JPH06137291A - Rolling piston type compressor - Google Patents

Abstract

PURPOSE:To improve the efficiency of a compressor by ensuring the feed of oil during rotation at a low speed and reducing a filling amount of lubricating oil. CONSTITUTION:A rolling piston type compressor comprises first and second compression means 4 and 5 coupled in parallel to each other to the drive shaft 32 of a drive means. A centrifugal pump 61 to feed lubricating oil to the rear bearing part 53b of the second compression means 5 and the roller fit-in part 55 is arranged to the one end part of the drive part 32. Further, an auxiliary pump 63 to feed lubricating oil for the roller fit-in part 55 of the second compression means 5 to the end part on the opening 44a side of the roller fit-in part 45 of the first compression means 4 is arranged to the through-part of the opening 44a of the middle plate 44 of the drive shaft 32. In addition, an oil groove 64 through which lubricating oil is fed to the whole of the roller fit-in part 45 and a front bearing part 43b is formed on the opposite load side in the roller fit-in part 45 of the first compression means 4 of the drive shaft 32.

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 compressor provided with two compression means, and more particularly to a measure for supplying lubricating oil.

[0002]

2. Description of the Related Art Generally, some rolling piston type compressors provided in refrigerators and the like are provided with two compression means as disclosed in Japanese Patent Laid-Open No. 1443483/1992. As shown in FIG. 6, this rolling piston compressor has an electric motor housed in a casing and two first compression compressors connected in parallel to the drive shaft (a) of the electric motor, though not shown. The means (b) and the second compression means (c) are housed in the casing.
The first compression means (b) on the upper side is provided with the roller (b2) in the cylinder (b1), the front plate (b3) on the upper end face of the cylinder (b1), and the middle plate on the lower end face. plate
(d) is attached, and the lower second compression means (c) has a roller (c2) disposed in a cylinder (c1) and
A middle plate (d) is attached to the upper end surface of (c1), and a rear plate (c3) is attached to the lower end surface thereof. A front bearing portion (b4) and a rear bearing portion (c4) are formed on the front plate (b3) and the rear plate (c3), and the drive shaft (a) is formed on the both bearing portions (b4, C4). Is inserted and supported. On the other hand, in the center of the roller (b2), the drive shaft
Cams (b6, c6) formed on the roller fitting part (b5, c5) in (a)
Are inserted into the cylinders (b2, c2)
It is arranged eccentrically to 1, c1). Due to this eccentricity, a part of the outer peripheral surface of each roller (b2, c2) is
1, c1) and the above cylinder (b1, c1)
Between the inner peripheral surface of (1) and the outer peripheral surface of the rollers (b2, c2) is the compression chamber (b
7, c7). Furthermore, the above compression chambers (b7, c7)
Although not shown in the figure, the suction passage and the discharge passage of the refrigerant are opened, and the compression chamber (b7, c7) is provided in the cylinder (b1, c1).
Is equipped with a blade that can freely move in and out, and the tip of this blade contacts the outer peripheral surface of the roller (b2, c2)
(b7, c7) is divided into high pressure side and low pressure side. And
Each roller (b2, c2) rolls in the cylinder (b1, c1) by the rotation of the drive shaft (a), compresses the refrigerant flowing into the compression chamber (b7, c7), and then the casing from the discharge passage. Is discharged into the internal space of.

On the other hand, the lower end of the drive shaft (a) is immersed in the lubricating oil (e) stored at the bottom of the casing, and the centrifugal pump is attached to the lower end of the drive shaft (a). (a
1) is provided. Further, an oil supply passage (a2) extending in the axial direction of the drive shaft (a) is formed inside the drive shaft (a), and four branch passages branched from the oil supply passage (a2) are formed.
(a3 to a6) are the above-mentioned rear bearing part (c4) and both roller fitting parts (b5,
It is formed by opening at c5) and the front bearing portion (b4). The rotation of the drive shaft (a) causes the centrifugal pump (a
1) is driven to suck up the lubricating oil (e), and the lubricating oil (e) passes through the oil supply passage (a2) and each branch passage (a3 to a6) and both the rear bearing portion (c4) and Roller fitting part (b5, c5) and front bearing part (b5
4) and are supplied to.

[0004]

In the above rolling piston type compressor, since the lubricating oil (e) is supplied by one centrifugal pump (a1), the pump head cannot be sufficiently secured. There was a case where a shortage of lubricating oil occurred. In other words, in the current rolling piston type compressor, inverter control is performed and operation is controlled from low speed rotation to high speed rotation.On the other hand, since the centrifugal pump (a1) is used as the oil supply pump, at low speed rotation, There was a problem that the centrifugal pump (a1) lacked the pump head and the reliability at low speed rotation was low.

Therefore, in order to solve this shortage of lubricating oil at the time of low speed rotation, conventionally, the filling amount of the lubricating oil (e) in the casing has been increased to ensure sufficient lubricating oil (e). However, when the filling amount of the lubricating oil (e) is increased, the suction gas refrigerant is heated, the heating loss is large, and the volumetric efficiency is low. Furthermore, the above lubricating oil
When the filling amount of (e) is increased, the amount of oil rising increases and the efficiency of the compressor decreases.

The present invention has been made in view of the above problems, and an object thereof is to secure the oil supply at the low speed rotation and to reduce the filling amount of the lubricating oil to improve the efficiency of the compressor. Is.

[0007]

Means for Solving the Problems In order to achieve the above object, the means taken by the present invention is to provide an oil supply means between the first compression means and the second compression means.
Specifically, as shown in FIG. 1, the means taken by the invention according to claim 1 is as follows. First, the driving means (3) is provided in the casing (2).
And a first compression means (4) and a second compression means (5) connected in parallel to the drive shaft (32) of the drive means (3). Further, the first compression means (4) has a roller (42) housed in the cylinder (41), a front plate (43) at one end of the cylinder (41), and a middle plate (44) at the other end. ) Is attached, the second compression means (5) is a cylinder.
The roller (52) is housed in the (51) and the cylinder (5
The middle plate (44) is attached to one end of 1), and the rear plate (53) is attached to the other end. In addition, each of the rollers (42, 52) is a roller fitting portion (45, 55) of the drive shaft (32).
While being eccentrically supported by the front plate (43)
The rear plate (53) has a front bearing portion (43b) and a rear bearing portion (53b) that support the drive shaft (32), and the middle plate (44) has an opening through which the drive shaft (32) passes. (44a) is formed, and it is premised on a rolling piston type compressor in which the compression means (4, 5) compress the fluid.
Then, at one end of the drive shaft (32), the rear bearing portion (53b) of the second compression means (5) and the roller fitting portion near the end are provided.
A first oil supply means (67) for supplying the lubricating oil (11) to (55) is provided. In addition, the second compression means is provided at the penetrating portion of the opening (44a) of the middle plate (44) in the drive shaft (32).
The lubricating oil (11) supplied to the roller fitting part (55) of (5)
A second oil supply means (63) is provided for supplying to the end of the compression means (4) on the side of the opening (44a) of the roller fitting portion (45).
In addition, the roller fitting portion (45) of the first compression means (4) in the drive shaft (32) is provided with lubricating oil (11).
And an oil groove (64) for supplying the oil to the front bearing portion (43b) is formed on the anti-load side.

Further, the means taken by the invention according to claim 2 is that, instead of the first oil supply means (67) in the invention of claim 1, first, one end of the drive shaft (32) is provided with the end. Lubrication oil (11) for supplying the rear bearing portion (53b) of the second compression means (5) and the end portion of the roller fitting portion (55) on the rear bearing portion (53b) side close to the first portion Means (67) are provided. The roller fitting portion of the second compression means (5) on the drive shaft (32)
In (55), a first oil groove (68) for supplying the lubricating oil (11) to the entire roller fitting portion (55) is formed on the anti-load side.

The means taken by the invention according to claim 3 is the same as in the invention according to claims 1 and 2, wherein the drive shaft (32) has an oil supply passage (62) communicating with the first oil supply means (67). ) Is formed in the axial direction, and a branch passage (66c) for supplying lubricating oil (11) to the front bearing portion (43b) of the first compression means (4) is branched from the oil supply passage (62). It has a formed structure.

[0010]

With the above construction, in the invention according to claim 1,
First, when the driving means (3) is driven, this driving force is generated.
The roller (42, 52) of each compression means (4, 5) is transmitted to the (32) and rotates in the cylinder (41, 51). These rollers (42, 52)
By the rotation of the
1) It flows in and is compressed. During this compression operation,
The first oil supply means (67) is driven according to the rotation of the drive shaft (32),
The first oil supply means (67) sucks up the lubricating oil (11) stored in the casing (2), and the lubricating oil (11) fits into the rear bearing portion (53b) of the second compression means (5) and the roller fitting. It is supplied to the joint section (55). On the other hand, with the rotation of the drive shaft (32), the second oil supply means (63) is driven and the oil groove (64) is rotated, and the second compression means is rotated.
The lubricating oil (11) supplied to the roller fitting part (55) of (5) is supplied to the roller fitting part of the first compression means (4) by the second oil supply means (63).
Will be supplied to (45). And the roller fitting portion
The lubricating oil (11) supplied to (45) rises along the oil groove (64) and is supplied to the entire roller fitting portion (45), and at the same time, the first
It is supplied to the front bearing portion (43b) of the compression means (4).

According to the second aspect of the invention, the first oil groove (68) rotates with the rotation of the drive shaft (32), and the first oil groove (68) rotates.
The roller fitting part of the second compression means (5) by the oil supply means (67)
The lubricating oil (11) supplied to (55) is supplied to the entire roller fitting part (55) of the second compression means (5). The lubricating oil (11) supplied to the roller fitting portion (55) is first compressed by the second oil supply means (63) and the second oil groove (64) as in the first aspect. It is supplied to the roller fitting part (45) and to the front bearing part (43b).

Further, in the invention according to claim 3, during the high speed rotation such as the defrost operation, the second oil supply means is provided.
(63) and the oil amount of the lubricating oil (11) supplied from the oil groove (64) decrease, but the first oil supply means (67) through the oil supply path (62) and the branch path (66c) 1 Front bearing part of compression means (4)
Lubricating oil (11) is supplied to (43b).

[0013]

Therefore, according to the invention of claim 1,
A second oil supply means (63) is provided in a portion of the drive shaft (32) which penetrates the opening (44a) of the middle plate (44), and a roller fitting portion (1) of the first compression means (4) of the drive shaft (32) ( Oil groove (64) in 45)
Therefore, even if the amount of the lubricating oil (11) supplied by the first oil supply means (67) decreases at low speed rotation, the roller fitting portion (45) and the front bearing portion (43b) of the first compression means (4) are formed. It is possible to reliably supply the lubricating oil (11). As a result, reliability at low speed rotation can be improved. In addition, it is possible to eliminate the shortage of the lubricating oil (11) during low-speed rotation, so that it is possible to reduce the filling amount of the lubricating oil (11). The loss can be reduced and the volumetric efficiency can be improved. Further, by reducing the filling amount of the lubricating oil (11), the amount of oil rise can be suppressed and the compressor efficiency can be improved.

Further, according to the invention of claim 2,
Since the first oil groove (68) is also formed in the roller fitting portion (55) of the compression means (5), it is possible to reliably supply the lubricating oil (11) as in the first aspect, and at the same time, to perform lubrication. Since the filling amount of the oil (11) can be reduced, the compressor efficiency can be improved. According to the invention of claim 3,
In addition to the second oil supply means (63) and the like, the front bearing portion (43) of the first compression means (4) is supplied from the first oil supply means (67) via the oil supply path (62).
Since the oil is supplied to b), at the time of high speed rotation, the reliable supply of the lubricating oil (11) is ensured even if the amount of the lubricating oil (11) supplied by the second oil supply means (63) decreases. Therefore, the reliability can be further improved.

[0015]

Embodiments of the present invention will now be described in detail with reference to the drawings. As shown in FIG. 1, (1) is a rolling piston type compressor, which is provided in a refrigeration system to compress a refrigerant, and has a casing (2) in which a driving means (3) and a first compression means are provided. (4) and the second compression means (5) are housed and configured. The drive means (3) is an electric motor (31)
And a drive shaft (32) connected to the electric motor (31), the electric motor (31) being disposed above the internal space of the casing (2), and having an inner circumference of the casing (2). It is composed of a stator (33) fixed to the surface and a rotor (34) arranged in the center of the stator (33). The drive shaft (32) has the upper end of the drive shaft (32) as the rotor (34).
The lower end is connected to the center of the casing (2).
Each of the above-mentioned compression means (4, 5) is extended downward and connected. Also, the bottom of the casing (2) should be
While (11) is stored, a discharge pipe (21) connected to a condenser (not shown) is connected to the upper part of the casing (2), and a high temperature and high pressure refrigerant is led from the discharge pipe (21) to the condenser. It has become so.

The above-mentioned both compression means (4, 5) are arranged in parallel vertically, and the first compression means (4) is arranged above and the second compression means (5) is arranged below. The first compression means (4)
As shown in FIGS. 1 to 3, the roller (42) is housed in the cylinder (41) fixed to the casing (2), and the front plate is attached to the upper end surface of the cylinder (41).
(43) has a middle plate (44) attached to the lower end surface, and a space between the inner peripheral surface of the cylinder (41) and the outer peripheral surface of the roller (42) is formed in the first compression chamber (4a). ing. Further, the cylinder (41) is formed with a refrigerant suction passage (41a) opening to the first compression chamber (4a), and the suction passage (41a) has a suction pipe (22).
Are connected. Further, the roller fitting portion (45) of the drive shaft (32) is fitted in the central portion of the roller (42),
A cam (45a) eccentric from the shaft center of the drive shaft (32) is formed in the roller fitting portion (45), and the cam (45a) is formed on the roller (42).
Is rotatably fitted to. The roller (42) is eccentric to the cylinder (41) by the cam (45a),
A part of the outer peripheral surface of the roller (42) is in contact with the inner peripheral surface of the cylinder (41). Further, in the vicinity of the suction passage (41a) in the cylinder (41), a blade (46) is disposed so as to be retractable in the cylinder (41), and the blade (46) is
It is housed in a blade groove (46a) extending in the radial direction of the cylinder (41). And the blade (46) is a spring
The tip end is pressed against the outer peripheral surface of the roller (42) by the spring force of (46b) and the first compression chamber (4a) is divided into a low pressure side and a high pressure side. On the other hand, on the front plate (43),
A discharge passage (43a) is formed near the blade (46).
One end of the discharge passage (43a) is opened to the high pressure side of the first compression chamber (4a), and the other end is opened to the internal space of the casing (2) via a discharge valve (not shown). Further, the front plate (43) is formed with a front bearing portion (43b) for rotatably supporting the drive shaft (32). The front bearing portion (43b) and the drive shaft (32) are provided with a shaft. A spiral groove (43c) for guiding the lubricating oil (11) upward is formed on the sliding contact surface. The drive shaft (32) is attached to the middle plate (44).
Has an opening (44a) formed therethrough.

The second compression means (5) has substantially the same structure as the first compression means (4) described above, and the middle plate (44) is provided at the upper end of the cylinder (51) in which the roller (52) is housed. ) Has a rear plate (53) attached to the lower end,
A second compression chamber (5a) is formed in the (51), and a suction passage (51a) to which the suction pipe (22) is connected is formed in the cylinder (51). On the other hand, in the center of the roller (52), the roller fitting portion (55) of the drive shaft (32) having the cam (55a) is fitted and inserted to support the roller (52). 52) is set in a direction opposite to the eccentric direction of the roller (42) of the first compressing means (4), and the dynamic balance is maintained when the rollers (42, 52) rotate. Also, the second compression means
Also in (5), although not shown, a blade is provided, a discharge passage is provided, and the rear plate (5
The rear bearing (5) that rotatably supports the drive shaft (32)
3b) has been formed.

On the other hand, the drive shaft (32) is provided with an oil supply mechanism (6) which is a feature of the present invention, and the lower end of the drive shaft (32) is stored in the casing (2) as a lubricating oil. It is immersed in (11). The refueling mechanism (6) includes a centrifugal pump (61) and a refueling passage.
(62), an auxiliary pump (63) and an oil groove (64), and the centrifugal pump (61) is provided at the lower end of the drive shaft (32) and is stored in the casing (2). It is soaked in (11) that the lubricating oil (11) is supplied to the oil supply passage (62) by the rotation of the drive shaft (32). The oil supply passage (62) is connected to the drive shaft (3
2) is formed inside, the lower end opens to the lower end of the drive shaft (32) and is continuous with the centrifugal pump (61), and the upper end is located approximately in the center of the front bearing part (43b). Gas vent hole that opens continuously above the front plate (43) at the upper edge of (62)
(65) is formed on the drive shaft (32). Further, the drive shaft (32) has three branch passages (66a) continuous with the oil supply passage (62).
~ 66c) are formed, and the first branch path (66a) is a rear bearing portion.
The second branch (66b) so that it opens at the upper end of (53b).
Is opened in the center of the roller fitting portion (55) of the second compression means (5), and the third branch passage (66c) is connected to the front bearing portion (43b) of the first compression means (4). ) Is formed so as to open at the lower end. Then, the centrifugal pump (61) and the lower end of the oil supply passage (62) and the first and second
The branch passages (66a, 66b) constitute a first oil supply means (67), and the first oil supply means (67) includes a rear bearing portion (53b) of the second compression means (5) and a roller fitting portion (55). ) And the lubricating oil (11).

The auxiliary pump (63) includes a drive shaft (32)
Is attached to the outer peripheral portion of the middle plate (44) located at the opening (44a) of the middle plate (44), and is made of a resin or metal pipe and formed in a spiral shape as shown in FIG. The lower end of the auxiliary pump (63) is the second compression means.
The upper end of the roller fitting part (55) in (5), that is, the cam
The upper end of the auxiliary pump (63) is opened above the (45a) and the upper end is opened below the lower end of the roller fitting part (45) of the first compression means (4), that is, below the cam (45a). Is rotated by the rotation of the drive shaft (32), and the second compression means is generated by centrifugal force.
The lubricating oil (11) supplied to the roller fitting part (55) of (5)
This constitutes a second oil supply means for supplying the roller fitting portion (45) of the compression means (4). On the other hand, the oil groove (64) is the drive shaft (32)
The roller fitting portion (45) of the first compressing means (4) in the non-load side outer peripheral surface of the roller fitting portion (45).
Is formed from the lower end to the upper end. The oil groove (64) is filled with the lubricating oil supplied by the auxiliary pump (63).
(11) is supplied to the entire roller fitting section (45) by the centrifugal force generated by the rotation of the drive shaft (32) and the front bearing section (43
The lubricating oil (11) supplied to the front bearing portion (43b) is supplied to the spiral groove.
It is supplied to the entire front bearing part (43b) via (43c). The centrifugal pump (61) and the oil supply passage (62) are smaller in capacity and diameter than the conventional example (see FIG. 6), that is, the rear bearing portion (53b) of the second compression means (5). ) And the roller fitting part (55) so that the pump head can supply the lubricating oil (11) and the viscosity of the lubricating oil (11) is small at high speed during defrost operation. Since the auxiliary pump (63) and the oil groove (64) lack the lubricating oil (11) and there is a time lag in the auxiliary pump (63) and the like, the first compression means (4) is used during the defrosting operation. It has a pump head capable of supplying the lubricating oil (11) to the front bearing portion (43b) and the roller fitting portion (45).

Next, the rolling piston compressor
The compression operation in (1) will be described. First, when the electric motor (31) is driven, this driving force is transmitted to the drive shaft (32) and the cams (45a, 55a) of the drive shaft (32), and the respective cams (45
a, 55a) rotates and the rollers (42, 52) of each compression means (4,5) rotate in the cylinder (41, 51). These rollers (42, 52)
The rotation of the gas refrigerant causes the gas refrigerant to flow from each suction pipe (22) to each suction passage (41
a, 51a) and flows into the low pressure side of the first and second compression chambers (4a, 5a). After that, with the rotation of the rollers (42, 52),
The low pressure side of each compression chamber (4a, 5a) becomes high pressure, compresses the gas refrigerant, and when this refrigerant pressure reaches a predetermined value, the discharge valve opens due to this refrigerant pressure and the gas refrigerant in the high pressure state is stored in the casing (2). It is discharged into the internal space and then led out to the condenser via the discharge pipe (21).

During this compression operation, the centrifugal pump (61) is driven with the rotation of the drive shaft (32), and the centrifugal pump (61)
Sucks up the stored lubricating oil (11) in the casing (2) and
Supply to (62). Lubricating oil (11) supplied to the oil supply passage (62)
Is a rear bearing portion (53b) of the second compression means (5) and a roller fitting portion (5) mainly through the first and second branch passages (66a, 66b).
Supplied to 5). On the other hand, the auxiliary pump (63) and the oil groove (64) rotate with the rotation of the drive shaft (32), and the lubricating oil supplied to the roller fitting portion (55) of the second compression means (5). (11) is
It is supplied to the roller fitting part (45) of the first compression means (4) by the centrifugal force of the auxiliary pump (63). Then, the lubricating oil (11) supplied to the roller fitting portion (45) rises along the oil groove (64) and is supplied to the entire roller fitting portion (45), and the first compression It is supplied to the front bearing part (43b) of the means (4). Further, the lubricating oil (11) supplied to the front bearing portion (43b) is connected to the spiral groove (43) of the front bearing portion (43b).
Ascends along c) and is supplied to the entire front bearing part (43b), and excess lubricating oil (11) flows out from the upper end of the front bearing part (43b) to the upper surface of the front plate (43). Become.

On the other hand, at the time of high speed rotation, the lubricating oil (11) supplied from the centrifugal pump (61) becomes larger than at the time of low speed rotation, but the capacity of the centrifugal pump (61) and the oil supply passage (62) are increased.
Since the diameter of the oil is set to be small, the roller fitting portion (45) of the first compression means (4) and the front bearing portion from the oil supply passage (62)
The lubricating oil (11) supplied to the (43b) is not so much, and mainly from the auxiliary pump (63) and the oil groove (64) to the roller fitting portion (45) and the front of the first compression means (4). Bearing part (43b)
Is supplied to. Also, during high-speed rotation such as during defrost operation, the viscosity of the lubricating oil (11) may be small, and it may be insufficient to supply the lubricating oil (11) only with the auxiliary pump (63) and oil groove (64). Also, in the initial stage of rotation, there will be a time lag in the supply of the lubricating oil (11) by the auxiliary pump (63) and the oil groove (64), but from the centrifugal pump (61) via the oil supply passage (62). Of the first compression means (4)
Lubricating oil (11) is supplied to 3b).

As described above, according to this embodiment, the drive shaft is
An auxiliary pump (63) is provided in a portion of the (32) which penetrates the opening (44a) of the middle plate (44), and the roller fitting portion (45) of the first compression means (4) of the drive shaft (32) is provided with oil. Since the groove (64) is formed, the lubricating oil (1
Even if the supply amount of 1) is reduced, the lubricating oil (11) can be reliably supplied to the roller fitting part (45) and the front bearing part (43b) of the first compression means (4). As a result, reliability at low speed rotation can be improved. In addition, the lubricating oil (1
Since the shortage of 1) can be eliminated, the filling amount of the lubricating oil (11) can be reduced, so heating of the suction gas refrigerant can be prevented, heating loss is reduced, and volumetric efficiency is improved. Can be made. Furthermore, the lubricating oil (11)
By reducing the filling amount of the oil, the amount of oil rise can be suppressed, and the compressor efficiency can be improved. In addition, the first compression means from the centrifugal pump (61) via the oil supply passage (62).
Since the front bearing (43b) of (4) is lubricated, reliable lubrication (11) is ensured even when the amount of lubrication (11) supplied by the auxiliary pump (63) etc. decreases at high speeds. ), The reliability can be further improved.

FIG. 5 shows a second embodiment. In this embodiment, a second lower oil groove (68), which is a first oil groove similar to the oil groove (64) in the previous embodiment, is provided in the second embodiment. The first compression means formed in the roller fitting portion (55) of the compression means (5) in the previous embodiment.
The oil groove (64) of the roller fitting portion (45) in (4) is an upper oil groove (64) which is a second oil groove. Further, the second branch passage (66b) of the first oil supply means (67) in the first embodiment is formed so as to open below the cam (55a) in the roller fitting portion (55), and the centrifugal pump ( Lubricating oil (11) is supplied to the lower part of the roller fitting part (55) from 61). On the other hand, the lower oil groove (68) is a roller fitting portion (55) of the second compression means (5) of the drive shaft (32), and is formed on the outer peripheral surface on the anti-load side. The joint portion (55) is formed from the lower end to the upper end. The lower oil groove (68) is formed by the centrifugal pump.
Lubricating oil (11) supplied by (61) is configured to be supplied to the entire roller fitting portion (55) by the centrifugal force accompanying the rotation of the drive shaft (32), and the roller fitting portion (55) Lubricating oil (11)
It is supplied to the roller fitting portion (45) of the first compressing means (4) by the auxiliary pump (63). The centrifugal pump (61)
The capacity and the diameter of the oil supply passage (62) are the same as those of the lubricating oil (11) in the second branch passage.
Since it is sufficient to supply from the (66b) to the lower part of the roller fitting portion (55), it is set smaller than that of the first embodiment.

Therefore, according to the present embodiment, the second compression means
Since the lower oil groove (68) is also formed in the roller fitting portion (55) of (5), the lubricating oil (11) can be reliably supplied as in the case of claim 1, and the lubricating oil (11) Since the filling amount of)) can be reduced, the compressor efficiency can be improved.

In this embodiment, the auxiliary pump (63)
Although the centrifugal pump is a spiral tube, the second oil supply means of the present invention is not limited to the spiral tube, and may be a positive displacement pump such as a rotary pump or a trochoid pump.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a rolling piston compressor.

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is an enlarged vertical sectional view of first and second compression means.

FIG. 4 is a perspective view of an auxiliary pump.

FIG. 5 is an enlarged vertical sectional view of first and second compressing means showing a second embodiment.

FIG. 6 is an enlarged vertical sectional view of first and second compression means showing a conventional example.

[Explanation of symbols]

 2 Casing 3 Drive means 4 First compression means 5 Second compression means 6 Lubrication mechanism 11 Lubricating oil 32 Drive shaft 41,51 Cylinder 42,52 Roller 43 Front plate 43b Front bearing part 44 Middle plate 44a Opening 53 Rear plate 53b Rear bearing Part 61 Centrifugal pump 62 Oil supply passage 63 Auxiliary pump (second oil supply means) 64 Oil groove (second oil groove) 66a to 66c Branch path 67 First oil supply means 68 First oil groove

Claims (3)

[Claims] 1. A drive means (3) in a casing (2),
A first compression means (4) and a second compression means (5) connected in parallel to the drive shaft (32) of the drive means (3) are housed, and the first compression means (4) is a cylinder ( A roller (42) is housed in the cylinder (41), a front plate (43) is attached to one end of the cylinder (41), and a middle plate (44) is attached to the other end of the cylinder (41). ) Is configured such that the roller (52) is housed in the cylinder (51), the middle plate (44) is attached to one end of the cylinder (51), and the rear plate (53) is attached to the other end. The above rollers (42, 52) are connected to the roller fitting part (4) of the drive shaft (32).
5, 55) is eccentrically supported, while the front plate (43) and the rear plate (53) have a front bearing portion (43b) and a rear bearing portion (53b) that support the drive shaft (32). The middle plate (44) has an opening (4) through which the drive shaft (32) passes.
4a) is formed and the compression means (4, 5) compresses the fluid in the rolling piston type compressor, wherein one end of the drive shaft (32) has a second end close to the end. A first oil supply means (67) for supplying lubricating oil (11) is provided to the rear bearing portion (53b) of the compression means (5) and the roller fitting portion (55), and the middle plate of the drive shaft (32) is provided. Opening (44) (44
In the penetrating part of a), the roller fitting part of the second compression means (5)
A second oil supply means (63) is provided for supplying the lubricating oil (11) supplied to the (55) to the end of the first compression means (4) on the opening (44a) side of the roller fitting portion (45). The roller fitting portion (45) of the first compression means (4) of the drive shaft (32) is supplied with the lubricating oil (11) over the entire roller fitting portion (45), and the front bearing portion Oil groove to supply (43b)
A rolling piston type compressor characterized in that (64) is formed on the non-load side. 2. A drive means (3) in a casing (2),
A first compression means (4) and a second compression means (5) connected in parallel to the drive shaft (32) of the drive means (3) are housed, and the first compression means (4) is a cylinder ( A roller (42) is housed in the cylinder (41), a front plate (43) is attached to one end of the cylinder (41), and a middle plate (44) is attached to the other end of the cylinder (41). ) Is configured such that the roller (52) is housed in the cylinder (51), the middle plate (44) is attached to one end of the cylinder (51), and the rear plate (53) is attached to the other end. The above rollers (42, 52) are connected to the roller fitting part (4) of the drive shaft (32).
5, 55) is eccentrically supported, while the front plate (43) and the rear plate (53) have a front bearing portion (43b) and a rear bearing portion (53b) that support the drive shaft (32). The middle plate (44) has an opening (4) through which the drive shaft (32) passes.
4a) is formed and the compression means (4, 5) compresses the fluid in the rolling piston type compressor, wherein one end of the drive shaft (32) has a second end close to the end. First to supply lubricating oil (11) to the rear bearing portion (53b) of the compression means (5) and the end portion of the roller fitting portion (55) on the rear bearing portion (53b) side.
An oil supply means (67) is provided, and the lubricating oil (11) is supplied to the roller fitting portion (55) of the second compression means (5) of the drive shaft (32). The first oil groove (68) for supplying the whole is formed on the anti-load side, and the opening (44) of the middle plate (44) in the drive shaft (32) is formed.
In the penetrating part of a), the roller fitting part of the second compression means (5)
A second oil supply means (63) is provided for supplying the lubricating oil (11) supplied to the (55) to the end of the first compression means (4) on the opening (44a) side of the roller fitting portion (45). The roller fitting portion (45) of the first compression means (4) of the drive shaft (32) is supplied with the lubricating oil (11) over the entire roller fitting portion (45), and the front bearing portion Second supply to (43b)
A rolling piston type compressor characterized in that an oil groove (64) is formed on the non-load side. 3. The rolling piston type compressor according to claim 1, wherein an oil supply passage (62) communicating with the first oil supply means (67) is formed in the axial direction inside the drive shaft (32). In addition, the branch passage (66c) for supplying the lubricating oil (11) to the front bearing portion (43b) of the first compression means (4) is formed by branching from the oil supply passage (62). A rolling piston compressor.