JPH09137784A - Refrigerant compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent shortening of longevity of a refrigerating cycle device by restraining formation of sludge by restraining progress of abrasion on a contact point of a vane and a piston. SOLUTION: This compressor has a cylinder, a piston 6 rotating along an inner periphery of the cylinder, a vane 7 reciprocally moving in a groove provided on the cylinder with its head end making contact with the piston 6 and bearings 9, 10 to close both end opening parts of the cylinder. Guide grooves are drilled and provided on an end surface of the bearing 9 and an end surface of the piston 6 facing against it, respectively fit and inserted in the guide grooves free to reciprocate, and an Oldham's coupling 18 respective reciprocating sliding surfaces of which are orthogonal with each other is furnished.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant compressor used in a refrigerating cycle for refrigeration and air conditioning, and particularly to improvement of reliability when using a halogen derivative of hydrocarbon as a refrigerant which does not contain chlorine element in its molecular structure. It is about.

[0002]

2. Description of the Related Art Generally, in a rotary compressor, a piston is rotatably fitted in an eccentric crank portion of a shaft, so that the relative speed between the vane and the outer circumference of the piston may increase depending on operating conditions, and the lubrication condition is severe. May be.

[0003]

In the conventional rotary compressor (for example, Japanese Utility Model Publication No. 3-50314), since the piston is rotatably (rotatably) inserted in the crank portion of the shaft, the vane and the piston. The relative speed of the outer circumference may increase depending on the operating conditions, and the lubrication state may become severe. Especially in a refrigerant atmosphere that is a halogen derivative of hydrocarbon and does not contain chlorine element in the molecular structure, the extreme pressure effect of the chlorine compound cannot be expected, so that wear progresses at the contact point between the vane and the outer circumference of the piston, and the worn metal element and the refrigerant. , The so-called mechanochemical reaction in which the organic substances in the lubricating oil are combined becomes remarkable, and a large amount of sludge is generated,
There is a problem in that this sludge adheres to the main part of the refrigeration cycle and deteriorates or stops its function, which significantly shortens the life of the refrigeration cycle device.

A small protrusion is provided on the end face of the piston and an annular groove is provided on the bearing face so that the vane and the piston have zero slip, so that the rotation of the piston is restricted and the sliding loss of the vane and the piston is reduced. A rotary compressor that reduces the load has been proposed (see Japanese Patent Laid-Open No. 4-350379). However, since the size of the annular groove of this rotary compressor is geometrically determined by the dimensions of the components of the compression mechanism, such as the amount of eccentricity of the crank, it is necessary to change the annular groove size by changing the displacement of the compressor. Therefore, there is a problem that productivity is low when a compressor having a plurality of displacements is simultaneously produced. Also, at a crank angle of 0 °, the small protrusion is located at the end of the annular groove on the major axis side. At this time, when the piston revolves along the inner circumference of the cylinder along with the rotation of the shaft, the next moment, for example, crank At an angle of 60 °, the small protrusion can move to either the left or right side of the mechanism. Therefore, depending on the balance of various forces applied to the piston, the small protrusion moves in the tangential direction of the annular groove at the end point on the major axis side of the annular groove. Becomes impossible. As a result, the rotation of the crankshaft pushes the small projections inside the annular groove, and the frictional force at the contact point restrains the revolution of the piston and prevents the rotation of the crankshaft, making it impossible to operate the compressor. There was a problem.

Further, a rotary piston compressor of a swivel motion type, which can apply a force in an axial direction and a radial direction to a swirling cylinder-shaped piston to facilitate sealing and prevent leakage between the cylindrical piston and the cylinder housing. Has been proposed (JP-A-6-288358). However, this rotary motion type rotary compressor requires a large Oldham joint because the inertial force of the rotary member is large and the force applied to the Oldham joint is large. In addition, since the refrigerant gas pressure applied to the orbiting plate during compression is held by the thrust surface of the bearing, the number of sliding points where the gas pressure is applied increases compared to the normal rotary compressor, resulting in increased mechanical loss. There was a problem that the efficiency of the compressor was poor.

The present invention has been made in order to solve the above problems, and means for restraining the rotation of the piston to suppress the wear at the contact portion between the vane and the piston and restraining the rotation of the piston. Provides a high-efficiency, high-productivity refrigerant compressor that does not restrict the revolution of the piston, and is suitable for refrigerants that use hydrocarbon halogen derivatives that do not contain chlorine elements in their molecular structure. The purpose is to do.

[0007]

A refrigerant compressor according to claim 1 reciprocates in a cylinder, a piston rotating along an inner circumference of the cylinder, and a groove provided in the cylinder while its tip is in contact with the piston. Having a vane and a bearing that closes the openings at both ends of the cylinder, a guide groove is bored in the end face of the bearing and the end face of the piston that faces the bearing, and the guide groove is reciprocally fitted and inserted into each of the guide grooves. , And an Oldham coupling in which the respective reciprocating sliding surfaces are orthogonal to each other.

According to a second aspect of the present invention, there is provided the refrigerant compressor according to the first aspect, wherein the guide groove on the end face of the bearing is reciprocable in the tangential direction of the inner diameter of the bearing and is provided at a position where it is opened to the inner diameter portion of the bearing. It is characterized by that.

According to a third aspect of the present invention, in the refrigerant compressor according to the first aspect, the guide groove on the end face of the piston is reciprocally movable in the tangential direction of the inner diameter of the piston, and is formed at a position where it is opened to the inner diameter portion of the piston. It is characterized by that.

According to a fourth aspect of the present invention, in the refrigerant compressor according to the first aspect, the guide groove of the bearing end face is provided in parallel with the reciprocating direction of the vane, and the vane and Oldham coupling are connected to bring the vane and the piston into contact with each other. The feature is that it has been made possible.

According to another aspect of the refrigerant compressor of the present invention, a cylinder, a piston that moves along the inner circumference of the cylinder, a vane that reciprocates in a groove provided in the cylinder while its tip is in contact with the piston, and a cylinder of the cylinder. In a refrigerant compressor having a bearing that closes openings at both ends, a groove linearly bored in a radial direction on one end surface of the piston and one of the end surfaces of the bearing facing the piston, and a groove freely slidable on the other end. It is characterized in that it is provided with a small protrusion that is moved and erected, and that the piston oscillates.

According to a sixth aspect of the present invention, there is provided the refrigerant compressor according to the first or fifth aspect, wherein both the piston and the vane are in contact with each other in a flat shape.

According to a seventh aspect of the present invention, there is provided the refrigerant compressor according to the first or fifth aspect, wherein a refrigerant which is a halogen derivative of hydrocarbon and does not contain chlorine element in its molecular structure is used.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiment 1 FIG. Embodiment 1 of the present invention will be described below with reference to the drawings. 1 is a longitudinal sectional view of a refrigerant compressor according to Embodiment 1 of the present invention, FIG. 2 is a plan sectional view of a compression mechanism portion thereof, FIG. 3 is an exploded perspective view of its essential portion, and FIGS. 2 is a plan view showing the state at crank angles of 0 °, 90 ° and 180 °. In the figure, reference numeral 1 denotes a closed container, and the electric motor 2 and the compression mechanism portion 3 are housed in the closed container 1. The compression mechanism portion 3 is rotated by the cylinder 4 and the electric motor 2 and has a shaft 5 having a crank portion 5a. The shaft 5 is rotatably fitted into the crank portion 5a of the shaft 5 so that the inside of the cylinder 4 is rotated as the shaft 5 rotates. A piston 6 that revolves around the circumference, a vane 7 that reciprocates in a groove 4a formed in the cylinder 4 while its tip is in contact with the piston 6, a spring 8 that presses the vane 7 toward the piston from the back, and The shaft 5 is rotatably fitted on both sides of the cylinder 4 and includes an upper bearing 9 and a lower bearing 10. The upper bearing 9 has an end surface 9a of an end plate integrally formed with the lower bearing 10. Cylinder 4 at end face 10a of plate
Is closed. A suction pipe 11 having a suction muffler 11a is inserted into the suction port 4b of the cylinder 4 from the outside of the closed container 1, and the refrigerant gas guided from the suction pipe 11 into the cylinder 4 is rotated by the shaft 5 as described above. A volume portion formed by a piston 6 that revolves along the inner circumference of the cylinder 4 and a vane 7 that reciprocates in a groove 4a formed in the cylinder 4 while the tip of the piston 6 contacts the contact point 15 at the contact point 15. It is compressed by the volume change of 12, is discharged from the cylinder 4 into the closed container 1 through the discharge port 4c, and is discharged into the refrigeration cycle from the discharge pipe 13 inserted in the closed container 1. Lubricating oil 14 is enclosed in the bottom of the closed container 1 and supplied to each sliding portion in the compression mechanism portion. Reference numeral 18 is an Oldham joint, which has upper and lower claws 18a, 18
b, each of which is reciprocable in a linear groove 19 formed in the end surface 9a of the end plate integrally formed with the upper bearing 9 and a linear groove 20 orthogonal to the groove 19 formed in the end surface of the piston 6. Is fitted to. Also, the piston 6 has a relief surface 6
There is a, and the Oldham coupling 18 is housed between the relief surface 6a and the upper bearing 19 between the end surfaces 9a of the end plates integrated with each other.

Next, the operation will be described. With the above-described configuration, the piston 6 is revolved along the inner circumference of the cylinder 4 in accordance with the rotation of the shaft 5 while the degree of freedom of the rotation direction is restricted by the Oldham coupling 18. That is, the piston 6 makes a turning motion. Therefore, when the rotation speed of the shaft 5 is constant, the relative speed at the contact point 15 between the piston 6 and the vane 7 does not change regardless of the operating conditions, and it is possible to prevent the lubrication state of the contact point 5 from becoming severe. The effect of reducing wear is obtained.

For example, in a conventional rotary compressor having a cylinder inner diameter, a piston outer diameter, and a crank eccentricity ratio of a: b: c, when the piston rotates at a rotation speed of 1 / n times the crank rotation speed. On the other hand, in the compressor of the present embodiment having the same ratio, the relative speed at the contact point 15 between the piston 6 and the vane 7 is given by the following average speed ratio (this embodiment / conventional rotary type). ).
Here, π has a relationship of pi and a = b + c. Speed ratio = {b × arcsin (c / b)} / {b × π
X1 / n} For example, in the case of a: b: c = 10: 9: 1 and n = 5, the speed ratio is 0.18, and the relative speed of the contact portion in this embodiment is lower than that of the conventional rotary. Greatly reduced. Therefore, it is possible to reduce the wear of the contact portion, and it is possible to suppress the generation of sludge due to a so-called mechanochemical reaction in which the worn metal atoms are combined with the refrigerant and the organic matter in the lubricating oil.

Particularly when a halogen derivative of hydrocarbon which does not contain chlorine element in the molecular structure is used as the refrigerant,
Since the extreme pressure effect of the chlorine compound cannot be expected, wear tends to progress at the contact point 15 in the conventional rotary compressor, but the present embodiment has an effect of suppressing wear.

Further, the force applied to the sliding portion of the Oldham coupling 18 is much smaller than the reaction force of the contact portion 15 and does not serve as a starting point for newly generating sludge.

In this embodiment, the Oldham coupling 1 is used.
The number of eight claws is two at the top and bottom, but can be increased or decreased as necessary. Further, although the relief of the Oldham's joint 18 is provided in the piston 6 in this example, it may be provided in the end surface of the end plate of the upper bearing 9.

Embodiment 2 In the above embodiment, the Oldham's joint 18 has a ring-shaped main body with claw-shaped projections on both sides. However, as shown in FIG. 7, the rectangular parallelepiped claw 18 has an end surface 9 a of the end plate of the upper bearing 9. The linear groove 19 formed on the piston and the linear groove 20 formed on the end face of the piston at right angles to the groove 19 may be reciprocally fitted to each other, and the same effect as that of the first embodiment is obtained. Play.

Embodiment 3 8 and 9, the guide groove 19 for the Oldham coupling 18 is formed in a position tangential to the inner diameter of the upper bearing 9, and the guide groove 20 is opened in the inner diameter portion in the tangential direction of the inner diameter of the piston 6. Indicates. According to this embodiment, it becomes easy to supply oil to the sliding portion of the claw portion of the Oldham coupling 18. Further, since the guide groove 19 on the bearing end face is located at the innermost side, a sufficient seal length can be secured without interfering with the seal portion on the piston end face. In addition, in this embodiment, the contact portions of the piston 6 and the vane 7 are both flat. As a result, the contact pressure at the contact portion is reduced, and the effect of reducing wear of the contact portion is further enhanced.

Embodiment 4 In FIGS. 10 and 11, the guide groove 19 of the Oldham coupling 18 is formed in the end surface 9a of the end plate in parallel with the reciprocating direction of the vane 7, and the Oldham joint 18 and the vane 7 are connected by a rigid connecting rod 21. Show. As a result, the state in which the vane 7 and the outer circumference of the piston 6 are in contact with each other can be maintained without the spring 8 that presses the vane from the back of the vane, so that the space in the back of the vane that was conventionally required to attach the spring 8 is unnecessary, and Since there is no size restriction, it is possible to obtain the optimum size in terms of efficiency and reliability, and it is possible to obtain a refrigerant compressor with a high degree of perfection. Here, the connecting rod 21 is a groove 2 formed in the upper bearing 9.
Since the vane 7 and the piston 6 are accommodated in the housing 2, and the contact portions of the vane 7 and the piston 6 are both flat, the groove 22 is always sealed at the vane end surface or the piston end surface regardless of the crank rotation angle. Further, since the contact portion between the vane 7 and the piston 6 is flat, the contact pressure is reduced, and the effect of reducing the wear of the contact portion is further enhanced.

Embodiment 5 The fifth embodiment of the present invention will be described with reference to FIGS. In this embodiment, the groove 2 is linearly formed on the upper end surface of the piston 6 in the piston radial direction.
2 is opened, while a small protrusion 23 is formed on the upper bearing end surface 19a.
The small projection 23 is slidable in the groove 22 with respect to the rotation of the shaft.

In the refrigerant compressor constructed as described above, the piston 6 swings with the rotation of the shaft 5 so as to swing around the small projection 23, and comes into contact with the vane 7 on the outer circumference of the piston 6. The range is limited. Therefore, under constant shaft speed, the piston 6 and the vane 7 are independent of the operating conditions.
The relative speed at the contact point 15 with respect to does not change, and the lubrication state of the contact point 15 can be maintained. In addition, in this embodiment, the portion of the piston 6 that comes into contact with the vane has a flat shape, so that the contact pressure at the contact portion 15 is reduced, and the effect of reducing wear of the contact portion is further enhanced.

Embodiment 6 FIG. In addition, FIG. 14 and FIG.
A groove 2 linearly formed in the cylinder radial direction on the upper bearing end surface 19a
2 is opened, while a small protrusion 2 is formed on the upper end face of the piston 6.
3, the small projection 23 is slidable in the groove 22 with respect to the shaft rotation. Such a mechanism also has the same effect as that of the fifth embodiment.

In the above description, the means for restraining the rotation of the piston according to the present invention, such as the Oldham coupling and the small projection, are all located on the upper end face portion of the piston of the vertical type compressor having one cylinder. However, the present invention is not limited to this, and may be a lower end surface of the piston, a complicated number of cylinders, or a horizontal compressor.

[0027]

The refrigerant compressor according to the first aspect of the present invention comprises a cylinder,
In a bearing having a piston that rotates along the inner circumference of the cylinder, a vane that reciprocates in a groove provided in the cylinder while its tip is in contact with the piston, and a bearing that closes both end openings of the cylinder, The piston is provided with an end face and an Oldham coupling having a guide groove formed in the end face of the piston facing the end face, the guide groove being reciprocally fitted and inserted into each of the guide grooves, and the respective reciprocating sliding faces being orthogonal to each other. By suppressing the progress of wear at the contact portion between the vane and the piston without rotating and without restraining the revolving motion, it is possible to suppress the generation of sludge and prevent the life of the refrigeration cycle apparatus from being shortened.

According to a second aspect of the present invention, there is provided the refrigerant compressor according to the first aspect, wherein the guide groove on the end face of the bearing is reciprocable in the tangential direction of the inner diameter of the bearing and is formed at a position where it is opened to the inner diameter portion of the bearing. With this configuration, it is easy to lubricate the sliding parts of the Oldham's joint and reliability is improved.

According to a third aspect of the present invention, in the refrigerant compressor according to the first aspect, the guide groove on the end face of the piston is reciprocable in the tangential direction of the inner diameter of the piston and is formed at a position where it is opened to the inner diameter portion of the piston. Since the guide groove does not interfere with the seal portion of the piston end face, a sufficient seal length can be secured and a highly efficient refrigerant compressor with less leakage loss during compression can be obtained.

According to a fourth aspect of the present invention, in the refrigerant compressor according to the first aspect, the guide groove of the bearing end face is provided parallel to the reciprocating direction of the vane, and the vane and Oldham coupling are connected to bring the vane and the piston into contact with each other. Since this is possible, a spring for pushing the vane from the back toward the piston is not required, and the space in this part is saved, and the optimum dimensions can be taken in terms of efficiency and reliability.

According to a fifth aspect of the present invention, there is provided a refrigerant compressor in which a cylinder, a piston which moves along the inner circumference of the cylinder, a vane which reciprocates in a groove provided in the cylinder while its tip is in contact with the piston, and a cylinder of the cylinder. In a refrigerant compressor having a bearing that closes openings at both ends, a groove linearly bored in a radial direction on one end surface of the piston and one of the end surfaces of the bearing facing the piston, and a groove freely slidable on the other end. Since it has a small protrusion that moves and stands, and the piston is configured to oscillate,
The range of contact with the vane on the outer circumference of the piston is limited, and by suppressing the progress of wear at the contact point between the vane and the piston, it is possible to suppress the generation of sludge and prevent the shortening of the life of the refrigeration cycle apparatus.

According to a sixth aspect of the present invention, in the refrigerant compressor according to the first or fifth aspect, the portions where the piston and the vane contact each other have a flat shape. By further suppressing the progress, it is possible to suppress the generation of sludge and prevent the life of the refrigeration cycle apparatus from being shortened.

The refrigerant compressor according to claim 7 is the refrigerant compressor according to claim 1 or 5, wherein the refrigerant is a halogen derivative of hydrocarbon and does not contain chlorine element in its molecular structure.
A long-life refrigerant compressor that does not destroy the ozone layer can be obtained.

[Brief description of the drawings]

FIG. 1 is a vertical sectional view of a refrigerant compressor according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view of the compression mechanism portion of the refrigerant compressor according to the first embodiment of the present invention.

FIG. 3 is an exploded perspective view of essential parts of the refrigerant compressor according to the first embodiment of the present invention.

FIG. 4 is a plan view showing a state where the crank angle of the compression mechanism portion of the refrigerant compressor according to Embodiment 1 of the present invention is 0 °.

FIG. 5 is a plan view showing a state where the compression mechanism portion of the refrigerant compressor according to the first embodiment of the present invention has a crank angle of 90 °.

FIG. 6 is a plan view showing a state where the compression mechanism portion of the refrigerant compressor according to Embodiment 1 of the present invention has a crank angle of 180 °.

FIG. 7 is an exploded perspective view of a compression mechanism portion of a refrigerant compressor according to Embodiment 2 of the present invention.

FIG. 8 is an exploded perspective view of a compression mechanism portion of a refrigerant compressor according to a third embodiment of the present invention.

FIG. 9 is a plan view showing a state where a crank angle of a compression mechanism portion of a refrigerant compressor according to a third embodiment of the present invention is 0 °.

FIG. 10 is an exploded perspective view of a compression mechanism portion of a refrigerant compressor according to Embodiment 4 of the present invention.

11A and 11B are a plan view and a sectional view showing a state where a crank angle of a compression mechanism portion of a refrigerant compressor according to a fourth embodiment of the present invention is 0 °.

FIG. 12 is an exploded perspective view of a compression mechanism portion of a refrigerant compressor according to Embodiment 5 of the present invention.

FIG. 13 is a plan view showing a state of crank angles of 0 °, 90 ° and 180 ° of the compression mechanism portion of the refrigerant compressor according to the fifth embodiment of the present invention.

FIG. 14 is an exploded perspective view of a compression mechanism portion of a refrigerant compressor according to Embodiment 6 of the present invention.

FIG. 15 is a plan view showing a state of crank angles of 0 °, 90 ° and 180 ° of the compression mechanism portion of the refrigerant compressor according to the sixth embodiment of the present invention.

[Explanation of symbols]

3 compression mechanism part, 4 cylinder, 6 piston, 7 vane, 8 spring, 9 bearing, 9a end plate end face, 10 bearing, 10a end plate end face, 18 Oldham coupling, 18
a, 18b Claw, 19, 20 Guide groove, 21 Connecting rod.

Claims (7)

[Claims] 1. A cylinder, a piston that rotates along the inner circumference of the cylinder, a vane that reciprocates in a groove provided in the cylinder while its tip is in contact with the piston, and openings at both ends of the cylinder. In a refrigerant compressor having a bearing that closes, a guide groove is bored in the end surface of the bearing and the end surface of the piston that faces the bearing, and the guide groove is reciprocally fitted and inserted into each of the reciprocating members. A refrigerant compressor, comprising: an Oldham coupling having sliding surfaces orthogonal to each other. 2. The refrigerant compression according to claim 1, wherein the guide groove on the end face of the bearing is reciprocally movable in a tangential direction of the inner diameter of the bearing, and is formed at a position opening to the inner diameter portion of the bearing. Machine. 3. The guide groove on the end face of the piston is reciprocable in the tangential direction of the inner diameter of the piston, and is formed at a position opening to the inner diameter portion of the piston.
A refrigerant compressor according to any of the preceding claims. 4. The guide groove on the end face of the bearing is provided in parallel with the reciprocating direction of the vane, and the vane and Oldham coupling are connected so that the vane and the piston can contact each other. Refrigerant compressor. 5. A cylinder, a piston that moves along the inner circumference of the cylinder, a vane that reciprocates in a groove provided in the cylinder while its tip is in contact with the piston, and openings at both ends of the cylinder. In a refrigerant compressor having a bearing that closes the end of the piston, a groove linearly formed in a radial direction on one of the end surface of the piston and the end surface of the bearing facing the end surface, and the other end freely slidable in the groove. A refrigerant compressor, characterized in that it is provided with a small protrusion that moves and is erected, and the piston oscillates. 6. The refrigerant compressor according to claim 1 or 5, wherein both of the portions where the piston and the vane contact each other have a flat shape. 7. The refrigerant compressor according to claim 1, wherein the refrigerant is a halogen derivative of hydrocarbon and does not contain chlorine element in its molecular structure.