sidewall portion (7b) in contact with) the side,
Rotary compressor.