JPS5847182A - Rotary swash plate compressor - Google Patents

Abstract

PURPOSE:To prevent the shortage of lubricating oil in a radial bearing on the basis of the jet stream of suction gas by providing oil-supply passages opened to a suction gas passage at least passing through a radial bearing from a swash plate chamber. CONSTITUTION:A suction gas passage P is used to conduct a part of the suction gas sucked from a suction pipe passage 29 containing lubricating oil straight to a swash plate chamber 9, while oil-supply passages Q1 and Q2 are opened from the swash plate chamber 9 to the suction gas passage P, and constructed of gaps of thrust bearings 10a and 10b, gaps between shaft insert holes 4a and 4b and a drive shaft 6, and gaps of radial bearings 11a and 11b. Since suction holes 35a and 35b are given negative pressure by the jet stream of the suction gas passing through suction holes 30a and 30b on valve plates 2a and 2b, lubricating oil is sucked from the swash plate chamber 9 via these oil supply passsage Q1 and Q2.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary swash plate compressor that compresses gas such as refrigerant gas, and is particularly useful for improving an oil supply mechanism.

A rotating swash plate compressor is configured so that a piston reciprocates within a cylinder bore as the swash plate, which is fixedly mounted at an angle to the drive shaft, rotates, and performs a compression action in cooperation with the suction and discharge valves. has been done. The drive shaft, together with the swash plate, is rotatably supported by a thrust bearing that receives a load in the thrust direction and a radial bearing that receives a load in the radial direction.

Conventionally, as a mechanism for supplying lubricating oil to the thrust and radial bearings, an oil pump is installed at the shaft end of the drive shaft, and as the drive shaft rotates, the lubricating oil collected in the oil reservoir below the swash plate chamber is pumped out. A so-called oil pump type was used in which oil was forcibly sucked up through an oil supply hole formed in the center of the drive shaft. However, since oil pumps are relatively expensive and require power to drive, oil supply mechanisms that do not use oil pumps have recently come into use.

One of them is a differential pressure type, in which the rotation of the swash plate causes the lubricating oil in the oil pool below the swash plate chamber to be thrown up into oil mist, and the gas in the swash plate chamber mixed with this oil mist is transferred to the swash plate chamber. By utilizing the pressure difference between the oil pressure chamber and the low pressure chamber, oil is supplied through a passage that passes between the thrust bearings, the gap between the drive shaft and the cylinder block, and between the radial bearings and reaches the low pressure chamber. however,
The pressure difference between the swash plate chamber and the low pressure chamber is caused by blow-by gas that enters the swash plate chamber through the gap between the piston and cylinder pore during the discharge stroke of the piston. A sufficient pressure difference cannot be obtained at the initial stage or during low-speed operation. Also,
Since the thrust bearing also revolves as the drive shaft rotates, large resistance due to centrifugal force is applied to the oil mist that attempts to pass between the thrust pair 9/ during high-speed operation. Therefore, due to these factors, there has been a problem in that sufficient lubricating oil cannot be supplied particularly to the radial bearings.

Furthermore, since only the lubricating oil contained in the blow-by gas mentioned above is returned to the oil reservoir below the swash plate chamber, the amount of lubricant discharged into the piping system along with the discharged gas tends to increase, and the amount of lubricating oil that accumulates in the oil reservoir tends to increase. There is a risk that there will be a shortage of lubricating oil, and when used in refrigeration or cold storage, there is a problem that the heat exchange coefficient of the heat exchanger will be deteriorated.

Therefore, in order to solve the above-mentioned problems, the present invention provides a suction gas passage that goes straight from the suction pipe line and guides a part of the suction gas containing lubricating oil to the swash plate chamber, and also connects at least a radial bearing from the swash plate chamber to the swash plate chamber. An oil supply passage is provided which opens into the suction gas passage through the suction gas passage, and lubricating oil on the side of the root chamber is forcibly sucked into the radial bearing by a jet flow of suction gas passing through the suction gas passage, thereby supplying oil to the radial bearing. Provided is a rotary swash plate type compressor having a new oil supply mechanism capable of achieving sufficient fuel efficiency, promoting separation of suction gas and lubricating oil, and preventing leakage of lubricating oil to the outside of the compressor. This is what I am trying to do.

Embodiments of the present invention will be described below with reference to the drawings.

In FIGS. 1 to 4, a pair of cylinder blocks la and lb have pulp plates 2a and 2b on both sides.
The cylinder heads 3a and 3b are fixed and sealed between them. Shaft insertion holes 4a, 4b are formed in the centers of the cylinder blocks la, lb, and pulp plates)
Center holes 5a, 5b are formed in the centers of 2a, 2b corresponding to the shaft insertion holes 4&, 4b, and the cylinder block/l
The a, lbO shaft insertion holes 4a, 4b and the center hole 5aVc drive shaft 6 of the pulp grate 2a on the front side are inserted with a gap therebetween. The front side of this drive shaft 6 protrudes outward from the cylinder head 3a to receive rotational force from a power source, and there is a seal between the drive shaft 6 and the cylinder head 3a. A device 7 is provided and sealed.

The swash plate 8 is fixed to the drive shaft 6Vc with an inclined position, and is arranged in a swash plate chamber 9 formed in the cylinder blocks la and lb.
An oil reservoir 37 is formed below this swash plate chamber 9. The swash plate 8 and the drive shaft 6 are connected to the boss N8 a of the swash plate 8.
Thrust bearings 10a, 10b provided on both sides of
and radial bearings 11a provided near both ends of the shaft insertion holes 4a and 4b.

11b and is rotatably supported.

The double-acting piston 12 has a hollowed-out central portion, and hemispherical ball pockets 13 a t 13 b i” are formed on opposing surfaces of the hollowed-out portion, and balls are fitted into the ball pockets 13 a and 13 b. 14a, 14
The swash plate 8Vc is engaged with the swash plate 8Vc so as to sandwich both sides of the swash plate 8 via shoes 15a and 15b that engage the balls 14a and 14b. The piston 12 is slidably inserted into three cylinder bores 16 formed in the cylinder blocks la and lb parallel to the drive shaft 6 and at equal intervals in the circumferential direction. .

Therefore, when the drive shaft 6 rotates, the swash plate 8 swings and rotates, and each piston 13 reciprocates within the cylinder bore 16 with a phase difference of one foot.

The cylinder bore 16 is closed at its side ends with the valve plates 2a, 2bK via the suction valve 17, and connected at its center to the swash plate i9&l.

A partition wall 18 is provided on each of the 7 cylinder heads 3a and 3b.
．． a, 18b are formed, and this partition wall 18a.

18bK, low pressures M19a, 19b and high pressures 1zoff, zob are defined in the cylinder heads 3a, 3b, respectively. low pressure chambers 19a, 19b and high pressure chamber 20a,
20b is pulp grade 2a.

Gasket 21a made of metal or rubber coated metal is sandwiched between gasket 2b and cylinder heads 3a and 3b.

21b. and) low pressure 5d
19a and 19b are intake holes 2 formed with valve plates 2a and 2bVc corresponding to each cylinder bore 16;
2 to the cylinder bore 15, and the suction hole 22
are closed by the suction valves 16a and 16b. on the other hand,
The high pressure chambers 20a and 20b are the same (valve play) 2a
, 2b-VC is connected to the cylinder bore 16 through a discharge hole 23 formed, and the discharge hole 23 is connected to the valve plate) 2a
, 2. b, and is closed by a discharge valve 24 provided at the end.

Furthermore, between the low pressure chambers 19a and 19b on both sides and the high pressure chamber 20
A and 20b are connected to the suction communication passage 25 or discharge communication passage 26 formed in the cylinder blocks la and 1b and the communication holes 27a and 27b formed in the valve plates 2a and 2b (β on the discharge communication passage 26 side is not shown). They are communicated through a front side communication hole and a rear side communication hole 27c).

These suction communication passage 25 and exhalation communication passage 26 are formed so as to straddle the swash plate chamber 9, and the swash plate chamber 9 is different from the cylinder blocks la, 1. Partition walls 28a and 28b formed in b
It is separated by

The suction gas passage P directs a portion of suction gas containing lubricating oil sucked from the suction pipe line 29 straight into the swash plate chamber 9.
A suction hole 30a formed in 'b.

30b, a part of the suction communication passage 25, and through holes 31a, 31b formed in the partition walls 28a of the cylinder blocks la, lb on extensions of the suction holes 30a, 30b of the lubricating grates 2a, 2b. The suction hole 3Qb of the rear valve plate 2b is connected to the suction pipe 29.
This suction pipe line 29 is connected to a low pressure chamber 19'' in a suction joint 32 provided in the rear cylinder head 3b.
It is partitioned into b. On the other hand, on the front side)
The suction hole 30a of the compressor 2a is open to the low pressure [19a]. Note that the front side suction holes 30a have the same function as the communication holes 27a, so they may be grouped into 11 holes.

The discharge pipe line 33 is formed in a discharge joint part 34 provided in the rear cylinder head 3b, and is connected to a high pressure "4" on the rear side.
Connected to 2ob.

The oil supply passages Q, , Q2 open from the swash plate chamber 9 to the suction gas passage P, and in this embodiment, the oil supply passages Q, , and Q2 open from the swash plate chamber 9 to the suction gas passage P. Gap, radial bear 1 long lla, llb
gap,) between the center hole 5a of the cooling grate 2a and the drive shaft 6
The gap or hole (the center hole 5b of the rub plate 2b,
and JL35a for suction described below.

35b.

The suction holes 35a and 35b are in the valve plate 2a.

Grooves 36 formed in the valve plates 2a, 2b are provided to communicate the center holes 5a, 5b of the valve plates 2b with the suction holes 30a, 30b, as shown in detail in FIG.
a, 36 bT said gas cap/nod 21a.

21b. Therefore, the suction holes 35a, 35 are
Since b becomes negative pressure, this oil supply path Q,, Q
2 through lubricating oil power; suction 1 to 5. In addition, as another example, a suction hole 35a.

35b may be formed by making a hole in the pulp plates 2a, 2b, and as long as it opens into the suction gas path P, the ejection effect by the jet flow of suction gas can be obtained. It is also possible to form it on the cylinder head 3a, 3b side.

In the above configuration, when the drive shaft 6 rotates, the swash plate 8 swings and rotates, the piston 12 reciprocates within the cylinder bore 16, and the suction valve 17 and discharge valve 24 alternately open and close. to perform the compression action.

Explaining the flow of gas and lubricating oil at this time step by step, the suction gas containing the lubricating oil in a mist state first flows from the suction pipe 29 through the suction hole 30b of the pulp play (2b) to the rear of the suction communication path 25. There's someone in the room on the side. In this suction communication passage 25, one that goes straight and passes through the suction gas passage P, and one that goes straight and passes through the suction gas passage P, and the low pressure chambers 19a and 19bi on the front side and the rear side.
Divided into C. The suction gas that passes through the suction gas path P and reaches the swash plate chamber 9 contains a large amount of lubricating oil because it is difficult for the lubricating oil in a mist state to change direction, and the lubricating oil rotates within the swash plate chamber 9. It hits the swash plate 8 and is separated from the intake gas. The separated lubricating oil, together with the lubricating oil thrown up from the oil reservoir 37 by the rotation of the swash plate 8, flows into the suction holes 35a of the oil supply paths Q, Q2.

35b is under negative pressure due to the jet flow of suction gas, part of it is supplied to the thrust bearings 1'Oa and 10b and the radial bearings lla and llb through the oil supply passages Q, , and Q2, and the remaining lubrication is The oil is returned to the oil reservoir 31C.

On the other hand, the suction gas that has entered the low pressure m19a, 19b is sucked into the cylinder bore 16 through the suction holes 22 of the pulp plates 2a, 2b, and is compressed.
, 2b are temporarily stored in the high pressure chambers 20a, 20b, and discharged from the discharge pipe line 33. This discharged gas is the one after the lubricating oil has been separated as described above, and contains a small amount of lubricating oil from the pan.

As described above, according to the present invention, there is provided a suction gas passage which goes straight from the suction pipe and leads a part of the suction gas containing lubricating oil to the swash plate, and also passes through at least the radial bearing from the swash plate chamber. Since the oil supply passage is provided which opens into the suction gas passage, the lubricating oil in the swash plate chamber is forcibly sucked and supplied to the radial bearing via the oil supply passage due to the ejection effect of the jet flow of suction gas passing through the suction gas passage. ,
Therefore, it is possible to prevent the radial bearing from running out of lubricating oil. In addition, since the lubricating oil in the suction gas is separated from the suction gas in the suction gas path and the swash plate chamber, the amount of lubricant discharged can be reduced, ensuring a sufficient amount of lubricating oil in the oil reservoir, and cooling, This has advantages such as being able to improve the thermal efficiency of the heat exchanger of the cooling cycle.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing a rotary swash plate compressor of the present invention;
Figure 2 is a cross-sectional view taken along line A-A in Figure 1, and Figure 3 is B in Figure 1.
-B sectional view, Figure 4 is a C-C sectional view of Figure 3,
The figure is an enlarged sectional view of the main parts of the same as above. 1atlb...Fist cylinder block, 2a, 2b00.
Pulp plate, 4a, 4b @ shaft insertion hole, 5a, 5
b...O center hole, 6...drive shaft 18@...swash plate, 9
@e * Swash plate chamber, 10a, 10b・Fist・Thrust bearing, lla, llb・・Fist radial bearing, 1
9a, 19b...low pressure chamber, 21a, 7:,
l bO@ 11 gasket, 25... suction communication path,
28a, 28kl... partition wall, 29... suction pipe line,
30a, -30b... Suction hole, 31a131b@;6
Through holes, 35a, 35b...suction holes. Figure 1 1.7> B, a No. 211 6

Claims (1)

[Scope of Claims] 1. A suction gas path is provided that goes straight from the suction pipe and leads a portion of the suction gas containing lubricating oil to the swash plate chamber, and at least a swash plate disposed in the swash plate chamber is provided from the swash plate chamber. A rotary swash plate compressor, characterized in that an oil supply path is provided that opens into the suction gas path through a radial bearing that rotatably supports a fixed drive shaft. 2. The suction gas path includes a suction hole formed in at least one pulp plate, and a suction connection connected to the suction hole and formed in the cylinder block so as to communicate between the low pressure chambers located on both sides of the cylinder block. a passage, and a through hole formed on a partition wall that partitions the suction communication passage and the swash plate chamber as an extension of the suction hole of the pulp grate,
2. The rotary swash plate compressor according to claim 1, wherein a suction pipe is connected to the suction hole of said one pulp plate. 3. The oil supply path consists of the gap between the thrust bearings provided on both sides of the swash plate, the gap between the drive shaft and the shaft insertion hole of the cylinder block into which the drive shaft is inserted, the gap between the radial bearing, and the shaft. Consisting of a center hole formed in the pulp plate corresponding to the insertion hole or a gap between the center hole and the drive shaft, and a suction hole that communicates the center hole of the pulp plate with the suction hole of the pulp plate. A rotating swash plate compressor according to claim 1 or 2, characterized in that: