KR960004244B1 - Variable swash plate type compressor - Google Patents

Abstract

No content.

Description

Variable displacement swing swash plate compressor

1 is a side cross-sectional view showing an embodiment embodying the present invention.

2 is a partial plan view showing the vicinity of the lag plate.

3 is a cross-sectional view taken along line a-a in FIG.

4 is a cross-sectional view taken along line b-b in FIG.

5 is a view similar to the third view showing another embodiment of the present invention.

* Explanation of symbols for main parts of the drawings

1 cylinder block 2 front housing

3: rear housing 5: crank seal

10 lag plate 13 rotation drive body

15A, 15B: Guide pin 16a, 16b: Guide hole

17: rocking swash plate 18: mooring recess

19: shoe 21: suction chamber

22: discharge chamber

The present invention partitions the crank chamber, the suction chamber, the discharge chamber, and the cylinder holes connecting the chambers, and supports the lag plate on the rotation axis in the housing for reciprocally linearly accommodating the piston in the cylinder holes. At the same time, the swing swash plate slidably supported on the rotational shaft is slidably supported in the forward and backward direction with respect to the rack plate via a hinge mechanism, and the lag plate is rotated through a coupling mechanism interposed between the swing swash plate and the piston. Variable displacement type that changes the rotational capacity of the swing swash plate to reciprocating linear motion of the piston and controls the inclination angle of the swing swash plate based on the differential pressure between the suction pressure and the pressure of the crank chamber through the piston It relates to a swash plate compressor.

As a conventional variable displacement swing swash plate type compressor, one disclosed in Japanese Patent Application Laid-Open No. 62-183082 is proposed. In such a compressor, the rotation drive body is connected to the lag plate fixed to the rotation shaft via a connecting pin such that the rotation drive body can be tilted in the front and rear direction, and the rotation drive body supports the swing swash plate. Between the pistons accommodated in the plurality of cylinder holes and the swing swash plate, a piston rod is interposed to convert the rotational motion of the rotary drive into reciprocating linear motion of each piston.

The support arm protruding from the rack plate is formed with a long hole for sliding guide the connecting pin. As a result, the upper clearance of the piston is always kept substantially constant at the end of compression while allowing the inclined movement of the rotary drive member and the swinging swash plate, and the upper position of the swinging swash plate does not shift back and forth in spite of the change in the inclination angle of the swinging swash plate. I'm not.

In the rocking swash plate type compressor, when the dimensional accuracy of the arc-shaped long hole for guiding the connecting pin is low, the upper clearance of the piston cannot be kept substantially constant, and the gap between the long hole and the connecting pin is large. Although noisy, it is difficult to make the dimensional accuracy of the long hole higher.

The compressor has a working point in the rocking swash plate of the compression reaction force acting on the rocking swash plate through the piston and the piston rod when the inclination of the rocking swash plate is the maximum and the discharge capacity of the compressor is the maximum, and the connecting pin in the long hole. Rough compression reactions are designed such that the support points are located on a straight line parallel to the axis of rotation. As a result of the decrease in the inclination angle of the swing swash plate, the point of compression reaction force through the connecting pin moves downward in the long hole, while the acting point of the swing swash plate type subjected to the compression reaction force of the piston in the upper position is relative to the support point. To move upwards.

As a result, the position of the action point of the compression reaction force through the piston in the upper position is farther from the rotation axis than the position of the support point of the compression reaction force through the connecting pin, and a moment is generated to further reduce the inclination angle of the rocking swash plate based on the compression reaction force. do. Under the influence of this moment, the action of reducing the discharge capacity becomes sensitive. On the other hand, since the operation to increase the inclination angle of the rocking swash plate is greatly inhibited by the moment, the operation of increasing the discharge capacity is slow and the controllability of the discharge capacity as a whole is not necessarily good.

An object of the present invention is to provide a variable displacement swing swash plate type compressor which can maintain the constant upper clearance of a piston without causing problems such as noise and excellent in controllability of discharge capacity.

In order to solve the above problems, the present invention rotatably supports the guide pin in the front-rear direction with respect to the lag plate, and at the swing swash plate side, a guide hole is installed, and the guide pin is slidably passed through the guide hole. And a hinge mechanism for connecting the swinging swash plate to the inclined movement.

As the inclination angle of the swing swash plate changes based on the pressure in the crank chamber and the differential pressure between the suction pressure, the guide pin rotates in the front and rear direction with respect to the lag plate, while the swing swash plate has its upper position in the correct position. Tilt and move while sliding on the rotating shaft to be maintained. Thereby, the upper clearance of the piston is always kept substantially constant despite the inclination angle of the rocking swash plate.

Moreover, unlike the conventional case, even if the inclination angle of the rocking swash plate changes, the position of the support point of the compression reaction force in the lag plate does not change. For this reason, the position of the operating point on the rocking swash plate of the compression reaction force and the position of the support point can be set to be almost equal from the rotation axis, and a moment based on the compression reaction through the piston with respect to the rocking swash plate may not occur. . Therefore, the inclined movement as both directions of the increase and decrease of the inclination angle of the rocking swash plate is smooth and the controllability of the discharge capacity is improved.

In the following, a first embodiment incorporating the present invention will be described with reference to Figs.

As shown in FIG. 1, the front housing 2 is joined to the one end side of the cylinder block 1, and the rear housing 3 is joined to the other end via the valve plate 4. As shown in FIG. The crank chamber 5 formed by the cylinder block 1 and the front housing 2 is accommodated with the rotation shaft 6, and the rotation shaft 6 is rotatably supported by the bearing 7. A plurality of cylinder holes are drilled in the cylinder block 1 at positions surrounding the rotation shaft 6, and pistons 9 are fitted in the cylinder holes 8, respectively. The center axis of the piston 9 is parallel to the axis of the rotation shaft 6.

In the crank chamber 5, the lag plate 10 is supported by the rotation shaft 6 so as to be synchronously rotatable with the rotation shaft 6, and the spherical sleeve 11 is rotatably and slidably supported. A pressing spring 12 is interposed between the lag plate 10 and the spherical sleeve 11, and the pressing spring 12 pushes the spherical sleeve 11 in the rear housing 3 direction.

As shown in FIGS. 1 to 4, the rotary drive member 13 is supported on the spherical sleeve 11 so as to be able to swing back and forth. The rotary drive body 13 is formed in an annular shape as surrounding the rotary shaft 6, and a pair of brackets 13a and 13b protrude in the left and right positions in which the rotary shaft 6 is fitted on the upper rear surface. On the upper front surface of the lag plate 10, a pair of support arms 14A and 14B protrude from the brackets 13a and 13b.

Spherical recesses 14a and 14b are provided at the leading ends of both support arms 14A and 14B. Guide pins 15A and 15A are rotatably inserted in each spherical recess 14a and 1b through their spherical body portions 15a and guide pins 15A and 15B are supported by support arms 14A and 14B. We can swing about.

Bosses 16A, 16B are provided at the tip end of each of the brackets 13a, 13b of the rotary drive body 13, and the rod-shaped portions 15b of the guide pins 15A, 15B guide the bosses 16A, 16B. It is slidably fitted into the holes 16a and 16b. The guide pins 15A, 15B are guide holes 16a, 15b of the bosses 16A, 16B according to the front and rear slides of the spherical sleeve 11 and the front and rear swings of the rotary drive body 13 on the rotary shaft 6. While sliding the inside, it swings about the spherical body part 15a. Therefore, despite the position of the spherical sleeve 11 on the rotating shaft 6 and the inclination angle of the rotating driving body 13, the lag plate 10 and the rotating driving body 13 are both guide pins 15A and 15B. Is connected rotatably through the pottery.

In the most constricted state of the pressing spring 12 shown in FIG. 1, the contact surface 13c formed inclined on the lower back surface of the rotation drive body 13 contacts the lag plate 10, and thereby the rotation drive body Reference numeral 13 controls the inclination movement in the inclination angle increasing direction.

As shown in FIG. 1, the rocking swash plate 17 is fitted in the outer peripheral part of the rotation drive body 13. Mooring recesses 18 are formed at the proximal ends of the pistons 9 in the respective cylinder holes 8, rocking swash plates 17 are formed in each of the mooring recesses 18, and in each of the mooring recesses 18. The outer periphery of the swinging swash plate 17 is moored via the pair of shoes 19. Therefore, the rotational movement of the rotation shaft 6 is changed into the rotational movement of the swash plate 17 and the forward and backward reciprocating rocking motion via the lag plate 10 guide pin 15 and the rotation drive body 13, and the shoe 19 Each piston 9 reciprocates in the back and forth direction inside the cylinder hole 8 via the following.

The inside of the rear housing 3 is partitioned into the suction chamber 22 and the discharge chamber 22 by the partition 20. The inlet port 23 and the outlet port 24 are formed in the valve plate 4 corresponding to each cylinder hole 8, and the compression chamber 25 formed between the valve plate 4 and the piston 9 is formed. The suction port 21 and the discharge port 24 communicate with the suction chamber 21 and the discharge chamber 22. Inlet valves 26 and outlet valves 27 are respectively provided at the inlet port 23 and the outlet port 24, and these open and close the inlet port 23 and the outlet port 24 in accordance with the reciprocating motion of the piston 9. .

The refrigerant gas sucked into the compression chamber 25 from the suction chamber 21 by the reciprocating motion of the piston 9 is discharged to the discharge chamber 22 while being compressed. In this compression operation, the pressure acting on the cross section of each piston 9 in the cylinder hole 8 changes between the suction pressure and the discharge pressure depending on the suction or discharge stroke of each piston 9, The foot shoe 19 transmits a compression reaction force to the swash plate 17 according to the pressure difference between the pressure acting on the end face of the piston 9 and the pressure in the crank chamber 5 acting on the rear surface of the piston 9. The moment which rotates the rocking swash plate 17 forward or backward about the spherical sleeve 11 based on the combined force of these compression reaction forces, the inclination angle of the rocking swash plate 17 changes, and the piston 9 Stroke changes. In addition, the capacity control valve mechanism 28 is provided in the rear housing 3, and the pressure in the crank chamber 5 is controlled by the use amount control valve mechanism 28.

The guide holes 16a are rotated with the two guide pins 15A and 15B rotating with respect to the lag plate 16 in accordance with the change in the inclination angle of the swing swash plate 17 based on the pressure difference in the crank chamber 5 and the suction pressure. At the same time as the slide 16b, the rotary drive body 13 is tilted while sliding on the rotary shaft 6 so that the upper position of the swinging swash plate 12 is kept in the correct position. Thereby, the upper clearance of the piston 9 is always kept substantially constant despite the inclination angle of the rocking swash plate 17.

In this embodiment, since the guide pins 15A, 15B are rotatably supported by the support arms 14A, 14B integrally formed on the lag plate 10, the support point Mk of the compression reaction force is changed even if the inclination angle of the swing swash plate 17 changes. In Fig. 1, only the supporting point Mk corresponding to the guide pin 15A is not changed in position. For this reason, the acting point Mf and the supporting point Mk of the compression reaction force on the rocking swash plate 17 passing through the piston 9 corresponding to the upper position of the rocking swash plate 17 form the center axis of the piston 9. It can be set to be located on the same virtual plane (P) including. That is, the center of the line segment connecting the point Mk corresponding to the guide pin 15A and the point Mk corresponding to the guide pin 15B can always be set on the central axis line of the piston 9. .

This makes it possible to prevent the rotation moment acting on the swing swash plate 17 based on the compression reaction force through the piston 9 in the upper position, and to increase and decrease the tilt angle of the swing swash plate 17 in both directions. The movement is smooth and the controllability of the discharge capacity is increased.

By the way, the inventors of the present application, in the application No. 2-286675 (oscillation swash plate type variable displacement compressor, filed Oct. 28, 2012), rotatably support the bearing having the guide hole in the front and rear direction while rotating A rocking swash plate type compressor has been proposed in which a simple rod-shaped guide pin is fixed to a drive body, and the guide pin is inserted into a guide hole of the bearing to form a hinge mechanism for connecting a lag plate and a rotating drive body.

According to this configuration, the guide pin moves inside the guide hole in the radial direction of the compressor in accordance with the change of the inclination angle of the rocking swash plate, but since the guide hole is provided on the lag plate side, the tip end of the guide pin is located far from the rotation axis. The guide hole is reciprocated. The situation where the guide pin is reciprocated in a position away from the rotating shaft changes the load balance of the integral rotating body which is attached to the rotating shaft and rotates with the rotating shaft, causing vibration and the like.

On the other hand, according to the structure of this embodiment, the spherical body part 15a of the guide pin 15A, 15B is rotatably supported with respect to the support arm 14A, 14B of the lag plate 10, and the guide pin ( 15A and 15B do not protrude outward from the support arms 14A and 14B, and the rods 15b of the guide pins 15A and 15B are moved as close as possible to the rotational shaft 6 to guide holes 16a and 16b. Since it is made to slide about, the change of the load balance of the integral rotation of the rotating shaft 6 according to the reciprocation slide of the guide pins 15A and 15B is extremely small. Therefore, the rotation drive body 13 and the swing swash plate 17 can be stably rotated without vibration or the like.

According to the composition of Japanese Patent Application No. 2-286675. The centrifugal force generated in the guide pin in accordance with the rotation of the rotary shaft tries to move the guide pin outward along the guide hole of the bearing, whereby the swing swash plate is pushed in the direction of increasing the inclination angle. On the other hand, according to this embodiment, since the centrifugal force acting on the guide pins 15A and 15B is supported and stopped by the support arms 14A and 14B, the swing swash plate 17 is moved in a specific direction by this centrifugal force. The tilt does not move. Therefore, even if the rotation speed of the rotating shaft 6 increases and a large centrifugal force acts on the guide pins 15A and 15B, the controllability of the discharge capacity does not deteriorate.

In particular, such oscillating swash plate type compressors are often used as compressors for cooling apparatuses mounted on automobiles, and in such cooling apparatuses, the larger the rotation speed of the rotating shaft, the smaller the swash plate inclination angle and the smaller the discharge capacity. Also in this respect, the compressor of this embodiment has desirable characteristics.

Further, according to the present embodiment, since the guide pins 15A and 15B do not protrude outward from the support arms 14A and 14B, the support arms 14A and 14B of the lag plate 10 as shown in FIG. Can be provided at a position close to the inner wall of the cylinder block 1, and the diameter of the compressor can be reduced.

In addition, this invention is not limited to the said Example, You may implement in the following form. That is, (1) as shown in FIG. 5, the rotary support hole 31 is provided in the front-end | tip of 14 A of support arms of the lagplate 10, and the support shaft 33 is rotated in the rotation support hole 31. FIG. At the same time, the plate-shaped support portion 32 is formed on the head of the guide pin 15A, and the support pin 33A is rotatably supported in the front-rear direction by the support shaft 33 via the plate-shaped support portion 32; (2) Instead of the coupling mechanism using the shoe 19 of the said embodiment, there exists a thing which connects the rocking swash plate 17 and each piston 9 by a piston rod.

As described above, according to the present invention, the guide pin is rotatably supported in the front-rear direction with respect to the lag plate, a guide hole is provided on the swing swash plate side, and the guide pin is slidably inserted into the guide hole to make the lag. Since the hinge mechanism connects the plate and the swinging swash plate to be inclined, the upper clearance of the piston can be kept substantially constant without problems such as joints, and the swinging swash plate at the time of increasing and decreasing the discharge capacity It is possible to increase the controllability of the discharge capacity by smoothing the tilt movement operation together.

Claims (1)

The crank chamber, the suction chamber, the discharge chamber, and the cylinder holes connecting these chambers are partitioned, and the lag plate is synchronously rotatably supported and hinged to the rotational livestock in the housing in which the piston is reciprocally linearly accommodated in the cylinder holes. The swash plate is slidably supported on the rotational shaft to be slidably movable in the front-rear direction with respect to the lag plate, and the lag plate is rotated according to the rotation of the lag plate through a coupling mechanism interposed between the rocking plate and the piston. In a variable displacement swing swash plate type compressor which converts rotational motion into a reciprocating linear motion of a piston and simultaneously controls the inclination angle of the swing swash plate based on the differential pressure of the crank chamber and suction pressure through the piston to vary the discharge capacity. Guide pin for the lag plate A variable displacement rocking swash plate compressor comprising a guide hole on the swinging swash plate side and a guide pin slidably inserted in the guide hole so as to be rotatably supported in the front-rear direction.