JPS60164690A - Vane type rotary compressor - Google Patents

Abstract

PURPOSE:To prevent abrasion of vane by providing a pressure control valve for holding the differential pressure between intake pressure and the lubricant pressure in back pressure path at predetermined level in a lubrication path communicating between intake section and back pressure path thereby maintaining the lubricant pressure in back pressure path at proper level. CONSTITUTION:Under relatively low rotation of rotor 12 where the differential pressure between intake pressure and delivery pressure is low, the differential pressure between the back pressure path 15 and a pump chamber 17a located in the intake stroke or the differential pressure between the chambers 22, 26 is also low thereby the ball valve 33 in pressure control valve 32 is resiliently pressed against the seat face through a spring 35 thus to close the lubrication path 31. The lubricant sucked from the high pressure section 7 into the back pressure path 15 will return to the pump chamber 17a only through a sliding gap 28. Consequently, the working oil in the back pressure path 15 is held at proper level resulting in prevention of abnormal abrasion of vane 17 or cam ring 3 or noise to be produced through landing of vane 17.

Description

DETAILED DESCRIPTION OF THE INVENTION (Technical Field) The present invention relates to a vane-type rotary compressor used in a cooling device or the like.

(Prior art) Conventionally, this type of vane-type rotary compressor has been constructed in such a way that: (1) a constriction section is provided between the high pressure section of the lubrication system and the vane back pressure of the rotor, and lubricating oil is passed through the constriction section into the back pressure passage; By guiding the air to the low pressure part through the gap between the rotor side surface and the plate, an appropriate pressure proportional to the discharge pressure is applied to the back surface of the vane, thereby significantly preventing vane wear. Something has already been proposed (Jitgan 5th year)
No. 5-169127. ) First, such a vane type rotary compressor will be explained with reference to FIGS. 1 and 2.

In the figure, reference numeral 12 denotes a pair of front plates and rear plates, between which the cam ring 3 is fixed by bolts 4.

Reference numeral 5 denotes an outer cylinder that covers these and defines a high pressure chamber 5a, and a discharge hole (not shown) that communicates with a pump chamber (described later) in the compression stroke is opened on the side of the filter plate 2 in the outer cylinder 5. A gas/oil separation member 6 is provided facing this, and this serves as a high pressure part 7 for lubricating oil. Reference numeral 8 denotes a discharge port attached to the outer cylinder 5 so as to communicate with the high pressure section 7, and guides the compressed gas to a cooling device (not shown). Reference numeral 9 denotes a loader shaft of a rotor 12 supported in the center hole of each of the plates 1.2 through needle bearings 1o and 11.

Reference numeral 13 designates an orifice ring that is juxtaposed to the needle bearing 1o and forms a first constricted portion 13a between it and the rotor shaft 9, and 14 designates a thrust bearing.

The rotor 12 is provided with a back pressure passage 15 through which lubricating oil passes and a plurality of substantially radial slits 16 that are continuous with the passage and open on the outer circumferential surface, and vanes 17 are slidably attached to these slits.

These vanes 17 come into sliding contact with the inner peripheral surface of the cam ring 3 as the rotor 12 rotates, and define a plurality of pump chambers 17a in which suction and compression strokes are repeated. 18 is a head attached to the front plate 1 side, and in the center hole of this head is a seal ring 2 that is engaged with a snap ring 19.
The end of the rotor shaft 9' is inserted through the rotor shaft 9', and a mechanical seal 21 is in sliding contact with the rotor shaft 9 inside thereof.

The chamber 22 accommodating these seals 20 , 21 communicates via a passage 23 with a passage U provided in the front plate 1 . This passage 24 opens facing the left end face of the rotor 12, and its opening position is appropriately selected in order to keep the pressure in the back pressure passage 15 and the pressure in the chamber 22 for the mechanical seal 21 etc. at an optimum level. Ru. Note that 25 is a suction hole for a refrigerant introduced from a cooling device (not shown), and 26 is a chamber connected to this.

In the vane type rotary compressor having such a configuration, as shown by the arrow in the figure, the high pressure lubricating oil in the high pressure section 7 passes through the through hole 27 provided in the filter plate 2 and the first constricted portion 13a due to the discharge pressure. After being sucked into the needle bearing 10, it is introduced into the back pressure passage 15 through an annular chamber 29 defined between the rotor 12 and the rear plate 2.

At this time, the orifice ring 13 arranged in parallel to the needle bearing 10 forms a first constriction portion 13a to throttle the flow of the lubricating oil, so that the lubricating oil with reduced pressure is introduced into the back pressure passage 15 and the vane 17 is Press it against the inner circumference of the cam ring 3 with a predetermined pressure. Note that the vane back pressure at this time is set to the minimum necessary pressure that does not allow the vane 17 to separate from the inner circumferential surface of the cam ring 3.

Further, the lubricating oil sucked into the back pressure passage 15 lubricates the thrust bearing 14 and the needle bearing 11, and is led out to the chamber 22, and after lubricating the seals 20.21, passes through the passage 23.24 to the front plate 1. and the rotor 12 (second constricted portion) 28, and then sent into the suction chamber as a low pressure section. In this case, since the lubricating oil is guided into the back pressure passage 15 at an appropriate pressure via the orifice ring 13, the contact pressure of the vane 17 against the inner peripheral surface of the cam ring 3 is maintained at an appropriate level, and the mechanical seal is maintained at an appropriate pressure. Lubricate 21. Furthermore, due to the throttling effect of the sliding gap 28, the lubricating oil in the back pressure passage 15 is maintained at an appropriate pressure, and the amount of lubricating oil led out to the low pressure section is controlled to the minimum necessary, so that the entire cooling system is The amount of lubricating oil circulated can also be minimized.

However, in such a vane type rotary compressor, the discharge pressure is reduced at the first constricted portion 13a formed by the orifice ring 13 and the sliding gap 28 to obtain the extrusion hydraulic pressure of the vane 17, so that the discharge pressure is 10 (kg /cd)
When used as a compressor for an automobile cooling system that fluctuates in the range of ~30 (kg/aJ), the vane 17
It is difficult to maintain the extrusion hydraulic pressure at an appropriate pressure, and when the discharge pressure is relatively high, the tip of the vane 17 that slides on the cam ring 3 is likely to wear, reducing durability. When the vane 17 is relatively low, the pressing force of the vane 17 against the cam ring 3 is weakened, causing the vane 17 to land against the cam ring 3 (a repeated floating and landing motion), which causes breakage and abnormal noise. There was a problem.

(Object of the Invention) This invention was made in view of the above-mentioned problems, and includes providing a pressure control valve between the back pressure passage and the low pressure side to maintain the hydraulic pressure in the back pressure passage at an appropriate value. Therefore, it is an object of the present invention to provide a vane type rotary compressor in which the appropriate pressing force of the vane against the cam ring is ensured regardless of changes in discharge pressure, thereby effectively preventing wear and landing of the vane and the cam ring. It is an object.

(Structure of the Invention) The vane type rotary compressor according to the present invention includes a cam ring installed between the front plate and the retainer plate,
The cam ring includes a rotor having a slidable vane housed in a slit having a back pressure passage in the radial direction, and the rotor shaft of the rotor is supported on each of the plates via bearings. The vane is moved in and out as it rotates, and one end of the vane is brought into sliding contact with the inner periphery of the cam ring.The cam ring has a lubrication system that circulates lubricating oil based on the pressure difference between the discharge pressure and suction pressure to lubricate each rotating sliding part. In a vane-type rotary compressor, a lubrication passage is formed between the suction overwhelm, that is, the low pressure side, and the back pressure passage of the rotor, and the pressure between the suction pressure and the lubricating oil pressure in the back pressure passage is applied to the lubrication passage. A pressure control valve is provided to maintain the difference at a predetermined value.

(Example) Embodiments of the present invention will be described below based on the drawings.

FIG. 3 is a diagram showing a first embodiment of the present invention. In the following description, the same components as those of the vane type rotary compressor shown in FIGS. 1 and 2 described above are given the same numbers, and the description thereof will be omitted.

First, to explain the configuration, the head 18 is formed with a lubrication passage 31 that communicates the chamber 22 and the chamber 26! ,
'! This lubricating passage 31 has a large diameter portion 31a that opens into the chamber.
and a small diameter part 31b opening into the chamber 22, and a pressure control valve 32 is housed in the large diameter part 31a.

The pressure control valve 32 is fitted with a ball valve 33 that can be moved into and out of a seat surface formed at a step between the large diameter section 31a and the small diameter section 31b of the lubricating passage 31, and a wall surface of the large diameter section 31a. Ta Suna 1. A spring 35 is provided between the spring 34 and the ball valve 33 to bring the ball valve 33 into elastic contact with the seat surface with a predetermined elastic force.

This pressure control valve 32 is configured such that when the pressure difference between the chamber 22 and the chamber 26 exceeds a predetermined value, this pressure difference causes the lipoll valve 33 to move away from the seat surface against the elastic force of the spring 35, thereby providing lubrication. The passage 31 is opened to a flow path area corresponding to the pressure difference, and the chamber 2
The pressure difference between 2 and the chamber is kept constant.

Next, the operation of the vane type rotary compressor having such a configuration will be explained.

First, when the rotor 12 of the vane type rotary compressor rotates at a relatively low speed and the pressure difference between the suction pressure and the discharge pressure is small, the pressure difference between the back pressure passage 15 and the pump chamber 17a in the suction stroke, that is, the pressure difference in the chamber n Since the pressure difference between the pressure and the chamber pressure is also small, the ball valve 33 of the pressure control valve 32 is in a state of being pressed against the seat surface by the spring 35, and the lubrication passage 31 is closed. Therefore, the lubricating oil in the high pressure section 7 is introduced into the back pressure passage 15 through the through hole 27, the first constricted portion 13a and the annular chamber 29, and then, as described above, the lubricating oil is introduced into the back pressure passage 15,
4 and the needle bearing 11 and the passage guide, 24
It is pushed into the sliding gap 28, and then sent into the pump chamber 17a, which is in the suction stroke and serves as a low pressure section. That is, the lubricating oil supplied from the high pressure section 7 to the back pressure passage 15 flows back to the pump chamber 17a through only the sliding gap 28 having a throttling effect. Therefore, the hydraulic oil in the back pressure passage 15 is maintained at a relatively high pressure, and the vane 17 is
.

3.

Next, when the rotational speed of the rotor 12 increases and the pressure difference between the suction pressure and the discharge pressure increases, the pump chamber 1 in the suction stroke
Since the pressure difference between chamber 7a and back pressure passage 15, that is, the pressure difference between chamber 4 and chamber 22 also increases, the pressure control valve 32 causes the ball valve 33 to seed against the elastic force of the spring 35 due to this pressure difference. The lubricating passage 31 is opened to a flow passage area corresponding to the pressure difference between the chamber 22 and the chamber 26. Therefore, the back pressure passage 15 also communicates with the pump chamber +78 in the suction stroke via the WR sliding passage 31, and the lubricating oil supplied from the high pressure section 7 to the back pressure passage 15 flows through the sliding gap 28 and the lubrication passage. 31 to the pump chamber 17a. At this time, the pressure control valve 32 changes the flow area of the lubricant passage 31 so that the pressure difference between the lubricant pressure in the back pressure passage 15 and the suction pressure is constant. is controlled to an appropriate relatively low pressure to bring the vane 17 into pressure contact with the cam ring 3.

As described above, in the vane type rotary compressor according to the present invention, the lubricating passage 31 has a passage area corresponding to the pressure difference between the suction pressure and the lubricating oil pressure in the back pressure passage 15, and 15
In order to maintain the lubricating oil pressure at a proper pressure, abnormal wear of the vanes 17 and the cam ring 3 and generation of abnormal noise due to landing of the vanes 17 are prevented.

Embodiments 2 to 5 of the present invention are shown in FIGS. 4 to 7, respectively. In each of the following embodiments, the same components as those in the first embodiment described above are designated by the same numbers and their explanations will be omitted.

First, a second embodiment will be explained with reference to FIG.

The vane type rotary compressor according to this embodiment has a head 18
A lubrication passage 31 is formed in the front plate 1 to communicate the pump chamber 17a and the chamber 22 during the suction stroke. That is, as shown in the figure, the lubrication passage 31
A first lubricating passage 31C is formed in the head 18 and branches from the passage 23, and a pump chamber 1 is formed in the front plate 1 in parallel with the passage 24 and is in the suction stroke.
It consists of a second lubricating passage 31d that opens at 7H, and the aforementioned pressure control valve 32 is housed in the second lubricating passage 31d.

Note that 3a is a guide hole formed in the cam ring 3, and this guide hole 3a communicates with the chamber through the hole 1a formed in the front plate 1, and communicates with the pump chamber in the suction stroke through the through hole 3b. It communicates with 17a.

Even in this vane type rotary compressor, the lubrication passage 31 is controlled by the pressure control valve 32 to have a flow passage area according to the pressure difference between the lubricating oil pressure in the back pressure passage 15 and the suction pressure, so that the back pressure passage is opened. Since the lubricating oil pressure is maintained at an appropriate level, abnormal wear of the vanes 17 and the like is eliminated, durability is improved, and abnormal noises are prevented from occurring.

Next, a third embodiment will be explained with reference to FIG.

The vane type rotary compressor according to this embodiment has a lubricating passage 31 formed in the front plate 1, and this lubricating passage 31 has an annular shape with one end defined by the thrust bearing 14 and the inner circumferential surface of the front plate 1. Opening to space,
The other end opens into the chamber 26.

In this vane type rotary compressor, a pressure control valve 32 provided in a lubricating passage 31 operates according to the pressure difference between the annular space and the chamber 26, that is, the pressure difference between the back pressure passage 15 and the pump chamber 17a in the suction stroke. The flow area of the lubricating passage 31 is changed to maintain the lubricating oil pressure in the back pressure passage 15 at an appropriate value.

Further, a fourth embodiment will be explained with reference to FIG.

The vane type rotary compressor according to this embodiment has a lubricating passage 31 formed in the front plate l that communicates the pump chamber 17a in the suction stroke with the annular space in the third embodiment, and the other parts are as described above. This is similar to the example.

Further, a fifth embodiment will be explained with reference to FIG.

The vane-type rotary compressor according to this embodiment has a lubricating passage 31 formed in the rear plate 2 that communicates the pump chamber 17a in the suction stroke with the annular chamber 29, that is, the back pressure passage 15. This is similar to each of the embodiments described above.

(・Effects of the Invention) As explained above, according to the rotor compressor according to the present invention, a lubrication passage is provided that communicates the suction section and the back pressure passage, and the lubrication passage is provided with a lubrication passage that communicates between the suction pressure and the back pressure passage. A pressure control valve is installed to maintain the pressure difference with the lubricating oil pressure at a predetermined value, so even if the discharge pressure changes, the lubricating oil pressure in the back pressure passage can be maintained at an appropriate value. Excessive wear of the vanes and the like is prevented, improving durability, and furthermore, generation of abnormal noise due to vane landing is effectively prevented.

[Brief explanation of drawings]

1 and 2 are views showing a conventional vane type rotary compressor, with FIG. 1 being a front sectional view and FIG. 2 being a partially sectional side view. 3 to 7 are front sectional views showing vane type rotary compressors according to embodiments of the present invention, respectively. FIG. 3 shows the first embodiment, and FIG. 4 shows the second embodiment. FIG. 5 shows a third embodiment, FIG. 6 a fourth embodiment, and FIG. 7 a fifth embodiment. 1--Front plate, 2--Rear plate, 3--Cam ring, 7--High pressure section, 9--Rotor shaft, 10.11--1 --Needle bearing (rotating part) 13a ----- Part 1 throttle part, 12-...
-Rotor 14--Thrust bearing (rotating part), 1
5--Back pressure passage, 16--Slit, 17--Vane, 17a--Pump chamber (low pressure part), 20--Seal ring (rotating part) ), 21・---
---Mechanical seal (rotating part), 23, etc.--
・Passage, 27------Through hole, 28--Sliding gap (second throttle part), 31---'
- Lubrication passage, 32... Pressure control valve. Patent applicant: Atsugi Auto Parts Co., Ltd. Representative Patent Attorney: Ugagun Part Figure 1 Figure 2

Claims (1)

[Claims] A cam ring is mounted between the front plate and the carrier plate, and within the cam ring is a rotor having a slidable vane housed in a substantially radial slit having a back pressure passage; The vanes are supported by the respective plates via bearings, and are moved in and out as the rotor rotates, with one end of the vanes slidingly in contact with the inner periphery of the cam ring. In a vane type rotary compressor having a lubrication system of lubricating oil for lubricating moving parts, a lubrication passage is formed between the suction pressure side, that is, the low pressure side and the back pressure passage of the rotor,
A vane type rotary compressor, characterized in that the lubricating passage is provided with a pressure control valve that maintains a pressure difference between the suction pressure and the lubricating oil pressure in the back pressure passage at a predetermined value.