KR910002785B1 - Variable capacity compressor - Google Patents

Abstract

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Description

Variable displacement compressor

1 to 6 show one embodiment of the present invention, and FIG. 1 is a longitudinal sectional view showing a variable displacement vane compressor.

2 is a cross-sectional view taken along the line II-II of FIG. 1, showing some operating positions.

3 is a cross-sectional view similar to FIG. 2 showing the entire operating position.

4 is a cross-sectional view taken along line IV-VI of FIG.

5 is an exploded perspective view of the main parts.

6 is a plan view of the control member.

7 is a plan view showing another control member.

8 is a schematic configuration diagram showing a discharge capacity control mechanism.

9 is a cross-sectional view taken along line IV-VI of FIG.

* Explanation of symbols for main parts of the drawings

12 ₁ : compression chamber on one side 12 ₂ : compression chamber on the other side

14 ₁ -14 _s : Vane 27, 27 ': Control material

28 ₁ -28 ₂ : Notch part Pc: Control pressure

Ps: suction pressure

The present invention provides a variable displacement compressor capable of variable control of discharge capacity by controlling the start time of compression, in particular, the variable discharge rate of the discharge capacity in one of the two compression chambers is greater than that of the other compressor. It relates to a variable displacement compressor with an enlarged variable rate of.

Conventionally, as the variable displacement compressor, techniques such as Japanese Patent Application No. 62-193274, Japanese Patent Application No. 62-323490 have been proposed by the present applicant.

This technique has two compression chambers located at symmetrical positions in the circumferential direction, and two compression chambers each having a notch corresponding to each of the compression chambers, and each compression according to the rotational motion according to the difference between the high pressure control pressure and the low pressure suction pressure. A control member for controlling the compression start timing of the yarn is provided, and the shape of each notch portion is changed so that the compression start timing at some operating positions of the compression chamber is later than that of the other compression chamber. The variable rate of the discharge capacity of the compressor is enlarged more than that of the other compression chambers.

However, in the prior art, the control pressure is generally supplied from one side of the two compression chambers. In addition, since the control member is located at some operating positions at the start of the compressor, the compression start time at some operating positions is different. In the case where the control pressure is supplied from the compression chamber as described above, the discharge pressure at some operating positions is lower than that of the seal, there is a problem that the control pressure does not easily rise at the start of the compressor, so that startability is not good.

SUMMARY OF THE INVENTION The present invention has been made in view of such a conventional problem, and an object of the present invention is to provide a variable displacement compressor capable of improving startability while increasing the variable rate of the discharge capacity of the entire compressor.

In order to achieve the above object, the variable displacement compressor according to the present invention has two compression chambers located at symmetrical positions in the circumferential direction and two notches corresponding to the respective compression chambers on the outer periphery, and the control pressure and the low pressure suction are high pressure. A control member for controlling the compression start timing of each compression chamber according to the rotational motion according to the pressure difference is provided, and the compression start timing at some operating positions in one compression chamber is later than that of the other compression chamber. In a variable displacement compressor having a different notch shape, a control member is arranged to supply control pressure from the other compression chamber described above.

As described above, in the variable displacement compressor, the control pressure is supplied from the compression chamber on the other side, in which the compression start time in some operating positions is faster than the compression chamber on the one hand, and a sufficiently large discharge capacity can be obtained in the some operating positions. As a result, the time until the control pressure rises immediately at the start of the compressor to obtain the control pressure necessary for control is shortened.

Next, an embodiment of the present invention will be described with reference to the accompanying drawings. 1 to 6 show a variable displacement vane compressor in accordance with one embodiment of the present invention, and FIG. 1 is a longitudinal sectional view of the vane compressor.

As shown in FIGS. 1 and 2, the variable displacement vane compressor has a cam ring 1 having a generally elliptical inner circumferential la and a cylindrical rotor housed freely in the cam ring 1. At the outer end of the front side block (3) and the rear side block (4) and their side blocks (3) and (4), respectively fixed to both ends thereof so as to close both ends of the cam ring (1) and (2). The main head (5) is fixed to the rear head (6) and the rotating shaft (7) of the rotor (2) as the main components, respectively, the rotating shaft (7) is installed on both side blocks (3), (4) It is supported by one bearing 8, 9 so that rotation is possible.

A discharge port 5a of the refrigerant gas, which is a heat medium, is formed on the upper surface of the front head 5, and a suction port 6a of the refrigerant gas is formed on the upper surface of the rear head 6, respectively.

The outlet 5a is a suction chamber 6a formed along the rear head 6 and the rear side block 4 in the discharge chamber 10 partitioned along the front head 5 and the front side block 3, and the like. Each chamber 11 is in communication with each other.

As shown in FIG. 2, two compression chambers 12 ₁ and 12 ₂ are symmetrically partitioned by 180 degrees in the circumferential direction between the inner circumferential surface la of the cam ring 1 and the outer circumferential surface of the rotor 2. It is.

A rotor (2) and subsequent vane groove 13 in the radial direction are provided several (e.g., five) placed the same distance in the circumferential direction, the vanes (14 ₁ -17 ₅₎ in these vane grooves 13 Each of these is inserted in the radial direction so as to be free from haunting. As shown in FIGS. 1 and 4, the rear side block 4 described above is provided with a suction port 15 symmetrically with a 180 degree deviation in the circumferential direction.

1 is a longitudinal cross-sectional view cut at an angle of 45 degrees through the centerline of the shaft, so that only one suction port 15 is shown in the same figure.

These intake ports 15 are arranged at positions where the volume between the two vanes which are front and rear of each other in the vanes 14 _{1 to} 14 ₅ is maximized. Each of the suction ports 15 penetrates in the thickness direction of the rear side block 4, and the suction chambers 11, the compression chambers 12 ₁ and 12 ₂ communicate with each other through the respective suction ports 15. .

On the outer circumferential wall of the cam ring 1, the discharge ports 16 ₁ and 16 ₂ are laid out symmetrically, for example, two by two, 180 degrees in the circumferential direction as shown in FIGS. 1 and 2.

On the outer circumferential wall of the cam ring _{1 with} its outlets 16 ₁ , 16 ₂ , there are discharge valve covers 17, 17 with valve retaining parts 17a, 17a according to the bolt 18. Each one is fixed.

Discharge valves 19 and 19 supported on the discharge valve cover 17 side are interposed between the outer circumferential wall of the cam ring 1 and the valve fixing part 17a, and each discharge valve 19 has a discharge pressure. When it is received, injection is started to open the respective discharge ports 16 ₁ and 16 ₂ , respectively. Further, the cam ring 1 has communication paths 20 ₁ , 20 ₂ , and all side blocks 3 which communicate with each outlet 16 ₁ , 16 ₂ , respectively, at the start of injection of each discharge valve 19. The communication paths 21 ₁ and 21 ₂ , which communicate with the communication paths 20 ₁ and 20 ₂ , respectively, are formed at substantially symmetrical positions 180 degrees apart in the circumferential direction.

When each outlet 16 ₁ is opened, the compressed refrigerant gas in the compression chamber 12 ₁ is discharge outlet 16 ₁ , communication path 20 ₁ , 21 ₁ discharge chamber 10, and outlet 5 a. a is sequentially interposed in the discharge of each discharge port (16 _2), the compressed refrigerant gas outlet port (16 _2), the communication passage (20 _1, 21 _2), the discharge chamber (10 in case hayeoteul opening the compression chamber (16 ₂₎ ) And the outlet 5a are sequentially discharged.

Moreover, between the discharge valve cover 17 and the outer circumferential wall of the cam ring 1, between the front end of the cam ring 1 and the front side block 3, and the right end of the cam ring 1 and the rear side block 4. The 0 rings 22, 23, and 24 are each interposed in order to maintain air tightness between them. As shown in FIG. 1, FIG. 4, FIG. 5 and FIG. 9, the rear side block 4 is provided with an annular recess 25 on the side surface of the rotor 2, and within the annular recess 25. FIG. The two pressure actuating chambers 26 and 26 are installed approximately symmetrically with a 180 degree shift in the circumferential direction.

In the annular recess 25, a ring-shaped control member 27 shown in FIG. 6 is mounted so as to rotate in the forward and reverse directions.

The control member 27 is for controlling the start time of compression of each of the compression chambers 12 ₁ and 12 ₂ , and on the outer circumference of the arcuate notch portion 28 ₁ , ( 28 ₂ ) is installed. On one side surface of the control member 27, projections 29, 29 of protrusions symmetrically in a circumferential direction are formed integrally with each other.

The above-mentioned teeth each node (28 _1, 28 ₂₎ is compressed the other hand, depending on is slow the compression start timing of some operating positions of the compression chamber (12 ₁₎ on the other hand than the other side compression chamber (12 ₂₎ It is a different shape so that the variable rate of discharge | emission capacity in the chamber 12 ₁ may be larger than the other compression chamber 2 ₂ .

In other words the cut rotation ends (28, ₁₀₎ forward of the (FIG. 2 and 6 and in Fig. Counterclockwise in that then the rotor rotation direction) of the (28 _1), a rotor (2) in the corresponding notch (28 ₂₎ at an angle than the symmetric positions in the peripheral direction of the front end portion (28, ₂₀₎ is cut by a low (second degree and third degree hatched portion a).

Therefore, the front ends of the notched portions (28 ₁₎ (28, ₁₀₎ is in a binary difference of an angle in front of the rotational direction of the rotor than the front end portion (28, ₂₀₎ of the cutout (28 ₂₎ position.

The control member 27 having such notches 28 ₁ , 28 ₂ compresses _one compression chamber 12 ₁ according to the notches 28 ₁ as shown in FIGS. 2 and 3. according to the start timing to the notched portions (28 ₂₎ to each other controls the time compression initiation convenience compression chamber (12 ₂₎ is fitted so as to rotate in both the forward and reverse in the annular recess (25).

As shown in FIG. 4 and FIG. 5, the hydraulic parts 29 and 29 of the control member 27 are inserted in the pressure operation chambers 26 and 26 so as to be able to slide, respectively.

Each pressure working chamber 26 are each 2 minute low-pressure chamber (26 ₁₎ and the high-pressure chamber (26 ₂₎ with each pressure receiver (29).

Each low-pressure chamber (26 ₁₎ is in the respective via the inlet 15 was in communication with the suction chamber (11) that each low-pressure chamber (26) is introduced into the low pressure of the suction pressure (P _3).

On the other hand, one of the high pressure chamber (26 ₂ ), (26 ₂ ) is an orifice (40) and a communication path (41) respectively provided in the rear side block (4), and a control pressure supply port (42) provided in the cam ring (1). The communication path 20 ₂ communicates with the communication path 20 ₂ described above. Each of the high pressure chambers 26 ₂ , 26 ₂ communicates with each other via a communication path 43 provided in the rear head 6.

Therefore, when each outlet 16 ₂ is opened, the high-pressure refrigerant gas discharged from the other compression chamber 12 ₂ is discharge outlet 16 ₂ , communication path 20 ₂ , control pressure supply port 42 communication path ( 41) and via an orifice (43 communication path at the same time as introducing the high-pressure chamber (26 ₂₎ of the other hand through a 40) is introduced in the other side high pressure chamber (26 ₂₎ of each high-pressure chamber (26 _2), ( The control pressure Pc is formed in 26 ₂ ).

That is, the control pressure Pc is supplied from the other compression chamber 12 ₂ .

Further, one of the high pressure chambers 26 ₂ , 26 ₂ is provided with a suction chamber 11 via a communication hole 30 and an open / close valve mechanism 31 provided inside the rear side side block 4 as shown in FIG. You can communicate with). The on-off valve mechanism 31 opens and closes according to the suction pressure Ps in the suction chamber 11 to leak the control pressure Pc in the high pressure chamber 26 ₂ to the suction chamber 11 side at the start of injection. And a spring 31d for pressurizing the corrugated container 31a, the case 31b, the bowl valve 31c, and the bowl valve 31c which move in accordance with the pressure in the injection closing direction.

The corrugated container 31a is arranged to be stretchable in the suction chamber 11, and the case 31b is installed in the rear side block 4 and in the mounting hole 44 communicating with the communication path 30. have. Holes 31g and 31f are formed in the casing 31b to communicate with each other via the chamber 31h.

The above-mentioned valve | bulb valve 31c is arrange | positioned in the chamber 31b of the case 31b, and opens and closes the hole 31f.

The spring 31d described above is disposed in the chamber 31h and pressurizes the valve 30c in the injection closing direction.

The corrugated container 31a is reduced when the suction pressure is greater than or equal to a predetermined value set by the control member 31e, and the valve valve 31c ejects and closes the central hole 31f of the case 31b. On the other hand, when the suction pressure Ps is lower than or equal to a predetermined value, the corrugated container 31a extends, and the valve valve 31c starts spraying the center hole 31f. The central hole of the high-pressure chamber (26 ₂₎ of a hand (30) in communication with the mounting hole 44, a case (31b) holes (31g), the chamber (31h) and the casing (31b) in the housing (31b) of ( It communicates with the suction chamber 11 via 31f).

As shown in FIG. 1, FIG. 5, FIG. 6, and FIG. 9, the seal groove 27a is continuously formed in one side, the inner circumference, the outer circumference, and the circumferential edge of the hydraulic part 29 of the control member 27. As shown in FIG. The simultaneous working groove 27a is equipped with a special shape sealing member 37. The simultaneous working member 37 is a double structure of the elastic sealing member 37a and the resin sealing member 37b (see Fig. 1).

As shown in FIG. 1, the control member 27 is pressed counterclockwise in FIG. 8 along the torsion coil spring 38. As shown in FIG.

The torsion coil spring 38 is arranged on the outer circumference of the boss portion 4a of the rear side block 4 extending to the suction chamber 11 side, and one end thereof is connected and fixed to one side of the control member 27. The other end is fixed to the end surface of the boss portion 4a (not shown).

In this way, the control member 27 is normally and reversely rotated according to the difference between the pressure in the chamber (26 ₁₎ and the return helical pressure and pressure chamber (26a) of the urging force of the spring 37 in the.

That is, as the pressure in the suction chamber 26 ₂ is controlled by the on / off valve mechanism 31, the control member 27 obtains the maximum discharge capacity shown in the solid line of FIG. 8 and in FIG. It is to be rotated forward and backward between the entire operating position and the two dashed line in FIG. 2 and some operating positions to obtain the minimum discharge capacity shown in FIG.

Fifth, as also and shown in Figure 6 the teeth furnace in the circumferential direction one another (28 _1, 28 ₂₎ notched rotor rotation direction front end (28, ₁₀₎ of (28 ₁₎ in is the inner the side was cut to the groove shape is a shape leaving a protrusion (28, ₁₂₎ on the outer peripheral side of the groove-shaped notch (28, _11).

On the other hand the cut (28 _2), the rotor rotation direction front end (28, ₂₀₎ is supposed to end in a line.

Next, the operation of the variable displacement vane compressor having the above-described configuration will be described. Inlet from the respective compression chamber (12 _1, 12 ₂₎ refrigerant gas suction chamber (11) within each of the compression between the two vanes to each other after which the intake-stroke chamber (12 _1, 12 ₂₎ in the ( 15), (15) and notches (28 ₁ ), (28 ₂ ) are respectively sucked through the rotor vane rotational side vanes of the two vanes of each notch (28 ₁ ), (28 ₂ ) The point at which the communication between the respective compression chambers 12 ₁ , 12 ₂ and each of the suction ports 15, 15 between the two vanes described above passes through the front ends 28 ₁₀ , 28 ₂₀ . The compression stroke is started at.

The compression start time is delayed as the control member 27 rotates from the overall operating position of FIG. 3 toward a partial operating position of FIG. 2 and thus the discharge capacity is continuously reduced. That is, the control member 27 is partially operated. When not in front of each of the notches (28 ₁ ), (28 ₂ ) of the control member (27), 28 ( ₁₀ ), (28 ₂₀ ) is in the most forward position in the rotor rotation direction, the compression start time late and when in two's be in a minimum volume of refrigerant gas confined let come out between the vanes is in the minimum discharge capacity, and so the whole operation control member 27 positions before and after each other teeth each node (28 _1), ( 28 ₂ ), the front ends 28 ₁₀ and 28 ₂₀ are located at the rearmost position in the rotor rotational direction, and the refrigerant gas is confined to prevent compression between the two vanes which are the fastest and the first to start compression. Volume is maximized Standing discharge capacity is maximum.

When the compressor is used, the rotary shaft 7 rotates with the driving force from the engine of the vehicle so that the rotor 2 rotates counterclockwise in the second direction.

As described above, at start-up, the control member 27 is in a partial operating position of FIG.

Some working position other side compression chamber (12 ₂₎ on the two vanes for example vanes (14 _3), the rotor rotation direction rear side of the vane (14 ₄₎ of the (14 _4), before and after each other in the intake stroke notched For (28 ₂₎ and passes through the front end portion (28, _20), the vanes (14 _3, 14 _4), the contents of the cut off communication of the compression chamber (12 ₂₎ and suction port (15) between the relative as the compression stroke is started while two vanes to each other before and after in the suction stroke with respect to the compression chamber (12 _1), for example, the vanes (14 _5), as is shown in FIG. 2 rotor rotation direction rear side of the vane (14 ₁₎ of the (14 ₁₎ Likewise, when the communication between the compression chamber 12 ₁ and the suction port 15 between the vanes 14 ₅ and 14 ₁ through the front end 28 ₁₀ of the notch 28 ₁ is cut off, that is, the compression of the other side The compression stroke is started at a time delayed from the yarn 12 ₂ by a certain angle indicated by the hatched portion A. FIG. Therefore, the discharge capacity of the refrigerant gas discharged from the other compression chamber 12 ₂ in some operating positions is larger than the compression chamber 12 _{1 on the} other hand. The high-pressure refrigerant gas discharged from the other compression chamber 12 ₂ is interposed between the discharge port 16 ₂ , the communication path 20 ₂ , the control pressure supply port 42, the communication path 41, and the orifice 40. Is introduced into one of the high pressure chambers (26 ₂ ) and simultaneously into the other high pressure chamber (26 ₂ ) via the communication path (43) to control pressure (Pc) in each of the high pressure chambers (26 ₂ ), (26 ₂ ). This is manifest. That is, since the control pressure Pc is supplied from the compression chamber 12 _{2 of} the other side which can obtain a larger discharge capacity than the compression chamber 12 _{1 of the one} in some operating positions, the control pressure Pc at the start of the compressor. This rises soon, the time until the control pressure Pc necessary for the control of the control member 27 is obtained is shortened, and the startability is improved.

As the control pressure Pc rises, the control member 27 rotates from the partial operating position in FIG. 2 toward the entire operating position in FIG. 3 and compresses in the compression shaft chambers 12 ₁ and 12 ₂ according to the same rotational movement. The start-up time is faster and the discharge capacity is increased.

And the suction pressure (Ps) is when below a certain value on-off valve mechanism 31, the injection start to decrease by the control pressure (Pc) to leak into the low pressure side of the suction chamber 11 in the high-pressure chamber (26 ₂₎ therefore this The control member 27 rotates toward a part of the operating position to reduce the discharge capacity.

In this way, the discharge capacity is controlled as the control member 27 rotates forward and reverse so that the suction pressure Ps becomes a constant value.

Further, in the delay in the time by a constant angle as shown in the other side compression chamber (12 ₂₎ with respect to the compression chamber (12 ₁₎ on the one hand, the hatched portion (A), because the compression stroke is started while the in the compression chamber (12 ₁₎ The variable discharge rate is larger than that of the other compression chamber 12 ₂ , and thus the variable rate of the discharge capacity of the entire compressor is expanded.

Furthermore, the variable displacement compressor according to the present invention may be replaced with the control member 27 shown in FIG. 6 and may use the control member 27 'as shown in FIG. 7. In this case as well, The discharge capacity can be increased and the startability can be improved.

That is, the control member 27 'has notches 28 ₁ and 28 ₂ at positions symmetrical with each other in the circumferential direction, and the front end 28 _{10 of the} notches 28 ₁₀ has its inner peripheral side. It cuts into a groove shape and leaves the protrusion part 28 ₁₂ on the outer peripheral side of the groove-shaped notch part 28 ₁₁ .

In contrast, the front end portion 28 ₂₀ of the notch portion 28 ₂ is a straight end portion.

Thus formed cutout of the control member 27 (28 _1), the front end (28 ₂₎ (28, _10), (28, _20), the teeth each node of the control member 27 (28, _1), ( 28 ₂ ) corresponding to the front ends 28 ₁₀ and 28 ₂₀ , respectively.

And the control member (27 ') is that the notch (28 _1), the compression start timing of the compression chamber (12 ₁₎ of the above-described hand the cutout (28, ₂₎ compression of the other side compression chamber (12 ₂₎ according to according to the It is fitted in the annular recess 25 so as to be rotated in the forward and reverse directions so as to control the start timing.

In the case where the control member 27 'is used, when the control member 27' is in a partially acting position, the rotor rotation of the two vanes which are moved back and forth with each other in the suction stroke with respect to the compression chamber 12 ₁ . while in this direction rear side of the vane until the end (28 _'11) greater passage of the projections (28, ₁₂₎ flows out into the suction port 15 from the (28, ₁₁₎ refrigerant gas that no groove-shaped teeth in the compression chamber (13). As a result, the compression start timing of operation at some position in the compression chamber (12 ₁₎ on the other hand is delayed by an angle of a minute (28 ₁₁₎ no groove-shaped teeth than the other side compression chamber (12 _2).

Therefore, the minimum discharge capacity is large, the foregoing control pressure (Pc) the other side compression chamber than the compression chamber (12 ₁₎ on the other hand in this case also other side compression chamber as in the above-described bar Example (12 ₂₎ to ( Since it is supplied from 12 ₂ ), the time until the control pressure Pc immediately rises at the start of the compressor to obtain the control pressure Pc necessary for the control of the control member 27 ′ is shortened, and the startability is improved.

In addition, in one compression chamber 12 ₁ , as in the case of the above-described embodiment, the compression stroke is started later than the other compression chamber 12 ₂ at some operating positions, so that discharge in the other compression chamber 12 ₁ is achieved. The variable rate of the capacity is larger than that of the other compression chamber 12 ₂ , thereby expanding the variable rate of the discharge capacity of the entire compressor.

As described in detail above, according to the variable displacement compressor according to the present invention, two compression chambers located at symmetrical positions in the circumferential direction and two notch portions corresponding to the respective compression chambers have outer periphery and control pressure and low pressure suction which are high pressure. A control member for controlling the compression start timing of each compression chamber according to the rotational motion according to the pressure difference is provided, and each notch part is arranged so that the compression start timing at one operating position in one compression chamber is later than that of the other compression chamber. According to the configuration in which the control member is arranged to supply the control pressure from the other compression chamber in the variable displacement compressor having a different shape, the control pressure is shorter than the compression chamber at the beginning of the compression chamber and also in the partial operation position. The supply pressure from the other side of the compression chamber is large enough to achieve a large discharge capacity. It may correspond sikilsu and reduce the time required to obtain the control pressure necessary for the control, accordingly it is possible to improve the startability while expanding the variation ratio of the discharge capacity of the entire compressor.

Claims (2)

Compression start time of each compression chamber according to the rotational motion of two compression chambers in the symmetrical position in the circumferential direction and two notches corresponding to each compression chamber on the outer periphery and the difference between the high pressure control pressure and the low pressure suction pressure A variable capacity compressor having a different shape of each notch so that the start of compression at a part of the operating position in one compression chamber is later than that of the other compression chamber. The variable displacement compressor characterized in that the control unit is arranged to supply the control pressure from the. Two compression chambers partitioned at the circumferentially symmetrical position between the inner circumferential surface of the cam ring closed by the side block and the outer circumferential surface of the rotor rotating in the cam ring, and a plurality of radially inserted into the rotor freely radially The control member having two notches extending in the circumferential direction at a symmetrical position in the circumferential direction communicating with the suction port and the compression chamber installed on one side of the side block as described above, and capable of rotating in the other side block. The control material is operated as a starting point for compressing the fluid at the time when the rear vanes in the rotational direction of the two vanes in the suction stroke among the several vanes pass through the front end of the rotor rotation direction in each notch. In a variable melt compressor for changing the discharge flow by rotating the position between the position and the partial operating position, A variable displacement compressor, characterized in that the front end of one of the two notches described above is cut in its inner circumferential side in a flaw shape, leaving a protrusion on the outer circumferential side of the groove-shaped notch portion.

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