JPS6240130Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a swash plate compressor for vehicle air conditioning, and in particular, it provides good lubrication to the internal operating members and sliding surfaces of the compressor to achieve smooth compression even during continuous long-term use. The present invention relates to an improvement in a lubrication device for a swash plate compressor.

The swash plate compressor has a pair of cylinder blocks arranged in the axial direction, and a plurality of double-headed pistons that can reciprocate in accordance with the rotation of the swash plate are inserted into cylinder holes formed in the cylinder blocks. A type of compressor has already been proposed. In this swash plate compressor, the refrigerant gas returned from the refrigeration circuit is mixed with lubricating oil droplets and introduced into the compressor through an inflow hole provided in the cylinder block, and then is introduced into the suction passage formed in the cylinder block. Upon collision with the wall surface, the flow is deflected in two opposite directions in the axial direction, and at this time, oil droplets with high inertia mixed in the refrigerant gas are separated from the refrigerant. The deflected refrigerant gas flow then further enters the relatively large volume oil separation chamber of the cylinder block, where its flow velocity is slowed down, and the remaining oil droplets in the refrigerant gas are now absorbed into the refrigerant under the influence of gravity. configured to be separated from the gas. The refrigerant gas from which the oil has been separated is sucked into the cylinder hole through suction chambers in the cylinder head provided at both ends of the cylinder block, where it is compressed. On the other hand, oil droplets separated from the refrigerant gas are attracted and distributed as a lubricating fluid to the operating members and sliding surfaces within the swash plate compressor, thereby lubricating these members and surfaces. In addition, in this known swash plate compressor, an oil reservoir chamber for storing lubricating oil is formed inside or outside the bottom of the cylinder block, and oil is secured in this oil reservoir chamber when the compressor is not operating. ing.
However, in conventional swash plate compressors that do not have such a forced lubrication mechanism, the lubricating liquid is distributed to the operating members by flowing into the gap provided between the cylinder block and the drive shaft. This method makes it possible to directly and actively supply lubricating oil to operating members such as bearings and sliding surfaces such as swash plates that require lubrication during compressor operation. Therefore, it lacks reliability in preventing burn-in even when used continuously for a long time. In addition, the higher the efficiency of oil separation for the returned refrigerant, the lower the lubricity of the cylinder hole, and this tendency is particularly noticeable for cylinder holes located higher or further away from the valve plate passage hole for suction.

Therefore, the main purpose of the present invention is to provide a lubricating device that can eliminate the above-mentioned drawbacks of conventional swash plate compressors.
A swash plate type compressor that is equipped with a device that can actively supply lubricating oil to the cylinder hole, the steel balls and shoes that connect the swash plate and the piston, without adding any special parts to the conventional swash plate type compressor. The goal is to provide opportunities.

That is, the present invention allows the high-pressure blow-by gas that leaks from the cylinder hole into the swash plate storage chamber when the piston compresses the refrigerant gas to flow into the suction chamber of the cylinder head via the lubricating oil storage chamber, and removes the suction from the oil separation chamber. The blow-by gas collects the lubricating oil that has flowed into the suction chamber from the oil separation chamber into the refrigerant gas sucked into the chamber, and distributes the lubricating oil to each cylinder hole and the operating member.
In addition, a through hole is provided in the partition wall between the swash plate storage chamber and the above suction passage on the central extension of the return refrigerant gas inflow hole opened on the suction passage of the cylinder block, and the opening area is set so that the return refrigerant gas is mixed in the return refrigerant. A portion of the lubricating oil droplets are introduced into the swash plate storage chamber, and after lubricating the steel balls, shoes, etc. that connect the swash plate and the piston in the swash plate storage chamber, the lubricant oil is stored below the cylinder block. It is characterized by the fact that it can be dripped into the chamber to provide comprehensive lubrication inside the compressor. Moreover, the oil droplets introduced into the swash plate storage chamber also have a cooling effect on the internal elements.

Hereinafter, based on the embodiments of the present invention shown in the accompanying drawings,
Explain in detail. In addition, in the attached drawing, the first
5 to 5 relate to the first embodiment of the present invention, and FIGS. 6 and 7 relate to the second and third embodiments of the present invention.

In FIGS. 1 to 5, a pair of cylinder blocks 11a and 11b have three cylinder holes 13.
, oil separation chambers 14a and 14b having a fan-shaped cross section formed between the cylinder holes 13, a discharge chamber 15 for compressed refrigerant gas, an oil reservoir chamber 16 disposed at the bottom, and an oil separation chamber 14a, 14b disposed in the center. A swash plate storage chamber 17 is provided, and a front valve plate 18 is provided at the front and rear ends of the swash plate storage chamber 17.
A pair of cylinder heads 20, 21 are fixed via a rear valve plate 18b, and refrigerant is supplied to both cylinder heads 20, 21 by partition walls 20a, 20b and 21a, 21b protruding from inner surfaces 48, 49, respectively. Gas suction outer chambers 22 and 23 and suction inner chamber 2 communicating with the gas suction outer chambers 22 and 23.
6, 27 and discharge chambers 24, 25 are partitioned. Both valve plates 18a, 18b have through holes 28a, 28b that communicate the oil separation chambers 14a, 14b with the suction outer chambers 22, 23, and discharge chambers 24, 25.
and a through hole (not shown) that communicates with the compressed refrigerant discharge chamber 15, a suction hole 52 that communicates the external suction chambers 22 and 23 with each cylinder hole 13, and a suction hole 52 that communicates between each cylinder hole 13 and the discharge chamber 24 and 25. A discharge hole 29 that communicates with
a, 29b and through holes 30a, 30b that communicate the oil separation chambers 14a, 14b with the suction inner chambers 26, 27.
is installed through it. Cylinder block 11a, 1
A swash plate 33 is stored in the swash plate chamber 17 of 1b and is fixed to a drive shaft 31 with screws or the like, while the drive shaft 31 is connected to the cylinder blocks 11a and 11b.
and needle bearings 32a, 32 extending through the front cylinder head 20 and fitted into both ends of both cylinder blocks 11a, 11b.
It is rotatably supported by b. Swash plate 33
is a double-headed piston 3 slidably inserted into the cylinder hole 13 via a steel ball 35 and a shoe 36.
4, and the cylinder hole 13 is connected to the swash plate 33.
Since the double-headed piston 34 is provided in parallel with the drive shaft 31 of the cylinder hole 13, the double-headed piston 34 reciprocates within the cylinder hole 13 due to the rotation of the swash plate 33. Also piston 3
The axial load generated by the reciprocating motion of the swash plate 33 is applied to both end surfaces of the hub of the swash plate 33, the cylinder block 11a,
Thrust bearing 37 interposed between
a, 37b. Note that the openings 53a and 53b formed in the valve plates 18a and 18b are oil supply holes that communicate the aforementioned suction inner chambers 26 and 27 with the needle bearings 32a and 32b, and the lubricating oil that flows through the oil supply holes 53a and 53b is After lubricating the needle bearings 32a, 32b, the oil flows further into the oil supply passages 39a, 39b, reaches the thrust bearings 37a, 37b, and lubricates them. In addition, 40 is the front cylinder head 2
This is a shaft sealing device provided on the 0 side. Opening passages 41 provided in cylinder blocks 11a and 11b,
42 is an inflow hole for introducing the refrigerant gas returned from the refrigeration circuit to the compressor into the oil separation chambers 14a, 14b, and these inflow holes 41, 42 are connected to the outermost walls 12a, 12 of the cylinder blocks 11a, 11b.
The suction passages 43 and 44, which have relatively narrow grain-shaped cross sections formed by the circumferential surfaces of the partition walls 17a and 17b constituting the swash plate chamber 17, are bored to communicate with the upper portions of the suction passages 43 and 44, respectively. In addition, the above-mentioned suction passage 4
Reference numerals 3 and 44 denote oil separation chambers 14a and 14b formed by outer walls 12a and 12b of cylinder blocks 11a and 11b, side surfaces of partition walls 17a and 17b, and wall surfaces bent along the surrounding circumferential surface of cylinder hole 13, respectively.
connected to. A part of the flow of refrigerant gas mixed with oil droplets flowing from the inflow holes 41 and 42 is divided into the partition walls 17a and 17b that partition the suction passages 43 and 44 and the swash plate chamber 17, and the flow is divided according to the inertia of the flow. Diversion hole 4 that directly enters the swash plate chamber 17
5 and 46 are provided, and their positions are preferably located on extensions of the center lines of the aforementioned inflow holes 41 and 42 in terms of the flow of refrigerant gas, and the opening areas of the branch holes 45 and 46 are As mentioned above, it is sufficient that the refrigerant gas has a sufficient area so that a part of the return refrigerant gas, especially the oil droplets mixed in the refrigerant gas, can enter into the swash plate chamber 17 according to the inertia of the flow. It is. Note that the opening passage 47 shown in FIG.
This is an outflow hole through which the compressed refrigerant gas collected in the discharge chamber 15 from 4 and 25 is led out to the refrigerant circuit of the vehicle. Furthermore, the swash plate chamber 17 has an oil reservoir chamber 16 and a lower partition wall 17.
Through holes 50 and 51 are provided at the lower ends of both sides of the lower partition walls 17c and 17d to spatially communicate the swash plate chamber 17 and the oil reservoir chamber 16 (second (See Figure 3). On the other hand, as shown in FIG. 2, the oil reservoir chamber 16 has grooves 19a, 19b (see FIG. 5) carved on the inner surface downward from the openings 53a, 53b of each valve plate 18a, 18b, and the openings 53a, 53b of each valve plate 18b. The suction inner chambers 26, 2 of the cylinder heads 20, 21 via 53a, 53b.
It is spatially connected to 7. As a result, swash plate chamber 1
7 is also the suction inner chamber 26 of the cylinder head 20, 21,
It will be spatially connected to 27.

Now, when the drive shaft 31 receives driving force from the vehicle and is driven, the swash plate 33 of the compressor rotates, and the compressor enters an operating state in which it performs a compression action. During operation of the compressor, refrigerant gas containing oil particles returned from the refrigeration circuit first flows into suction passages 43 and 44 through inflow holes 41 and 42, respectively, and is diverted through partition walls 17a and 17b above swash plate chamber 17. As mentioned above, a portion of the swash plate chamber 1 collides with the holes 45 and 46 and their vicinity.
7, and the remaining main flow flows through the partition walls 17a, 1
7b. In this way, when the oil fraction is forcibly deflected by colliding with the circumferential surfaces of the partition walls 17a and 17b, the oil fraction mixed in the refrigerant gas is not deflected due to the large inertia and is therefore separated from the refrigerant gas. This separated oil then flows down to the bottom of the oil separation chambers 14a, 14b. The refrigerant gas mixed with the oil droplets that have not been separated at this stage is transferred from the suction passages 43 and 44 to the oil separation chamber 14.
a, 14b. This oil separation chamber 14a, 1
4b has a larger passage cross-sectional area than the suction passages 43 and 44, the flow velocity of the refrigerant gas that has flowed into the oil separation chambers 14a and 14b decreases rapidly, and as a result, no residue remains in the refrigerant gas. Since the oil droplets are heavier than the refrigerant gas component, they are separated from the refrigerant gas by the action of gravity. The separated oil then falls onto the bottom walls of the oil separation chambers 14a, 14b, and then the valve plates 18a, 18.
cylinder head 2 through through holes 30a and 30b of
It flows into the suction internal chambers 26, 27 along the partition walls 20b, 21b of 0, 21. In the suction chamber 26 of the cylinder block 11a, the oil lubricates the shaft sealing device 40, flows into the oil supply passage 53a, lubricates the needle bearing 32a, and then further passes through the oil supply passage 39a to the thrust bearing 37.
Lubricate a. Inside the cylinder block 11b, the needle bearing 32b is lubricated from the suction inner chamber 27 through the oil supply passage 53b, and then the oil supply passage 39b
and lubricates the thrust bearing 37b.

What should be noted in this invention is that, as mentioned above, the swash plate chamber 17, the oil reservoir chamber 16, and the suction chambers 26, 27 of the cylinder heads 20, 21 are spatially connected to each other. During operation, high-pressure blow-by gas, which is inevitable for this type of compressor, leaks into the swash plate chamber 17 from the cylinder hole 13 and enters the swash plate chamber 17 through the through holes 50, 51, the grooves 19a, 19b, and the opening 53.
This means that it flows into the suction internal chambers 26 and 27 via a and 53b. Forming a flow of this blow-by gas flowing into the inner suction chambers 26, 27 is caused by the fact that the blow-by gas flows into the outer suction chambers 22, 23,
This is assisted by the fact that the refrigerant gas accumulated in the suction chambers 26, 27 is constantly sucked into the cylinder hole 13 via the suction holes 52 of the valve plates 18a, 18b. As a result, the suction chamber 2
The blow-by gas flowing into the external suction chambers 22, 27 flows along the flow direction shown by arrow B in FIG.
3 and into the cylinder hole 13 along with the refrigerant gas which is sucked into the cylinder hole 13 in the flow direction shown by arrow A. When sucked into the cylinder hole 13, the through holes 30a, 30
A part of the lubricating oil that has flowed into the suction inner chambers 26 and 27 along the direction b is carried into the cylinder hole 13 through the suction hole 52 and contributes to the lubrication of the sliding movement between the cylinder hole wall surface and the piston 34. Note that in FIG. 4, the arrow B reaches only two of the three cylinder bores 13 through the opening of the partition wall 21b;
are located directly below each of the through holes 28a or 28b of each valve plate 18a or 18b, so that refrigerant gas relatively containing oil droplets flows through the through holes 2.
After passing through 8a or 28b, it flows into this cylinder hole, so that ultimately all three cylinder holes 13 of this compressor can obtain an even lubrication effect. Since the blow-by gas mentioned above is in a high pressure state due to compression, it is also possible to apply inflow pressure to the lubricating oil flowing from the suction inner chambers 26 and 27 to the oil supply passages 53a and 53b to make the oil flow more active. It is contributing.

Now, in the above description, some of the oil particles and refrigerant gas that entered the swash plate chamber 17 through the through holes 45 and 46 of the partition walls 17a and 17b collided with the swash plate 33 that was rotating within the swash plate chamber 17, and as a result, Droplets of lubricating oil adhere to the swash plate 33 and moisten it, and the swash plate 3
3 rotates, and is supplied to the side surface of the swash plate 33 and the steel balls 35 and shoe 36 connecting the swash plate 33 and the piston 34, thereby reliably lubricating each sliding surface. These lubricating oil droplets flow down to the bottom of the swash plate chamber 17, and then flow through the through hole 5.
It flows into the oil sump chamber 16 through 0.0 and 51. Note that some of the refrigerant gas that has entered the swash plate chamber 17 is transferred to each cylinder head 2 together with the aforementioned blow-by gas.
0 and 21 to the suction inner chambers 26 and 27. In addition,
The groove structure of this embodiment, which allows a portion of the oil droplets to flow directly into the swash plate chamber together with the refrigerant gas returned from the refrigeration circuit, supplies low-temperature, high-viscosity lubricating oil to the sliding surface, so it has a high lubrication effect. This provides the advantage of also having a cooling effect. In addition, some of the oil that has flowed into the oil tank from the swash plate chamber flows into the suction chamber together with the blow-by gas, contributing to oil slippage in the cylinder bore, but this effect is due to the fact that the communication path between the suction chamber and the oil tank is It is also possible to connect the

FIG. 6 is a longitudinal cross-sectional view showing a second embodiment of the present invention, in which the outer walls 12a, 12b of the cylinder blocks 11a, 11b are different from the first embodiment shown in FIGS. 1 to 5. The structure and operation are the same as in the first embodiment, except that there is only one inflow hole 61 and therefore there is only one through hole 63 provided on the extension of the center line of this inflow hole 61. It has the following. Therefore, each member or portion is shown with the same reference numeral as in the first embodiment.

FIG. 7 is a longitudinal sectional view showing a third embodiment of the present invention. This third embodiment is similar to the first embodiment shown in FIG.
Compared to the embodiment, lower partition walls 17c and 17d that partition the swash plate 17 and the oil sump chamber 16 have both side walls removed and are extended along the left and right axial directions. It is characterized in that the upper part of the swash plate chamber 17 is enclosed in the swash plate chamber 17. As a result, oil is returned to the oil reservoir chamber 16 through a pair of gaps 54a and 54b formed between the extended lower partition wall end and the valve plates 18a and 18b. Therefore, in this embodiment, the blow-by gas is introduced into the suction chambers 26 and 27 without passing through the space defined as the oil reservoir chamber 16, but this embodiment is also the same as the first embodiment except for this. They have the same structural effect.

Now, in the above first, second and third embodiments, when the compressor is stopped, the grooves 19a and 19b provided in the front and rear valve plates 18a and 18b are connected to the cylinder heads 20 and 21. Partition walls 20b, 21 provided in suction inner chambers 26, 27 of
through hole 3 from oil separation chambers 14a and 14b in cooperation with b.
The lubricating oil flowing through 0a and 30b is transferred to the oil reservoir chamber 1.
It should also be noted that it also acts as an oil passageway returning to 6. When the compressor starts operating again, the lubricating oil returned to the oil sump chamber 16 in this way is transferred to the passages 50, 51 or 50 due to the homing phenomenon.
a, 54b, enters the swash plate chamber, is supplied to each sliding surface according to rotation of the swash plate, and is also supplied to the grooves 19a, 1.
It enters the suction inner chamber via 9b, enters the cylinder hole together with the refrigerant gas, and lubricates its wall surface.

As is clear from the explanation based on the above embodiments, according to the present invention, lubricating oil can be abundantly supplied to each operating member and sliding surface of the compressor without the need for a special device such as a lubricating pump. In particular, since the lubrication effect is ensured during the compression operation of the compressor, smooth operation of the compressor is guaranteed even during long-term continuous operation.

In addition, in a compression mechanism in which all of the return refrigerant is introduced into the swash plate chamber to lubricate the swash plate, shoe, etc., and the main circuit is a detour route passing through the swash plate chamber, the purpose of swash plate lubrication cannot be achieved. Not only does this unnecessarily increase the flow path resistance, but also the refrigerant diluted by the absorbed heat is sucked into the cylinder hole, which inevitably leads to a decrease in volumetric efficiency. In this invention, the main circuit is a circuit in which only a portion of the return refrigerant sufficient to lubricate the swash plate, shoe, etc. is guided into the swash plate chamber, and sucked directly into the cylinder hole, so that the volumetric efficiency as described above is improved. There is no cause for concern about the decline in the economy. Furthermore, since the blow-by gas captures a portion of the separated oil and flows into the cylinder hole, it contributes to lubrication of the cylinder hole and to an improvement in volumetric efficiency.

[Brief explanation of the drawing]

1 and 2 are two different vertical sectional views of a swash plate compressor according to an embodiment of the present invention, and FIG.
4 is a front view showing the internal structure of the rear cylinder head of the compressor shown in FIG. 1, FIG. 5 is a front view of the rear valve plate, and FIG. and FIG. 7 is a longitudinal sectional view similar to FIG. 2, showing compressors according to second and third embodiments of the present invention. In addition, in the figure, 11a, 1
1b is the cylinder block, 12a and 12b are the outer walls of the cylinder block, 13 is the cylinder hole, 14
a and 14b are oil separation chambers, 15 is a discharge chamber, 16 is an oil reservoir chamber, 17 is a swash plate chamber, 18a and 18b are valve plates, 19a and 19b are grooves, 20 and 21 are cylinder heads, and 22 and 23 are outside suction chambers. Room, 24, 25
is the discharge chamber, 26, 27 are the suction inner chambers, 30a, 30
b is the oil hole, 31 is the drive shaft, 33 is the swash plate, 34
is the piston, 35 is the steel ball, 36 is the shoe, 41,
42, 61 are inflow holes, 43, 44 are suction passages, 4
5, 46, and 63 are through holes, and 54a and 54b are gaps.

Claims (1)

[Scope of utility model registration request] The cylinder blocks, which are connected in a pair in the left and right axial directions, have a swash plate chamber for storing the swash plate in the center of the interior thereof, a lubricating oil storage chamber in the lower part, and a swash plate chamber in the lower part of the cylinder block, and a swash plate chamber for storing the swash plate in the lower part thereof. A refrigerant gas return inflow hole is provided to introduce the return refrigerant gas into the left and right oil separation chambers in the cylinder block to separate oil droplets in the return refrigerant gas, and then valve plates are installed at the left and right ends of the cylinder block. The return refrigerant gas after the oil separation is sucked and compressed into the cylinder hole through each suction chamber provided inside a pair of cylinder heads fixed through the cylinder head, and the compressed refrigerant gas is sent to the discharge chamber inside the cylinder head. A passageway is cut into the inner surface of each valve plate facing the cylinder block to spatially communicate the swash plate chamber with each suction chamber of the cylinder head to prevent blow-by from leaking into the swash plate chamber from the cylinder hole. In a swash plate compressor having a fluid passage that allows gas to flow into each suction chamber of the cylinder head, a partition wall between the suction passage and the swash plate chamber that leads the return refrigerant gas from the return inflow hole to the oil separation chamber is provided. A through hole is provided which faces each other on an extension of the inflow hole and the center line of the hole and has an opening area large enough to allow only a portion of the return refrigerant gas to enter the swash plate chamber, and which connects the swash plate chamber and the oil reservoir chamber. A swash plate compressor characterized in that a passage that spatially communicates with the swash plate chamber is provided at a position facing the lowest bottom portion of the swash plate chamber on a wall surface of a partition between the swash plate chamber and the oil reservoir chamber.