JP4659427B2 - Rolling piston compressor - Google Patents

Description

  The present invention relates to a rolling piston compressor, and more particularly to a cylinder structure in the vicinity of a vane groove of a rolling piston compressor.

  In a conventional hermetic compressor of this type, a slit is provided in the vicinity of the vane groove of the cylinder of the compression mechanism portion so as to be parallel to the vane groove and to form a partition wall with the vane groove. As the drive unit is driven, the rollers of the compression mechanism unit rotate to compress the refrigerant in the compression chamber, and the vane is pressed toward the vane groove direction by the pressure of the refrigerant in the high-pressure chamber. Due to the elastic deformation of the partition wall so as to narrow the width of the slit due to the pressing force, occurrence of contact between the vane and the vane groove is reduced (see, for example, Patent Documents 1 and 2).

Japanese Utility Model Publication No. 4-127882 (pages 7 to 10, FIG. 1) JP 61-229984 (2nd page, Fig. 1)

  However, in the conventional compressor, the slit formed in the vicinity of the vane groove of the cylinder and the partition formed by the vane groove are pressed in the slit direction by the compressive load, and are in contact with the upper and lower bearings attached to both end faces of the cylinder. Since the structure is elastically bent, the partition wall and the upper and lower bearings are brought into sliding contact with each other as the compression mechanism is driven, and both contact surfaces of the partition wall and the bearing are worn, resulting in an increase in mechanical loss.

  In addition, due to the slit formed near the vane groove of the cylinder, the partition wall and the upper and lower bearings of the cylinder repeat relative movement with a slight amplitude between the contact surfaces as the compression mechanism is driven. The contact surface is fragile due to surface hardening, and there is a problem of causing fretting wear that reduces fatigue strength.

  Furthermore, since the slit is provided in the vicinity of the vane groove of the cylinder of the compression mechanism portion in a position parallel to the vane groove and forming a partition wall with the vane groove, the vane is moved in the vane groove direction by the high-pressure refrigerant. When pressed against the wall, the partition wall may be deformed or damaged due to insufficient strength. In addition, if the depth of the slit is reduced to ensure strength, the partition wall will not bend sufficiently, so that the contact area can be secured, the piece contact cannot be relaxed, local surface pressure increases, and wear is reduced. There was an increasing problem.

  The present invention has been made to solve the above-described problems. When the compressive load is applied to the vane, the partition formed by the slit and vane groove provided near the vane groove of the cylinder and the upper and lower sides of the cylinder are attached. Sealed compressor that elastically deflects the bulkhead without causing wear on the bearing, prevents contact between the vane and the cylinder, lowers the contact surface pressure, prevents wear of the same part, and improves lubricity The purpose is to obtain.

  It is another object of the present invention to provide a hermetic compressor having a slit arrangement that forms a partition wall having sufficient strength and capable of elastic deformation.

  Another object of the present invention is to obtain a hermetic compressor having a slit that can be easily slit.

A rolling piston compressor according to the present invention includes a compression mechanism portion and a drive portion in a casing, and a compression chamber side and a compression chamber side of a vane disposed in a vane groove of a cylinder that is a component of the compression mechanism portion. When a compressive load is applied to the vane on the opposite side, the cylinder on the side where the vane presses the vane groove has a partition wall between the vane groove and a slit penetrating the cylinder vertically is formed. When a compression load is applied to the vane, in a rolling piston compressor in which both partition walls elastically bend in the vane pressing direction,
The upper and lower end surfaces of both partition walls are provided with clearances from the upper and lower bearings by forming relief grooves on the upper and lower end surfaces of the both partition walls, respectively.

In the rolling piston compressor according to the present invention, when the compressive load is applied to the vane, both partition walls are elastically bent in the pressing direction of the vane to prevent the vane and the cylinder from coming into contact with each other. Reduces wear, prevents wear of the same part, and improves lubricity. In addition, since the upper and lower bearings are provided with gaps on the upper and lower end surfaces of both partition walls, even if both partition walls are bent, the upper bearing and the lower bearing attached to the upper and lower surfaces of the partition walls and the cylinder are not worn.

Embodiment 1 FIG.
1 is a transverse sectional view showing a compression mechanism portion of a rolling piston compressor according to Embodiment 1 of the present invention, FIG. 2 is a longitudinal sectional view showing the same rolling piston compressor, and FIG. Similarly, it is explanatory drawing which shows a deformation | transformation of a partition when a compressive load is applied to the vane of a rolling piston compressor.
In these drawings, a rolling piston compressor 1 which is a hermetic compressor is a driving unit in a casing 2 that is a hermetic container, and is connected to the electric motor 4 composed of a rotor 4a and a stator 4b and the driving unit. The compression mechanism part is accommodated.
The stator 4 a is fixed to the inner peripheral surface of the casing 2, and the rotor 4 b is fixed to the crankshaft 5 at the center of the casing 2.
The crankshaft 5 fixes the rotor 4b, and the lower end portion is connected to the compression mechanism portion.
Lubricating oil 22 is stored at the bottom of the casing 2, and the lower end of the crankshaft 5 is immersed in the lubricating oil 22.

The compression mechanism portion includes a cylinder 7, a roller 8, an eccentric portion 5a of the crankshaft 5, an upper bearing 9, a lower bearing 10, and the like. The cylinder 7 is fixed to the inner wall of the casing 2, and the roller 8 is eccentrically stored in the cylinder 7. The roller 8 is fitted with an eccentric portion 5a of the crankshaft 5 of the drive portion.
An upper bearing 9 is attached to the upper end surface of the cylinder 7, and a lower bearing 10 is attached to the lower end surface, and the upper bearing 9 and the lower bearing 10 provide a space between the inner peripheral surface of the cylinder 7 and the outer peripheral surface of the roller 8. Is formed with a compression chamber 12.
The cylinder 7 is formed with a refrigerant inlet 7 a communicating with the low pressure chamber 12 a of the compression chamber 12. The suction port 7 a communicates with a suction pipe 15 attached to the casing 2.
On the other hand, the eccentric portion 5 a of the crankshaft 5 is fitted into the roller 8, the roller 8 is provided eccentrically with respect to the cylinder 7, and a part of the outer peripheral surface of the roller 8 comes into contact with the inner peripheral surface of the cylinder 7. ing.

Further, the cylinder 7 is formed with a vane groove 7b extending in a radial direction from between a suction port 7a of the compression chamber 12 and a discharge port 7c described later. The vane groove 7b extends from the compression chamber 12 in the radial direction of the cylinder 7 and penetrates the upper and lower surfaces of the cylinder 7. The outer peripheral side of the vane groove 7b is connected to the outer peripheral hole 7d that penetrates the upper and lower surfaces. A vane 14 for separating the compression chamber 12 into a low-pressure side low-pressure chamber 12a and a high-pressure side high-pressure chamber 12b is inserted into the vane groove 7b. The vane 14 is accommodated in the hole 7d from the back. The tip is in contact with the outer peripheral surface of the roller 8.
Further, a discharge port 7c is provided on the high pressure chamber 12b side near the vane 14. The discharge port 7 c communicates with an opening that opens into the internal space of the casing 2. A discharge pipe 25 is attached to the upper part of the casing 2, and the high-temperature and high-pressure refrigerant discharged from the compression mechanism portion into the internal space of the casing 2 is discharged from the discharge pipe 25 to the outside of the compressor.

As shown in FIG. 1, the cylinder 7 is formed with a suction side slit 16 that is a slit and a discharge side slit 17 that is a slit.
The suction side slit 16 is a slit that opens on the inner peripheral surface of the compression chamber 9 of the cylinder 7 between the vane groove 7 b and the suction port 7 a and extends in a direction away from the compression chamber 9. It penetrates vertically. In FIG. 1, the suction side partition wall 19, which will be described later, formed by the vane groove 7 b is extended in such a direction that the front end side on the compression chamber side becomes thinner.
On the other hand, the discharge-side slit 17 is a slit that opens on the inner peripheral surface of the hole 7d that accommodates the spring 14a on the side opposite to the suction-side slit 16 with respect to the vane groove 7b and extends toward the compression chamber 12 side. Similarly, it penetrates the cylinder 7 in the vertical direction. In FIG. 1, it extends in the direction where the front end side on the hole 7d side of the discharge side partition wall 20 to be described later formed by the vane groove 7b becomes narrower.

By forming both slits 16 and 17 in this way, a suction side partition wall 19 which is an elastically deformable partition wall and a discharge side partition wall 20 which is a partition wall are formed between the slits 16 and 17 and the vane groove 7b, respectively. Is done. That is, the suction side partition wall 19 is formed on the vane groove 7b on the side of the compression chamber 12, and the discharge side partition wall 20 is formed on the side of the vane groove 7b away from the compression chamber 12.
Further, the upper bearing side relief grooves are provided in the suction side partition wall 19 so that gaps can be secured on the upper and lower end faces of the both partition walls 19 and 20 so as not to contact the upper and lower bearings 9 and 10 attached to the cylinder 7, respectively. 19a, the lower bearing side relief groove 19b, and the discharge side partition wall 20 are provided with a groove including an upper bearing side relief groove 20a and a lower bearing side relief groove 20b. For example, the depth of the groove, that is, the gap to be formed is set to 0.05 to 0.1 mm.

Next, the operation will be described.
When the rolling piston compressor 1 drives the electric motor 4, this driving force is transmitted to the roller 8 of the compression mechanism through the crankshaft 5, and the roller 8 rotates eccentrically in the cylinder 7. Thereby, the refrigerant gas flows into the low pressure chamber 12a of the compression chamber 12 through the suction port 7a, is compressed in the high pressure chamber 12b, and the high pressure refrigerant gas is discharged from the discharge port 7c to the internal space of the casing 2, and then It is discharged from the discharge pipe 25 to the refrigeration circuit outside the compressor 1.
In the compression process, the vane 14 that protrudes into the compression chamber 12 and separates the low pressure chamber 12a and the high pressure chamber 12b while coming into contact with the roller 8 is caused by the compression load of the high pressure refrigerant (arrow P in FIG. 3). It is pressed in the direction of the groove 7b. That is, the vane 14 by the compressive load P causes the compression chamber 12 side to be in the direction in which the compressive load P is applied (to the right in FIG. 3), and the opposite side (the hole 7d side) from the compression chamber 12 is in the direction in which the compressive load P is applied. Pushed in the opposite direction. The suction-side partition wall 19 and the discharge-side partition wall 20 are elastically bent in the pressing direction as shown in FIG.

Therefore, it is possible to prevent the vane 24 and the vane groove 7b from coming into contact with each other, to prevent wear due to the contact, and to facilitate the movement of the vane 24.
Further, when the suction-side partition wall 19 and the discharge-side partition wall 20 are bent, the upper and lower bearings 9 and 10 attached to the cylinder 7 are formed by the relief grooves 19a, 19b, 20a, and 20b formed on the upper and lower end surfaces, respectively. Does not touch. Therefore, the suction-side partition wall 19 and the discharge-side partition wall 20 do not come into sliding contact with the upper bearing 9 and the lower bearing 10, respectively, so that the suction-side partition wall 19, the discharge-side partition wall 20, the upper bearing 9 and the lower bearing 10 are prevented from being worn. An increase in loss can be prevented.

  Here, the extending direction of the suction side slit 16 and the discharge side slit 17 may be parallel to the vane groove 7b or inclined from the parallel direction. Further, the extension length, slit width, installation position, and the like are such that the partition walls 19 and 20 to be formed are elastically bent due to the size of the vane 14, the size of the compressive load, and the like. Predetermined settings are made so as to prevent contact with the vane groove 7b.

  In the present embodiment, when a compression load is applied to the vane 14 on the compression chamber side and the side opposite to the compression chamber side of the vane 14, the vane 14 presses the vane groove 7 b to the cylinder 7 on the side. The suction-side slit 16 and the suction-side partition wall 19 and the discharge-side slit 17 and the discharge-side partition wall 20 are formed, but the slits 16 and 17 are always provided on both the compression chamber side and the opposite side of the compression chamber side of the vane 14 as described above. The partition walls 19 and 20 do not need to be formed, and even if they are formed on either one, they have the effect of preventing contact. However, in the case of forming in either one, the partition wall 19 (20) is formed with partition relief grooves 19a and 19b (20a and 20b), and a gap between the upper bearing 9 and the lower bearing 10 is formed. Even if (20) is bent, the upper bearing 9 and the lower bearing 10 attached to the upper and lower sides of the partition wall 19 (20) and the cylinder 7 are not worn.

Embodiment 2. FIG.
In the rolling piston compressor 1 of the first embodiment, the suction side slit 16 and the discharge side slit 17 are provided in the vicinity of the vane groove 7b of the cylinder 7, and the suction side partition wall 19 and the discharge formed between the vane groove 7b and each of them. The relief grooves 19a, 19b and 120a, 205b are provided on the upper and lower end faces of the side partition wall 20, respectively. The direction is specified. Other configurations are the same as those in the first embodiment.

FIG. 4 shows the arrangement of the suction side slit 16 and the discharge side slit 17 provided in the cylinder 7 with respect to the vane groove 7b. In the rolling piston compressor 1 of the present embodiment, as shown in FIG. 4, the extending direction of the suction side slit 16 and the discharge side slit 17 is not parallel to the direction of the vane groove 7b but predetermined from the direction of the vane groove 7b. The angle is tilted. For example, the suction side slit 16 is disposed so as to satisfy X2 / X1 <1.0, and the discharge side slit 17 is disposed such that Y1 / Y2 <1.0. X1 and X2 are distances from the tip and opening of the suction side slit 16 to the vane groove 7b, respectively. Y1 and Y2 are vanes from the tip and opening of the discharge side slit 17, respectively. This is the distance to the groove 7b.
Therefore, the suction-side partition wall 19 and the discharge-side partition wall 20 formed by the suction-side slit 16 and the discharge-side slit 17 respectively have a tapered shape in which the compression chamber 12 and the hole 7d side are narrowed.

  As described above, the suction side partition wall 19 and the discharge side partition wall 20 formed by the suction side slit 16 and the discharge side slit 17, respectively, and the vane groove 7b have a tapered shape in which the front end side of the elastic deformation is narrowed. As shown, the suction-side partition wall 19 and the discharge-side partition wall 20 are formed with less stress with respect to the compressive load applied to the vane 14 than when the slits 16 and 17 are arranged in parallel with the vane groove 7b. Since it can be bent, it is possible to prevent the vane 14 and the cylinder 7 from coming into contact with each other while ensuring the strength of both the partition walls 19 and 20, to reduce the contact surface pressure, and to improve the occurrence of wear and lubricity. Can be planned.

Embodiment 3 FIG.
The rolling piston compressor 1 according to this embodiment is the same as the rolling piston compressor 1 according to the second embodiment, except that the extending directions of the suction side slit 16 and the discharge side slit 17 are made parallel to each other. That is, the extending direction of the suction side slit 16 and the discharge side slit 17 is not parallel to the direction of the vane groove 7b, but is inclined at a predetermined angle from the direction of the vane groove 7b and parallel (shown in FIG. 1).

  As described above, by making the extending direction of the suction side slit 16 and the discharge side slit 17 parallel, in addition to the effect of the second embodiment, the processing phase of the blade during processing becomes the same phase, and the phase of the blade The change time is not required, and the processing time can be shortened.

  The rolling piston compressor 1 according to the first, second, and third embodiments is particularly effective when the refrigerant used is compressed with a high differential pressure such as carbon dioxide.

It is a cross-sectional view which shows the compression mechanism part of the rolling piston type compressor of Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the rolling piston type compressor of Embodiment 1 of this invention. It is explanatory drawing which shows a deformation | transformation of the suction side partition and discharge side partition when a compressive load is applied to the vane of the rolling piston compressor of Embodiment 1 of this invention. It is explanatory drawing which shows the arrangement | positioning with respect to the vane groove of the suction side slit and discharge side slit which were provided in the cylinder of the rolling piston type compressor of Embodiment 2 of this invention. It is explanatory drawing which shows the relationship between the deformation | transformation amount and generated stress of the suction side partition and discharge side partition of the rolling piston type compressor of Embodiment 1 of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rolling piston type compressor, 2 Casing, 7 Cylinder, 7b Vane groove, 9 Upper bearing, 10 Lower bearing, 14 Vane, 16, 17 Slit, 19, 20 Bulkhead.

Claims (7)

Provided with a compression mechanism part and a drive part in the casing,
When a compression load is applied to the vane on the compression chamber side and the side opposite to the compression chamber side of the vane disposed in the vane groove of the cylinder, which is a component of the compression mechanism, the vane presses the vane groove. The cylinder on the side to have a partition between the vane groove, and to form a slit penetrating the cylinder in the vertical direction,
When a compression load is applied to the vane, in the rolling piston type compressor, the both partitions elastically bend in the pressing direction of the vane.
A rolling piston compressor characterized in that clearances are formed on upper and lower end surfaces of the both partition walls by forming relief grooves on the upper and lower end surfaces of the both partition walls, respectively. Provided with a compression mechanism part and a drive part in the casing,
When a compression load is applied to the vane on the compression chamber side of the vane disposed in the vane groove of the cylinder that is a component of the compression mechanism, the cylinder on the side on which the vane presses the vane groove Having a partition wall with the vane groove, forming a slit penetrating the cylinder in the vertical direction;
When a compression load is applied to the vane, in the rolling piston compressor, the partition is elastically bent in the pressing direction of the vane.
A rolling piston compressor, wherein clearances are provided on upper and lower end surfaces of the partition wall by forming relief grooves on the upper and lower end surfaces of the partition wall, respectively. Provided with a compression mechanism part and a drive part in the casing,
A cylinder on the side of the vane that presses the vane groove when a compression load is applied to the vane on the side opposite to the compression chamber side of the vane disposed in the vane groove of the cylinder that is a component of the compression mechanism section In addition, a partition is formed between the vane groove and a slit penetrating the cylinder in the vertical direction is formed.
When a compression load is applied to the vane, in the rolling piston compressor, the partition is elastically bent in the pressing direction of the vane.
Wherein the end faces of the upper and lower partition walls, a rolling piston type compressor, characterized in that a respective upper bearing and the lower bearing and the gap by forming a groove missed the end surfaces of the upper and lower of the partition wall.   The extending direction of the slit is not parallel to the vane groove direction but extends with a predetermined inclination with respect to the vane groove direction. The rolling piston compressor according to the item. Provided with a compression mechanism part and a drive part in the casing,
When a compression load is applied to the vane on the compression chamber side and the side opposite to the compression chamber side of the vane disposed in the vane groove of the cylinder, which is a component of the compression mechanism, the vane presses the vane groove. The cylinder on the side to have a partition between the vane groove, and to form a slit penetrating the cylinder in the vertical direction,
When a compression load is applied to the vane, in the rolling piston type compressor, the both partitions elastically bend in the pressing direction of the vane.
On the upper and lower end surfaces of the both partition walls, a clearance groove is provided on each of the upper and lower end surfaces of the both partition walls to form a clearance with the upper bearing and the lower bearing,
A rolling piston compressor characterized in that the extending direction of both slits is not parallel to the vane groove direction but has a predetermined inclination with respect to the vane groove direction and extends in parallel to each other.   The rolling piston compressor according to any one of claims 1 to 5, wherein the refrigerant used is carbon dioxide.   The size of the said clearance gap is 0.05 mm-0.1 mm, The rolling piston type compressor of any one of Claims 1-6 characterized by the above-mentioned.

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