JPH1089245A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve durability of a bearing and a shaft without upsizing and increasing the manufacturing cost of a compressor to compress a refrigerant mixed with lubricating oil. SOLUTION: A lubricating oil passage 36 through which a refrigerant sucked in a swash plate chamber 13 is guided to a portion wherein radial bearings 4 and 5 are disposed is formed independently from a suction passage through which fluid sucked in the swash plate chamber 13 is guided to suction chambers 29 and 30. This constitution more reliably guides a refrigerant to radial bearings 4 and 5 compared with a device wherein the lubrication oil passages 36 and 37 are formed in a state to be branched from suction passages 34 and 35. Further, since there is no need to arrange a forced lubrication means for an oil pump and an impeller, upsizing and increased manufacturing cost of a compressor are not necessary.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a compressor, and is effective for use in a refrigeration cycle.

[0002]

2. Description of the Related Art Conventionally, lubricating oil has been mixed with a fluid to be compressed (a refrigerant such as Freon in a refrigeration cycle) as a means for lubricating a movable portion such as a bearing or a sliding surface between a piston and a cylinder. Means are known for lubricating a movable part by sucking and compressing a fluid containing lubricating oil.

Most of the fluid sucked into the compressor is sucked and compressed in a working chamber formed by a piston and a cylinder, and is discharged from the compressor. Therefore,
Since a fluid containing a sufficient amount of lubricating oil cannot be supplied to the bearing, there arises a problem that the durability of the bearing and the shaft supported by the bearing is reduced.

In order to solve this problem, conventionally,
An oil passage for guiding the fluid containing the lubricating oil to the bearing is provided branching from the middle of the suction passage for guiding the fluid sucked from the suction port to the suction chamber for supplying the fluid to the working chamber.

[0005]

SUMMARY OF THE INVENTION By the way, the inventor
When the degree of improvement in the durability of the bearing and the shaft due to the provision of the oil passage was examined by a test, it was not possible to obtain the improvement in durability as calculated in advance. Therefore, the inventor continued research and examination,
The following causes have been found.

That is, the fluid flowing through the suction passage flows into the suction chamber via the suction passage as described above, whereas the fluid flowing through the oil passage reaches the bearing via the suction passage and the oil passage. It flows into the suction chamber through a minute gap between the shaft and the bearing and the shaft. Therefore,
The oil passage system (passage from the suction passage to the suction chamber via the oil passage) has a larger pressure loss than the suction passage, and most of the fluid flows through the suction passage without being diverted toward the oil passage. And flows into the suction chamber. For this reason, when focusing on the lubrication of the bearings, it has been found that the lubrication is substantially equal to that of a compressor having no oil passage.

[0007] To cope with such a cause, an oil pan or the like is provided to store the lubricating oil in the compressor, and the lubricating oil is forcibly lubricated by an oil pump that moves in conjunction with a shaft, or the oil is driven by an impeller. Means such as splashing the lubricating oil in the pan onto the bearing are conceivable. However, these means increase the size of the compressor and increase the manufacturing cost.

In view of the above, it is an object of the present invention to improve the durability of a bearing and a shaft while preventing an increase in the size of a compressor and an increase in manufacturing costs.

[0009]

The present invention uses the following technical means to achieve the above object. Claim 1,
In the inventions described in 3 to 5, the lubricating oil passages (36, 37) for guiding the fluid mixed with the lubricating oil sucked from the suction port (12) to the bearings (4, 5) are provided in the suction port (12). A suction passage (3) for guiding the fluid sucked from the air into suction chambers (29, 30).
4, 35).

[0010] Thereby, the fluid mixed with the lubricating oil is surely applied to the bearings (4, 5) as compared with the case where the lubricating oil passages (36, 37) are branched from the suction passages (34, 35). I can guide you. Therefore, as described in the section of “Problems to be Solved by the Invention”, the lubricating oil passage (36,
The fluid can be surely guided to the bearings (4, 5) by simple means such as forming the 37) independently from the suction passages (34, 35), thereby preventing the compressor from increasing in size and increasing manufacturing costs. Bearing (4, 5) and shaft (1)
Can be improved in durability.

According to the second to fifth aspects of the present invention, the lubricating oil passages (36, 37) for guiding the fluid mixed with the lubricating oil sucked into the swash plate chamber (13) to the bearings (4, 5) are provided. And the fluid sucked into the swash plate chamber (13).
0) is formed independently of the suction passages (34, 35). According to the third aspect of the present invention, the lubricating oil passage (36) on the external drive source side is formed by a through hole communicating with the swash plate chamber (13) from a portion where the bearing (4) on the external drive source side is disposed. And the other end of the lubricating oil passage (37)
Is formed by a groove opened on the bearing (5) side on the other end side.

According to the fourth aspect of the present invention, the lubricating oil passage (3
6, 37) are formed in a portion of the cylinder block (2, 3) near the suction port (12). By the way, as described above, the fluid guided to the bearings (4, 5) flows into the gap (2) having a large pressure loss.
a, 3a) must flow into the suction chambers (29, 30), so that a sufficient amount of the fluid to lubricate the bearings (4, 5) and the shaft (1) flows into the lubrication passages (36, 37). For this purpose, it is necessary to keep the pressure of the refrigerant at the inlet of the lubrication path (36, 37) as large as possible.

On the other hand, according to the present invention, since the lubricating passages (36, 37) are formed near the suction port (12), the pressure of the fluid at the inlet of the lubricating passages (36, 37) is increased. Can be kept large. Therefore, the bearings (4, 5)
Further, since a sufficient amount of fluid for lubricating the shaft (1) can be poured into the lubrication passages (36, 37), the durability of the bearings (4, 5) and the shaft (1) can be further improved. it can.

According to the fifth aspect of the present invention, the lubricating oil passage (3
6, 37) and the number of suction paths (34, 35) are equal to the number of cylinders (82, 83). In addition, the code | symbol in the parenthesis of each said means shows the correspondence with the concrete means of embodiment mentioned later.

[0015]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing an embodiment of the present invention; (Embodiment) FIG. 1 shows an example in which the compressor according to the present embodiment is applied to a swash plate type compressor used in a refrigeration cycle, and the moving parts of the compressor are lubricated in the refrigerant as described above. This is done by mixing the oil.

In FIG. 1, reference numeral 1 denotes a shaft which rotates by obtaining a driving force from an external drive source (vehicle driving engine or the like) via an electromagnetic clutch (not shown).
It is rotatably held by radial bearings 4 and 5 and thrust bearings 6 and 7 provided on the front cylinder block 2 on the external drive source side and the rear cylinder block 3 on the other side, respectively. Here, the radial bearings 4, 5
Are opposed to the load in the vertical direction of the shaft 1, and the thrust bearings 6 and 7 are opposed to the load in the axial direction of the shaft 1.

In addition, between the cylinder blocks 2 and 3 and the shaft 1, suction chambers 29 and 30 to be described later and portions of the cylinder blocks 2 and 3 in which the radial bearings 4 and 5 are disposed are communicated. Gaps 2a, 3a are formed. In the cylinder blocks 2 and 3, cylindrical cylinders 82 and 83 are formed at positions parallel to the shaft 1 and equally divided into five parts in the circumferential direction around the shaft 1. Five cylinders 82 on the side and five cylinders 83 on the rear cylinder block 3 side.
And 10 in total (see FIGS. 3 and 4).

As shown in FIG. 1, the cylinders 82 and 83 have cylindrical piston portions 9 on both front and rear sides in the axial direction.
A double-headed piston 9 having 2, 93 is inserted, and working chambers 982, 983 are formed by the piston portions 92, 93 of the double-headed piston 9 and the two cylinders 82, 83. The double-headed piston 9 is inclined with respect to the shaft 1 by a predetermined amount and rotates integrally with the shaft 1.
The swash plate 10 converts the rotational motion of the shaft 1 into a reciprocating motion to reciprocate the double-headed piston 9 in the two cylinders 82 and 83. A pair of shoes 11 is provided between the swash plate 10 and the double-headed piston 9 so as to swingably connect the two to each other so that the double-headed piston 9 moves smoothly.
Are arranged.

The rear cylinder block 3 has a structure shown in FIG.
As shown in FIG. 3, a suction port 12 for sucking the refrigerant flowing out of an evaporator (not shown) of the refrigeration cycle is formed above the compressor. As shown, lubrication paths 36 and 37 described later are formed. In addition, as shown in FIG.
Is connected to the swash plate chamber 13 in which the swash plate chamber 1 is disposed.
3 is formed on the mating surface of the two cylinder blocks 2 and 3.

A valve plate 1 for closing both cylinders 82 and 83 is provided on the end faces of both cylinder blocks 2 and 3.
4 and 15 are arranged.
The suction ports 4 and 15 are formed with suction ports 16 and 17 and discharge ports 18 and 19 which communicate with the cylinders 82 and 83, respectively. The suction ports 16 and 17 are provided with suction valves 20 and 21 for preventing the backflow of the refrigerant sucked into the working chambers 982 and 983, respectively.
9 is provided with discharge valves 22 and 23 for preventing backflow of the refrigerant discharged from the working chambers 982 and 983. Incidentally, the discharge valves 22 and 23 are provided with valve stop plates (stoppers) 24 and 2
5, the maximum opening is regulated.

The valve plate 14, the suction valve 20 and the discharge valve 22 are sandwiched between the front housing 26 and the front cylinder block 2 and fastened together by bolts 27. Similarly, the valve plate 15,
The suction valve 21 and the discharge valve 23 are sandwiched between the rear housing 28 and the rear cylinder
Has been tightened together.

Also, as shown in FIG.
6 and 28 and the two cylinder blocks 2 and 3
9 to 32 are formed, and the spaces 29 and 30 form a suction chamber for distributing and supplying the refrigerant to the respective working chambers 982 and 983 (hereinafter, the spaces 29 and 30 are referred to as the suction chambers 29 and 30). 31 and 32 are discharge chambers that collect the refrigerant discharged from the working chambers 982 and 983 and guide the refrigerant to a discharge port 33 (see FIG. 2) that discharges the refrigerant toward a condenser (not shown) of the refrigeration cycle. (Hereinafter, the spaces 31, 32 are referred to as discharge chambers 31, 32).

As shown in FIGS. 3 and 4, the refrigerant in the swash plate chamber 13 is supplied to the two cylinder blocks 2 and 3 by the suction chambers 2.
A plurality of suction passages 34 and 35 leading to the swash plate chambers 9 and 30;
A lubricating oil passage 36 that guides the refrigerant in 3 to the radial bearings 4 and 5;
37 (see FIG. 1) is formed at a portion between the cylinders 82 and 83, and the lubricating oil passages 36 and 37
It is formed independently without branching from 4, 35.

The lubricating oil passages 36 and 37 are formed in each of the cylinder blocks 2 and 3, and the suction passages 34 and 35 are formed in each of the cylinder blocks 2 and 3 such that four refrigerant passages are formed. I have. And the front cylinder block 2
The lubricating passage 36 formed in the swash plate chamber 1 extends obliquely to the axial direction of the shaft 1 from the portion where the radial bearing 4 is disposed.
The lubrication passage 37 formed in the rear cylinder block 3 is formed by a through hole communicating with the lubrication passage 3, and is formed by a groove opened to the radial bearing 5 side.

Next, the features of this embodiment will be described. According to the present embodiment, the lubricating oil passages 36 and 37 are
Since it is formed independently without branching from 5,
As compared with the case where the lubricating oil passages 36, 37 are branched from the suction passages 34, 35, the refrigerant can be surely supplied to the radial bearings 4, 5
Can be led to.

Therefore, as described in the section of "Problems to be Solved by the Invention", the lubricating oil passages 36, 37 are separated from the suction passages 34, 35 without providing a forced lubricating means such as an oil pump or an impeller. By simple means such as forming independently without branching, it is ensured that the refrigerant is supplied to the radial bearing 4,
5, it is possible to improve the durability of the radial bearings 4, 5 and the shaft 1 while preventing the compressor from increasing in size and increasing manufacturing costs.

By the way, the refrigerant guided to the radial bearings 4 and 5 passes through the gaps 2a and 3a having a large pressure loss to the suction chambers 29 and 30 as described in the section "Problems to be Solved by the Invention". Since the coolant must flow, the pressure of the coolant at the inlets of the lubrication passages 36 and 37 is kept as high as possible in order to flow the refrigerant into the lubrication passages 36 and 37 in an amount sufficient for lubrication of the radial bearings 4 and 5 and the shaft 1. There is a need.

On the other hand, according to the present embodiment, since the lubricating passages 36 and 37 are formed near the suction port 12, it is possible to keep the refrigerant pressure at the inlets of the lubricating passages 36 and 37 large. it can. Therefore, a sufficient amount of refrigerant for lubrication of the radial bearings 4 and 5 and the shaft 1 is supplied to the lubrication paths 36 and 3.
7, the durability of the radial bearings 4, 5 and the shaft 1 can be further improved.

Further, the suction passages 34 and 35 are
2, 83, the suction passages 34, 35
By flowing the relatively low-temperature refrigerant sucked from the suction port 12 to the cylinders, the cylinders 82 and 83 whose temperatures have increased due to friction with the double-headed piston 9 can be cooled.
Therefore, seizure between the cylinders 82 and 83 and the double-headed piston 9 can be prevented, so that the durability of the compressor can be further improved.

According to the examination and examination by the inventor, in order to improve the durability of the radial bearings 4, 5 and the shaft 1 while exerting the cooling effect of the cylinders 82, 83, the lubricating oil passages 36, 37 are required. And the number of suction passages 34 and 35 are desirably equal to the number of cylinders 82 and 83. In the present embodiment, the lubricating oil passages 36 and 37 are connected to each cylinder block. One cylinder 2 and 3 and four suction passages 34 and 35 are formed in each of the cylinder blocks 2 and 3.

As is apparent from FIG. 1, the dimension L ₁ from the end surface of the front cylinder block 2 on the swash plate chamber 13 side to the lubrication passage 36 is determined by the distance from the end surface of the rear cylinder block 3 on the swash plate chamber 13 side to the lubrication passage 37. is smaller than the dimension L ₂ of the up, lubrication passage 36 can be easily formed through holes by a general purpose drill, such as drilling or machining center.

On the other hand, the lubricating passage 37, the dimension L ₂ dimension L ₁
It is difficult to make a through hole for the lubrication path 37 with a larger, general-purpose drill. On the other hand, according to the present embodiment, since the lubrication passage 37 of the rear cylinder block 3 is formed by the groove opened to the radial bearing 5 side,
The machining can be easily performed by a general-purpose milling machine or the like for machining a keyway or the like without requiring a special drill.

The compressor according to the present invention can also be applied to a so-called swash plate type compressor having a working chamber only at one end in the axial direction. In the above-described embodiment, the suction port 12 is formed on the upper side.
Is not limited to the upper side, and may be in any direction such as a lower direction or a horizontal direction.

[Brief description of the drawings]

FIG. 1 is an axial sectional view of a swash plate type compressor.

FIG. 2 is a view taken in the direction of arrow A in FIG. 1;

3 (a) is a perspective view of a front cylinder block, and FIG. 3 (b) is a view taken in the direction of arrow C in FIG. 3 (a).

FIG. 4A is a perspective view of a rear cylinder block, and FIG. 4B is a view taken in the direction of arrow D in FIG.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Shaft, 2 ... Front cylinder block, 3 ... Rear cylinder block, 4, 5 ... Radial bearing, 6, 7 ...
Thrust bearing, 82, 83 ... cylinder, 9 ... piston,
10 swash plate, 11 shoe, 12 suction port, 13 swash plate chamber, 29, 30 suction chamber, 34, 35 suction path, 36,
37 ... Lubrication path.

Claims (5)

[Claims] A shaft (1) which rotates by obtaining a driving force.
And bearings (4, 4) rotatably supporting the shaft (1).
5), a cylinder block (2, 3) for holding the shaft (1) while holding the bearings (4, 5), and a lubricating oil for lubricating the bearings (4, 5) were mixed. A suction port (12) for sucking fluid into the cylinder block (2, 3); and a plurality of cylinders (82, 82) formed in the cylinder block (2, 3) in parallel with the shaft (1). 8
3), a piston (9) reciprocating in the cylinder (82, 83), and a plurality of working chambers (982, 983) formed by the cylinder (82, 83) and the piston (9). Suction chambers (29, 30) for distributing and supplying the fluid to the cylinder block (2, 3) and the shaft (1)
And a gap (2) formed between the suction chambers (29, 30) and the portion where the bearings (4, 5) are arranged and the suction chambers (29, 30).
a, 3a), a suction path (34, 35) for guiding the fluid sucked from the suction port (12) to the suction chamber (29, 30), and independently of the suction path (34, 35). The fluid formed and sucked from the suction port (12) is supplied to the bearing (4,
A compressor characterized by comprising a lubricating oil passage (36, 37) leading to 5). 2. A shaft (1) rotating by obtaining a driving force from an external drive source, and the shaft (1) at least at two positions of the shaft (1), the external drive source side and the other end side. ) Rotatably supporting the bearings (4, 5) and the cylinder blocks (2, 3) holding the bearings (4, 5) and accommodating the shaft (1); A swash plate (10) inclined at a predetermined angle with respect to the shaft (1) and swinging in association with the rotation of the shaft (1); and a swash plate (2) formed in the cylinder block (2, 3). And a plurality of cylinders (82, 8) formed in the cylinder blocks (2, 3) in parallel with the shaft (1).
3) a lubricating oil that is swingably connected to the swash plate (10) and reciprocates in the cylinders (82, 83), and lubricates the bearings (4, 5). A plurality of working chambers (982, 983) formed by the suction port (12) for sucking the fluid mixed with the fluid into the swash plate chamber (13), the cylinders (82, 83) and the piston (9). Suction chambers (29, 30) for distributing and supplying the fluid to the cylinder block (2, 3) and the shaft (1)
And a gap (2) formed between the suction chambers (29, 30) and the portion where the bearings (4, 5) are arranged and the suction chambers (29, 30).
a, 3a), suction paths (34, 35) for guiding the fluid sucked into the swash plate chamber (13) to the suction chambers (29, 30), and independent of the suction paths (34, 35). The fluid sucked into the swash plate chamber (13) is formed by the bearing (4,
A compressor characterized by comprising a lubricating oil passage (36, 37) leading to 5). 3. The lubricating oil passage (36) on the external drive source side.
Is formed by a through hole communicating with the swash plate chamber (13) from a portion of the external drive source on which the bearing (4) is disposed, and the lubricating oil passage (37) on the other end is connected to the other end. The compressor according to claim 2, wherein the compressor is formed by a groove opened on the side of the bearing (5). 4. The lubricating oil passage (36, 37) is formed in a portion of the cylinder block (2, 3) near the suction port (12).
4. The compressor according to any one of items 3 to 3. 5. The sum of the number of the lubricating oil passages (36, 37) and the number of the suction passages (34, 35) is equal to the number of the cylinders (82, 83). 5. The compressor according to any one of 1 to 4.