JP2003214369A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary compressor having a cylinder room with a sectional form capable of reducing leakage loss and improving efficiency. <P>SOLUTION: In a rotary compressor 20 with a single blade, a rotor 28 fixed to an eccentric section 27a of a rotary shaft 27 rotates inside the cylinder room 34 to introduce and compress the transferred fluid. The cylinder room 34 has a noncircular sectional form with a plurality of curvatures. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used for refrigerant compression of an air conditioner and a refrigeration system, and more particularly to a cylinder shape of the rotary compressor.

[0002]

2. Description of the Related Art Conventionally, in a refrigerating apparatus, an air conditioner, etc., a gas refrigerant vaporized in an evaporator is sucked and compressed to a pressure necessary for condensing the high-temperature high-pressure gas refrigerant in a refrigerant circuit. A compressor is used to pump out. A rotary compressor is known as one of such compressors. This rotary compressor includes a cylindrical housing, a motor disposed in the housing, and a rotary compression mechanism that is driven by the motor and compresses a conveyed (compressed) fluid such as a gas refrigerant. There is.

As shown in FIG. 7, for example, the rotary compression mechanism 10 is rotatably fitted to a rotary shaft (main shaft) 1 joined to a drive shaft of a motor and an eccentric portion (eccentric shaft) 1a of the rotary shaft 1. And a rotor 2 eccentric from the shaft center, and a space having a circular cross section that makes sliding contact with the outer peripheral surface of the rotor 2 at one location, and a cylinder inserted into the housing 11 with the rotor 2 arranged in this space. 3 and
A groove is provided at one position of the cylinder 3, and the blade is reciprocally fitted in the groove to come into contact with the rotor 2 to divide the space formed by the cylinder 3 and the rotor 2 into two blades, and the upper end surface of the cylinder 3. An upper bearing 4 fixed to the rotor 2 to rotatably support the rotating shaft 1 above the rotor 2, and a lower bearing 6 fixed to the lower end surface of the cylinder 3 to rotatably support the rotating shaft 1 below the rotor 2. Is equipped with.

The cylinder 3 is opened with a suction port 7 for sucking gas toward a suction chamber formed in a cylinder chamber 6, and the upper bearing 4 is provided with a gas from a compression chamber formed by turning from the suction chamber. A discharge port 8 that discharges the rotor 2 is opened, and the rotor 2 is housed in a cylinder chamber 6 formed by closing a cylinder 3 from above and below by an upper bearing 4 and a lower bearing 5.

The cylinder chamber 6 is provided on one side of the blade by a blade (not shown) being pushed toward the outer peripheral surface of the rotor 2 so as to communicate with the suction port 7, and on the other side of the blade. And is divided into a compression chamber communicating with the discharge port 8.

The intake port 7 is opened in the outer peripheral side wall surface of the cylinder chamber 6, and is provided so as to penetrate the cylinder 3 and the housing 11. A suction pipe 13 is connected to the suction port 7 via a suction fitting 12. Reference numeral 14 in the figure is an outer pipe welded to the housing 11.

The discharge port 8 is formed as a circular hole in a plan view penetrating the upper bearing 4, and a discharge valve 9 which is opened when a pressure of a predetermined magnitude or more is released is formed on the upper surface of the discharge port 8. It is provided.

In the rotary compressor having the above-described structure, the sliding contact portion of the rotor 2 on the suction chamber side passes through the suction port 7 to gradually expand the suction chamber and move away from the suction port 7 into the suction chamber. Inhale gas. On the other hand, on the compression chamber side, the sliding portion of the rotor 2 approaches the discharge port 8 while gradually shrinking the compression chamber, and when compressed to a predetermined pressure or higher, the discharge valve 9 opens and gas is discharged from the discharge port 8. Drain.

By the way, in the above-mentioned conventional rotary compressor, the cross-sectional shape of the cylinder chamber 6 is designed to be a perfect circle. However, in reality, a machining error due to lathe machining etc. is unavoidable, so it becomes a non-circular shape that is slightly deviated from the exact perfect circle, that is, the machining error (currently several μm order) within the range of the machining error. ing.
The rotary shaft 1 of the rotor 2 is supported by a plurality of bearings such as an upper bearing 4, a lower bearing 5 and a pin portion bearing 2b. Therefore, the axial center locus of the rotating shaft 6 that rotates in the bearing is affected by the bearing gap, and is, for example, as shown in FIG.
It becomes a non-circular shape as shown in. Therefore, the envelope locus drawn by the outer diameter (outer peripheral surface) of the rotor 2 when the rotary shaft 6 makes one revolution is also affected by the axial center locus and is approximately several tens of μm.
It becomes a non-circular shape with an order deviation.

On the other hand, in a rolling piston type fluid machine such as a rotary compressor, the outer peripheral surface 2a of the rotor 2 is
And the side wall surface 6a of the cylinder chamber 6 come into contact with each other,
In particular, there is a concern that seizure or wear may occur at the blade tip. Therefore, as shown in FIG.
A minute gap W is provided between the outer peripheral surface 2a and the side wall surface 6a, and the size of the leakage area S determined by the minute gap W and the height H of the cylinder chamber 6 affects the efficiency of the compressor. Will have an effect. Therefore, if the minute gap W between the rotor 2 and the cylinder wall surface is increased so that they do not contact each other, the problems of seizure and wear are solved, but through this minute gap W, suction of low pressure from the high pressure compression chamber side is performed. There is a problem that the amount of compressed fluid flowing out to the chamber side increases. That is, since the compressed fluid to be conveyed leaks from the minute gap W to increase the loss (hereinafter, referred to as “leakage loss”), a new problem arises that the efficiency of the fluid machine is reduced.

Therefore, in consideration of the above-described machining accuracy and the axial center locus of the rotary shaft 6, a component that can secure the minimum minute gap W such that the rotor 2 and the wall surface of the cylinder chamber 6 do not contact each other is selected. There is. Alternatively, when the rotor 2 is closest to the side wall surface 6a of the cylinder chamber 6, the bearing is preliminarily displaced from the center of the cylinder chamber 6 based on the axis trace so that the minute gap W is minimized. The method, so-called "eccentric assembly", has been put to practical use.

In an internal combustion engine, the cross-sectional shape of the cylinder is intentionally changed at room temperature in order to make the cylinder shape a perfect circle when thermal distortion occurs in the cylinder due to temperature rise due to operation, that is, in steady operation. It is being processed into a non-circular shape.

[0013]

The rotary compressor having the above-described conventional structure has the sectional shape of the cylinder chamber 6 and the rotor 2.
Since the envelopes of (1) and (2) are both unintended non-circular shapes, these are taken into consideration when setting the minute gap W, and it is set on the safe side so as not to contact even in the worst condition. Therefore, the minute gap W tends to be large, and the minute gap W changes with the rotation angle during one rotation of the rotor 2. Therefore, for example, by adopting an eccentric assembly, the rotor 2 can be installed in
Even if the minute gap W that does not come into contact with the closest position to is set, there is a problem that the minute gap W becomes larger than necessary at other rotation positions. Therefore, the amount of leakage generated during one rotation of the rotor 2 is large except for the position of the minimum gap W, and there is a problem to be solved in that overall leakage loss also increases and the efficiency of the compressor is reduced. . That is, in the rotary compressor in which the cross-sectional shape of the cylinder chamber 6 is designed to have a circular cross-section, it is inevitable that the closest position becomes the smallest minute gap W and increases with rotation. There is.

However, in recent years, it has been desired to further improve the efficiency of an air conditioner or the like in which a refrigerant is circulated by a compressor, and in order to achieve this, it is important to further improve the efficiency of the compressor. . The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a rotary compressor having a cylinder chamber cross-sectional shape that can reduce leakage loss and improve efficiency.

[0015]

The present invention adopts the following means in order to solve the above problems. In the rotary compressor according to claim 1, a rotor rotatably fitted to the shaft eccentric portion swivels in a cylinder chamber, a groove is provided in the cylinder, and a blade fitted with a reciprocable gap therein is provided. In the single-blade rotary compressor for sucking and compressing the fluid to be conveyed by forming a closed space by the cylinder chamber, the cylinder chamber has a non-circular cross-sectional shape with a plurality of curvatures. Is.

According to such a rotary compressor, since the cross-sectional shape of the cylinder chamber has a non-circular shape having a plurality of curvatures, even if the envelope locus of the rotor becomes non-circular due to the influence of the axial center locus, etc. It becomes possible to keep the minute gap W constant during rotation.

A rotary compressor according to a second aspect of the present invention is characterized in that the cross-sectional shape of the non-circular cylinder according to the first aspect is a shape in which an arbitrary set clearance (δ) is added to the envelope trajectory of the rotor outer diameter. It is a thing.

According to such a rotary compressor, since the non-circular cross-sectional shape is a shape obtained by adding an arbitrary set clearance (δ) to the envelope trajectory of the rotor outer diameter, a minute clearance during one rotation of the rotor. W can be maintained at a constant set gap (δ).

According to a third aspect of the rotary compressor of the present invention, the cross-sectional shape of the non-circular cylinder according to the first aspect has an arbitrary set clearance (δ) and a machining error (Δδ) in the envelope trajectory of the rotor outer diameter.
It is characterized by the addition of

According to such a rotary compressor, since the non-circular cross-sectional shape is a shape obtained by adding an arbitrary set clearance (δ) and machining error (Δδ) to the envelope trajectory of the rotor outer diameter,
The minute gap W can be maintained at a constant value (set gap δ + machining error Δδ) during one rotation of the rotor. In this case, since the processing error (Δδ) is reflected, the minimum minute gap W can be maintained over the entire circumference.

A rotary compressor according to a fourth aspect is the rotary compressor according to any one of the first to third aspects,
A reference position processing portion is provided at an appropriate position of the cylinder member in which the cylinder chamber is formed.

According to such a rotary compressor, since the reference position processing portion is provided at an appropriate position of the cylinder member, the reference position processing portion is used as a reference when assembling the rotary compressor in which the cylinder chamber has a non-circular sectional shape. As a result, the bearing can be easily installed at a predetermined position.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of a rotary compressor according to the present invention will be described below with reference to FIGS.
As shown in FIG. 1, the rotary compressor 20 has a cylindrical housing 21, a motor 22 arranged in the housing 21, and a hermetically sealed structure that is driven by the motor 22 to compress a gas (a fluid to be transported) of a refrigerant. Type rotary compression mechanism 23
It is a single-cylinder compressor configured with.

The housing 21 has a hollow cylindrical shape in which a bottom portion 21b and a lid portion 21c are welded and closed above and below a tubular portion 21a. One end of a suction pipe 24 connected to the rotary compression mechanism 23 via a suction fitting 24a is provided in the cylindrical portion 21a in a penetrating state, and the lid portion 21c is connected to a cooling mechanism (refrigeration cycle) not shown. The discharged discharge pipe 25 is arranged in a penetrating state. Reference numeral 21d in the drawing is an outer pipe through which the suction fitting 24a is passed, and is welded to the tubular portion 21a.

In the motor 22, the stator 22a is fixed to the housing 21, and the lower end of the drive shaft 26 to which the rotor 22b is fixed is extended toward the rotary compression mechanism 23 located below. The rotary compression mechanism 23 includes the rotary shaft 2 press-fitted into the lower end of the hollow drive shaft 26.
7, a rotor 28 fixed to an eccentric portion (eccentric shaft) 27a with respect to the rotating shaft 27, and a non-circular cross-sectional space that linearly slidably contacts the outer peripheral surface 28a of the rotor 28 at one location (a cylinder chamber described later). 34), and a cylinder 29 welded to the housing 21 in a state where the rotor 28 is arranged in this space, and a rotary shaft 27 rotatably supported above the rotor 28 by being fixed to the upper end surface of the cylinder 29. An upper bearing 30 and a lower bearing 31 fixed to the lower end surface of the cylinder 29 and rotatably supporting the rotating shaft 27 below the rotor 28 are provided. The inner peripheral surface of the rotor 28 that is in contact with the eccentric portion 27a of the rotary shaft 27 is referred to as a pin portion bearing 28b.

The rotary shaft 27 is supported with its lower end protruding from the lower bearing 23. An oil pump mechanism 32 for supplying lubricating oil to the hollow interior is provided at the lower end of the rotary shaft 27, and a lubricating oil sump 33 is formed at the bottom of the housing 21.

The rotor 28 is housed in a cylinder chamber 34 formed by closing a space of a non-circular cross section provided in the cylinder 29 with an upper bearing 30 and a lower bearing 31. The non-circular cross-sectional shape of the cylinder chamber 34 will be described later in detail. As shown in FIG. 2, a slot hole 29a is formed on the inner surface of the cylinder 29 forming the cylinder chamber 34, and a blade 35 having one side having a length substantially the same as the thickness of the rotor 28 is formed in the slot hole 29a. One side is fitted in the cylinder chamber 34 so that it can be retracted and retracted, and the blade 3 is placed behind the blade 35.
A spring body 36 that pushes 5 toward the cylinder chamber 34 is provided. The blade 35 is a plate-like member having one side having a length substantially equal to the length of the rotor 28 in the thickness direction, and is biased by the spring body 36 so that its one side (tip portion) is directed toward the outer peripheral surface of the rotor 28. It is designed to be pressed.

Further, the cylinder 29 forming the cylinder chamber 34 is provided with a suction port 37 which is located in front of the blade 35 in the rotational direction of the rotor 28 and communicates with the suction pipe 24. The upper bearing 30 is provided with the blade 35. From rotor 2
A discharge port 38 that is located at the rear of the rotation direction of 8 and communicates with the discharge pipe 25 is opened. The cylinder chamber 34 is provided on one side of the blade 35 by the tip of the blade 35 being pressed against the outer peripheral surface of the rotor 28 and communicates with the suction port 37, and on the other side of the blade 35. And is divided into a compression chamber communicating with the discharge port 38.

The discharge port 38 is formed as a circular hole in plan view penetrating the upper bearing 30, and communicates with an upper muffler chamber 40 formed by a cover 39 covering the upper surface of the upper bearing 30. Further, the discharge port 38 opening to the upper muffler chamber 40 side is provided with a discharge valve 41 which is opened when a pressure of a predetermined magnitude or more is received.

Further, the rotary compressor 20 is provided with an accumulator 50 for the purpose of separating the lubricating oil contained in a small amount from the gas flowing through the cooling mechanism. The accumulator 50 has a cylindrical container 51 connected to a pipe through which gas flows. The other end of the suction pipe 24 is opened upward above the inside of the cylindrical container 51. Reference numeral 52 in the figure is a connecting portion of a pipe for introducing gas into the accumulator 50.

Now, in the rotary compressor 20 of the present invention,
The cross-sectional shape of the cylinder chamber 34 described above is intentionally designed to have a non-circular cross section having a plurality of curvatures. The non-circular cross-sectional shape of the cylinder chamber 34 will be specifically described below. 3A to 3C, the upper bearing 30 and the pin portion bearing 2 are shown.
Regarding the axis center locus of 8b, three types of different load conditions (load A <load B <load C) are illustrated. In this figure, (a) shows the axial center locus of the upper bearing 30, and (b)
The axis center locus of the pin portion bearing 28b is shown in (c), and the origin 0 and an explanatory view of the rotation direction (rotation angle θ) of the rotary compressor are shown in (c).

The axial center loci of FIGS. 3A and 3B are shown in FIG.
As shown in (c), the center of the upper bearing 30 and the lower bearing 31 is the origin 0, and the rotation angle θ of the rotor 28 is based on the position of the blade 35 (rotation angle θ = 0). The rotation angle θ is defined as a positive rotation angle when the rotor 28 rotates counterclockwise, the positive direction of the x-axis is the direction of the blade 35 (direction of rotation angle θ = 0), and the positive direction of the y-axis is the rotation direction. The angle θ is 270 °.

Here, the axial center locus of the upper bearing 30 is Su
(X (θ), y (θ)). x (θ): x-coordinate at the rotation angle θ y (θ): y-coordinate at the rotation angle θ In the example shown in FIG. 3A, the axial locus Su becomes larger as the load becomes larger. Blade 35 from origin 0
A non-circular turning locus is drawn at a position deviated to the side opposite to. The circle R1 in FIG. 3A indicates the bearing clearance circle of the upper bearing 30 (the maximum locus circle when the shaft contacts the upper bearing and rotates).

Subsequently, the axial center locus of the pin bearing 28b is S
Let p (x (θ), y (θ)). This axial center locus does not include the axial center locus Su of the upper bearing 30.
This is the trajectory of b alone. x (θ): x coordinate at the rotation angle θ y (θ): y coordinate at the rotation angle θ In the example shown in FIG. 3B, this axis locus Sp is similar to the above-described axis locus Su. , The larger the load, the more δ from the origin 0 to the side opposite to the blade 35.
A non-circular turning locus is drawn at a position shifted by about p. The circle R2 in FIG. 3 (b) indicates the pin portion bearing clearance circle.

The diagram shown in FIG. 4 is a sum of the above-described axial center locus Su of the upper bearing 30 and the axial center locus Sp of the pin portion bearing 28b for each load condition. It is added for each rotation angle θ. In addition, the circle R3 in FIG. 4 indicates a circle obtained by adding the upper bearing gap and the pin portion bearing gap. If the eccentric amount of the rotary shaft (main shaft) 27 is ε and the rotor radius of the rotor 28 is r ₀ , the locus line S _ro (x (θ),
y (θ)) is given by the following equation. S _ro = Su + ε + Sp

The above mathematical expressions are all expressed in the vector format, and the trajectory line S _ro can be expressed as the following [Equation 1].

[Equation 1]

Envelope Se (x) of the outer diameter of the rotor 28
(Θ), y (θ)) is given by the following equation (2).

[Equation 2] Here, φ represents the angle of movement of the rotor center with respect to the pin center.

In the present invention, a shape obtained by adding a set gap δ to the shape of the non-circular (composite circle) envelope Se having a plurality of curvatures given by [Equation 2], that is, only the set gap δ is larger than the envelope Se. It is preferable to design the inner diameter (cross-sectional shape) of the cylinder chamber 34 to be large. With this configuration, when there is no processing error, the gap becomes the set gap δ at all rotation angles θ. The set gap δ is 0 or more (δ ≧ 0)
Is a positive value.

Further, since a machining error Δδ actually occurs, a shape obtained by adding both the set gap δ and the machining error Δδ to the shape of the non-circular envelope Se having a plurality of curvatures given by [Equation 2]. Is more preferable. As a result,
The inner diameter (cross-sectional shape) of the cylinder chamber 34 is designed to be larger than the envelope Se by the set gap δ and the machining error Δδ, whereby the rotor 28 is set in the cylinder chamber 3 in consideration of the machining error.
The optimum minimum clearance that does not interfere with 4 can be given to all rotation angles. Note that the sum of the set clearance δ and the processing error Δδ is 0 or more (δ + Δδ ≧
Set it to be a positive value of 0).

FIG. 5 shows three load conditions A, which differ in the shape of the composite circular cylinder based on the envelope Se of the present invention described above.
It is calculated and shown for each of B and C, and is illustrated so that the degree of non-circle with respect to the reference perfect circular cylinder can be seen at a glance. In the illustrated example, the cylinder chamber 34 is widened by intentionally increasing the cutting amount in the 90 ° direction by about 18 μm as compared with the true circular cylinder. In other words, a cylinder having a radius of curvature in the 90 ° direction larger than the true circle. It is as a shape. On the contrary, in the 270 ° direction, the cutting amount is intentionally reduced by about 4 to 16 μm from that of the true circular cylinder to narrow the cylinder chamber 34. In other words, the radius of curvature in the 270 ° direction is smaller than that of the true circular cylinder. It has a reduced cylinder shape.
In addition, also in other rotation angle directions, the shape of the cylinder chamber 34 is determined by appropriately changing the cutting amount (curvature radius) based on the envelope Se by the outer diameter (outer peripheral surface) of the rotor 28.

Therefore, the composite circular cylinder shape based on the envelope Se described above is a composite circular shape having a plurality of curvatures having at least two radii of curvature. Such a composite circular shape can be processed using a tool such as an end mill. Numerical values such as the eccentricity direction and the amount of eccentricity of the shaft center locus illustrated in FIGS. 3 and 4 and the cutting amount with respect to the perfect circle illustrated in FIG. 5 are merely examples, and various conditions such as the bearing used and the operating pressure It changes sequentially by.

With the above-described compound circular cylinder shape, the cylinder chamber 34 is aligned with the envelope Se at which the rotor 28 actually swings under the influence of the axial center locus of the upper bearing 30 and the like.
As shown in FIG. 6, the rotation angle θ becomes
The gap Wa of the compound circular cylinder corresponding to is always constant. As a result, the leakage area S can be kept to a minimum over the entire circumference, so that the leakage loss of the rotary compressor 20 can be reduced and the efficiency can be improved.

In this case, if a sectional shape in which the set gap δ is added to the envelope Se is adopted, the gap (Wa) = the set gap (δ) ≧ 0, and if there is no processing error, this gap Wa is maintained over the entire circumference. To be done. Further, when a sectional shape obtained by adding both the set gap δ and the processing error Δδ to the envelope Se is adopted, the gap (Wa) = the set gap (δ) + the processing error (Δ
δ) ≧ 0, and even when the machining error Δδ under the most severe conditions is taken into consideration, the minimum gap Wa can be secured and the interference of the rotor 28 can be prevented.

Further, according to FIG. 6, in the conventional perfect circular cylinder, the gap becomes the smallest when the rotation angle θ exceeds 180 °, and the gap becomes large at the front and rear rotation angles θ. As described as the problem of (1), it is understood that there is a disadvantage in terms of leakage loss.

Hereinafter, the process of operating the rotary compressor 20 having the above-described structure to compress and convey gas will be described. First, when the motor 22 is operated, the rotary shaft 27 connected to the drive shaft 26 rotates and the rotor 28 also starts to rotate. The rotor 28 is in the cylinder chamber 3
The eccentric rotary motion is performed in the cylinder 4, and along with this, the gas is sucked from the suction pipe 24 into the suction chamber, and at the same time, the gas already sucked into the compression chamber is gradually compressed. At this time, the rotor 28
Since the cylinder chamber 34 has a cross-sectional shape that matches the envelope line Se, the leakage area S is small over the entire circumference of the rotation angle θ of 0 to 360 °, and as a result, leakage loss is suppressed.

The gas compressed in the compression chamber pushes up the discharge valve 41 from the discharge port 38 and flows into the upper muffler chamber 40, and its pulsating component is removed. The gas flowing into the upper muffler chamber 40 passes through a through hole (not shown) formed in the cover 39, flows below the motor 22 and expands, so that the pulsating component is further removed. The gas flowing into the lower part of the motor 22 passes through the air gap between the stator 22 a and the rotor 22 b and the gas passage formed between the stator 22 a and the housing 21, and flows into the upper part of the motor 22 to expand. By doing so, the pulsating component is further removed. The gas that has flowed above the motor 22 flows into the discharge pipe 25 and is conveyed toward a cooling mechanism (not shown).

On the other hand, the gas flowing through the cooling mechanism flows into the accumulator 50, and becomes fine oil droplets (mist-like) to separate the lubricating oil scattered in the gas. Also,
The lubricating oil accumulated in the oil sump 33 is moved upward in the rotary shaft 27 by being urged by the pump action generated by the rotational movement of the oil pump mechanism 32, and the rotor 28 in the cylinder chamber 34 is supplied from a supply path (not shown). Is supplied to the sliding position between the cylinder 29 and the cylinder 29 and is jetted from the upper end of the rotary shaft 27 to cool the rotary compression mechanism 23.

By the way, the rotary compressor 20 having a non-circular cross section having a plurality of curvatures as described above is particularly suitable for the cylinder chamber 34.
Since the cross-sectional shape of the is non-circular, a standard is required to accurately perform its processing and assembly. In the example shown in FIG. 2, two reference position processing parts 60 are provided on the upper surface of the cylinder 29 and are drilled at diagonal positions sandwiching the cylinder chamber 34. By providing such a reference position processing portion 60, for example, a positioning pin (not shown) is inserted into the reference position processing portion 60 and the upper bearing 3 for the cylinder 29 is inserted.
It can be used as a machining standard or an assembly standard such as positioning 0.

The above-mentioned reference position processing unit 60 is not limited to the above-mentioned example, and for example, the reference position processing unit 6 can be used.
It is also possible to provide a rectangular groove or protrusion as 0. In this case, since the rectangular shape other than the square shape can be positioned in two directions, the reference position processing section 60 can be provided at an appropriate position. The reference position processing unit 60
The installation position, shape, and number of are not particularly limited.

As described above, in the rotary compressor 20 of the present invention, the envelope of the rotor 28 is non-circular because the axial locus of the bearing that supports the rotating shaft 27 does not form a perfect circle. Therefore, a non-circular cross section having a plurality of curvatures is adopted mainly for the purpose of solving the problem of increasing the leakage loss. In addition, in the above-described rotary compressor 20, although the value is considerably smaller than the influence of the axial center locus, the temperature of the high pressure side (compression chamber side) where the temperature becomes high and the low temperature side (suction chamber side) where the temperature becomes low. Since there is an influence of thermal strain due to the difference and welding strain when the cylinder 29 is welded and fixed to the housing 21, it is possible to determine an optimal non-circular cross-sectional shape for the cylinder chamber 34 including these.

In the above description, the single-cylinder rotary compressor 20 has been described, but the present invention is not limited to a single-cylinder, and can be applied to a rotary compressor having a plurality of two or more cylinders. Needless to say. Further, the configuration of the present invention is not limited to the above-described embodiment, and can be appropriately modified within the scope of the present invention.

[0052]

According to the rotary compressor of the present invention described above, since the sectional shape of the rotary chamber is a non-circular shape having a plurality of curvatures, the gap is minimized over the entire circumference, and the leakage area S and the leakage loss are reduced. can do. When the leakage loss is reduced in this way, the operating efficiency under rated and intermediate performance conditions is improved by several percent, and further improvement in operating efficiency can be expected especially under high pressure differential conditions where the ratio of leakage loss is large. .

Further, if the cross-sectional shape is such that an arbitrary set clearance δ is added to the envelope trajectory of the rotor outer diameter, the desired clearance δ can be maintained over the entire circumference, so that good operating efficiency can be obtained. . Then, the processing error Δ
If the cross-sectional shape is further added with δ, it does not interfere with the rotor due to the processing error, and the optimum cross-sectional shape with a small leakage loss can be obtained to further improve the operating efficiency.

By providing the reference position processing portion, the processing of the cylinder chamber having a non-circular cross section and the work of incorporating the upper bearing and the like in a predetermined position can be easily and accurately performed.

[Brief description of drawings]

FIG. 1 is a side sectional view showing an embodiment of a rotary compressor according to the present invention.

FIG. 2 is a cross-sectional view showing a configuration example of a rotary compression mechanism.

3A and 3B are diagrams showing an example of an axial center locus, FIG. 3A is a diagram showing an axial center locus of an upper bearing, FIG. 3B is a diagram showing an axial center locus of a pin bearing, and FIG. And rotor rotation angle θ
FIG.

FIG. 4 is a view showing a total of axial loci of the upper bearing and the pin bearing shown in FIGS. 3A and 3B.

FIG. 5 is a diagram showing an example of a cylinder shape having a non-circular (composite circle) cross section according to the present invention.

FIG. 6 is a diagram showing a relationship between a rotation angle θ of a rotor and a clearance for the compound circular cylinder shown in FIG. 5 and a conventional perfect circular cylinder.

FIG. 7 is a cross-sectional view of essential parts showing a conventional example of a rotary compression mechanism.

FIG. 8 is an explanatory diagram showing a leakage area S.

[Explanation of symbols]

20 rotary compressor 21 housing 22 motor 23 Rotary compression mechanism 24 Inhalation tube 25 discharge pipe 27 rotating shaft 27a Eccentric part (eccentric shaft) 28 rotor 28a outer peripheral surface 28b Pin bearing 29 cylinders 30 upper bearing 31 Lower bearing 34 Cylinder chamber 35 blade 37 Inhalation port 38 Discharge port 60 Reference position processing part S Leakage area H cylinder height

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Toshiyuki Goto             1 Takamichi, Iwatsuka-cho, Nakamura-ku, Nagoya-shi, Aichi               Mitsubishi Heavy Industries Nagoya Research Center F-term (reference) 3H029 AA04 AA13 AB03 BB16 BB31                       BB33 BB43 CC03

Claims (4)

[Claims] 1. A hermetically sealed space is formed by a rotor rotatably fitted to an eccentric part of a shaft, revolving in a cylinder chamber, a groove being installed in the cylinder, and a blade fitted therein with a reciprocable gap therein. In the single-blade rotary compressor for sucking and compressing the fluid to be conveyed, the cylinder chamber has a non-circular cross-sectional shape with a plurality of curvatures. 2. The rotary compressor according to claim 1, wherein a cross-sectional shape of the non-circular cylinder is a shape obtained by adding an arbitrary set clearance (δ) to an envelope trajectory of a rotor outer diameter. 3. The rotary compression according to claim 1, wherein the cross-sectional shape of the non-circular cylinder is a shape obtained by adding an arbitrary set clearance (δ) and a processing error (Δδ) to an envelope trajectory of a rotor outer diameter. Machine. 4. The rotary compressor according to claim 1, wherein a reference position processing portion is provided at an appropriate position on the cylinder member in which the cylinder chamber is formed.