JPH03217683A - Through vane type compressor - Google Patents

Abstract

PURPOSE:To abolish process of a recessed escape member and to improve performance of a compressor by fixing a block member to block the end in the axial direction of a vane groove to the end of a rotor, and forming the end surface in the axial direction of the vane groove with this block member. CONSTITUTION:To a small bore of boss 7 at the front side of a rotor 3, a ring member 60 as a block member is fixed by the method of press fitting or the like. The end surface 61 of the ring member 60 forms the end surface of a vane groove 2 actually. This end surface 61 is polished beforehand. The length of the vane groove 2 in the axial direction is determined by the end surface 61. In such a way, a complicated process of a recessed escape member can be abolished. And since leakage of coolant from the operation chamber can be reduced, performance of the compressor can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a through-vane compressor that is effective as a refrigerant compressor used, for example, in an automobile air conditioner.

[Conventional technology] In general, a through-vane compressor has an inner surface of the housing,
The inner surface of the side plate covering both ends of this housing,
A working chamber is formed by the outer periphery of a rotor that is housed in this housing and rotates together with the shaft, and the side surface of a vane that is slidably attached in the radial direction to a vane groove formed in this rotor. The refrigerant is sucked in, compressed, and discharged according to changes in volume.

In such a compressor, in order to prevent the high-pressure refrigerant during the compression process from leaking from the working chamber to other working chambers and to ensure the cooling performance of the compressor, the above-mentioned parts forming the working chamber are Its dimensions must be strictly controlled with tolerances of several tens of microns, and these surfaces facing the working chamber are finished by polishing.

Furthermore, the vane grooves provided in the rotor are also polished with high precision in order to strictly control the clearance with the vanes.

Conventional vane grooves will be explained based on the rotor shown in FIGS. 6 to 8.

Figure 6 is a diagram showing the entire shaft and rotor, and Figure 7
The figure shows the rear shaft 106 from the shaft & rotor in Figure 6.
It is a diagram with the holder removed.

The rotor 103 formed integrally with the shaft 105 includes
Four grooves 102 are formed at equal intervals in the circumferential direction. These vane grooves 102 are formed on one axial end surface of the rotor 103, that is, on the rear shaft 1.
The end face on the side where 06 is connected is open and communicated with each other in a cross shape (see Fig. 5).

Further, the other front end surface of these vane grooves 102 in the axial direction is a front side small diameter boss portion 107 of the rotor 103.
It is blocked.

The vanes 101 are fitted into these vane grooves 102 so as to be slidable in the radial direction.

Therefore, the axial length ρ of the vane groove 102 is
It is necessary to strictly specify the dimensional tolerance in relation to the axial length of the vane groove 102, and the radial dimension of the vane groove 102, that is, the width W of the vane groove, must be determined with high precision in relation to the width of the vane 101. It is necessary to specify. Therefore, the vane groove 102 is finished by grinding each end surface 111 and side surface 112 (each shown in detail in FIG. 8) with the rear shaft 106 shown in FIG. 7 removed.

On the other hand, the vanes 101 that are slidably disposed in these vane grooves 102 have edges 101a at their axial ends that are processed into a nearly right-angled shape without chamfering in order to ensure a refrigerant sealing length.

On the other hand, the corner portion of the vane groove 102 where the axial end surface 111 and the side surface 112 intersect needs to be made as perpendicular as possible so that the vane 101 can freely slide without interference.

However, in reality, as described above, the inner surface of the vane groove 102 is polished, and it is difficult to control the dimensions of the corners due to wear and chipping of the polishing wheel during manufacturing, which increases manufacturing costs.

For this reason, conventionally, a concave relief 113 as shown in FIG. 8 is formed at the corner before the polishing process.

[Problems to be Solved by the Invention] However, when the concave escape portion 113 is provided at the corner of the vane groove 102, the vane 1
When 01 was assembled and the compressor was operated, a gap 109 as shown in FIG. 8 was formed, which increased the leakage of the compressed refrigerant and became one of the factors that reduced the performance of the compressor.

In addition, the concave relief portion 113 requires special machining and causes a deterioration of the symmetry with respect to the vane groove 102. Therefore, dimensional control of the relief portion 113 is necessary to stabilize the performance of the compressor. Therefore, there are some problems that require time and effort.

The present invention has been made based on the above-mentioned circumstances, and it is possible to eliminate the machining of the concave relief part, and the polishing process is easy and requires no manufacturing effort, and the gap between the vane and the vane groove can be formed with high precision. The objective is to provide a Thruhan type compressor that can be controlled and improve the performance of the compressor.

[Means for Solving the Problems] The present invention provides a method in which a closing member such as a ring member is attached to the small-diameter boss portion of the rotor, and the end of the vane groove is closed with the closing member. It is characterized in that the end face of the vane groove is formed of a member.

[Function] According to the present invention, when machining the vane groove, the axial dimension of the vane groove is made slightly smaller than the predetermined dimension g (for example, 0.5 to 1 mm), and then finish only the side surfaces of the vane groove to the required width W by grinding. At this time, the axial end face of the Hoehn groove is not ground. Next, a closing member such as a ring member is attached to the small-diameter boss portion on the front side of the rotor, and the axial end of the vane groove is closed with this closing member. As a result, the axial end surface of the vane groove is constituted by the side surface of the closing member.

Since the side surface of this closing member can be polished in advance, the axial length of the vane groove can be set to a predetermined dimension p.

Such a vane groove is formed by a side surface that has been polished in advance and an end surface formed by the closing member, so that the corners of the vane groove are at right angles.

Therefore, there is no need to control the corner dimensions of the vane groove, and there is no need to consider dimensional changes due to wear of the grindstone.

In addition, since there is no need to consider interference between the vanes and the corners of the vane grooves, there is no need to chamfer the edges of the end faces, and the length of the vanes can be set longer, and the gap between the vane grooves and the vanes This reduces refrigerant leakage from the working chamber within the compressor, improving performance.

[Example] The present invention will be described below based on an example shown in FIGS. 1 to 5.

First, the overall structure of the through-vane compressor will be explained based on FIGS. 4 and 5.

In the figure, 5 is a drive shaft, and 3 is a rotor formed integrally with this shaft 5.
is made of chromium steel (SCr9), and its coefficient of thermal expansion is 12
It is about X10-6. A vane groove 2 is formed in the rotor 3 in the shape of a cross from one side surface of the rotor 3 over its entire length in the width direction. (Illustrated in Figure 5) ① is a vane that is slidably disposed in this vane groove 2 and has a substantially U-shape, and the wall thickness of the central portion 1a is thinner than the wall thickness of the vane main body portion 1b. ing. The vane 1 is made of a high-silicon aluminum alloy, and its coefficient of thermal expansion is 18.
It is about X10-6.

Further, the tip IC of the vane 1 has a tapered shape that is somewhat thin.

A rear shaft 6 covers one end surface of the rotor 3, and is connected to the rotor 3 via a bolt (not shown).

As shown in Figures 1 and 2, the axial length of the vane 1 is equal to the axial length of the rotor 3 at room temperature (about 20°C)! It is about 0.05 city smaller than the previous year. Specifically, the axial length of the vane 1 is, for example, 35+++u
Based on the difference in thermal expansion coefficient between the rotor 3 and the vane 1 mentioned above, the temperature of the rotor 3 and the vane 1 are both 120
℃, the axial length of the vane 1 matches the axial length Ω of the rotor 3, and when the temperature rises further, the axial length of the vane 1 matches the axial length of the rotor 3. The length is set to be larger than the length g.

Note that the vane groove 2 will be explained in detail later.

A housing 8 houses the rotor 3, and is made of metal, such as cast iron (FC), and has a substantially cylindrical inner surface 8a. The inner surface 8a of the housing, the outer surface of the rotor 3, and the vane 1 form a working chamber R.

9 is a discharge hole formed in the housing 8, 10 is a discharge valve that covers this discharge hole, and 11 is a cover of this discharge valve 10. These discharge valve 10 and cover 11 are fixed to housing 8 with screws 12.

13 is a discharge chamber l1 housing that covers the discharge valve 10, and is fixed to the housing 8 with a bolt 15 via an elastic ring 14.

A rear side plate 16 is disposed at one end of the housing 8 via an O-ring 17, and is made of cast iron (FC), which is the same metal as the housing 8. This side plate 16 has a sludge pot 19 opened at a position facing the discharge passage 18 communicating with the discharge chamber 13a and the working chamber R. Further, a bearing 38 is press-fitted into the side plate 16, and the rear shaft 6 is rotatably supported by this bearing 38.

Note that 22 indicates the discharge chamber housing 13 and the side plate 1.
This is an O-ring that seals between the discharge passage 18 and the periphery of No. 6.

An oil separator 20 is disposed on the side plate 16 via a gasket 21, and communicates with the discharge chamber 13a via the discharge passage 18.

Inside this oil separator 20 is a sludge hull 2.
3, and this valve 23 is fixed to the side plate 16 with a spring 24 and a valve holder 25 with screws 26.

This slack valve 23 opens when the pressure in the working chamber R becomes higher than the pressure in the oil separator 20 by more than the set force of the spring 24, and prevents abnormally high pressure in the working chamber R. be.

An oil supply passage 27 is formed in the valve holder 25, and this passage 27 communicates with the lower surface of the oil separator 2o via an oil supply valve 28. Therefore, the lubricating oil accumulated in the lower part of the oil separator 2o is pushed up toward the oil supply passage 27 side by the pressure difference.
It is supplied to one end surface of the rerotor 3.

In addition, 29 is an oil filter, 3o is an oil check valve, and 31 is connected to the oil separator 2o via an O ring 32.
This is a discharge pipe attached with bolts 33. 3
4 is a blind plug for sealing this discharge pipe 31, and 49 is a discharge charging valve attached to the pipe 31.

After the refrigerant discharged from the discharge chamber 13a to the oil separator 20 separates the lubricating curve in the oil separator 20,
It is discharged from the discharge pipe 31.

A front side plate 35 is attached to the other end of the housing 8 via an O-ring 36, and is made of cast iron (FC), which is the same metal as the housing 8. A bearing 37 is driven into this side plate 35, and this bearing 37 causes the shaft 5 to
is rotatably supported.

This side plate 35 has a suction chamber and a working chamber R, which will be described later.
A suction hole 56 is opened to connect the two.

39 is a front housing attached to the side plate 35 via a gasket 40, and has a suction chamber 4 inside.
1 and an oil storage chamber 42. A boss portion 43 is formed on the outer periphery of the front housing 39, and an electromagnetic clutch (not shown) is attached to the boss portion 43.

44 is a suction pipe attached to the front housing 39 via an O-ring 45 with a bolt 46; 47 is a suction charging valve provided in the middle of this pipe 44;
48 is a blind stopper that seals this vibrator 44.

Reference numeral 50 denotes a shaft seal for sealing between the shaft 5 and the front housing 39, which includes a carbon ring 51 that rotates integrally with the shaft 5, and an O-ring 5 attached to the housing 39.
It consists of a fixing ring 53 fixed via 2.

The front housing 39, the gas nut 40, the side plate 35, the housing 8, the side plate 16,
The gasket 21 and the oil separator 20 are integrally connected by a through bolt 55.

The vane groove 2 will now be explained based on FIGS. 1 to 3.

Figure 1 shows the entire shaft and rotor, and Figure 2 shows the entire shaft and rotor.
The figure shows a state in which the rear shaft 6 is removed from the shaft and rotor shown in FIG. 1.

As explained earlier, the axial length of the vane groove 2 formed in the rotor 3 must be strictly regulated in relation to the axial length of the vane 1. Groove 2
is formed from the rear side end of the rotor 3 to extend over the front side small diameter boss portion 7, thereby making it slightly longer than the predetermined axial length g, for example, about 0.5 to 1 w.

In this case, only the side surface 62 of the vane groove 2 is ground, thereby finishing the width of the vane groove 2 to the required width dimension W, and the axial end surface 63 of the vane groove 2 that hangs over the small diameter boss 7 is polished. Not processed.

The front small-diameter boss portion 7 of the rotor 3 includes:
A ring member 60 serving as a closing member is fixed by means such as a presser. This ring member 60 is made of the same type of chromium steel (S C r 9) as the rotor 3, and covers the axial end surface 63 of the vane groove 2 that extends over the small diameter boss 7, and the end surface 61 of this ring member 60 is substantially vane groove 2
It forms the end face of

The end surface 61 of this ring member 60 is polished in advance, and when it is fitted into the front small diameter boss portion 7 of the rotor 3 and faces the vane groove 2, the ring member 60
The axial length g of the bevel groove 2 is determined by the edge 61 of 0.

The operation of the compressor according to the embodiment having such a configuration will be explained.

When the rotational force of the automobile engine is transmitted to the shaft 5 via an electromagnetic clutch (not shown), the shaft 5 rotates within the housing 8. In a region where the working chamber R expands in volume with this rotation, the refrigerant introduced into the suction chamber 41 from the evaporator of the refrigeration cycle is sucked into the working chamber R through the suction hole 56. The sucked refrigerant is compressed as the volume of the working chamber R decreases, and is discharged from the discharge valve 9 into the discharge chamber 13a.Then, after separating the lubricating oil in the oil separator 20, the refrigerant is sent from the discharge pipe 31 to the condenser of the refrigeration cycle. It is discharged to the side.

When starting up, if there is liquefied refrigerant in the working chamber, if the engine continues to rotate, the pressure in the working chamber R will become abnormally high. However, in the compressor of this embodiment, when the pressure in the working chamber R becomes abnormally high, the sludging knob 23 or the sludge port 19 is opened, so the liquid refrigerant escapes from the sludge port 19 to the oil separator 20 side. , an abnormal rise in pressure within the working chamber R and the resulting damage to the vane 1 are prevented.

Moreover, in the compressor of this embodiment, the axial length of the vane 1 is set to a special value, and during low-temperature operation, the axial length L of the vane 1 is the length of the rotor 3, that is, the axis of the vane groove 2. The axial length of the vane 1 becomes smaller than the axial length g of the rotor only during high temperature operation. Therefore,
During low temperature operation, the end face of the rotor 3 may experience side play}35.
16 to prevent displacement of the rotor 3 in the axial direction. Then, the end or side play of vane 1 only during high temperature operation.
Contact with 16.35. Therefore, the metals of the rotor 3 and the side plate 16.35 do not come into direct contact with each other during high temperature operation, and the rotor 3 and the side plate 16.35 do not come into direct contact with each other.
5 is prevented from galling.

Further, in this embodiment, the lubricating oil accumulated in the lower part of the oil separator 20 is supplied to the end surface of the rear shaft 6 from the suction passage 27, and the lubricating oil is then guided from the outer surface of the rotor to the bearing 37 side due to the pressure difference. . Therefore, the bearings 37 and 38, the space between the rotor 3 and the housing 8, and each part of the shaft seal 50 are reliably supplied with oil.

According to this embodiment, since the end surface 61 of the ring member 60 press-fitted into the front small diameter boss portion 7 of the rotor 3 forms the front end surface of the vane groove 2, the axial length of the vane groove 2 is It is possible to determine the distance P with high precision, and it is easy to process and manufacture.

That is, when machining the vane groove 2, the rotor 3 is pre-processed with a diameter slightly longer than the predetermined dimension g of the vane groove, for example, 0.5 mm.
A groove approximately 1 mm long is machined, and only the side surface 62 of this vane groove 2 is ground to the required width W.

At this time, the axial end face of the vane groove 2 is not ground.

Next, a ring member 60 is attached to the front small-diameter boss portion 7 of the rotor 3, and the end of the ring member 60 covers the axial end of the vane groove 2. As a result, the axial end surface of the revane groove 2 is substantially formed by the end surface 61 of the ring member 60.

With such a configuration, the end surface 61 of the ring member 60 can be polished in advance, so that the axial direction of the vane groove 2 can be regulated by setting the mounting position of the ring member 60. I can do it.

Since this vane groove 2 has a corner formed by the previously polished side surface 62 and the end surface formed by the end surface 61 of the ring member 60, this corner becomes a right angle.

Therefore, there is no need to manage the corner dimensions of the vane groove 2, and there is no need to consider dimensional changes due to wear of the grindstone.

In addition, since there is no need to consider the interference of the vane 1 with the corners of the vane groove 2, there is no need to chamfer the edges of the vane.
The seal length of the vane 1 can be set long, reducing refrigerant leakage from the working chamber R within the compressor, and improving compression performance.

The inventors conducted experiments and studies comparing a conventional compressor with a concave relief part and a compressor with vane grooves 2 as in the above embodiment, and found that the compressor At a rotational speed of about 100 rpm, it was observed that the volumetric efficiency, which indicates the performance of the compressor, was improved by 2 to 3% in this example.

In the above embodiment, the rotor 3, the housing 8, and the sight plates 16 and 35 are made of iron, and the vane 1 is made of an aluminum alloy, but it is of course possible to use metal materials other than those mentioned above. In other words, any material may be used as long as the rotor 3, housing 8, side plates 16 and 35 are made of the same metal, and the vane 1 is made of a metal material with a higher coefficient of thermal expansion. Other materials such as carbon fiber resin and ceramic may be used instead of the material.

Further, in the case of the above embodiment, the ring member 60 is fixed to the front side small diameter boss portion 7 of the rotor 3 by press fitting, or the ring member 60 may be fixed to the rotor 3 by screwing.

Further, in the embodiment, the material of the ring member 60 is made of steel similar to that of the rotor 3, but if the rotor 3 is made of steel and the front side plate 35 is made of aluminum, the ring member 60 may be made of aluminum or resin. With such a combination of materials, if the temperature inside the compressor rises during operation, the ring member 60 will thermally expand and the side plate 3 will
5, it is possible to prevent the gap between the small diameter boss portion 7 on the front side from expanding due to thermal expansion.

Furthermore, in the case of the above embodiment, the ring member 60 press-fitted into the front side small diameter boss portion 7 was used as a member for closing the end of the vane groove 2, but such a closing member is not necessarily limited to the ring shape. It may be a pro-socket member that closes the end of the vane groove 2.

[Effects of the Invention] As explained above, according to the present invention, the axial end of the vane groove is closed by the closing member attached to the rotor, and the end face of the closing member constitutes the axial end face of the vane groove. , there is no need to machine a special concave relief part at the corner of the vane groove, and thus the troublesome machining of the concave relief part can be abolished, and the polishing process of the inner surface of the vane groove becomes easy. It saves manufacturing time. Furthermore, the gap between the vane and the vane groove can be managed with high precision, and refrigerant leakage from the working chamber can be reduced, so that the performance of the compressor can be improved.

[Brief explanation of drawings]

1 to 5 show an embodiment of the present invention,
Figure 1 is a side view showing the entire shaft and rotor, Figure 2 is a sectional view with the rear shaft removed from the shaft and rotor, Figure 3 is an enlarged view of the part ■ in Figure 1, and Figure 4 is 5 is a sectional view showing the entire compressor, FIGS. 6 to 8 show the conventional configuration, FIG. 6 is a side view showing the entire shaft and rotor, and FIG. 7 is a sectional view showing the entire compressor. FIG. 8 is an enlarged view of the part 2 in FIG. 6. 1... Vane, 2... Vane groove, 3... Rotor, 5
... Shaft, 6... Rear shaft, 7... Boss portion, 8... Housing, 16, 35... Side plate, 60... Ring member, 61... End surface of ring member, 62 ...Side surface of vane groove, 63... End surface of vane groove.

Claims (1)

[Claims] A shaft that rotates in response to a driving force, a cylindrical rotor that rotates together with the shaft and has a vane groove extending from one end in the axial direction to the other end, and a cylindrical rotor that is slidably arranged in the vane groove of the rotor. A through-vane compressor comprising: a vane installed in the rotor; a housing that houses the rotor and forms an operating chamber between the outer periphery of the rotor and the vane; and a side plate that covers an end surface of the housing. A through-vane type compressor, characterized in that a closing member for closing an axial end of the vane groove is attached to an end of the vane groove, and the closing member forms an axial end face of the vane groove.