JPS6149186A - Vane type rotary compressor - Google Patents

Abstract

PURPOSE:To prevent the contact part between a rotor and a cylinder from seizing, by forming an oil groove extending in the direction of the main shaft, in the outer peripheral surface of the rotor or the top seal section of the cylinder. CONSTITUTION:In a vane type compressor, an oil groove 105 extending in the direction of the main shaft is formed in the contact part between a cam ring 38 and a rotor or the top seal part of the cam ring 38. Therefore, oil mixed in working fluid is pooled in the oil groove 105 to enhance the lubrication ability of this part which is therefore prevented from seizing. The same effect may be obtained if the oil groove is formed in the outer peripheral surface of the rotor 31, extending over the entire width thereof.

Description

[Detailed description of the invention] (Technical field) The present invention relates to a vane type rotary compressor.

(Prior art) Generally, in a vane type rotary compressor, a top clearance is formed between the outer circumferential surface of the rotor and the inner circumferential surface of the rotor housing. In order to prevent seizing and to prevent fluid (refrigerant) from leaking from the high-pressure side pump chamber to the low-pressure side pump chamber, it is maintained at a predetermined minute size.

Conventional vane type rotary compressors of this type include, for example,
A vane type rotary compressor as shown in Japanese Utility Model Application Publication No. 38-42089'3 is known, and the vane type rotary compressor shown in this publication is as shown in Fig. 15.16. In the figure, first, when the rotational force of the engine is transmitted to a boot (not shown) fixed to the rotating shaft 1a of the rotor 1 via a drive belt (not shown), the rotor 1 moves in the forward direction (arrow A The lubricating oil 3 stored in the case 2 is pressurized by the fluid (refrigerant) discharged into the case 2, and moves up the flow path 5 of the rear side plate 4, filling the gap C.
1, the vane 8 formed on the rotor 1 is introduced into the back pressure groove 7 when it protrudes, and after pressing the vane 8 against the cam surface 10 of the cam ring 9, the flow path 12 formed on the front side plate 11 is introduced. .13, it is supplied to the pump chamber 14 in the suction area through the gap C2. As the rotor 1 rotates further, the pump chamber 14 reaches the discharge area. On the other hand, the vane 8 is recessed into the back pressure groove 7. Therefore, the lubricating oil 3 introduced into the back pressure groove 7 is distributed between the vane 8 and the back pressure m7, between the rotor 1, the front side plate 11, and the rear side plate 4.
After passing between them and lubricating the sliding motion between them, the pump is supplied to the pump chamber 14 in the discharge area. The lubricating oil 3 thus accumulated in the pump chamber 14 in the discharge area is transferred to the cam surface 10 and the rotor 1.
It is used to lubricate the gap (top clearance ho) between the cam ring 9 and the cam ring 9, and is stored in the case 2 again through the discharge hole 16 formed in the cam ring 9.

However, such conventional vane type rotary compressors have the following problems. First, when a vane-type rotary compressor is operated at a high discharge pressure, or when the tension of the drive belt applied to the boob fluctuates due to vibration of the drive belt, the rotor 1 is subjected to an external force in the radial direction. , the center of the rotor 1 is eccentric from the center of the cam ring 9. Incidentally, both the cam surface [0] and the outer circumferential surface of the rotor 1 at a top clearance of 90 parts are flat surfaces that have been precisely machined. Therefore, in the top clearance of 90 parts, only a slight restoring force is generated to return the center of the opening to the opening 1 to the center of the cam ring 9. Therefore, at the top clearance of 90 parts, the outer peripheral surface of the rotor 1 slides into contact with the cam surface 10 while pressing it. As a result, the oil film between the outer peripheral surface of the rotor 1 and the cam surface 10 is cut, and the rotor 1
There was a problem that the outer circumferential surface of the cam surface 10 and the cam surface 10 were seized.

(Structure and purpose of the invention) This invention was made focusing on the above-mentioned problems.
A rotatable rotor, a rotor storage body that stores the rotor, an oil groove formed on one of the outer peripheral surface of the rotor or the inner peripheral surface of the rotor storage body in the top clearance, and a rotor that fits into the rotor so as to be retractable in approximately radial directions. a pump chamber that is defined in the space between the rotor and the rotor housing between adjacent vanes and that expands and contracts as the rotor rotates in the forward direction; and a suction boat that communicates with the pump chamber when expanding. A discharge boat communicating with the pump chamber during contraction, and a case storing lubricating oil that is pressurized by fluid discharged from the pump chamber during contraction and is supplied to the oil groove. The purpose is to solve the problem i11.

(Example) Hereinafter, a first example of the present invention will be described based on the drawings.

In Fig. 1.2.3.4.5.6, 31 is a rotatable rotor, and this rotor 31 has an outer diameter D = 62
It is made up of am. On the outer periphery of the rotor 31, a large number (for example, four) of back pressure grooves 32 extending substantially in the radial direction are formed at equal intervals in the circumferential direction of the rotor 31. Each back pressure groove 3
The front end and the rear end of the rotor 2 are open to the front side and rear side of the rotor 31, respectively. A front shaft body 33 and a rear shaft body 34 that protrude forward and rearward are formed coaxially with the rotor 31 on the front and rear side surfaces of the rotor 31, respectively. 36 is the longitudinal length L = 47
This cam ring 36 has a through hole 38 whose inner peripheral surface forms a cam surface 37 with a substantially oval cross section;
A suction hole 39 is spaced 180° from the through hole 38, and a discharge hole 40 is located between the suction holes 39 and spaced 180° from the through hole 38. A rotor 31 is rotatably housed in the through hole 38 . A top clearance ho is formed between the cam surface 37 and the outer peripheral surface of the rotor 31 on the minor axis of the through hole 38, and this top clear rank, h
o = 27.5 μm.

A large number of oil grooves 41 extending in the axial direction of the cam ring 36 are formed in the cam surface 37 at the 1-tube clearance hO, as shown in detail in FIG. 3.4.5. As shown in detail in FIG. 6, each oil groove 41 has a depth a=15 μm.
, width B = 5.77+u, and the distance between the oil grooves 41 is B = 8 mm. The front end opening of the through hole 38 is closed by a front side plate 43, and the front side plate 43 has a through hole 44 and a flow path 45 formed therein. Through hole 4
4 is fitted with a needle bearing 46, and this needle bearing 46 rotatably supports the front shaft body 33.

The rear end opening of the through hole 38 is closed by a rear side plate 48, and the rear side plate 48 has a through hole 49 and a flow path 50 formed therein.

A needle bearing 51 is fitted into the through hole 49, and this needle bearing 51 rotatably supports the rear shaft body 34. Both the through hole 44 and the through hole 49 communicate with the radially inner end of the back pressure groove 32 of the rotor 31. Through hole 49 behind needle hair ring 51
An aperture ring 53 is fitted into the aperture ring 53, and the rear shaft body 34 is loosely inserted into the aperture ring 53 with a predetermined gap C3. One end of the channel 50 opens at the lower outer surface of the beamer side plate 48, and the other end opens into the through hole 4 through the gap C1.
It is connected to 9. The cam ring 36, front side plate 43, and rear side plate 48 as a whole are:
A rotor storage body 55 is configured. A vane 57 is fitted into each back pressure groove 32 so as to be retractable.

As a result, a large number of vanes 57- are fitted onto the rotor 3 so as to be able to protrude and retract substantially in the radial direction. Between the vanes 57 adjacent to each other, in the space between the rotor 31 and the rotor housing 55, there is a space between the vanes 57 in the forward direction of the rotor 31 (in the direction of arrow A).
A pump chamber 59 is defined which expands and contracts as the pump rotates. The pump chamber 59 in the so-called suction area when expanding is the suction hole 39
The pump chamber 59 in the so-called discharge region when contracting communicates with the discharge hole 40 . A thrust bearing 61 is fitted into the rear end of the through hole 44 , and this thrust bearing 61 receives a thrust load in the forward direction of the rotor 31 , thereby supporting the front side plate 43 and the rotor 3 .
1, a predetermined gap C2 is formed between the two. Said flow path 4
5 communicates with a pump chamber 59 in the suction area via a gap C2. The rotor 31, rotor housing 55, and vane 57 are
The cartridge 63 is configured as a whole. Reference numeral 65 denotes a separator plate that is bent into a disconnection/'t throat shape, and this separator plate 65 closes the rear end opening of the through hole 49 via an O ring 66. The separator plate 65 is covered with an oil separator 68 bent to have a substantially hat-shaped cross section. A vertical wall 69 of the oil separator 68 is formed with a hole 70 whose diameter increases toward the front. A hole 72 is formed in the hole 72 . The upper flange portion 74 of the separator plate 65 and the upper flange portion 75 of the oil separator 68 are fixed to the rear side plate 48 by screws 76.

Reference numeral 79 denotes a rear throat that accommodates the cartridge 63, and the internal space of this rear head 79 forms a discharge chamber 80 that communicates with the discharge hole 40. A discharge boat 81 is formed on the peripheral wall of the rear throat 79, and the inner end of the discharge boat 81 communicates with the discharge chamber 80, and the outer end is connected to a condenser (not shown). 83 is a front head, and this front head 83 opens the opening of the rear head 79 to 0.
It is closed via a ring 84. The cartridge 6
3 is fixed to the rear side surface of the front head 83.

The front head 83 is formed with a suction chamber 85 and a suction boat 86 whose inner end communicates with the suction chamber 85.The suction chamber 85 communicates with the suction hole 39, and the outer end of the suction boat 86 is connected to an evaporator (not shown). It is connected to the.

A strainer 87 is fitted into the suction boat 86 .

A through hole 89 communicating with the through hole 44 is formed in the center of the front head 83, and the front shaft body 33 is inserted through the through hole 89 via a mechanical seal 90. The through hole 89 and the flow path 45 communicate with each other through a flow path 9I formed in the throat 83 to the front. Discharge chamber 80
Lubricating oil 93 is stored at the bottom of the lubricating oil 9.
3 is supplied to the oil groove 41 by being pressurized by the refrigerant discharged from the discharge hole 40. The front head 83 and the rear head 79 collectively constitute a case 93 in which lubricating oil 93 is stored. A pulley 97 is attached to the front shaft body 33 that protrudes forward from the front head 83 via an electromagnetic clutch 95. The pulley 97 is rotationally driven by the automobile engine via a drive belt (not shown).

Next, the operation of the first embodiment of the present invention will be explained.

First, when the electromagnetic clutch 95 is connected while the engine is rotating, the rotational force of the engine is transmitted to the front shaft body 33 via the drive belt, pulley 97, and electromagnetic clutch 95, and the rotor 31 rotates in the forward direction. Therefore, the refrigerant supplied from the evaporation lake to the suction port 86 is sucked into the pump chamber 59 in the suction area via the strainer 87, the suction chamber 85, and the suction hole 39.

As the rotor 31 further rotates, the pump chamber 59
When the refrigerant reaches the discharge region, the refrigerant in the pump chamber 59 is pressurized as the rotor rotates, becomes a high-pressure refrigerant, is discharged into the discharge chamber 80 through the discharge hole 40, and is stored in the lower part of the discharge chamber 80. After pressurizing the lubricating oil 93, the discharge port 8
1 to the capacitor. The lubricating oil 93 in the discharge chamber 80 pressurized by the refrigerant ascends the flow path 50, passes through the gap C1 and the needle bearing 51, and reaches the vane 5.
When the vane 57 protrudes, the back pressure 'a32 is introduced, and the vane 57
After firmly pressing against the cam surface 37, the thrust bearing 61, needle bearing 46, through hole 89, flow path 91
, the flow path 45, and the gap C2, it flows into the pump chamber 59 in the suction area, and mixes with the low-pressure refrigerant. When the rotor 31 rotates further, the pump chamber 59 into which the lubricating oil 93 entered during the suction region reaches the discharge region. On the other hand, the vane 57 is connected to the back pressure groove 32.
immerse yourself in Therefore, the lubricating oil 93 introduced into the back pressure groove 32 is distributed between the vane 57 and the back pressure groove 32 and the rotor 31.
After passing between the front side plate 43 and the rear side plate 48 to lubricate the sliding surfaces therebetween, it is supplied to the pump chamber 59 in the discharge area. In this way, the lubricating oil 93 accumulated in the pump chamber 59 in the discharge area together with the refrigerant is used to lubricate the top clearance ho.

By the way, the cam surface 3 at the top clearance of 90 parts
Since the oil groove 41 is formed in the top clearance 90, the top clearance 90 is filled with lubricating oil 93, as shown in FIG. A large amount of pressure is also generated. Moreover, this generated pressure increases as the top clearance ho becomes smaller. Therefore, when the center of the rotor 31 is eccentric from the center of the through hole 38, a pressure difference occurs between the pressures generated at each top clearance hO. Therefore, a force F per unit length acts on the rotor 31, which attempts to return the center of the rotor 31 to the center of the through hole 38. This force F per unit length is expressed by the following formula.

F=ηUB” (CP/ho) However, η−−−−−Viscosity coefficient of lubricating oil U−・−1−−
Peripheral speed of rotor B - Distance between oil grooves cp - Load coefficient ho - Top clearance Here, the eccentricity ff1e between the center of the rotor 31 and the center of the through hole 38 is 17. When it is 5 μm or more, that is, the larger top clearance ho'=ho+e≧27.5+17
．． 5 = 45μm1 Smaller top clearance ho
=ho+e≦27.5-17.5=When the top clearance hO is 10 μm, it becomes easy for foreign matter to get caught in the top clearance hO, so let us find the force F per unit length when the eccentricity e=7.5 μm. However, the rotation speed n of the rotor 31
= 400Or, p, m, outer diameter D of rotor 31 = 62
m11, axial length of rotor 31 = 47 Dragon, kinematic viscosity coefficient ν of lubricating oil (refrigerating machine oil Suniso 5GS) interposed in top clearance 90 parts = 8.9 cSt, = 8.9
XIOm”/s, the density of the same lubricating oil ρ-925kg/
m', and the distance B between the oil grooves 41 is 8 mm.

First, in the graph of Figure 8.9 or the attached table, the eccentricity e = 7.5 μm, that is, the smaller top clearance h
o -h o -e =27.5-7.5 =20cz
m, when the depth d of the oil groove 41 is 15, Cp / h o
”=375(1/m+=”). Also, viscosity coefficient η=ρ×J/ =925 X8.9 XIO=0.0
823kg/mx s, rotor 31 (7) Peripheral speed U =
rcDn=3.14X62X4000
/60=13m/s. Therefore, force per unit length F=η♂B” (Cp/h oL) = 0.
0823x 13 xs2×373 = 2.55X
10'kg/s'L. Therefore, rotor 3
Restoring force P that attempts to return the center of 1 to the center of through hole 38 =
FXL=2.55X10X47=122kgF. On the other hand, the tension T of the drive belt is about 50 kg. Therefore, even if the tension T of the drive belt fluctuates due to vibration of the drive belt, the restoring force P is
can be adequately countered. For this reason, the rotor 31
does not come into contact with the cam surface 37 at the top clearance hO portion, and as a result, seizure between the rotor 31 and the cam surface 37 is prevented. On the other hand, among the lubricating oil 93 in the pump chamber 59 in the discharge area, the lubricating oil 93 that has not been used to lubricate the top clearance hO is discharged from the discharge hole 40 toward the oil separator 68 together with the refrigerant. The hole 72 is separated from the refrigerant by hitting the hole 72.
The discharge chamber 80 is then returned to the lower part of the discharge chamber 80. Lubrication, lubricating oil 9
The refrigerant separated from the refrigerant 3 is supplied to the condenser through the discharge chamber 80 and the discharge port 81.

Next, a second embodiment of the present invention will be described based on the drawings. Incidentally, the same parts as those in the first embodiment are given the same reference numerals, and the explanation thereof will be omitted.

In FIG. 10.11, 36 is a cam ring, and a large number of oil grooves 105 are formed in the cam surface 37 of the cam ring 36 at the top clearance hO portion.

These oil grooves 105 are inclined at a predetermined angle with respect to the rotational direction of the rotor 31. In this example, base 7
57 can be brought into smooth sliding contact with the cam surface 37 on which the oil groove 105 is formed, so that the oil groove 105 and the oil groove 1
05 can be made longer (as a result, the oil groove 1
05 can be easily processed.

Next, a third embodiment of the present invention will be described based on the drawings. Incidentally, the same parts as those in the first embodiment are given the same reference numerals and the explanation thereof will be omitted.

In FIG. 12, 31 is a rotor, and this rotor 3
A large number of first oil grooves 110 and a large number of second oil grooves 111 are formed on the right half and left half of the outer periphery of the oil pump 1, respectively. The first oil groove 110 is inclined in the direction opposite to the rotational direction of the rotor 31 as it goes rearward, and the second oil groove 111 is inclined in the rotational direction of the rotor 31 as it goes rearward.

In this embodiment, when the rotor 31 is formed of sintered metal or the like, the first oil groove 110 and the second oil groove 111 can be formed in advance, so that the rotor 31 can be manufactured easily. It will be done.

In addition, in the above-mentioned 1.2.3 embodiment, m? Although the case where the cross-sectional shape of M is a rectangular cross-section has been described, this cross-sectional shape can be made into a taberand-shaped oil groove 115 as shown in FIG. 13, or an arc run-shaped oil groove a116 as shown in FIG. 14. Good too.

(Effects of the Invention) As explained above, according to the present invention, an oil groove is formed on either the outer circumferential surface of the rotor or the inner circumferential surface of the rotor storage body at the top clearance, so that oil grooves are formed in the pump chamber when contracting. Since lubricating oil pressurized by the discharged fluid is supplied to the oil groove, a restoring force is generated in the rotor to return the center of the rotor to the center of the rotor housing, and as a result, the rotor and rotor housing at the top clearance are The effect is that it is possible to prevent burning with the body.

[Brief explanation of the drawing]

FIG. 1 is a front sectional view showing a first embodiment of a vane type rotary compressor according to the present invention, FIG. 2 is a sectional view taken along the nn arrow in FIG. 1, and FIG. 3 is a main part of FIG. 2. FIG. 4 is an enlarged sectional view, FIG. 4 is a perspective view of the cam ring used in the first embodiment, FIG. 5 is an enlarged perspective view of the main part of FIG. 4, and FIG. 6 is a top clearance section of the first embodiment. 7 is an explanatory diagram of the operation of the first embodiment, and FIG. 8 is a diagram showing the deviation e between the center of the rotor and the center of the cam ring and the restoring force Cp/of the rotor.
Figure 9 is a graph showing the relationship between oil groove depth and rotor restoring force Cp/h for various oil groove depths.
10 is a perspective view showing the second embodiment of the present invention, FIG. 11 is an enlarged perspective view of the main part of FIG. A perspective view showing the third embodiment, Figures 13 and 14 are cross-sectional views showing examples of changes in the cross-sectional shape of the oil groove formed on the cam surface or rotor, and Figure 15 is a perspective view showing a conventional vane type rotary pressure machine. 16 is a perspective view of main parts of a conventional vane type rotary compressor. 31--Rotor, 37-1--Inner peripheral surface, 41.105.110.111 .115.116・-・
---Oil groove, 55--1--Rotor storage body, 57--Vane, 59--Pump chamber, 81---M-Discharge boat, 86---Suction boat, 93-- ---Lubricating oil, 94---Case, ho--Top clearance, A--Forward direction.

Claims (1)

[Scope of Claims] A rotatable rotor, a rotor housing that houses the rotor, an oil groove formed on one of the outer circumferential surface of the rotor or the inner circumferential surface of the rotor housing at the top clearance, and an oil groove substantially radiating from the rotor. a pump chamber that is defined in the space between the rotor and the rotor storage body between adjacent vanes and that expands and contracts as the rotor rotates in the forward direction; and a pump chamber that expands and contracts when the rotor rotates in the forward direction. A suction port communicating with the pump chamber, a discharge port communicating with the pump chamber when contracting, and lubricating oil to be supplied to the oil groove by being pressurized by the fluid discharged from the pump chamber when contracting is stored. A vane-type rotary compressor characterized by comprising a case.