JP3156895B2 - Rotary compressor with integrated blade and roller - 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 in a refrigeration system, which eliminates relative movement between a blade and a roller to reduce friction loss and the like.

[0002]

2. Description of the Related Art Conventionally, as a rotary compressor, for example, there is a rotary compressor described in Japanese Utility Model Laid-Open Publication No. 61-114082. In this conventional compressor, as shown in FIGS. 4 and 5, a compressor section A driven by a motor is provided in a closed casing, and the compression section A is a cylinder C having a cylinder chamber B. A roller E inserted into 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; a suction port F and a discharge port G provided in the cylinder C; And a blade H arranged to be able to move forward and backward at an intermediate portion between the blade H and the blade H. The blade H causes a part of the high-pressure gas discharged from the discharge port G to act as a back pressure on the back side thereof. The back pressure causes the blade H
Is constantly in contact with a part of the outer peripheral surface of the roller E, so that the cylinder chamber B is compressed with the compression chamber X and the suction chamber Y.
And it is divided into. Further, the discharge port G is provided with a plate-shaped discharge valve I which opens or closes the discharge port G by contacting or separating from 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 discharge valve I, and the discharge stroke ends and shifts to the suction stroke. At this time, the discharge valve I is closed to close the discharge port G, and low-pressure gas is sucked from the suction port F into a suction chamber Y defined by the blades H in the cylinder chamber B, The compression stroke and the discharge stroke are repeated.

[0004]

However, as described above, the blade H and the cylinder C are supported so as to be able to move forward and backward and a back pressure is applied, so that the tip of the blade H is
When the blade H and the roller E are caused to move relatively to each other, a back pressure is applied to the blade H to press the leading end of the blade H against the outer peripheral surface of the roller to make contact therewith. In addition, since the contact between the blade H and the outer peripheral surface of the roller becomes metal contact without oil, the friction loss due to the sliding between the blade H and the outer peripheral surface of the roller is large, and the power loss is also large. was there. 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. 4, the high-pressure gas in the rear chamber leaks into the suction chamber Y through the space between the side surface of the blade H and the blade sliding groove, and there is a problem that the volumetric efficiency is reduced. Further, since the pressure in 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 is generated by the blade H.
Leaks into the compression chamber X through the gap between the side surface of the blade and the blade sliding groove, and there is also a problem that the pointing efficiency is reduced. Furthermore,
The high-pressure gas compressed in the compression chamber X may leak into the suction chamber Y from the contact portion between the tip of the blade H and the roller E, as shown by an arrow b in FIG. There is a problem that the volumetric efficiency is further reduced in combination with the leakage from the pipe.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to eliminate the relative movement between the blade and the roller, thereby reducing the friction loss and the power loss. Another object of the present invention is to make it possible to increase the volumetric efficiency and the indicating efficiency by reducing gas leakage from the chamber to the suction chamber.

[0006]

In order to achieve the above object, the present invention provides a cylinder having a cylinder chamber, a roller provided in the cylinder chamber and revolving along a peripheral surface of the cylinder chamber, A rotary compressor including a blade that partitions a chamber into a compression chamber and a suction chamber, and configured to compress gas sucked from a suction port opening to the suction chamber and discharge the compressed gas from a discharge port opening to the compression chamber. An eccentric shaft portion of a drive shaft to which lubricating oil is supplied is rotatably fitted to the roller, and the blade is integrated with the roller so as to protrude radially outward of the roller. The cylinder has a semicircular member having two substantially semicircular cross-sections, and a support member rotatably provided between the flat portions of the two semicircular members and forming a receiving portion for freely receiving and moving the tip of the blade forward and backward. ,Previous The plane portions of the semicircular member, thereby positioning said blade slidably, characterized in that the tip of the blade is located radially outward of the roller than the rotation center of the support.

[0007]

In the rotary compressor having the above construction, the eccentric shaft portion of the drive shaft to which the lubricating oil is supplied is relatively rotated with respect to the roller, thereby eliminating the relative movement between the blade and the roller as in the conventional example. Therefore, friction loss and power loss can be reduced as compared with the conventional example in which the blade is relatively moved with the roller. That is, the eccentric shaft portion of the drive shaft to which the roller is fitted is always supplied with lubricating oil from an oil supply passage of the drive shaft, and is in fluid contact with the eccentric shaft portion in relative rotation between the roller and the eccentric shaft portion. The frictional resistance can be reduced, and the friction loss and the power loss can be reduced as compared with the case where the blade and the roller are relatively moved by applying a back pressure to the blade. In addition, since the blade and roller are integrated to eliminate the need to apply back pressure to the blade, gas leakage from the rear chamber of the blade to the suction chamber and compression chamber can be eliminated, and volumetric efficiency can be reduced. And the indicating efficiency can be increased. Further, since the blade and the roller are integrated, gas does not leak from the compression chamber to the suction chamber through the space between the blade and the roller as in the conventional example. The volumetric efficiency can be further improved in combination with the absence of gas leakage from the chamber.

[0008] The support is composed of two semicircular members, of which the semicircular member on the compression chamber side is a wall surface (cylindrical surface or spherical surface) of a holding hole for accommodating the same.
Of these, the roller is pressed against the radially outer portion of the roller from the side facing the compression chamber side under pressure. As a result, the semicircular member on the compression chamber side is pressed toward the blade by a cam action of the wall surface of the holding hole like a wedge, and the sealing performance between the flat portion of the semicircular member and the blade is improved. I do. In addition, the semicircular member on the suction chamber side is also pressed via the blade toward the wall surface of the holding hole that houses the semicircular member by the wedge action of the semicircular member on the compression chamber side, and the semicircular member on the suction chamber side. The seal between the blade and the wall surfaces of the blade and the cylinder is also improved. Therefore, the leakage of the compressed gas is prevented, and the volumetric efficiency is improved. further,
Since the tip of the blade is always located radially outward of the roller from the center of rotation of the support, the contact area between the blade and the plane portion of the semicircular member increases, that is,
The sealing length is increased, and the sealing performance is improved. Therefore,
This also prevents the compressed gas from leaking and improves the volumetric efficiency.

Further, since the support is composed of two semicircular members completely separated from each other, the operation of inserting the blade into the central receiving portion of the support is simplified, and the assembling property is improved.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the embodiments shown in FIGS. FIG. 3 is an overall view of the rotary compressor, and FIGS. 1 and 2 are cross-sectional views respectively showing states of the compression section of the rotary compressor during the compression stroke and immediately before the end of the compression stroke.

In the rotary compressor shown in FIG. 3, a motor 2 is provided in an upper portion inside a closed casing 1 and a compression section 3 is provided in a lower portion of the motor 2 so that the motor 2
The compression section 3 is driven by a drive shaft 21 extending from the compression section 3. The compression section 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 opening portions of the cylinder 4, and the cylinder chamber 41.
And a roller 7 rotatably mounted inside the bearing. The lower part of the drive shaft 21 is supported by bearings provided on the respective heads 5 and 6, and the eccentric shaft 22 of the drive shaft 21 is The roller 7 is rotatably inserted, and the drive shaft 21 is
The roller 7 is rotated while sliding on the eccentric shaft portion 22 with the rotation of the roller 7. 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.
The pump section 24 is attached to the inlet of the
Is opened at the sliding contact surface between the roller 7 and the eccentric shaft portion 22, and the lubricating oil pumped from the oil reservoir 1 b by the pump portion 24 is supplied from the oil supply passage 23 to the sliding contact surface. I am trying to supply. 1a is an external discharge pipe connected to the upper side of the casing 1.

As shown by broken lines in FIGS. 1 and 2, the compression section 3 has a suction port 3a for suction gas which opens into the cylinder chamber 41 in the cylinder 4, and the suction port 3a.
The compressed gas discharge port 3b which opens to the cylinder chamber 41 is formed in the cylinder 4 in the vicinity of the cylinder chamber 41, and a compression chamber X is formed in the cylinder chamber 41 at an intermediate portion between the suction port 3a and the discharge port 3b. Blade 20 defined with suction port Y
8 is integrated with the roller 7, and the discharge port 3b has a plate-shaped discharge valve (see FIG. 4) which opens and closes the discharge port 3b by contacting or separating from a valve seat surface formed around the outlet. ). The discharge valve is not shown in FIGS. 1 and 2 for simplification of the drawing.

The blade 208 is integrally 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. In this embodiment, the blade 208
Is integrally formed with the roller 7, but a blade separate from the roller 7 may be combined with the roller 7 by using an adhesive or an engagement pin to integrate the two. Good.

The blade 208 is provided so as to be freely inserted into and removed from a central receiving portion 210 of a support 211 which is swingably mounted in a cylindrical or cylindrical holding hole 42 of the cylinder 4. The support body 211 includes two semicircular members 211a and 211b which are completely separated from each other and have a substantially semicircular cross section.
a and 211b are in sliding contact with the plane portion. The cylindrical surfaces of the semicircular members 211a and 211b are in sliding contact with the cylindrical surface of the holding hole 42. In this embodiment, the semicircular member 211 is used.
Although a and 211b have a semi-cylindrical shape, they may have a hemispherical shape.

As shown in FIG. 1, when the roller 7 is located farthest from the support 211, the drive shaft 22
Is longer than the distance L2 between the center of the drive shaft 22 and the center O of the support 211. That is, the blade 208 is
Even in a state where the roller 7 protrudes radially inward from the receiving portion 210 of the roller 11, a part of the blade 208 is located at the center O of the support 211. Note that FIG.
Indicates a state in which the compression stroke in which the roller 7 comes closest to the support 211 has been completed.

In the above configuration, the tip of the blade 208 provided on the roller 7 moves in and out of the receiving portion 210 of the support 211 with the driving of the driving shaft 21, and
As the support body 211 rotates and moves in the radial direction while swinging, the inside of the cylinder chamber 41 is defined as a compression chamber X and a suction chamber Y. At this time, the roller 7 relatively rotates with respect to the eccentric shaft 22, and the tip of the blade 208 contacts the outer peripheral surface of the roller 7 as in the related art, so that the blade 208 and the roller 7 relatively move. Therefore, wear due to friction between the blade 208 and the roller 7 and power loss due to the friction can be eliminated. In other words, instead of the blade 208 and the roller 7 moving relative to each other, the roller 7 and the eccentric shaft 22 rotate relative to each other. Is that the lubricating oil is constantly supplied from the oil supply passage 23 of the drive shaft 21 and the frictional resistance can be reduced because of the fluid contact. Therefore, the back pressure is applied to the blade 208 so that the blade 208 contacts the roller 7. The friction loss can be reduced and the power loss can be reduced as compared with the conventional one in which the relative movement is performed.

Further, since the blade 208 is provided integrally with the roller 7, there is no need to apply back pressure as in the prior art. Therefore, unlike the conventional example, the blade 208 is moved from the rear chamber of the blade to the suction chamber. Gas leakage to Y and compression 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. In addition, since the blade 208 and the roller 7 are integrated with each other, gas does not leak from the compression chamber X to the suction chamber Y through the space between the blade 208 and the roller 7, so that the compression efficiency can be increased. Can be. Further, as will be understood from the following description, both side wall surfaces of the blade 208 and the support body 211 into which the blade 208 is inserted are described.
From the receiving portion 210 or between the support body 211 and the wall surface of the holding hole 42, it is possible to minimize the possibility that the gas fluid in the compression chamber X leaks to the suction chamber Y side. This can also increase the compression efficiency.

That is, the support 211 is composed of two semicircular members 211a and 211b.
1a, 211b, semicircular member 211a on the compression chamber X side
Is pressed in the direction indicated by arrow Z under pressure from the side facing the compression chamber X. As a result, the semicircular member 211a on the compression chamber X side is sandwiched between the cylindrical wall surface of the holding hole 42 and the blade 208 like a wedge, and a seal is formed between the plane portion of the semicircular member 211a and the blade 208. The performance is improved. The semicircular member 211b on the suction chamber Y side
The suction chamber Y is also pressed toward the cylindrical wall surface of the holding hole 42 for accommodating the suction chamber Y by the wedge action of the semicircular member 211a on the compression chamber X side.
The sealing performance between the semicircular member 211b on the side and the cylindrical wall surface of the blade 208 and the holding hole 42 is also improved. Therefore, gas leakage can be effectively prevented, and the volumetric efficiency is improved. Further, since the tip of the blade 208 is always located radially outward of the roller 7 from the rotation center O of the support 211, the blade 208 and the semicircular member 21
The contact area of the flat portions 1a and 211b with the flat portion is increased, that is, the sealing length is increased, and the sealing performance is improved. Therefore, this also improves the volumetric efficiency.

Since the support member 211 is composed of two separate semicircular members 211a and 211b, the blade 2
08 can be easily inserted into the central receiving portion of the support 211.

[0020]

As is apparent from the above description, the rotary compressor of the present invention uses a roller which defines a cylinder chamber of a cylinder as a compression chamber and a suction chamber so as to project radially outward of the roller. And a support member formed of two semicircular members having a substantially semicircular cross section and forming a receiving portion between the flat portions of the semicircular member for freely receiving and moving the tip of the blade. The blade is moved in the radial direction by the rotation of the support, and the eccentric shaft of the drive shaft to which the lubricating oil is supplied is moved relative to the roller. The relative rotation is performed. Thus, in this rotary compressor, 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, and the two are in fluid contact. Therefore, the frictional resistance can be reduced as compared with the conventional example in which a back pressure is applied to the blade to bring the blade into contact with the roller, and therefore, the friction loss and the power loss can be reduced as compared with the conventional example. Further, by integrating the blade and the roller, it is not necessary to apply back pressure to the blade, so that gas leakage from the rear chamber of the blade to the suction chamber and the compression chamber can be eliminated, and the volumetric efficiency and indicating efficiency can be reduced. Can be enhanced. Further, since the blade and the roller are integrated, it is possible to prevent the gas from leaking from the compression chamber to the suction chamber through the space between the blade and the roller as in the conventional example, thereby also improving the volumetric efficiency. Can be enhanced.

Further, according to the present invention, the support comprises two semicircular members, and the blade is slidably disposed on the opposing flat surface of the semicircular member. 2 of the support
Of the semicircular members, the semicircular member on the compression chamber side is the side facing the compression chamber side toward the radially outer portion of the roller among the wall surfaces of the cylindrical or spherical holding holes for accommodating the same. Because it is pressed under pressure, the semicircular member on the compression chamber side is pressed toward the blade by a cam action on the wall surface of the holding hole like a wedge, and the flat part of the semicircular member on the compression chamber side The sealing performance between the blade and the blade is improved. Further, the semicircular member on the suction chamber side is also pressed via the blade toward the cylindrical wall surface of the holding hole for accommodating the same by the wedge action of the semicircular member on the compression chamber side. The sealing performance between the semicircular member and the wall surfaces of the blade and the cylinder is improved. Therefore, it is possible to prevent gas in the compression chamber from leaking to the suction chamber side from between the both side wall surfaces of the blade and the receiving portion of the support or between the support and the wall surface of the holding hole accommodating the support. It is possible to further improve the volumetric efficiency in combination with the prevention of the leakage of the compressed gas by integrating the blade and the roller. In addition, since the tip of the blade is always located radially outward of the roller from the center of rotation of the support, the contact area between the blade and the flat portion of the semicircular member increases, that is, the seal length Becomes longer,
The sealing performance is improved. Therefore, this also prevents the leakage of the compressed gas and improves the volumetric efficiency.

Further, since the support is composed of two semicircular members completely separated from each other, the operation of inserting the blade into the central receiving portion of the support is simplified, and the assembling property is improved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a rotary compressor according to an embodiment of the present invention in a state where a compression section is in a compression stroke.

FIG. 2 is a sectional view of a state immediately before the end of a compression stroke of a compression section of the rotary compressor.

FIG. 3 is a longitudinal sectional view showing the entire structure of the rotary compressor.

FIG. 4 is a plan sectional view showing a compression section of a conventional rotary compressor.

FIG. 5 is a partial sectional view of the conventional rotary compressor.

[Explanation of symbols]

3a ... suction port, 3b ... discharge port, 4 ... cylinder, 7 ... roller, 21 ... drive shaft, 22 ... eccentric shaft section, 41 ... cylinder chamber, 208 ... blade, 210 ... receiving section, 211 ... support body, 211a, 211b: semicircular member, X: compression chamber, Y
... inhalation chamber.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Takahiro Uematsu 3-12 Chikko Shinmachi, Sakai City, Osaka Prefecture Daikin Industries, Ltd. Sakai Plant Rinkai Plant (72) Inventor Masanori Masuda 3, 12 Chikko Shinmachi, Sakai City, Osaka Prefecture Address Daikin Industries Co., Ltd. Sakai Plant Rinkai Plant (56) References JP-A-3-70890 (JP, A)

Claims (1)

(57) [Claims] 1. A cylinder (4) having a cylinder chamber (41), and a roller (7) provided inside the cylinder chamber (41) and revolving along the peripheral surface of the cylinder chamber (41).
And a blade (208) for partitioning the cylinder chamber (41) into a compression chamber (X) and a suction chamber (Y), and the gas sucked from a suction port (3a) opening to the suction chamber (Y). Eccentric shaft portion of a drive shaft (21) for supplying lubricating oil to the roller (7) in a rotary compressor configured to compress the oil and discharge the compressed air from a discharge port (3b) opened to a compression chamber (X). (22) is fitted so as to be relatively rotatable, and the blade (208) is integrated with the roller (7) so as to protrude radially outward of the roller (7) and the cylinder (4). In addition, two semicircular members (2
11a, 211b), the two semi-circular members (21
1a, 211b) between the plane portions.
Receiving unit (210) that freely receives the tip of 8)
A support (211) that forms the second member (211) is rotatably provided, and the blade (208) is slidably disposed on a plane portion of the two semicircular members (211a, 211b). A rotary compressor, wherein a tip portion is located radially outward of the roller (7) from a rotation center of the support (211).