JP5366856B2 - Vane rotary type fluid apparatus and compressor - Google Patents

Abstract

The invention provides a vane rotary type fluid device and a compressor capable of reducing the loss due to the sliding of the front end of a vane on the inner circumferential surface of a cylinder and improving the compression or expansion efficiency. A compression element (12) and an electric element (15) served as the driving source of the compression element (12) are arranged inside an enclosed container. The compression element (12) is equipped with a shaft (6), a roller (7), a cylinder (5), two bearings (3, 4), a separation vane (8), a suction inlet (18), an outlet (19) and a position restriction mechanism. The position restriction mechanism limits the position of the front end of the vane (8), so that the front end of the vane is placed along the inner circumferential surface of the cylinder (5). The position restriction mechanism is equipped with an annular groove (17) formed on at least one of the two bearings (3, 4) and on a concentric circle of the inner circumferential surface of the cylinder (5) and a ring (9) combined with the front end of the vane (8) and slidably and freely arranged inside the annular groove (7).

Description

  The present invention relates to a vane rotary type fluid device used as a compressor or an expander constituting a refrigeration cycle, and a compressor using the compression function thereof, and particularly relates to a vane position regulating structure. In the following description, a vane rotary type compressor will be mainly described as an example.

  The vane rotary compressor is a shaft that is driven to rotate by an electric element, a roller that rotates together with the shaft, and a vane groove formed on the roller that reciprocally slides during a compression process into a plurality of working chambers. A vane for partitioning is provided, and the tip of the vane rotates and slides along the inner surface of the cylinder.

  This type of vane rotary type compressor needs to behave so that the tip of the vane follows the inner surface of the cylinder. To do so, it is necessary to control the behavior of the vane, and various mechanisms are considered. Has been. For example, two types of mechanisms have been proposed as examples of the vane position regulating mechanism (see, for example, Patent Document 1).

  The first position restricting mechanism (hereinafter referred to as the first position restricting mechanism) is configured to slide a vane guide portion provided on the vane and a groove portion provided concentrically with the inner peripheral surface of the cylinder. This is a mechanism that regulates the position of the vane and rotates and slides so that the tip of the vane follows the inner surface of the cylinder.

  The second position restricting mechanism (hereinafter referred to as the second position restricting mechanism) is configured such that the protrusion provided on the vane rotates and slides in a groove concentric with the inner peripheral surface of the cylinder. It is a mechanism that regulates the position of the vane and rotates and slides so that the tip of the vane is along the inner surface of the cylinder.

JP 2006-125361 A (FIG. 1)

  The occurrence of surface damage such as friction, wear, seizure, etc. between the two surfaces of the machine part. Preventing or reducing it can not only improve the reliability of the part but also improve the efficiency. it can. Therefore, the supply of the lubricant between the two surfaces protects the relative motion surface and prevents the occurrence of surface damage. The form of lubrication by this lubricant can be broadly divided into fluid lubrication and boundary lubrication. Fluid lubrication is a lubrication state in which a fluid film sufficiently thicker than the surface roughness is formed between the friction surfaces and the friction surfaces are completely separated, and loss due to friction is small. On the other hand, boundary lubrication is a lubrication state in which the fluid film becomes thin and direct contact between friction surfaces occurs, and loss due to friction is large.

  By the way, the conventional vane rotary type fluid device controls the vane behavior so that the tip of the vane follows the inner surface of the cylinder as described above. At this time, since the two surfaces slide, the loss due to friction is large, and the compression efficiency or the expansion efficiency is lowered. In order to reduce the loss due to friction, various mechanisms have been studied. In the above-mentioned Patent Document 1, the first position restricting mechanism and the second position restricting mechanism are proposed as described above.

  However, the first position regulating mechanism is not a curvature that fits in the sliding part between the tip of the vane and the groove provided in the cylinder. The lubrication state with the provided groove is boundary lubrication. Therefore, loss due to friction is large, and compression efficiency or expansion efficiency is reduced.

  In the second position regulating mechanism, the center of the R shape of the vane and the center of the pin do not coincide with each other, so the distance between the center of the R shape of the vane and the inner surface of the cylinder changes. Therefore, in order to prevent the tip of the vane from sliding on the inner surface of the cylinder, at least one of the inner surface shape of the cylinder and the groove shape of the bearing must be a distorted shape that is not a circular shape. Therefore, there is a problem that machining becomes difficult.

  In addition, in the sliding portion between the vane projection and the groove provided in the bearing, the two are not curvatures that fit together, but the shapes are greatly different, so the vane projection and the groove provided in the bearing The lubrication state is boundary lubrication. Therefore, loss due to friction is large, and compression efficiency or expansion efficiency is reduced.

  The present invention has been made to solve the above problems, and at least a vane rotary type in which a loss due to sliding between the tip of the vane and the inner peripheral surface of the cylinder is reduced to improve the compression efficiency or the expansion efficiency. An object is to provide a fluid device and a compressor using the compression function thereof.

The vane rotary type fluid device according to the present invention includes a compression element or an expansion element that compresses or expands a refrigerant in an airtight container, and an electric element that is a drive source of the compression element or the expansion element. In the apparatus, the compression element or the expansion element includes a shaft that is rotationally driven by the electric element, a roller that is attached to the shaft, rotates, and is on a coaxial axis with a central axis of the shaft, and stores the roller. A cylinder having an inner peripheral surface having a cylindrical shape and a center axis of the inner peripheral surface being eccentric with respect to the rotation axis of the shaft, two bearings closing both end surfaces of the cylinder, and the roller A reciprocating slide is performed in the compressed vane groove during the compression process or during the expansion stroke, and a plurality of compression chambers or expansion chambers formed by the cylinder, the roller, and the bearing are provided. A vane dividing the dynamic chamber, the tip of the vane along the inner circumferential surface of the cylinder, Ru and a position regulating means for regulating the position of the tip of said vane. The vane has an R-shaped tip, and the position restricting means is provided in at least one of the two bearings, and is formed on a ring groove concentrically with the inner peripheral surface of the cylinder, and the ring has a slidably disposed a ring in the groove, and a cylindrical member that connects the tip and the ring of said vane, said cylinder such that the tip of the vane is rotatable with respect to the ring It is attached to the ring via a member, and is arranged so that the center of the R shape at the tip of the vane coincides with the center of the cylindrical member .

  According to the vane rotary type fluid device according to the present invention, by adopting the above-described configuration, it is possible to prevent sliding between the two surfaces of the vane tip and the inner peripheral surface of the cylinder. For this reason, loss due to sliding between the tip of the conventional vane and the inner peripheral surface of the cylinder is reduced, loss due to sliding is reduced, and compression efficiency or expansion efficiency is improved.

It is a longitudinal cross-sectional view of the vane rotary type compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the positional relationship of the vane in the compression process in the compressor of FIG. It is a figure which shows the connection state of the vane in the compressor of FIG. It is a figure which shows the relationship between the front-end | tip of a vane and the internal peripheral surface of a cylinder in the compressor of FIG. It is a figure which shows the detail of the compression element in the compressor of FIG. 1, The vane of FIG. 7 has shown the cross section of the position of 180 degrees. FIG. 2 is an exploded schematic configuration diagram illustrating a relationship between center lines of compression elements in the compressor of FIG. It is a figure which shows the vane position of the compression process in the compressor of FIG. It is a figure which shows the connection state of the vane and ring which concern on Embodiment 5 of this invention. It is a figure which shows sliding with the inner peripheral surface of the ring which concerns on Embodiment 6 of this invention, the inner peripheral surface of a ring groove, and the outer peripheral surface of a ring, and the outer peripheral surface of a ring groove.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view of a vane rotary type compressor according to Embodiment 1 of the present invention, and FIG. 2 is a diagram showing a positional relationship of vanes during a compression process of the compressor of FIG. FIG. 3 is a view showing a connection state of the vane and the ring and the pin, and FIG. 4 is a view showing a relationship between the vane tip and the cylinder inner peripheral surface. FIG. 5 is a diagram showing details of the compression element in the compressor of FIG. 1, and shows a cross section where the vane of FIG. 7 is 180 degrees. FIG. 6 is an exploded schematic configuration diagram showing the relationship of the center lines of the compression elements in the compressor of FIG. FIG. 7 is a view showing vane positions in the compression process in the compressor of FIG.

As shown in FIG. 1 and FIG. 2, the vane rotary compressor includes a compression element 12, an electric element 15, and a refrigerating machine oil (not shown) in a sealed container composed of a lower container 1 and an upper container 2. Is housed.
A suction pipe 1 a communicating with the accumulator 30 is connected to the lower container 1, and refrigerant (gas) is taken from the accumulator 30. A discharge pipe 2a is connected to the upper part of the upper container 2, and the compressed refrigerant is discharged.
The electric element 15 includes a stator 13 fixed to the lower container 1 and a rotor 14 that rotates inside the stator 13.
The compression element 12 includes an upper bearing 3, a lower bearing 4, a cylinder 5, a shaft 6, a roller 7, and a vane 8, and the mutual positional relationship between them is a cross-sectional view of FIG. 5 and an exploded schematic configuration diagram of FIG. 6. It has the configuration shown in
The cylinder 5 has a cylindrical inner peripheral surface, and the central axis of the inner peripheral surface is eccentric with respect to the rotation axis of the shaft 6 (see FIGS. 2, 5, and 6). Are arranged in a minute section. The cylinder 5 has a suction port 18 and a discharge port 19 (see FIG. 2). The suction port 18 communicates with the suction pipe 1a. A discharge valve (not shown) that opens when the pressure becomes equal to or higher than a predetermined pressure is provided at the discharge port 19 or downstream thereof.
The shaft 6 is rotatably supported by the upper bearing 3 and the lower bearing 4 and is driven to rotate by the electric element 15.
The roller 7 is fitted to the shaft 6 and rotates. The roller 7 is coaxial with the central axis of the shaft 6 and rotates together with the shaft 6. The roller 7 is formed with a vane groove 7a for slidably storing the vane 8.
The upper bearing 3 and the lower bearing 4 close both end surfaces of the cylinder 5 (see FIGS. 5 and 6).
The vane 8 reciprocally slides in a working chamber 20 (in this embodiment, a compression chamber) formed by the cylinder 5, the roller 7, and the bearings 3 and 4 in the vane groove 7a formed in the roller 7 during the compression process. Thus, the working chamber 20 is partitioned into a plurality of working chambers 20a and 20b.

  Further, at least one of the upper bearing 3 and the lower bearing 4 is formed with a ring groove 17 concentrically with the working chamber 20 (see FIGS. 4 to 6 and 9). Then, the lower bearing 4 is formed. A ring 9 is slidably disposed in the ring groove 17 (see FIGS. 4 to 6). A vane 8 is attached to the ring 9.

Next, the attachment structure of the vane 8 and the ring 9 will be described.
2 and 3, the ring 9 and the vane 8 are provided with pin holes 9a and 8a, respectively, and the cylindrical pin 10 is inserted into the pin holes 9a and 8a. Becomes rotatable with respect to the ring groove 17.

  Further, as shown in FIG. 4, both are coupled so that the center of the R shape of the tip of the vane 8 coincides with the center of the pin 10.

  The ring groove 17, the ring 9, and the pin 10 that couples the ring 9 and the vane 8 constitute the position restricting means of the present invention.

Next, the operation of the above vane rotary compressor will be described.
The compressor sucks the refrigerant of the accumulator 30 into the working chamber 20a of the working chamber 20 (compression chamber) through the suction pipe 1a and the suction port 18. The shaft 6 is rotated by the electric element 15, and the roller 7 fitted to the shaft 6 is also rotated. A vane 8 reciprocating in a vane groove 7a formed in the roller 7 and a ring 9 connected to the vane 8 via a pin 10 also rotate. At this time, since the cylinder 5 has a cylindrical inner peripheral surface and the central axis of the inner peripheral surface is eccentrically arranged with respect to the rotation axis of the shaft 6, the rotation of the roller 7 causes the inner periphery of the roller 7 and the cylinder 5 to be arranged. The distance to the surface varies. However, the vane 8 is connected to a ring 9 that slides in a ring groove 17 concentric with the working chamber 20 and can rotate in the cylinder 5, and the center of the tip R shape coincides with the center of the pin 10. Since they are attached, there is always a clearance (clearance) between the center of the R shape of the tip of the vane 8 and the inner peripheral surface of the cylinder 5, and it is possible to prevent the two surfaces from sliding. This is the operation of the vane position regulating means of the present invention. And the refrigerant | coolant compressed with rotation of the roller 7 is discharged | emitted from the discharge outlet 19, and is finally discharged | emitted from the discharge pipe 2a.

Next, the compression operation of the working chamber 20 which is a compression chamber will be described with reference to FIG.
When the vane 8 is at 0 deg, the tip of the vane 8 is substantially the same position as the outer peripheral position of the roller 7, and refrigerant leakage between the tip of the vane 8 and the inner peripheral surface of the cylinder 5 does not affect the compression efficiency. It is partitioned by a slight gap. Since the tip end portion of the vane 8 is connected to the ring 9 that slides in the ring groove 17, the ring 9 rotates and the vane 8 is pulled out from the roller 7 as the roller 7 rotates. In order to rotate while maintaining a minute gap that does not affect the leakage of the refrigerant along the inner peripheral surface of the cylinder 5, the refrigerant in the working chamber 20b is compressed. Then, the vane 8 returns to the position in the roller 7 from the position where the vane 8 is 180 deg and is compressed in the working chamber 20b to reach a predetermined discharge pressure, and the refrigerant is discharged from the discharge port 19. During the refrigerant compression operation, the refrigerant is drawn into the working chamber 20 a from the suction port 18, so that the suction of the refrigerant from the suction port 18 and the discharge from the discharge port 19 are repeated by the rotation of the roller 7. .

Then, the effect of the above-mentioned vane rotary type compressor is explained.
As shown in FIG. 3, a ring groove 17 is provided in at least one of the two bearings 3, 4, and a pin hole 9 a is formed in each of the ring 9 sliding with the ring groove 17 and the vane 8. , 8a are provided, and the cylindrical pins 10 are inserted into the pin holes 9a, 8a and are connected to each other, so that the vane 8 rotates with respect to the ring groove 17. Furthermore, since the center of the tip R shape of the vane 8 coincides with the center of the pin 10, a gap (clearance) is always formed between the center of the tip R shape of the vane 8 and the inner peripheral surface of the cylinder 5. . Here, since a gap is formed between the tip of the vane 8 and the inner peripheral surface of the cylinder 5, the gap is so small that it does not significantly affect the decrease in volume efficiency. The lubrication state between the tip of the vane 8 and the inner peripheral surface of the cylinder 5 is fluid lubrication, and there is little loss due to sliding, so that the compression efficiency is improved.

  Further, since the center of the tip R shape of the vane 8 and the center of the pin 10 coincide with each other, even if both the inner peripheral surface shape of the cylinder 5 and the ring groove 17 shape of the bearings 3 and 4 are circular, the compression is in progress. Further, the tip of the vane 8 can be prevented from sliding on the inner peripheral surface of the cylinder 5. As a result, machining of the inner peripheral surface shape of the cylinder 5 and the ring groove 17 shape of the bearings 3 and 4 is facilitated.

  Further, the pin 10 slides with at least one of the pin holes 8a and 9a of the vane 8 and the ring 9, but the pin holes 8a, 9a and the pin 10 are in the sliding portion between the pin 10 and the pin holes 8a and 9a. Since the shapes of the pins 10 and the pin holes 8a and 9a are similar to each other with the fitting curvature, the lubrication state between the pins 10 and the pin holes 8a and 9a is fluid lubrication. As a result, since the loss due to sliding is small, the compression efficiency is improved.

  The ring 9 is provided on at least one of the two bearings 3 and 4 and slides with the ring groove 17 concentrically with the cylinder 5. In the sliding portion between the ring 9 and the ring groove 17, Since the ring 9 and the ring groove 17 have such curvatures as to be fitted and the shapes thereof are similar, the lubrication state between the ring 9 and the ring groove 17 is fluid lubrication. As a result, since the loss due to sliding is small, the compression efficiency is improved.

  In addition, since the sliding portion between the pin 10 and the ring 9 is supplied with oil by a centrifugal force due to the rotation of the shaft 6 (not shown), the sliding does not cause abnormal wear.

Embodiment 2. FIG.
In Embodiment 1 described above, the roller 7 is fitted to the shaft 6 and rotates. However, the roller 7 may be integrated with the shaft 6.

Embodiment 3 FIG.
In the first embodiment, as the position regulating means, the ring 9 that slides with the ring groove 17 provided in at least one of the two bearings 3 and 4, and the pin holes 9 a and 8 a in the vane 8, respectively. The example in which the cylindrical pin 10 is inserted into the pin holes 9a and 8a has been described. However, when inserting the cylindrical pin 10 into the pin holes 9a and 8a, the pin 10 is inserted into the vane 8 and the ring 9. You may make it insert in both the pin holes 8a and 9a by clearance fit. The pin holes 9a and 8a are not necessarily through holes, and may be bottomed recesses.

Embodiment 4 FIG.
When the cylindrical pin 10 is inserted into the pin holes 9a and 8a, it is inserted into one pin hole (for example, 8a) and inserted into the other pin hole (for example, 9a) with a clearance fit. May be. The pin holes 9a and 8a are not necessarily through holes, and may be bottomed recesses.

Embodiment 5 FIG.
In the first embodiment, the example in which the pin 10 is provided as the position restricting means has been described. However, instead of the pin 10, a protrusion may be provided on the vane 8 or the ring 9.
FIG. 8A is an example in which a protrusion 10a is provided on the vane 8, and a hole 9b into which the protrusion 10a is inserted is provided in the ring 9. FIG. 8B is an illustration in which the protrusion 9b is provided on the ring 9. This is an example in which a hole 8b into which the protruding portion 10b is inserted is provided in the vane 8.
Also in this case, the protrusions 10 a and 10 b are inserted into the holes 9 b and 8 b with clearance fit, and the vane 8 rotates with respect to the ring groove 17. The holes 9b and 8b are not necessarily through holes, and may be bottomed recesses.

Embodiment 6 FIG.
In the first embodiment, as shown in FIGS. 9A and 9B, the ring 9 may slide with either the inner peripheral surface or the outer peripheral surface of the ring groove 17. Good.

First, as shown in FIG. 9A, when the inner peripheral surface of the ring 9 slides on the inner peripheral surface of the ring groove 17, the outer peripheral surface of the ring 9 is the outer peripheral surface of the ring groove 17. Since the distance that the ring 9 slides in the ring groove 17 is smaller than when the ring is slid, the compression efficiency is improved.
Next, as shown in FIG. 9B, when the outer peripheral surface of the ring 9 slides on the outer peripheral surface of the ring groove 17, the inner peripheral surface of the ring 9 is the inner periphery of the ring groove 17. Since the gap between the ring 9 and the ring groove 17 is smaller than when sliding on the surface, volume efficiency is improved.

Embodiment 7 FIG.
In addition, although all said description is a case where the vane rotary type fluid apparatus of this invention is applied to a compressor, this invention is applicable also to an expander (vane rotary type expander). In that case, in the example of FIG. 2, the roller 7 is rotationally driven in the opposite direction to the above example, the refrigerant to be expanded is taken in from the discharge port 19, and the expanded refrigerant is discharged from the suction port 18. To be configured.

Embodiment 8 FIG.
In any of the vane rotary type fluid devices of the present invention described above, the pressure difference between the working chambers 20a and 20b acts on the vane 8 as a differential pressure, and the vane groove 7a of the roller 7 is easily deformed. Therefore, hydrocarbons with a low operating pressure and a normal boiling point of −45 ° C. or higher (for example, propane, butane, isobutane, etc.), saturated hydrofluorocarbons with a low operating pressure of a standard boiling point of −45 ° C. or higher (for example, R134a, R152a, etc.) , Unsaturated hydrofluorocarbons having a low normal pressure and a normal boiling point of −45 ° C. or higher (for example, HFO1234yf, 1234ze, 1243zf, etc.), or mixed refrigerants having a low normal pressure and a normal boiling point of −45 ° C. R422D etc.) is desirable.

  1 Lower container, 1a Suction pipe, 2 Upper container, 2a Discharge pipe, 3 Upper bearing, 4 Lower bearing, 5 Cylinder, 6 Shaft, 7 Roller, 7a Vane groove, 8 vane, 9 ring, 10 pin, 12 Compression element , 13 Stator, 14 Rotor, 15 Electric element, 16 Back pressure chamber, 17 Ring groove, 18 Suction port, 19 Discharge port, 20, 20a, 20b Working chamber, 30 Accumulator.

Claims (9)

In a vane rotary fluid device comprising a compression element or an expansion element that compresses or expands a refrigerant in an airtight container, and an electric element that is a drive source of the compression element or the expansion element.
The compression element or expansion element is
A shaft that is rotationally driven by the electric element;
A roller attached to the shaft and rotating, the roller being on the same axis as the central axis of the shaft;
A cylinder in which an inner peripheral surface for storing the roller is cylindrical and a central axis of the inner peripheral surface is eccentrically arranged with respect to a rotation axis of the shaft;
Two bearings for closing both end faces of the cylinder;
A vane that reciprocally slides in a vane groove formed in the roller during a compression process or during an expansion stroke, and partitions the compression chamber or the expansion chamber formed by the cylinder, the roller, and the bearing into a plurality of working chambers; ,
Position regulating means for regulating the tip position of the vane so that the tip of the vane is along the inner peripheral surface of the cylinder;
The vane has a rounded tip.
The position regulating means is
A ring groove provided on at least one of the two bearings and formed concentrically with the inner peripheral surface of the cylinder;
A ring slidably disposed in the ring groove;
A cylindrical member connecting the tip of the vane and the ring, and attached to the ring via the cylindrical member so that the tip of the vane is rotatable with respect to the ring, The vane rotary fluid apparatus , wherein the center of the R shape at the tip of the vane and the center of the columnar member coincide with each other . The cylindrical member is composed of a cylindrical pin,
The attachment part of the ring at the tip of the vane is
2. A pin hole formed in each of the vane and the ring, wherein the cylindrical pin is inserted into the pin hole, and the vane is disposed so as to be rotatable with respect to the ring groove. A vane rotary fluid device according to claim 1. The pin is
The vane rotary fluid device according to claim 2, wherein the vane rotary fluid device is inserted into the pin holes of both the vane and the ring by clearance fit. The pin is
3. The vane rotary type fluid device according to claim 2, wherein the vane rotary fluid device is inserted into one of the pin holes of the vane and the ring with an interference fit and inserted into the other pin hole with a clearance fit. The cylindrical member is composed of a protrusion formed on one of the vane and the ring,
The position regulating means is
Formed on the other of the front Symbol vanes and the ring, the protrusion includes a hole portion <br/> to be inserted, said vane is rotatably disposed with respect to the ring groove, the tip of the vane of the R shape 2. The vane rotary fluid device according to claim 1, wherein the center and the center of the protrusion are arranged to coincide with each other.   The vane rotary fluid device according to any one of claims 1 to 5, wherein the ring slides with any one of an outer peripheral surface and an inner peripheral surface of the ring groove.   The vane rotary type fluid device according to any one of claims 1 to 6, wherein the shaft and the roller are integrally formed.   The compressor according to any one of claims 1 to 7, wherein the compressor is a vane rotary compressor that has the compression chamber and compresses a refrigerant.   The vane rotary type fluid device according to any one of claims 1 to 8 is a hydrocarbon having a low normal pressure with a normal boiling point of −45 ° C. or higher, and a saturated or non-saturated or low standard boiling point with a low operating pressure of −45 ° C. or higher. A vane rotary type fluid device using a saturated hydrofluorocarbon or a mixed refrigerant having a low normal pressure and a normal boiling point of −45 ° C. or higher.

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