JPS62195485A - Vane type compressor - Google Patents

Abstract

PURPOSE:To improve the performance by making the edge surface of a side block on a suction chamber side, free from the contact part with the edge surface of a rotor and making the position in the axial direction of each suction chamber side edge surface of a cam ring and the rotor nearly same and reducing the clearance between parts. CONSTITUTION:A bypass port 23 formed on a side block 8 positioned on the fluid suction chamber 17 side in the both side blocks 8 and 9 and a recessed part 22 formed on the opposed edge surface to the side block 8 on the suction chamber 17 side are formed, and a control member 24 for controlling the opened port area of the bypass port fitted into the recessed part 22 is installed. The edge surface of the side block 8 is made free from the contact part with the edge surface of a rotor 10, and each position in the axial direction of the suction chamber 17 side edge surface of a cam ring 7 and the suction chamber 17 side edge surface of the rotor 10 is made nearly same. Therefore, the increase of the clearance between the parts is prevented with the variable discharge capacity, and the leak of coolant is reduced, and the driving power can be reduced, and the discharge temperature can be lowered.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vane compressor used as a refrigerant compressor for, for example, an automobile air conditioner.

(Prior art and its problems) Generally, a vane type compressor has a front side block 8 and a rear side block 9 on both sides, as shown in FIG.
Both end surfaces of the rotor 10 disposed within the cam ring 7 which is closed are held between the end surfaces of the two side blocks 8.9.

In this case, in order for the rotor 10 to rotate, a clearance t2 between the end face of the rear side block 9 and a clearance t2 between the end face of the front side block 8 is required. These clearance works and t
7 refers to variations in the individual dimensions of the cam ring 7 and rotor 10, deformation of the cam ring 7, etc. when the cam ring 7 is tightened by both side blocks 8.9, and cam ring 7 and side blocks 8.9 due to refrigerant pressure within the cam ring 7.
This is necessary to absorb deformation, etc.

By the way, in order to make the discharge capacity of the vane type compressor as described above variable, the rotor 1 of the front side block 8 is
By rotating a ring-shaped control member 24 provided in an annular recess 22 formed on the end face opposite to 0, the opening area of the bypass port 23 that communicates between the suction chamber 17 and the inside of the cam ring 7 is changed. A vane type compressor has been proposed by the present applicant (Japanese Patent Application No. 1986-160).
No. 760). This ring-shaped control member 24 is connected to the end face of the recess 22 of the front side block 8 and the end face of the cam ring 7 (
(The end face of the part where the inner peripheral surface of the cam ring 7 has the short diameter)
It is designed to be held in place.

In this case, in order for the ring-shaped control member 24 to rotate,
The end surface of the cam ring 7 (the portion 7b where the inner circumferential surface 7a is the minor diameter)
(See FIG. 3) and clearance between the end face of the recess 22 of the front side block 8, respectively. These clearances and
and t4 are also necessary for absorbing variations in individual dimensions and deformation of each component, similar to the above-mentioned clearance work and shi 2.

From the above, in the variable displacement vane compressor as described above, the clearance between the opposing end surfaces of the ring-shaped control member 24 and the rotor 10 is 1, +1. Therefore, the clearance from the inside of the cam ring 7 is 12+1. The amount of leaked refrigerant that leaks into the suction chamber 17 via the bypass port 23 increases to a certain extent, which requires extra rotational driving force and generates unnecessary heat, increasing the discharge temperature. There were problems such as

(Object of the Invention) The present invention has been made in view of the above circumstances, and although the discharge capacity is variable, the clearance between each part is not increased to reduce leakage refrigerant, thereby reducing driving force and The purpose of the present invention is to provide a high-performance vane compressor that reduces discharge temperature.

(Means for Solving the Problems) In order to achieve the above object, the present invention includes a cam ring whose both sides are closed with side blocks, a rotor rotatably disposed within the cam ring, and a rotor that is rotatably disposed within the cam ring. A vane type compressor is provided with a vane slidably fitted in a vane groove of the side block, the cam ring, the rotor, and the vane, and compresses fluid by changing the volume of a cavity defined by the side block, the cam ring, the rotor, and the vane. , a bypass port provided in the side block located on the fluid suction chamber side of both the side blocks, a recess formed in the end surface of the side block facing the rotor on the suction chamber side, and a recess formed in the recess. A control member is fitted to control the opening area of the bypass port, and the end face of the side block on the suction chamber side has no portion where the end face of the rotor abuts, and the end face of the cam ring on the suction chamber side and the The structure is such that the axial position of the rotor is substantially the same as the end surface of the rotor on the suction chamber side.

(Function) There is no part where the end face of the rotor hits the end face of the side block on the suction chamber side, and the axial positions of the end face of the cam ring on the suction chamber side and the end face of the rotor on the suction chamber side are approximately the same, so that the rotor and control The clearance between the end faces facing the member is shared by the rotor and the control member, that is, this clearance is a necessary clearance for the rotor to rotate and a clearance necessary for the control member to rotate. Therefore, the clearance between the opposing end surfaces of the control member and the rotor is reduced.

(Example) ' Hereinafter, one embodiment of the present invention will be described based on the accompanying drawings.

FIG. 1 is a side sectional view of a vane type compressor of the present invention, and in the figure, 1 is a housing, which is a cylindrical case 2 with one end open, and one end of the case 2 is closed with the opening. It consists of a front head 3 attached with bolts (not shown). A discharge port 4 for refrigerant gas, which is a heat medium, is provided on the upper surface of the rear side of the case 2, and a discharge port 4 for refrigerant gas, which is a heat medium,
A refrigerant gas inlet 5 is provided on the upper surface of each of the refrigerant gases.

The discharge port 4 and the suction port 5 communicate with a discharge chamber and a suction chamber, respectively, which will be described later.

A pump body 6 is housed inside the housing 1. The pump body 6 includes a cam ring 7, a front side block 8 and a rear side block 9 attached to both open ends of the cam ring 7 so as to close the opening surfaces.
The main components are a circular rotor 1o rotatably housed inside the cam ring 7 and a rotating shaft 11 of the rotor 10, and the rotating shaft 11 is connected to each bearing provided on both side blocks 8.9. 12.12' is rotatably supported. Further, there is a clearance t1 between the opposing end surfaces of the rotor 10 and the rear side block 9, and the axial positions of the end surface of the cam ring 7 on the suction chamber 17 side and the end surface of the rotor 10 on the suction chamber 17 side are made the same.

The inner circumferential surface 7a of the cam ring 7 has an elliptical shape, as shown in FIG. A void chamber 13.13 is defined.

A plurality (for example, four) of vane grooves 14 are provided in the rotor 10 at equal intervals in the circumferential direction along the radial direction of the rotor 10,
Vanes 15□ to 154 are fitted into these vane grooves 14 so as to be freely protrusive and retractable along the radial direction.

The front side block 8 is provided with suction ports 16, 16 symmetrically offset by 180 degrees in the circumferential direction (see FIGS. 2 to 7). These suction ports 16.16 are the void chambers 1 divided by the vanes 151-154.
It is placed at the position where the volume of No. 3 is maximum. The suction ports 16.16 pass through the front side block 8 in the thickness direction, and through these suction ports 16,
The suction chamber (low pressure side chamber) 17 between the front head; third front side block 8 and the gap chamber 13 communicate with each other.

Discharge ports 18 and 18 are provided on both side peripheral walls of the cam ring 7.
are provided, and a discharge chamber (high-pressure side chamber) 19 in the case 2 and the gap chamber 13 communicate with each other via these discharge ports 18 . These discharge ports 18, 18 are provided with a discharge valve 20 and a discharge valve stop 21, respectively, as shown in FIG.

As shown in FIG. 8, the front side block 8 is provided with an annular recess 22 having a larger diameter than the rotor 10 on the surface of one side (rotor 10 side). The end face of the rotor 10 has no abutting portion. Said recess 2
2, an arc-shaped bypass port 23.23 is located in the circumferential direction.
The suction chamber 17 and the void chamber 13 communicate with each other through the bypass ports 23, which are arranged symmetrically with an offset of 80 degrees.

Further, within this recess 22, the bypass port 23.2 is provided.
A ring-shaped control member 24 for controlling the opening angle of 3 is fitted so as to be rotatable in forward and reverse directions. There is a clearance t4 between the control member 24 and the recess 22, and a clearance t5 between the control member 24 and the cam ring 7, and between the control member 24 and the rotor 1o. . This clearance is also necessary for the rotation of the rotor 10 mentioned above, and the rearance t2 and the control member t
The clearance t required for the rotation of , is set to the larger value. Therefore, t, = t2 or ts < t
2 + t3. Furthermore, an arc-shaped notch 25.25 is provided on the outer peripheral edge of the control member 24 symmetrically and offset by 180 degrees in the circumferential direction. Furthermore, pressure receiving members 26 and 26 in the shape of protrusions are integrally provided on one side of the control member 24 and symmetrically offset by 180 degrees in the circumferential direction. These pressure receiving members 26.26 are connected to an arcuate pressure operating chamber 27.26 provided continuously with the bypass port 23.23.
27 so as to be slidable. The inside of these pressure working chambers 27 is divided into a first chamber 271 and a second chamber 27□ by the pressure receiving member 26, and the first chamber 27□ is connected to the suction chamber 17 through the suction port 16 and the bypass port 23. The second chamber 27□ is connected to the discharge chamber 19 through the orifice 28.
communicate with each other.

Said one second chamber 27. and the other second chamber 272 communicate with each other via the communication hole 29, and the one second chamber 27
The orifice 28 is interposed between □ and the discharge chamber 19.

A specially shaped seal member 30 is attached to the central portion of one side of the control member 24 and to both end faces of the pressure receiving member 26 . The sealing member 30 allows a gap between the first chamber 27□ and the second chamber 27□ as shown in FIG. 8 and the center portions of the annular recesses 22 are airtightly sealed.

The control member 24 uses a coil spring 31, which is a biasing member, to control the bypass port 23 in a direction (
(counterclockwise in FIG. 5). This coil spring 31 is fitted onto the outer circumferential side of the central boss portion 8a of the front side block 8 that extends toward the suction chamber 17 side. One end of this coil spring 31 is connected to the central boss portion 8a.

The other ends are connected to the control member 24, respectively.

The other second chamber 27□ is connected to the communication passage 3 as shown in FIG.
2, and communicates with the suction chamber 17 through the communication path 3.
2 is provided with an on-off valve mechanism 33. The opening/closing valve mechanism 33
is opened and closed in response to the pressure on the suction chamber 17 side (low pressure chamber side), and includes a bellows 34, a case 35, a ball valve body 36, and a spring that biases the ball valve body 36 in the valve closing direction. It consists of 37. When the pressure on the suction chamber 17 side is above a predetermined value, the bellows 34 is in a contracted state, and the ball valve body 36 closes the communication passage 32 by the biasing force of the spring 37. Further, when the pressure on the side of the suction chamber 17 is below a predetermined value, the bellows 34 is expanded and the rod 3 at the tip thereof is expanded.
4a, the ball valve body 36 is pressed against the urging force of the spring 37 to open the communication passage 32. An O-ring 38 is interposed between the case 35 and the front side block 8.

On the other hand, a magnetic clutch 40, which is a power transmission means, is connected to an end of the rotating shaft 11.

The magnetic clutch 40 connects to the rotating shaft 1 via a hub 41.
1; a pulley 43 rotatably supported on the boss portion of the front head 3 via a pole bearing; and a clutch coil 44 fixed to the end surface of the front head 3. .

(Operation) Next, the operation of the vane compressor of the present invention having the above configuration will be explained.

When the pulley 43 is rotated in relation to the engine of the vehicle and the rotor 10 is rotated clockwise in FIG. The vanes 15□ to 154 rotate together with the rotor 10 while their tip surfaces slide in contact with the inner circumferential surface 7a of the cam ring 7.
In the suction stroke to expand the volume of the void chamber 13 divided by is compressed, and in the discharge stroke at the end of the compression stroke, the discharge valve 20 is opened by the pressure of the compressed refrigerant gas, and the compressed refrigerant gas sequentially passes through the discharge port 18, the discharge chamber 19, and the discharge port 4 (not shown). Supplied to the heat exchange circuit of the air conditioner.

During operation of such a compressor, the pressure in the suction chamber 17, which is the low pressure side, is introduced into the first chamber 271.27 of both pressure working chambers 27.27 through the suction port 16,
In addition, the pressure in the discharge chamber 19 on the high pressure side flows through the orifice 28.
via both pressure working chambers 27.27 and the second chamber 27□
, 272. Therefore, the force (control member 2
4 in the direction that increases the opening angle of the bypass port 23, that is, the force that rotates it in the direction of arrow B in FIG. The control member 24 rotates in response to the differential pressure between the bypass port 23 and the force that presses the opening angle in the direction that reduces the opening angle (that is, the force that rotates it in the direction of arrow A in FIG. 5), thereby controlling the opening angle of the bypass port 23. By doing so, the compression start timing is controlled and the discharge capacity is controlled.

That is, when the compressor is operated at low speed, the pressure of refrigerant gas (suction pressure) in the suction chamber 17 is relatively high, so the bellows 34 of the on-off valve mechanism 33 contracts, and the ball valve body 36 closes the communication path 32. In the closed state, the pressure in the second chamber 27□ overcomes the sum of the pressure in the first chamber 271 and the biasing force of the coil spring 31, and the control member 24 moves in the direction indicated by the arrow in FIG. The control member 24 closes the entire bypass port 23 as shown by the two-dot chain line in FIG. 5 (the opening angle is zero). Therefore,
Since all of the refrigerant gas sent into the cavity chamber 13 from the suction boat 16 is compressed and discharged, the discharge capacity of the compressor becomes maximum and becomes fully operational.

Next, when the compressor enters a high-speed operation state, the suction pressure in the suction chamber 17 decreases, so the bellows 3 of the on-off valve mechanism 33
4 expands and the rod 34a pushes the ball valve body 36 against the spring 37.
The communication passage 32 opens because the valve is opened by pressing against the urging force of the valve. As a result, the pressure in the second chamber 27□ leaks into the suction chamber 17, which is the low pressure side, through the communication path 32, so the pressure in the second chamber 27□ decreases, and as a result, the control member 24 rotates in the direction of arrow B in FIG.
When the notch 25 of No. 4 matches the bypass port 23, the bypass port 23 opens as shown by the solid line in FIG. Therefore, the refrigerant gas sent into the cavity chamber 13 from the port 16 passes through the bypass port 23 and passes through the suction chamber 17.
Due to the leakage, the compression start timing is delayed by the amount that the bypass port 23 is opened, and the amount of compression of the refrigerant gas in the void chamber 13 is reduced, so the discharge capacity of the compressor is reduced and the compressor is in a partially operating state.

Note that the opening angle of the bypass port 23 is the same as that of the first chamber 2.
71 and the force of the spring 37, and the second chamber 27□
The rotational position of the control member 24 changes continuously according to changes in the pressure (suction pressure) in the suction chamber 17, which is the low pressure side, so the compressor continuously variable capacity control is possible. Further, although the pressure of the discharge chamber 19, that is, the discharge pressure, is introduced into the second chamber 27□, the pressure that acts to press the vanes 151 to 154 in the protruding direction, that is, the vane back pressure, is not limited to this. You may also do so.

Furthermore, in the above embodiment, the suction chamber 1 of the cam ring 7
Although the axial position of the end face of the rotor 10 on the suction chamber 17 side is the same as that of the end face of the rotor 10 in the axial direction, the end face of the rotor 10 on the suction chamber 17 side is aligned with the front side block as shown in FIG. 8, and the clearance t between the ring-shaped control member 24 and the rotor 10.

may be set to zero. In this case, the clearance t.

Even without the control member 24 due to the elasticity of the seal member 30,
can move in the axial direction, the rotation of the rotor 1o and the rotation of the control member 24 are not hindered.

(Effects of the Invention) As detailed above, the vane compressor of the present invention includes a cam ring whose both sides are closed with side blocks, a rotor rotatably disposed within the cam ring, and a vane of the rotor. In the vane type compressor, the vane is provided with a vane slidably fitted in the groove, and the fluid is compressed by a change in volume of a cavity defined by the side block, the cam ring, the rotor, and the vane. a bypass port provided on a side block located on the fluid suction chamber side of both side blocks; and a recess formed in an end surface of the side block on the suction chamber side facing the rotor;
a control member that is fitted into the recess and controls the opening area of the bypass port; the end face of the side block on the side of the suction chamber has no portion abutting with the end face of the rotor; Since the axial positions of the side end surface and the end surface of the rotor on the suction chamber side are made approximately the same, although the discharge capacity is variable, the clearance between each component is not increased and leakage of refrigerant is reduced.
This has the effect of reducing the driving force and the discharge temperature.

[Brief explanation of drawings]

FIG. 1 is a side sectional view showing one embodiment of the vane type compressor of the present invention, and FIG.
A sectional view along the line, Figure 3 is the same as Figure 1 or Figure 9 or Figure 10.
4 is a sectional view taken along line IV--IV of FIG. 1 or 9 or 10; FIG. 5 is a sectional view taken along line IV-IV of FIG. A cross-sectional view along the line ■-■ in the figure,
6 and 7 are cross-sectional views taken along line VI-VI in FIG. 4, FIG. 8 is an exploded perspective view of the main parts, and FIG. 9 shows another embodiment of the vane compressor of the present invention. FIG. 10 is a side sectional view showing an example of a conventional vane compressor. 7... Cam ring, 8... Front side block, 9.9a... Rear side block, 10... Rotor, 13... Gap chamber, 14... Vane groove, 151~
154... Vane, 16... Suction port, 17...
・Suction chamber (low pressure side chamber), 19...Discharge chamber (high pressure side chamber)
, 23... Bypass port, 24... Ring-shaped control member, 26... Pressure receiving member, 27... Pressure operating chamber, 2
7□...First room, 27□...Second room, 30...
・Seal member, 31... Coil spring (biasing member), 3
2... Communication path, 33... Open/close valve mechanism, 34... Bellows, 34a... Rod, 35... Case, 36... Ball valve body, 37... Spring.

Claims (2)

[Claims] 1. A cam ring with both sides closed by side blocks, a rotor rotatably disposed within the cam ring, and a vane slidably fitted into a vane groove of the rotor, the side block, the cam ring, In a vane compressor that compresses fluid by changing the volume of a cavity defined by a rotor and vanes, a bypass provided in the side block located on the fluid suction chamber side of both the side blocks. a port, a recess formed in an end surface of the side block facing the rotor on the suction chamber side, and a control member fitted in the recess to control the opening area of the bypass port; A vane type characterized in that the end face of the side block has no part where the end face of the rotor abuts, and the axial positions of the end face of the cam ring on the suction chamber side and the end face of the rotor on the suction chamber side are approximately the same. compressor. 2. 2. The vane compressor according to claim 1, wherein an end surface of the rotor on the suction chamber side is slightly inserted into a recess of the side block on the suction chamber side.