JP2001193679A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor with an enhanced performance by reducing leak of a high-pressure refrigerant gas from a compression chamber while securing sufficiently a gap required to prevent scuffing of component parts with one another and wear between a rotor and a side block or a cylinder. SOLUTION: At the shorter diameter part 1a of the elliptical bore of a cylinder 1, a slit-form groove 21 is provided so as to cross the flow of a refrigerant gas leaking to the low pressure part though a rotor periphery gap 19-2. Thereby the flow of high-pressure refrigerant gas leaking out to the low pressure part via the gap 19-2 varies steeply in the part of a labyrinth groove 20, causing a vortex 21 or turbulence in the flow of refrigerant gas. The vortex 21, etc., serves as a resistance against the leaking flow of the refrigerant gas passing the peripheral gap 19-2 to reduce the leaking amount of the high-pressure refrigerant gas to the low pressure part.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a gas compressor mounted on a vehicle as a part of a car air conditioner system,
In particular, the performance of the gas compressor is improved by reducing high-pressure refrigerant gas leakage from the compression chamber to the low-pressure section.

[0002]

2. Description of the Related Art Conventionally, this kind of gas compressor has a cylinder 1 having a substantially elliptical inner circumference, for example, as shown in FIG.
Side blocks 2 and 3 are attached to both end surfaces of the cylinder 1, and a rotor 4 is mounted on the inside of the cylinder 1. The rotor 4 is connected to a rotor shaft 5 having a shaft center and side blocks 2 and 3. Are rotatably supported via the bearings 6 and 7.

As shown in FIG. 7, a plurality of slit-shaped vane grooves 8 are formed on the outer peripheral surface side of the rotor 4, and vanes 9 are respectively mounted in these vane grooves 8. It is provided so as to be able to protrude and retract from the outer peripheral surface toward the inner wall of the cylinder 1.

The inside of the cylinder 1 includes an inner wall of the cylinder 1, inner surfaces of side blocks 2 and 3, an outer peripheral surface of the rotor 4 and a vane 9.
A plurality of small chambers are partitioned by both side surfaces on the tip side, and the partitioned small chambers are referred to as compression chambers 10, and the rotor 4 rotates in the direction of arrow B in the drawing to repeatedly change the volume. When the volume of the compression chamber 10 changes, the low-pressure refrigerant gas is sucked from the suction chamber 11 to the compression chamber 10 when the volume increases, and the refrigerant in the compression chamber 10 when the volume of the compression chamber 10 decreases. The compression of the gas and the discharge of the high-pressure refrigerant gas from the compression chamber 10 to the discharge chamber 12 are performed.

That is, in the suction process from the time when the volume of the compression chamber 10 becomes minimum to the maximum, the refrigerant gas in the suction chamber 11 is sucked into the suction passage 13 such as the cylinder 1 and the side blocks 2 and 3 communicating therewith. The air is sucked into the compression chamber 10 through the port 14. When the volume of the compression chamber 10 becomes close to the maximum, the compression chamber 10 separates from the suction port 14 to form a closed space, and the low-pressure refrigerant gas is confined in the compression chamber 10.
Next, when the volume of the compression chamber 10 as the closed space shifts from the maximum to the minimum, the compression chamber 10
The low-pressure refrigerant gas inside is compressed. Further, when the volume of the compression chamber 10 becomes close to the minimum, the pressure of the compressed high-pressure refrigerant gas opens the reed valve 16 attached to the discharge hole 15 of the cylinder 1, and opens the high-pressure refrigerant gas in the compression chamber 10. From the discharge hole 15 to the discharge chamber 17 on the outer peripheral surface side of the cylinder 1. The high-pressure refrigerant gas flowing into the discharge chamber 17 further flows into the rear side block 3.
After passing through a discharge passage (not shown), the oil is discharged into the discharge chamber 12 through an oil separator 18 attached to the side block 3.

Incidentally, in order to improve the performance (volume efficiency) of the gas compressor as described above, it is necessary to prevent refrigerant gas leakage from the high pressure section to the low pressure section. More specifically, immediately before the refrigerant gas is discharged from the compression chamber 10, that is, in the vicinity of the elliptical minor diameter portion 1a of the cylinder 1 where the volume of the compression chamber 10 approaches the minimum and the interior of the compression chamber 10 is considered to have the highest pressure, FIG. As shown by the middle arrow A, the clearance 19-1 (also referred to as rotor side clearance) between the end surface of the rotor 4 and the inner surfaces of the side blocks 2, 3 or the clearance 19-2 between the outer peripheral surface of the rotor 4 and the inner surface of the cylinder 1 is provided. It is necessary to prevent the high-pressure refrigerant gas in the compression chamber 10 from leaking to the low-pressure suction port 14 through the rotor outer diameter gap.

Under these circumstances, in the conventional gas compressor, the rotor side gap 19-1 and the rotor outer diameter gap 19-
2 by assembling them, these gaps 19-1,
Gas leakage to the suction port 14 side through 19-2 was reduced.

However, since the rotor 4 is a rotating part and the cylinder 1 and the side blocks 2 and 3 are fixed parts, if these parts 2, 3 and 4 are too tightly packed, the rotor 4 and the Galling, abrasion, etc. of the parts of the side blocks 2, 3 and the rotor 4 and the cylinder 1 occur. For this reason, in the above-mentioned conventional gas compressor, between the rotor 4 and the side blocks 2 and 3 or between the rotor 4 and the cylinder 1
, Especially the elliptical minor diameter portion 1a, the minimum gaps 19-1 and 19-2 necessary for preventing galling and wear between parts.
It is necessary to secure the gaps 19-1 and 19-2 at least as necessary.
1, 19-2 to the low pressure suction port 14 side to the compression chamber 10
It is inevitable that the high-pressure refrigerant gas leaks from the inside, and this gas leak hinders the performance improvement of the gas compressor.

[0009]

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a device which is provided between a rotor and a side block or between a rotor and a cylinder. Reduce the leakage of high-pressure refrigerant gas from the compression chamber to the low-pressure part side such as the suction port, while ensuring sufficient clearance required to prevent galling and wear between parts.
An object of the present invention is to provide a gas compressor capable of improving the performance (volume efficiency) of the gas compressor.

[0010]

In order to achieve the above object, the present invention provides a cylinder having a substantially elliptical inner circumference, side blocks attached to both end faces of the cylinder, and a rotatable inside of the cylinder. A plurality of vanes provided so as to be able to protrude and retract from the outer peripheral surface of the rotor toward the inner wall of the cylinder, and a compression chamber partitioned and formed by the cylinder, the side block, the rotor, and the vane. With the rotation of the rotor, the volume of the compression chamber repeatedly changes in size due to the rotation of the rotor, and the volume change of the compression chamber causes the suction of the refrigerant gas from the low-pressure section to the compression chamber, the compression of the refrigerant gas in the compression chamber, and In the gas compressor that discharges the refrigerant gas from the compression chamber to the high-pressure part side, leak to the low-pressure part side through the gap between the inner peripheral elliptical short diameter part of the cylinder and the rotor. So as to intersect the flow of the refrigerant gas to and is characterized in that a slit-like groove.

The present invention is characterized in that the slit-like groove is a labyrinth groove that causes a vortex or a turbulent flow in the flow of the refrigerant gas.

The present invention is characterized in that the slit-like groove is provided to be shorter than the width of the contact surface between the inner peripheral elliptical minor diameter portion of the cylinder and the vane.

The present invention is characterized in that the slit-like grooves are formed intermittently in dotted lines.

The present invention is characterized in that the cross-sectional shape of the slit-like groove is a curved shape.

According to the present invention, the cross-sectional shape of the slit-like groove is an involute curve shape in which the curvature gradually decreases along the flow direction of the refrigerant gas which tends to leak to the low pressure portion through the gap between the cylinder and the rotor. It is characterized by the following.

The present invention is characterized in that irregularities are provided at the bottom of the slit-shaped groove.

According to the present invention, the flow of the leaked refrigerant gas changes abruptly at the slit-shaped groove, and a vortex or a turbulent flow is generated in the flow of the leaked refrigerant gas. , The flow of the leaking refrigerant gas in the gap becomes worse, and the amount of the high-pressure refrigerant gas leaking to the low-pressure portion side is greatly reduced.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a gas compressor according to the present invention will be described below in detail with reference to FIGS.

The basic structure of the gas compressor according to the present embodiment, for example, with reference to FIGS. 6 and 7 of a conventional example, shows that the gas compressor has a cylinder 1 having a substantially elliptical inner circumference.
Side blocks 2 and 3 are attached to both end surfaces of the cylinder 1, and a rotor 4 is rotatably mounted horizontally inside the cylinder 1. Of the compression chamber 1 formed by the cylinder 1, the side blocks 2 and 3, the rotor 4 and the vane 9
When the volume of 0 changes due to the rotation of the rotor 4, the change in volume causes the suction of the low-pressure refrigerant gas from the suction chamber 11, which is the low-pressure portion, to the compression chamber 10 via the suction passage 13 and the suction port 14. The compression of the refrigerant gas in the compression chamber 10 and the discharge chamber 12 which is
The discharge of the refrigerant gas to the side and the like are the same as in the related art, so the same members are denoted by the same reference numerals, and detailed description thereof will be omitted.

FIG. 1 is an explanatory view of a main part of an embodiment of a gas compressor according to the present invention, wherein (a) is a sectional view of a cylinder,
(B) is a sectional view taken along line AA in (a), and (c) is an enlarged view of (b). As shown in the figure, in the gas compressor of the present embodiment, the inner peripheral elliptical minor diameter portion 1a of the cylinder 1
Is provided with a slit-shaped groove 20. The slit-shaped groove 20 is disposed particularly in the vicinity of the discharge hole 15 in the inner circumferential range of the cylinder 1 from the discharge hole 15 to the suction port 14. I have.

The slit-shaped groove 20 is used for the flow of the refrigerant gas in the direction indicated by the arrow C in FIG. 1, that is, the gap between the inner circumference elliptical short diameter portion 1a of the cylinder 1 and the rotor 4 (rotor outer diameter gap). ) Is formed so as to intersect the flow of the refrigerant gas which is going to leak to the low pressure portion side of the suction chamber 11 or the like through 19-2, and the vortex 2
1 or a groove that generates turbulence (hereinafter, “labyrinth groove”)
That. ).

Although the number, length, width, depth, cross-sectional shape and the like of the labyrinth groove 20 can be considered variously, these are considered from the viewpoint of whether or not the above-mentioned function of the labyrinth groove 20 can be exhibited more effectively. It can be changed as needed.

In the present embodiment, two labyrinth grooves 20 are arranged side by side in parallel. However, it is considered that two labyrinth grooves 20 can generate a vortex 21 and a turbulent flow more effectively than one. That is because In addition, the length L2 of the labyrinth groove 20 in the present embodiment is set shorter than the width L1 of the contact surface between the inner peripheral elliptical minor diameter portion 1a of the cylinder 1 and the vane 9. This is to prevent the vane tip 9a from jumping up by being caught in the labyrinth groove 20.
Further, the cross-sectional shape of the labyrinth groove 20 in the present embodiment is provided so as to have a substantially semicircular curved shape. This utilizes the fact that the refrigerant gas flows in a swirl along the curved shape, and the vortex 2 of the refrigerant gas flows into the labyrinth groove 20.
1 and turbulence are generated effectively.

Next, the operation of the gas compressor having the above-described configuration according to the present embodiment will be described with reference to FIG. 1 and FIGS. 6 and 7.

When the operation of the gas compressor is started, the volume of the compression chamber 10 repeatedly changes due to the rotation of the rotor 4, and the volume of the compression chamber 10 changes. Conventionally, the low-pressure refrigerant gas is sucked into the compression chamber 10 and the refrigerant gas is compressed in the compression chamber 10 and the high-pressure refrigerant gas is discharged from the compression chamber 10 to the discharge chamber 12 when the volume is reduced. (See FIGS. 6 and 7), and a detailed description thereof will be omitted.

By the way, in the gas compressor of the present embodiment, as in the conventional example (see FIGS. 6 and 7), the inside of the compression chamber 10 during the suction process of the low-pressure refrigerant gas as described above has the low-pressure refrigerant gas pressure. Although there is only a considerable pressure, immediately before the discharge of the refrigerant gas, that is, the compression chamber 10 that rotates clockwise while changing its volume around the axis of the rotor shaft 5 approaches the discharge hole 15 and approaches the compression chamber. When the volume of 10 becomes minimum, the pressure in the compression chamber 10 rapidly increases due to the pressure of the high-pressure refrigerant gas compressed due to the volume decrease. For this reason, the compression chamber 1
The high-pressure refrigerant gas in the chamber 0 tries to leak to the low-pressure part side (the suction port 14, the suction passage 13, the suction chamber 11 side) such as the suction chamber 11 via the rotor side gap 19-1 and the rotor outer diameter gap 19-2. However, the leakage amount, particularly the rotor outer diameter gap 19−
The leakage amount of the high-pressure refrigerant gas from 2 to the low-pressure part side is significantly smaller than in the past.

That is, in the gas compressor of the present embodiment, the flow of the high-pressure refrigerant gas that is leaking from the compression chamber 10 to the low-pressure portion through the rotor outer diameter gap 19-2 is crossed. Since the labyrinth groove 20 is arranged, the high-pressure refrigerant gas (hereinafter, also referred to as “leakage refrigerant gas”) that is leaking through such a leakage route must cross the labyrinth groove 20 without fail. However, at this time, the flow of the leaked refrigerant gas changes abruptly in the labyrinth groove 20, and a vortex 21 and a turbulent flow occur in the flow of the leaked refrigerant gas.
And since the vortex 21 and the turbulent flow generated as described above become the resistance of the flow of the leaked refrigerant gas passing through the rotor outer diameter gap 19-2, the rotor outer diameter gap 19-2 moves to the low pressure portion side. Greatly reduces the amount of high-pressure refrigerant gas leakage.

As described above, in the gas compressor according to the present embodiment, the labyrinth groove 20 is employed, so that the space between the two parts of the rotor 4 and the cylinder 1 can be reduced to the low-pressure part side without reducing the production. It is possible to reduce the amount of leakage of high-pressure refrigerant gas, improve the performance of the gas compressor which has been conventionally restricted by this kind of gas leakage, and cause galling and wear due to over-packing between both parts. Can be avoided, and the durability as a compressor is excellent.

The labyrinth groove 20 can be formed as a straight continuous long groove as shown in FIG. 1A, but is not limited to this. As shown in FIG. 3, it can also be formed intermittently in dotted lines. In particular, when the dotted labyrinth groove 20 in FIG. 3 is employed, the contact area between the vane tip 9a and the cylinder elliptical minor diameter portion can be increased, and the vane tip 9a
Can be more reliably prevented from being caught in the labyrinth groove 20.

The cross-sectional shape of the labyrinth groove 20 is not limited to a substantially semicircular curved shape, but may be, for example, a square shape or an involute curved shape as shown in FIG. In this case, the involute curve represents the rotor outer diameter gap 19-2 from the viewpoint of more effectively generating the vortex 21 and the turbulent flow in the leaked refrigerant gas.
It is preferable that the curvature gradually decreases along the flow direction (direction indicated by arrow C in the figure) of the refrigerant gas that is to leak to the low-pressure portion through the flow path. When such a labyrinth groove 20 having an involute cross section is adopted,
Due to the relationship between the rising shape or the winding shape of the involute curve, a stronger vortex 21 or turbulent flow is generated in the leaked refrigerant gas, and the leakage amount of the high-pressure refrigerant gas from the rotor outer diameter gap 19-2 to the low-pressure portion side is reduced. It can be further reduced.

The bottom of the labyrinth groove 20 can be a flat curved surface as shown in FIG. 1 or a flat surface (not shown). In addition, as shown in FIG. Can also be provided. When the labyrinth groove 20 having the unevenness at the bottom is employed, another vortex 22 or a turbulent flow which rolls up along the longitudinal direction of the labyrinth groove 20 is generated due to the relationship with the uneven shape. Is the resistance of the high-pressure refrigerant gas that escapes toward the rotor side gap 19-1 through the inside of the labyrinth groove 20, so that not only the leakage amount of the high-pressure refrigerant gas flowing across the labyrinth groove 20 but also The amount of leakage of the high-pressure refrigerant gas that escapes toward the rotor side gap 19-1 through the labyrinth groove 20 can also be reduced, and the amount of leakage of the high-pressure refrigerant gas to the low-pressure portion can be further reduced.

[0032]

As described above, in the gas compressor according to the present invention, the inner peripheral elliptical minor diameter portion of the cylinder passes through the gap between the inner peripheral elliptical minor diameter portion and the rotor (rotor outer diameter gap) toward the low pressure portion side. A slit-shaped groove is provided so as to intersect the flow of the refrigerant gas to be leaked. For this reason, the flow of the leaked refrigerant gas changes abruptly at the slit-shaped groove, and a vortex or a turbulent flow is generated in the flow of the leaked refrigerant gas. Since it becomes the resistance of the flow of the leaking refrigerant gas passing therethrough, the amount of leakage of the high-pressure refrigerant gas to the low-pressure part side can be greatly reduced as compared to the conventional one, without reducing the space between both parts of the rotor and the cylinder for manufacturing.
It is possible to improve the performance of a gas compressor which has been limited by this type of gas leakage.

[Brief description of the drawings]

FIG. 1 is an explanatory view of a main part of an embodiment of a gas compressor according to the present invention, wherein (a) is a cross-sectional view of a cylinder, and (b).
3A is a cross-sectional view taken along line AA in FIG. 3A, and FIG. 3C is an enlarged view of FIG.

FIG. 2 is an explanatory view of a main part of another embodiment of the present invention.

FIG. 3 is an explanatory view of a main part of another embodiment of the present invention.

FIG. 4 is an explanatory view of a main part of another embodiment of the present invention.

FIG. 5 is an explanatory view of a main part of another embodiment of the present invention;
(A) is a perspective view of the inner circumference of the cylinder, (b) is BB of FIG.
Line sectional view.

FIG. 6 is a sectional view of a conventional gas compressor.

FIG. 7 is a sectional view taken along line CC of FIG. 6;

[Explanation of symbols]

 Reference Signs List 1 cylinder 1a cylinder elliptical minor diameter portion 2 front side block 3 rear side block 4 rotor 5 rotor shaft 6, 7 bearing 8 vane groove 9 vane 9a vane tip 10 compression chamber 11 suction chamber 12 discharge chamber 13 suction passage 14 Inlet port 15 Discharge hole 16 Reed valve 17 Discharge chamber 18 Oil separator 19-1 Rotor side gap 19-2 Rotor outer diameter gap 20 Groove (labyrinth groove) 20a Irregularities at labyrinth groove bottom 21, 22 Eddy current

Claims (7)

[Claims] 1. A cylinder having a substantially elliptical inner periphery, side blocks attached to both end surfaces of the cylinder, a rotor rotatably mounted inside the cylinder, and a cylinder rotatable from an outer peripheral surface of the rotor. A plurality of vanes provided so as to be able to protrude and retract toward the inner wall of the cylinder, and a compression chamber partitioned and formed by the cylinder, the side block, the rotor and the vane, and the rotation of the rotor causes the volume of the compression chamber to change greatly. By repeatedly changing the volume of the compression chamber, the gas compression that sucks the refrigerant gas from the low pressure section side to the compression chamber side, compresses the refrigerant gas in the compression chamber, and discharges the refrigerant gas from the compression chamber to the high pressure section side. The inner peripheral elliptical minor diameter portion of the cylinder crosses the flow of the refrigerant gas leaking to the low pressure portion side through the gap between the inner peripheral elliptical minor portion and the rotor. Gas compressor, characterized in that a preparative-shaped groove. 2. The gas compressor according to claim 1, wherein the slit-shaped groove is a labyrinth groove that generates a vortex or a turbulent flow in the flow of the refrigerant gas. 3. The gas compressor according to claim 2, wherein the slit-shaped groove is provided to be shorter than a width of a contact surface between the inner peripheral elliptical minor diameter portion of the cylinder and the vane. 4. The gas compressor according to claim 2, wherein the slit-like groove is formed intermittently in a dotted line. 5. The gas compressor according to claim 2, wherein a cross-sectional shape of the slit-shaped groove is a curved shape. 6. A cross-sectional shape of the slit-shaped groove is an involute curve shape in which a curvature gradually decreases along a flow direction of a refrigerant gas which tends to leak to a low-pressure portion through a gap between a cylinder and a rotor. The gas compressor according to claim 2, characterized in that: 7. The gas compressor according to claim 2, wherein irregularities are provided at the bottom of the slit-shaped groove.