JPH0674170A - Rolling piston type rotary compressor - Google Patents

Abstract

PURPOSE:To provide a compressor which exhibits high energy efficien and being highly reliabable concerning friction by feeding oil constantly into a cylinder while maintaining sealing property at the end of a piston. CONSTITUTION:A rolling piston type rotary compressor is a high pressure compressor in which discharge gas is released in a closed container, and an oil sump recess 7b is formed at a position in which three sections comprising a section communicated with a space 7c in a cylinder 8 on at least one of the internal surface of a bearing plate 7a by the rotation of a piston 19, a section closed by the end of the piston 19, and a section communicated with the inner side of the piston 19 are formed by the rotation of the piston 19.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling piston type rotary compressor used in refrigerators and the like.

[0002]

2. Description of the Related Art In recent years, rolling piston type rotary compressors (hereinafter referred to as compressors) have undergone many improvements for high energy efficiency and high reliability.

A conventional compressor will be described below with reference to the drawings. 6 to 7 are disclosed in JP-A-1-170784.
FIG. 6 is a sectional view of the compressor, and FIG. 7 is an enlarged sectional view of an essential part of FIG.

In the figure, an electric element 2 is arranged in the upper part of a closed container 1, and a compression element 3 is arranged in the lower part. The electric element 2 comprises a stator 4 and a rotor 5. The compression element 3 is a shaft 6
And a cylinder 8 sandwiched by a pair of bearing plates 7 holding the shaft 6 and a pair of bearing plates 7, and rotatably fitted to an eccentric part (not shown) of the shaft 6, It is composed of a piston 9 having a taper or a step 11 on the end surface, and a vane 10 pressed by the piston 9 in the cylinder 8 chamber.

Regarding the compressor configured as described above,
The operation will be described below. Refrigerant gas sucked from a suction pipe (not shown) enters the compression element 3 and is gradually compressed by the rotation of the piston 9 to become a high pressure, and then passes through a valve (not shown) to form a high pressure sealed type container. It is discharged into the container 1, and further discharged from a discharge pipe (not shown) to a cycle (not shown).

Further, the oil conveyed by the oil supply pump (not shown) provided on the shaft 6 lubricates the shaft 6 system, but a part of the oil is a high pressure gas in the closed container 1 and a low pressure in the cylinder 8. After entering the cylinder 8 due to the pressure difference with the gas and lubricating the sliding parts of the piston 9 and the vane 10, they are discharged together with the refrigerant gas into the high-pressure closed container 1 from a valve (not shown). At this time, since the seal width of the piston end surface is narrowed by the taper or the step, the oil necessary for lubricating the cylinder 8 is sufficiently secured.

[0007]

However, in the above-mentioned conventional structure, due to the structural problem of ensuring the oil supply into the cylinder by narrowing the seal width of the piston end face, the low pressure from the high pressure chamber in the cylinder is reduced in the compression process. Refrigerant gas easily leaks into the chamber, reducing energy efficiency. In addition, in order to improve energy efficiency, it is necessary to widen the seal width of the piston end face, and it is not possible to sufficiently lubricate the inside of the cylinder.Furthermore, due to variations in the clearance between the piston and the bearing plate There is a problem in that the reliability is drastically reduced because the amount of variation is very large.

The present invention solves the problems of the prior art, and by ensuring a sufficient seal width at the end face of the piston, it is possible to achieve high energy efficiency and to quantitatively supply oil to the cylinder. The purpose is to obtain a highly manufactured compressor.

[0009]

In order to achieve this object, a compressor of the present invention is provided with a piston communicating with a cylinder inner space of at least one inner surface of a bearing plate or a high pressure chamber of the cylinder inner space of a piston by rotation of the piston. The oil sump recess is formed at three positions, that is, a section closed by the end surface of the piston and a section communicating with the inside of the piston.

In order to achieve this object, the compressor of the present invention has a section in which at least one inner surface of the bearing plate communicates with a high pressure chamber of the cylinder inner space or the cylinder inner space by the rotation of the piston, and the end surface of the piston. The groove-shaped oil sump concave portion is formed into three sections, a section closed by (1) and a section communicating with the inside of the piston.

[0011]

In the compressor of the present invention, the oil sump recess is located inside the piston by one rotation of the shaft during operation, and the oil inside the piston is supplied, and the end sump of the piston closes the oil sump recess. The oil that has accumulated in the depletion oil sump recess remains held in the oil sump recess, and the oil sump recess is located outside the piston so that the oil flows out from the oil sump recess to the cylinder internal space. Since the amount of oil that is proportional to the volume of the oil sump recess per rotation of the machine can be supplied to the cylinder internal space regardless of the pressure condition and regardless of the seal width of the piston end surface, high energy efficiency is achieved. A highly reliable compressor can be obtained. When the oil sump recess is provided on the high pressure chamber side, the oil is supplied into the cylinder after the start of compression, so that the volumetric efficiency does not decrease, so that a compressor with higher energy efficiency can be obtained.

Further, even in a compressor in which the thickness of the piston is larger than twice the amount of eccentricity of the shaft, by forming a groove-shaped oil reservoir recess on the inner surface of the bearing plate, the oil can be rotated by the rotation of the piston. One end of the sump recess communicates with the inside of the piston, and the oil inside the piston is supplied, and the oil sump recess is blocked by the end face of the piston and the oil accumulated in the sump recess is retained in the sump recess. As it is, and one end of the oil sump recess communicates with the outside of the piston, and oil flows out from the oil sump recess into the cylinder inner space. Therefore, the volume of the oil sump recess per rotation of the shaft by the operation of the compressor A proportional amount of oil can be supplied to the internal space of the cylinder regardless of the pressure condition and regardless of the seal width of the piston end face. The machine can be obtained. When the oil sump recess is provided on the high-pressure chamber side, the oil is supplied into the cylinder after the start of compression, so that the volumetric efficiency does not decrease, so that a compressor with higher energy efficiency can be obtained.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the compressor according to the present invention will be described below with reference to the drawings. It should be noted that the same components as those of the conventional one are designated by the same reference numerals and detailed description thereof will be omitted.

FIG. 1 is a sectional view of a compressor according to a first embodiment of the present invention. FIG. 2 is an enlarged sectional view of a main part of the embodiment. FIG. 3 is an enlarged sectional view of a main part of the same embodiment.

In FIGS. 1, 2 and 3, reference numeral 7b denotes an oil sump recess provided on the inner surface of the bearing plate, which is eccentrically rotated by the piston 19 while the shaft 6 makes one rotation so that the high pressure chamber 7c is provided in the cylinder 8. It is formed at a position that is a section that communicates, a section that is closed by the end surface of the piston 19, and a section that communicates with the inside of the piston 19.

Regarding the compressor configured as described above,
The operation will be described below. When the shaft 6 is rotated by the electric element 2, the refrigerant gas sucked from the suction pipe (not shown) enters the compression element 3 and the piston 19
After being gradually compressed to a high pressure by the rotation of No. 1, it is once discharged into the high-pressure closed container 1, and further discharged from a discharge pipe (not shown) to a cycle (not shown).

The oil carried by the oil supply pump (not shown) provided on the shaft 6 lubricates the shaft 6 system, but a part of the oil is a high pressure gas in the closed container 1 and a low pressure gas in the cylinder 8. After entering into the cylinder 8 due to the pressure difference between the two and lubricating the sliding parts of the piston 19 and the vane 10, they are discharged together with the refrigerant gas into the high-pressure closed container 1 from a valve (not shown).

In this embodiment, the shaft 6 is operated during operation.
By this one rotation, the oil sump recess 7b is positioned inside the piston 19, and in this state, the oil lubricating the shaft 6 system is supplied to the oil sump recess 7b. Next is the piston 19
When the oil sump recess 7b is closed by the end face of the oil, the oil is retained in the oil sump recess 7b. Further, in the state where the oil sump recess 7b communicates with the high pressure chamber of the cylinder 8, the pressure of the oil held in the oil sump recess 7b is higher than the pressure of the refrigerant gas in the high pressure chamber, so the held oil is After being supplied to the high pressure chamber therein, the sliding portions of the piston 19 and the vane 10 are lubricated, and finally discharged like the refrigerant gas into the closed container 1. Therefore, the amount of lubricating oil proportional to the volume of the oil sump concave portion 7b per one rotation of the shaft 6 due to the operation of the compressor is supplied to the high pressure chamber regardless of the pressure condition and the seal width / clearance of the end face of the piston 19 and stable. A lubricated state can be achieved.

Further, since the suction stroke has already been completed when the oil is supplied to the high pressure chamber, the compressor having high energy efficiency can be obtained without lowering the volumetric efficiency.

Next, a second embodiment of the compressor according to the present invention will be described with reference to the drawings. The same components as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.

FIG. 4 is an enlarged sectional view of the essential parts of a compressor according to the second embodiment of the present invention. FIG. 5 is an enlarged sectional view of the essential parts of the same embodiment.

4 and 5, a piston 59 is fitted in the eccentric portion of the shaft 56 and rolls along the inner wall of the cylinder 8. The thickness of the piston 59 is the shaft 56
Is larger than twice the eccentric dimension. 5
Reference numeral 7b denotes a pair of bearing plates for closing both end surfaces of the cylinder 8, and a section communicating with the inner surface of the cylinder 8 by the rotation of the shaft 56, a section closed by the end surface of the piston, and a section communicating with the inside of the piston 59. It has a groove-shaped oil sump concave portion which becomes three sections.

Regarding the compressor configured as described above,
The operation will be described below. The refrigerant gas sucked from the suction pipe (not shown) by the rotation of the shaft 56 by the electric element is introduced into the compression element 3 and the piston 5
It is gradually compressed by the rotation of 9 to become a high pressure, then is once discharged into a high-pressure closed container, and further discharged from a discharge pipe (not shown) to a cycle (not shown).

The oil carried by the hot water supply pump (not shown) provided on the shaft 56 is the shaft 56.
Although the system is lubricated, a part of the oil enters the cylinder 8 due to the pressure difference between the high pressure gas in the closed container and the low pressure gas in the cylinder 8 to lubricate the sliding parts of the piston 59 and the vane 10, and then the refrigerant. Along with the gas, it is discharged into a high-pressure closed container from a valve (not shown).

In this embodiment, the shaft 5 is operated during operation.
By one rotation of 6, one end of the oil sump recess 57b is positioned inside the piston 59, and in this state, the oil lubricating the shaft 56 system is supplied to the oil sump recess 57b.
Next, in the state where the oil sump recess 57b is closed by the end surface of the piston 59, the oil is retained in the oil sump recess 57b. Further, one end of the oil sump concave portion 57b is connected to the cylinder 8
In the state in which the oil is retained in the oil sump recess 57b, the pressure of the oil retained in the oil sump recess 57b is higher than the pressure of the refrigerant gas in the high pressure chamber. Piston 59 after being supplied to the chamber
And, the sliding portion of the vane 10 is lubricated, and finally discharged like the refrigerant gas into the closed container. Therefore, by forming a groove-shaped oil sump recess on the inner surface of the bearing plate, the amount of lubricating oil proportional to the volume of the oil sump recess 57b per one rotation of the shaft 56 due to the operation of the compressor causes the amount of lubricating oil to vary depending on the pressure condition and the end surface of the piston 59. Regardless of the seal width and clearance, it is supplied to the high-pressure chamber, enabling stable lubrication.

Further, since the suction stroke has already been completed when the oil is supplied to the high-pressure chamber, the compressor having high energy efficiency can be obtained without lowering the volumetric efficiency.

[0027]

As described above, according to the present invention, a section where at least one inner surface of the bearing plate communicates with the inner space of the cylinder due to the rotation of the piston, a section where the end surface of the piston is closed, and an inside of the piston. 3 sections of communication
The effect corresponding to claim 1 having the oil sump concave portion at the position of the section is that the oil can be quantitatively supplied to the internal space of the cylinder while maintaining the seal width of the piston end face, so that the compression is highly energy efficient and highly reliable against wear. You have the opportunity.

The present invention is also a rolling piston type rotary compressor in which the thickness of the piston is greater than twice the eccentric dimension of the eccentric portion of the shaft, and at least one of the bearing plates is rotated by the rotation of the piston. Corresponding to claim 3 by having a groove-shaped oil sump concave portion on the inner surface of which is three sections of a section communicating with the cylinder inner space, a section closed by the end surface of the piston, and a section communicating with the inner side of the piston. The effect is that even if the seal width of the piston end face is made sufficiently wide, the oil can be supplied in a fixed amount into the internal space of the cylinder, so a compressor with high energy efficiency and more reliable against wear can be obtained.

[Brief description of drawings]

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

FIG. 2 is an enlarged cross-sectional view of the main part of FIG.

FIG. 3 is an enlarged cross-sectional view of the main part of FIG.

FIG. 4 is an enlarged sectional view of an essential part of a second embodiment of the compressor according to the present invention.

FIG. 5 is an enlarged sectional view of an essential part of a second embodiment of the compressor according to the present invention.

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

7 is an enlarged cross-sectional view of the main part of FIG.

[Explanation of symbols]

 1 Airtight container 2 Electric element 6 Shaft 7a, 57a Bearing plate 7b, 57b Oil sump recess 8 Cylinder 10 Vane 19,59 Piston 56 Shaft

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Go Matsumoto 3-22 Takaidamoto-dori, Higashi-Osaka City, Osaka Prefecture Matsushita Refrigerating Machinery Co., Ltd. (72) Inventor Jun Sato 3-22 Takaida-hondori, East Osaka Within Matsushita Cold Machinery Co., Ltd.

Claims (4)

[Claims] 1. A piston which stores oil in a hermetic container and which rolls along a shaft driven by an electric element and an inner wall surface of a cylinder fitted to an eccentric portion provided on the shaft. A vane that contacts the outer peripheral surface of the piston to partition the inner space of the cylinder into a high-pressure chamber and a low-pressure chamber, and a pair of bearing plates that closes both end surfaces of the cylinder. A high-pressure rolling-piston rotary compressor that opens inside, a section in which at least one inner surface of the bearing plate communicates with the cylinder internal space due to rotation of the piston, and a section closed at the end surface of the piston, And a rolling piston type rotary compressor having an oil sump concave portion at a position corresponding to three sections which communicate with the inside of the piston. 2. A section in which at least one inner surface of a bearing plate communicates with a high pressure chamber in the cylinder inner space due to rotation of the piston, a section in which the end surface of the piston is closed, and a section in which the piston communicates with the inside of the piston. The rolling piston type rotary compressor according to claim 1, wherein the rolling piston type rotary compressor has an oil sump concave portion at a position. 3. A shaft which stores oil in a closed container and is driven by an electric element, and a piston which is fitted to an eccentric part provided on the shaft and rolls along an inner wall surface of a cylinder. A vane that is in contact with the outer peripheral surface of the piston to partition the internal space of the cylinder into a high-pressure chamber and a low-pressure chamber; and a pair of bearing plates that close both end surfaces of the cylinder, and discharge gas in the closed container. A rolling piston type rotary compressor which is a high-pressure type in which the wall thickness of the piston is larger than twice the eccentric dimension of the eccentric portion of the shaft, and the rotation of the piston causes A groove shape having at least one inner surface, which has three sections: a section communicating with the cylinder inner space, a section closed by the end surface of the piston, and a section communicating with the inner side of the piston. A rolling piston type rotary compressor characterized in that it has an oil sump recess. 4. A section in which at least one inner surface of the bearing plate communicates with a high-pressure chamber in the cylinder inner space due to rotation of the piston, a section closed by an end surface of the piston, and a section communicating with the inside of the piston. 4. The rolling piston type rotary compressor according to claim 3, wherein the rolling piston type rotary compressor has a groove-shaped oil sump recess.