JPH03258975A - Variable capacity swash plate type compressor - Google Patents

Abstract

PURPOSE:To enhance a reduction in vibration and noise by providing a part for balancing the unbalance quantity in the engagement part of a swash plate body to conform the center-of-gravity position of the swash plate body to the center of a spindle. CONSTITUTION:A swash plate body 12 is fastened to a sleeve 15 rotatably around a sleeve pin, 17 which forms the swash plate tilt rotating center of the swash plate body 12. As a piston support 21 has additive mass parts 216 (a)-216 (e) and 217 formed closed to a piston 31 side from the center of the sleeve pin 17, the mass center-of-gravity position of the piston support 21 can be situated on the center of the sleeve pin 17. thus, the unbalance accompanied by oscillating movement of the piston support 21 can be nearly reduced to zero. Thus, the unbalance quantity of centrifugal force can be reduced over the whole area of swash plate tilt rotating angle, and vibration and noise of the outside and inside of a vehicle chamber can be suppressed.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to the structure of a capacity control swash plate compressor used, for example, in a refrigerant compressor for an automobile air conditioner, and is particularly useful for reducing vibration noise of the compressor. The present invention relates to a suitable capacity control swash plate compressor.

[Conventional technology]

Conventional capacity-controlled swash plate compressors for automobile air conditioning are disclosed, for example, in Japanese Patent Publication No. 58-4195 and Japanese Utility Model Publication No. 1983-1999. -14218
No. 4 and Japanese Patent Application Laid-Open No. 61-286591. The conventional capacity-controlled swash plate compressor described above receives driving force from an automobile engine, transmits the power to a drive pin or drive ring fixed to a rotating main shaft, and engages with the drive pin or drive ring. The swash plate, whose inclination angle with respect to the main shaft (swash plate tilt angle) can be arbitrarily changed by a link mechanism or cam mechanism, rotates and oscillates, causing the piston to reciprocate.

[Problem to be solved by the invention]

In the above-mentioned conventional technology, the unbalance of the centrifugal force of the rotating member due to the rotation of the main shaft occurs as the sum of the centrifugal force of the drive pin or drive ring and the centrifugal force balance of the swash plate. Further, unbalance also occurs when the center of gravity of the oscillating plate that is hooked to the swash plate and swings is far from the center of tilting of the swash plate. Among the centrifugal force imbalances mentioned above, the centrifugal force of the drive pin or drive ring is determined regardless of the swash plate tilt angle. On the other hand, the centrifugal force of the swash plate and rocking plate changes depending on the tilting angle of the swash plate and the distance from the center of gravity and the center of the main axis of each element that makes up the swash plate and rocking plate. Varies with respect to the angle. Therefore, the unbalance of the combined centrifugal force changes with respect to the swash plate tilt angle even at the same rotational speed. In other words, since the unbalance of centrifugal force differs depending on the swash plate tilt angle, the unbalance of centrifugal force becomes large at the maximum swash plate tilt angle (maximum capacity) or the minimum swash plate tilt angle (minimum capacity), and this centrifugal force There was a problem in that the unbalanced forces caused the compressor to vibrate, causing large vibrations and noise inside and outside the vehicle body, especially when the engine was idling.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a variable capacity swash plate compressor which eliminates the drawbacks of the prior art described above and which produces less vibration and noise.

[Means to solve the problem]

In order to achieve the above object, a first means of the present invention includes a main shaft rotatably driven by a drive source, a drive plate fixed to the main shaft, and an engaging portion that engages the main shaft with respect to the main shaft. A swash plate body that rotates while being tiltably engaged in a tilted state, a piston support that is rotatably supported by the rotating swash plate body and swings, and a piston support that is hooked to the piston support and rotates inside the cylinder. In a variable capacity swash plate type compressor, which is configured with a piston that reciprocates, and which performs capacity control by changing the tilt angle of the swash plate body, the engagement of the swash plate body at a predetermined tilt angle within a tilt angle range is By providing a portion for balancing the unbalanced amount of the mating portion, at least the center of gravity of the swash plate body is configured to substantially coincide with the axis of the main shaft.

The second means includes a main shaft rotatably driven by a drive source, a drive plate fixed to the main shaft, and an engaging portion that engages the drive plate so as to be tiltable in a tilted state with respect to the main shaft. The swash plate body is composed of a swash plate body that rotates, a piston support that is rotatably supported by the rotating swash plate body and swings, and a piston that is hooked to the piston support and reciprocates within the cylinder. In a variable capacity swash plate type compressor that performs capacity control by changing the tilt angle of the plate body, the amount of unbalance of the engaging portion of the swash plate body is balanced, and the center of gravity is aligned approximately with the axis of the main shaft. , the center of gravity of the piston support is substantially aligned with the center of tilt of the swash plate main body.

Alternatively, a main shaft rotatably driven by a drive source, a drive plate fixed to the main shaft, and an inclined plane that is rotatably engaged with the drive plate through an engaging portion so as to be tiltable with respect to the main shaft. It is composed of a plate main body, a piston support that is rotatably supported by the rotating swash plate main body and swings, and a piston that is hooked to the piston support and reciprocates within the cylinder. In a variable capacity swash plate type compressor that performs capacity control by changing the rotation angle, the amount of unbalance of the engaging portion of the swash plate body is balanced, and the center of gravity is aligned approximately with the axis of the main shaft, and the swash plate The center of tilt of the main body is aligned with the center of gravity of the piston support.

Thirdly, an additional mass is provided on the side opposite to the main shaft from the engaging portion of the drive plate, and the tilting angle at which the centrifugal force acting on the main shaft becomes zero is determined by the size of the additional mass. It is being adjusted.

Or, the main shaft is equipped with an electromagnetic clutch,
By providing it in the armature portion of the electromagnetic clutch, the rotational balance of the drive plate is maintained.

[Effect]

The unbalance of the centrifugal force acting on the main shaft is caused by the drive plate fixed to the main shaft, the rotating body of the swash plate body which is mounted at an angle with respect to the main shaft, and the centrifugal force exerted on the swash plate body. Some cases occur due to the oscillation of the piston support, which oscillates as the swash plate main body rotates.

Here, the centrifugal force of the drive plate is constant regardless of the swash plate tilt angle, but the piston support is unbalanced due to the rotation of the center of gravity of the piston support around the main axis due to the centrifugal force and rocking movement of the swash plate. Varies depending on force and swash plate tilt angle. Therefore, the centrifugal force resulting from the combination of these also changes depending on the swash plate tilt angle. In the present invention, firstly, at least the center of gravity of the swash plate main body is configured to substantially coincide with the axis of the main shaft, so that the rate of change with respect to the swash plate tilt angle can be reduced. Secondly, the piston support and the center of tilt are configured to almost match, and the center of gravity of the swash plate body and piston support are configured to almost match the center of the main shaft, so the unbalance of the centrifugal force mentioned above is reduced. Moreover, since the rate of change with respect to the swash plate tilt angle can be reduced, the amount of unbalance of centrifugal force can be reduced over the entire range of the swash plate tilt angle, that is, the entire capacity range of the compressor, As a result, it is possible to suppress vibrations and noises inside and outside the vehicle interior, especially vibrations and noises at the idle speed of the engine.

Thirdly, by adjusting the size of the additional mass of the drive plate, it is possible to adjust the tilting angle at which the centrifugal force acting on the main shaft becomes zero.

〔Example〕

Embodiments of the present invention will be described below with reference to FIGS. 1 to 13. FIG. 1 shows the overall structure of the variable swash plate compressor according to this embodiment, and shows a state where the swash plate tilt angle is maximum, that is, the piston stroke is maximum. The housing consists of a front housing 1 and a cylinder block 2. That is, a bowl-shaped front housing 1 is installed and fixed to one end side of a cylindrical cylinder block 2. The main shaft 13 is rotatably supported at the center of these cross sections via radial needle roller bearings 18,19. A swash plate chamber lO in which a swash plate exists is formed in the front housing 1. Inside the cylinder block 2, a plurality of cylinders 33 are arranged circumferentially around the main shaft 13 and parallel to the axis 3 on the main shaft.

A drive plate 14 is fixed to the main shaft 13 by a pin 11 or a plastic connection. This drive plate 14 constitutes a swash plate together with the swash plate main body 12. That is, by dividing the swash plate into the drive plate 14 and the swash plate main body 12 and adopting the configuration described below, the inclination angle of the swash plate main body 2 (
It is possible to change the stroke of the piston, which changes the swash plate tilt angle. That is, this drive plate 14 is formed with an ear portion 141, and this ear portion 1
41 is provided with a cam groove 142. A pivot pin 16 on the swash plate side is movably attached within the cam groove 142. Furthermore, the lug portion 141 of the drive plate 14 and the swash plate lug @121 have a structure such that their side surfaces are in contact with each other. As a result, when the drive plate 14 rotates due to the rotation of the main shaft 13, a rotational force is applied from the lug 14.1 on the drive plate 14 to the swash plate lug shaft 121,
The swash plate main body 12 rotates. In addition, the drive plate 14
The cam groove 142 formed in the cam groove 142 has an edge consisting of one closed curve, and the curve is such that even if the pivot pin 16 moves within the cam groove 142, the top dead center position of the piston 31 does not change.

A sleeve 15 is incorporated into the main shaft 13 so as to be slidable in the axial direction with respect to the main shaft 13 . The sleeve 15 and the swash plate main body 12 are connected by a sleeve pin 17, and the swash plate main body 12 is fastened to the sleeve 15 so as to be rotatable around the sleeve pin 17. At this time, when the sleeve 5 slides rightward in the figure, the inclination of the swash plate body 12 becomes smaller. Note that due to the rotation of the main shaft 13, the drive plate 14. Swash plate body 12. The sleeve 5 rotates together. Therefore, the sleeve pin 17 is connected to the swash plate main body 12.
It becomes the center of tilt of the swash plate.

A piston support 21 is held in contact with the swash plate body 12 via a ball bearing 23. In addition, a balance ring 2 is attached to the nose portion 122 of the swash plate main body 12.
4 is fixed by a stopper 22 so as to apply pressure to the ball bearing 23, and the ball bearing 2
3 does not move relative to the swash plate main body 12 in the rotational direction.

Furthermore, the piston support 21 has a protrusion 211 that allows the piston support 21 to
Movement to the right in the figure is restricted by the ball bearing 23, and movement to the left in the figure is also restricted by the thrust bearing 25 installed between the swash plate body ↓2. Also.

A support pin 26 is fixed at a lower position of the piston support 21 and in the radial direction by a method such as press-fitting, screwing, or plastic coupling. This support pin 26 has a slide ball 27. The inner surface of the slide ball 27 that is in contact with the outer circumferential surface of the slide ball 27 is spherical, and a slide shoe 28 whose outer circumferential surface is cylindrical is attached, and the support pin 26 is rotatable and slidable in the axial groove 29. In this way, the slide shoe 28 reciprocates in the axial groove 29 provided at the bottom of the inner circumference of the front housing 1. As a result, the piston support 21 is connected to the main shaft 13.
The movement around the axis is restricted so that it does not rotate around the axis.

The piston support 21 holds one end of a connecting rod 32. That is, the connecting rod 32 is formed by connecting ball portions 321 and 322 to both ends of one stem portion 323 by welding or the like. One end of the connecting rod 32, ie, the ball 321, is held by the piston support 21. This holding is performed rotatably around the center of the ball 321. The other end, that is, the ball 322, is similarly held to the piston 31 by caulking or the like so as to be freely rotatable about the center of the ball 322. A plurality of such connecting rods 32 and pistons 31 exist.

The plurality of pistons 31 are fitted and built into a plurality of cylinders 33 provided in the cylinder block 2 so as to be able to reciprocate. Note that piston rings 34 and 35 are attached to the piston 31.

On the right side of the cylinder block 2 is a suction valve plate 5. Cylinder head 4. Discharge valve plate 6. A gasket 7 and a rear cover 3 are arranged. Further, the cylinder block 2 is integrally fixed to the front housing 1 with a through bolt (not shown) or the like.

Airtightness between the front housing l and the cylinder block 2 is maintained by an O-ring 38. The rear cover 3 and the cylinder block 2 are kept airtight by an O-ring 39.

The rear cover 3 is provided with an inlet 30 and an outlet (not shown). This suction port 30 is connected to a suction passage 301 and then to the suction chamber 8 via a control valve 400. The suction chamber 8 and the discharge chamber 9 are connected to a suction boat 401 and a discharge boat 40 through the suction valve plate 5 and the discharge valve plate 6, respectively.
It leads to 2. These suction boats 401 and discharge boats 402 are provided in the cylinder head 4 in correspondence with the cylinders 33, respectively.

The upstream side of the control valve 400 and the swash plate chamber 10 in the front housing 1 are communicated with each other to make the pressure the same. That is, rear cover 3. Stop pin 75 and screw member 2
02, and the communication passages 303, 76, and 203 provided in the center of the spindle 3, and the communication 131 provided in the center of the spindle 3,
This passage 131 is connected to the drive plate 14 through a passage 143 that opens in the radial direction. On the other hand,
The downstream side of the control valve 400 communicates with the suction chamber 8 .

This control valve 400 may be controlled outside the compressor, or may be of the type shown in FIG. 2.

First, the structure of the control valve 400 shown in FIG. 2 will be described.

A piston-shaped main valve 410 is installed in a flow path connecting the suction passage 301 and the suction chamber 8, and the main valve 410.
Main valve case 4 along with main pal spring 412
It is inserted in 11.

The main valve case 411 has an O ring 414.

415 and the lid 35 in an airtight manner and are fixed to the rear cover 3, and together with the main valve 4.10, form a flow path 413 on the downstream side of the control valve. The main valve spring 412 biases the main valve 410 to increase its opening degree. A bellows chamber 421 that accommodates a bellows 420 is formed on the opposite side of the main valve spring 412, and the bellows chamber 421 and the suction passage 30 are connected to each other.
1 is in communication with the pressure equalizing hole 422. A pressure equalizing passage 424 is provided in the outer wall of the case 423 forming the bellows chamber 421 and the rear cover 3, and communicates with the communication passage 303 provided in the rear cover 3. Therefore, the swash plate chamber 10, the bellows chamber 421, and the suction passage 301 have the same pressure, and are maintained at the suction pressure of the compressor.

The pilot valve 430 has a pilot valve spring 43
1, it is biased toward the bellows 420 side.

The bellows spring 425 is attached to the bellows 420.
20 is installed so as to bias it in the direction of contracting it. Head spring 4 via pilot valve spring 431
51 is installed, and an electromagnetic coil 452 is formed around the plunger 450.

A pilot valve chamber 432 in which a pilot valve 430 is provided communicates with the discharge chamber 9 through communication holes 433, 434, and 304, and communicates with the head of the main valve 410 through a communication passage 440 via the pilot valve 430. It's communicating.

Next, we will discuss the capacity control mechanism.

When the heat load on the evaporator (not shown) decreases, the bellows 420 expands because the suction pressure of the compressor, ie the pressure in the suction passage 3.01, decreases.

As a result, the pilot valve 430 opens, and the discharge pressure of the pilot valve chamber 432 acts on the head of the main valve 410 via the communication passage 440.
Press down on 0. Therefore, since the control valve downstream flow path 413 is narrowed, the pressure inside the suction chamber 8, that is, the suction port 40
The pressure immediately before 1 will decrease. As a result, the pressure difference between the left and right sides of the piston 31 (the difference between the pressure in the swash plate chamber 10 and the pressure immediately before the suction boats 4, 01) increases, so the swash plate tilt angle decreases and the piston stroke decreases.

On the other hand, if the heat load on the evaporator (not shown) increases, the above operation will be reversed. In other words, the heat load increases and the suction pressure increases, causing the bellows 420 to contract and the pilot valve 430 to close.

As a result, the head pressure of the main valve 410 decreases, and the downstream flow path 413 of the control valve opens, so that the piston 31
The pressure difference between the left and right sides decreases, the swash plate tilt angle increases, and the stroke of the piston 31 increases.

Next, capacity control using external control will be described.

The suction pressure of the compressor is controlled by changing the voltage applied to the electromagnetic coil 52 according to an external signal (eg, temperature, pressure, etc.). For example, when cooling power is required during cool-down or the like, lowering the voltage applied to the electromagnetic coil 452 reduces the suction force of the plunger 450 and increases the pressing load of the head spring 451, thereby closing the pilot valve 430. As a result, main valve 4
10 is fully opened, the compressor is operated at maximum stroke, that is, maximum capacity, the suction pressure of the compressor decreases, and the refrigerant flow rate increases.

Next, a structure for regulating the upper and lower limits of the swash plate tilt angle will be described. In the process where the swash plate tilt angle moves from small to large, the sleeve 15 slides on the main shaft 13 from right to left in FIG. As a result, the swash plate body 1
2 is tilted clockwise around the sleeve pin 17. And the swash plate tilt angle is maximum (viston stroke is maximum)
becomes. On the swash plate main body 2, two tilt regulating portions 123 are provided axially symmetrically on the side opposite to the swash plate ear shaft 121 with respect to the main shaft 13, and the tilt regulating portions 123 and the drive plate 14 The maximum tilt angle, that is, the maximum capacity position is determined by the contact with the tilt restriction portion 144. In the swash plate main body 12, a thrust load due to gas compression acts on the disk portion 124. This thrust load moves on the surface of the disk portion 124 while changing. Moreover, the center of the load is away from the center of the main shaft 13. Therefore, the swash plate body 1
2, the y-axis (axis corresponding to the I-I line in Figure 5)
A moment acts around the swash plate body 12 to rotate it, and this moment increases as the compressor capacity increases. In other words, this moment is the largest at the maximum tilt angle.

Conventionally, the methods for receiving this moment include (1) receiving it by the drive plate 14 and sleeve 15, and (2) receiving it by the drive plate 14 and the swash plate body 12 on the axis of the y-axis, and at one location.

Abnormal wear of the sleeve pin hole and sleeve 1 due to binding
This caused problems such as damage to the parts. However, the maximum capacity regulation structure described above, that is, the swash plate ear shaft 121 is located at a position opposite to the main shaft 13, and is located at a long distance from the center of the main shaft 13, and furthermore, at two locations on the left and right with respect to the y-axis. Since the structure is designed to receive the reaction force of the moment, the reaction force can be significantly reduced and stable support can be achieved, thereby solving the problems of the conventional method.

By the way, at the time of maximum capacity, appropriate gaps are provided between the sleeve 15, the drive plate 14, the pivot pin 16, and the cam groove 142, so that contact between these members is avoided. Furthermore, when the swash plate tilt angle is the minimum (the piston stroke is the minimum), the right end of the sleeve 15 is brought into contact with the stop shaft 132 and the spring member 133 installed on the main shaft 13, thereby regulating the position of the minimum stroke. There is. Drive plate 14 and sleeve 1 on main shaft 13
A spring 134 installed between the sleeve 15 and the stopper 132 is provided to bias the piston stroke in the minimum direction and the maximum direction, respectively.

A leftward thrust force (axial force) that acts on the main shaft 13 when compressing gas is supported by a thrust bearing 42 installed between the front housing l via the drive plate 14. Further, the radial force (force in the radial direction) acting on the main shaft 13 is supported by two radial needle roller bearings 19 and 18 provided in the front housing 1 and the bearing housing 20 of the cylinder block 2.

A thrust bearing 201 is fixed to the right end of the main shaft 13 within the bearing housing 20 of the cylinder block 2 by a screw member 202. Depending on the thickness of the thrust race used in the thrust bearing 42 and the tightening force of the screw member 202, the top clearance of the compressor (when the piston 31 is at the top dead center, the head of the piston 31 and the suction valve plate 5 (defined as the gap between the two) can be adjusted.

With the configuration described above, when driving force is input to the main shaft 13 of this compressor by the engine (not shown), the drive plate 14 and the swash plate main body 12 rotate, and the rotating shaft of the main spindle 3 rotates. In contrast, the piston support 21 swings. This rocking motion is called misosuri motion, and is similar to the motion that occurs when a liquid in a round container is subjected to circular motion. This swinging motion causes the piston 31 to reciprocate within the cylinder 33 (linear motion parallel to the axial direction of the main shaft 13).

The refrigerant returned from the refrigeration cycle (not shown).

After flowing into the suction port 30 and being lowered to an appropriate pressure by the control valve 400, it is introduced into the suction chamber 8 and is passed through the suction boat 401. of the cylinder head 4. Cylinder 33 via suction valve plate 5
and completes the suction stroke.

The refrigerant compressed by the piston 31 is delivered to the discharge port 402 of the cylinder head 4. The discharge passes through the discharge valve plate 6 into the discharge chamber 9 formed in the rear cover 3, and is discharged through a discharge port (not shown).
From there, it is discharged into a refrigeration cycle (not shown).

Next, as shown in FIGS. 3 to 6, the drive plate 14 is
．． The shape of the swash plate main body 12 is shown.

The drive plate 14 is provided with an ear portion 141 having a cam groove 142, as shown in FIGS. 3 and 4. Here, the direction of centrifugal force is defined in FIG.

With respect to the center of main @13, the upper direction is +y direction, and the lower direction is -
The right direction of the y-force direction is the +X direction, and the left direction is the -X direction.

The position of the ear portion provided with the cam groove 142 is provided on the positive side in the y direction and on the negative side in the x direction. This ear part 141
For the amount of unbalance, there is a balance mass part 1 in the X direction.
47, the amount of misalignment is almost zero.

Furthermore, by providing a balance mass section 146 in the y direction, the center of mass is on the negative side. The balance mass portion 146 is formed into a fan shape, and is provided with a space 148 to accommodate the disk portion 124 of the swash plate main body 12 when the swash plate tilt angle is maximum, that is, at maximum capacity. 148 is provided with a tilting regulating portion 144 that regulates the tilting position of the swash plate main body 12 at maximum capacity.

The swash plate main body 12 rotatably supports the sleeve pin 17 as shown in FIGS. 5 and 6, and the piston support 14
a nose portion 122 that supports the swash plate ear shaft 121 . Disk portion 124. It consists of a tilting restriction section 123. Nose part 12
A threaded portion 126 for attaching the balance ring 24 is formed at the tip of the balance ring 2, and an adjustment nut 99 applies preload to the ball bearing 23 and fixes the balance ring 24.

The swash plate main body 12 is approximately a combination of a disk shape and a cylindrical shape except for the swash plate ear shaft 121. Further, in order to reduce the amount of misalignment of the ear shaft 121, a recess portion 127 is formed on the ear shaft 121 side of the disc portion 124.

Next, the mass distribution formed in the piston support 21 will be described.

A member that swings around the sleeve pin F as the swash plate main body 12 rotates is a piston support 21. The outer ring of the ball bearing 23, the thrust race of the thrust hair ring 25 on the swash plate body 12 side, and the support pin 26.
It is composed of a rotation prevention mechanism section consisting of a slide ball 27 and a slide shoe 28. FIG. 7 is a front view of the piston support 21, and FIG. 8 is a cross-sectional view taken along the line II in FIG. 7. The connecting rod 3 is attached to the piston support 21.
The recessed part 212 (
a) ~ 212 (f), collar portion 213 (a) ~ 213
(f), oil supply holes 214 (a) to 214 (f), and a bearing housing portion 215 that accommodates the outer ring of the ball bearing 23. The protrusion 211 is formed. Further, additional mass portions 216 (a) to 216 (e) and 217 are formed closer to the piston 31 than the center of tilting of the swash plate main body 12, that is, the center of the sleeve pin 17. The additional mass portions 216 (a) to 216 (e) and 217 are connected to the recess portions 212 (a) to 212 (f) and the protrusion portions 211 etc. so that the mass center of gravity of the piston support 21 is aligned with the sleeve pin 17. It is formed to bring what was on the side of the drive plate 14 from the center to the center of the sleeve pin ↓7, and also includes a rotation prevention mechanism (only the support pin 26 is shown in FIGS. 7 and 8). ) is formed to balance the inertial force of Note that if only the inertia force of the detent mechanism is to be balanced, the additional mass parts 216(b) and 216
It is clear that (d) can be deleted. The additional mass portion 217 is provided at a symmetrical position with respect to the center of the main axis of the detent mechanism.

Further, the additional masses 216 (a), 216 (d), 216 (b), and 2-piece 6 (e) are each formed axially symmetrically.

With the above configuration, the mass center of gravity of the piston support 21 coincides with the center of the sleeve pin, so that the unbalance caused by the rocking movement of the piston support 21 can be reduced to almost zero, and the surroundings including the support pin 26 can be reduced to almost zero. Unbalance of the stop mechanism can be balanced.

9 and 10 show other embodiments of the present invention; FIG. 9 is a front view of a piston support according to the present invention, and FIG. 10 is a sectional view taken along the line I--I in FIG. 9. Note that parts having the same structure as those in FIGS. 7 and 8 described above are given the same numbers, and explanations of the structures will be omitted.

From the center of the sleeve pin 17 of the piston support 2 to the drive plate 14 side, there is a recess 218 (a).
, 218(b), 218(d).

218 (e) is formed at a symmetrical position with respect to the center of the main axis, and the recess 219 is also formed at a position symmetrical with respect to the main axis with respect to the support pin 26, similarly to the above. The recessed portions 218 (a) to 218 (e) and the recessed portion 219 act to substantially align the center of mass of the piston support 21 with the center of the sleeve pin 17, and reduce the mass of the piston support 21. can do. If the mass of the piston support 21 can be reduced, the reciprocating inertia mass including the piston support 21 can be reduced, and the load control characteristics of the compressor can be improved.

11 and 12 show other embodiments of the present invention, FIG. 11 is a front view of a piston support according to the present invention, and FIG. 2 is a cross-sectional view taken along line I-I in FIG. I1. . Similar to the above, parts having the same structure are denoted by the same reference numerals and explanations thereof will be omitted.

On the piston 31 side (rightward side in FIG. 11) from the center of the sleeve pin 17 of the piston support 2↓,
A member 22 with a specific gravity greater than the specific gravity of the piston support 21
0 (a), 220 (b).

220 (d), 220 (e) and 221 are formed. For example, since the piston support 21 is usually made of aluminum alloy, the above member 220 (a)
, 220 (b), 220 (d).

For 220 (e) and 221, it is effective to use a casting method as a casting. The above members 220 (a) and 220
(d), 220 (b) and 220 (e) and 221
and the support pin 26 are provided at symmetrical positions with respect to the center of the main axis.

With the above configuration, a member having a large specific gravity can be used, so the position of the mass center of gravity of the piston support can be easily adjusted.

In the above embodiment, the center of gravity of the piston support 21 is aligned with the center of the sleeve pin 17, but the center of the sleeve pin 17 may be aligned with the center of gravity of the piston support 21.

Also, the sleeve pin 17 is placed on the axis center line of the support pin 26.
It is desirable that the center of the ball portion 321 be aligned with the center of the ball portion 321.

FIG. 13 shows the effects of this embodiment configured as described above. The relationship between the swash plate tilt angle α and the centrifugal force Fy will be explained. Note that FIG. 13 shows the values at a compressor rotational speed Nc'' of 900 rpm.
Since balance is achieved by providing the recessed portion 127 on the 21 side, the mass of the swash plate main body can be reduced. Therefore, the center of gravity of the swash plate body 12 is adjusted to the main axis 13 due to the inclination of the swash plate body.
, but the inclination of the centrifugal force with respect to the swash plate tilt angle α becomes smaller.

Further, as described above, by increasing the balance mass portion 146 of the drive plate 14, as shown in FIG. 13, the centrifugal force determined by the swash plate body 12 can be shifted to the negative side.

That is, in this embodiment, balance is achieved by providing a recessed portion on the ear shaft 121 side of the disk portion 124 without providing additional mass on the swash plate main body 2, so that the centrifugal force with respect to the swash plate tilt angle is The inclination of the drive plate 14 is made smaller, and the balance mass portion of the drive plate 14 is made larger, thereby making the centrifugal force smaller on the maximum capacity side than on the minimum capacity side. Either reduce the absolute level of this centrifugal force on the maximum capacity side, or
Whether or not the capacity should be reduced on the minimum capacity side can be set in any manner by balancing either the drive plate 14 or the electromagnetic clutch 137 as described above.

In this embodiment, the unbalance due to centrifugal force is reduced on the maximum capacity side, for example: (1) Automotive engines have significantly reduced vibration and noise when rotating at low speeds. (2) Since the variable capacity compressor is driven by a V-belt by an automobile engine, the rotational speed of the compressor is approximately equal to the rotational speed of the engine. Incidentally, the capacity of the compressor changes depending on the heat load inside the vehicle cabin, but the compressor capacity is maximized when the engine speed is reduced, such as when idling or driving in traffic jams. Frequently. That is, the variable capacity compressor is often operated in the maximum capacity state during low speed rotation.

This is due to the following reasons. In addition, in this example, y
Not only the centrifugal force in the axial direction but also the centrifugal force in the x-axis direction is extremely small.

Next, in this embodiment, as shown in FIG.
4, that is, the center of the sleeve pin 17 is aligned. When the center of gravity of the piston support 14 is away from the center of the sleeve pin 17, an unbalance amount equal to the eccentricity multiplied by the piston support weight is generated due to the rocking motion of the piston support 21.

In this embodiment, the amount of unbalance of the piston support 21 is set to approximately zero. In addition, in this embodiment, when the axis passing through the center of the support pin 26 is extended as shown in FIG.
It is configured to pass through the center of the sphere No. 21. With such a configuration, the amount of unbalance caused by the rocking motion of the piston support 21 can be reduced.

Next, using FIGS. 14 and 15, calculate the swash plate tilt angle α
and the angle β of the center of the connecting rod sphere on the piston support side. Here, the swash plate tilt angle β is the inclination angle of the swash plate body 12 with respect to the axis of the main shaft 13 as described above, that is, the angle of inclination of the swash plate main body 12 from a plane passing through the center of the sleeve pin 17 and perpendicular to the main shaft 13. Represents the slope. β is an angle formed between a plane passing through the center of the sleeve pin 17 and perpendicular to the main axis ↓ 3 and an extension line connecting the center of the connecting rod ball portion 321 of the piston support 21 and the center of the sleeve pin 17. 14th
The figure shows the case when α<β, and Figure 15 α=β. In the present invention, the additional mass to be attached to the piston support 12 or the position of the recess is determined based on the relationship between α and β. In other words, if α≦β, an additional mass is provided on the piston support 21 on the side of the piston 31 from the plane passing through the center of the machine sleeve pin 17 and having a swash plate tilt angle, or on the side of the drive plate 14 from the same plane. A recessed portion is formed in the area.

If α>β, an additional mass is provided on the drive plate side from the above surface, or a recess is formed on the piston side.

The above embodiments have been made for a variable capacity swash plate compressor in which the pressure in the swash plate chamber is kept constant and the swash plate tilting angle is changed by lowering the pressure at the cylinder suction port below the pressure in the swash plate chamber using a control valve. However, as disclosed in Japanese Patent Publication No. 58-4195, etc., the cylinder inlet pressure is kept constant, blow-by gas or discharge gas is introduced to increase the pressure in the swash plate chamber, and the swash plate is tilted. A similar effect can be obtained with a variable capacity swash plate compressor that uses angle control.

Next, another embodiment of the present invention will be described with reference to FIGS. 16 to 21. Drive plate 14 according to FIGS. 16 to 21. The shape of the swash plate body 12 and the balance ring 24 is shown, and the direction of centrifugal force is defined here. In FIG. 1, the upward direction with respect to the center of the main shaft 13 is the +y force direction, the downward direction is the -y direction, and the vertical direction in the figure is the X direction.

The drive plate 14 shown in FIGS. 16 and 17 includes
Ear portion 141 with cam groove 142. A mass portion 145 for providing a communication portion 143 and a tilting restriction portion 144 are connected to the main shaft 13.
It is installed in the y-axis direction with respect to the center of. On the other hand, on the lower side (-y axis direction) with respect to the center of the main shaft 13, the above-described ear portion 141° mass portion 145 and the y
A balance mass portion 146 is provided to balance the centrifugal force in the axial direction.
is provided. Further, the centrifugal force in the X-axis direction is also substantially balanced with respect to the center of the main shaft 13. Therefore, the drive plate 14 is configured such that the centrifugal force is balanced by the drive plate 14 alone.

The swash plate main body 12 shown in FIGS. 18 and 19 includes a nose portion 122 that rotatably supports the sleeve pin 17, and a swash plate ear shaft 121. The disk portion 124° consists of a tilting restriction portion 123 and an additional mass portion 125.

The eccentric mass part 125 is provided on the axis opposite to the ear axis 121 of the disk part 124 as shown in FIG. It is formed to fit in a space surrounded by the inner peripheral part of the mass part 146 and the front housing 1. Since the swash plate body 12 is substantially symmetrical with respect to the center of the main shaft 13, the centrifugal force in the X-axis direction is substantially balanced. However, the centrifugal force in the y-axis direction with respect to the center of the main shaft 13 changes depending on the swash plate tilt angle because the swash plate main body 12 tilts.

The balance ring 24 shown in FIGS. 20 and 21 is provided with a protrusion 241 in order to position the balance ring 24 on the nose portion 1322 of the swash plate body 12. direction, i.e. the swash plate body 12
An eccentric mass portion 242 is formed on the ear shaft 121 side.

Since the balance ring 24 is configured symmetrically with respect to the center of the main shaft 13, the centrifugal force in the X-axis direction is perfectly balanced. Since the eccentric mass portion 242 and the balance ring 24 are fixed to the swash plate main body 12, the centrifugal force in the y-axis direction relative to the center of the main shaft 13 changes depending on the swash plate tilt angle.

FIG. 22 shows that in this embodiment, the compressor rotational speed Nc=
A centrifugal force Fy in the y-axis direction at 90 Orpm is applied to the drive plate 14. When the swash plate main body 12 and the balance ring 24 are divided into each element, the centrifugal force for each element and the combined centrifugal force are shown with respect to the slant plate tilt angle α. That is, in FIG. 22, straight lines (1) and (2) are the drive plate 14, and straight line (3) is the knob part 1 of the swash plate main body 12.
22, the straight line (4) is the ear part 121 and the pivot pin 16 of the swash plate main body 12, the straight line (5) is the disk part 124 and the tilt restriction part 123 of the swash plate main body 12, and the straight line (6) is the swash plate main body 1
2 additional mass part 125, the straight line (7) is the balance ring 2
represents the centrifugal force Fy for each α of 4. In addition,
As described above, the centrifugal force Fy in the X-axis direction is almost balanced. Straight lines (1) and (2) are constant regardless of α, and Fyt+Fyz=O. Straight line (2) to (6)
And the straight line (7) becomes a straight line with a certain slope with respect to α, and the sign and magnitude of the slope vary depending on each element.In this example, a mJIX = 20 degrees.
So Fy=0.5kgf, α□. F y = − at 20 degrees
0.5kg f, and the intermediate swash plate tilt angle αmean
= I Q degrees, the centrifugal force Fy"O. In other words, the centrifugal force acting on the compressor is balanced at the intermediate value of the swash plate tilt angle, and at the maximum and minimum swash plate tilt angles,
Drive plate 14 so that centrifugal force is below ±0.5 kgf. This constitutes the mass distribution of the swash plate main body 12 and the balance ring 24.

Here, the maximum centrifugal force generated in the compressor is ±0.5 kg.
f was set by stopping the compression operation of the compressor, mounting a model machine with an inertial mass on the main shaft 13 in a car, and conducting an evaluation test by actually measuring vibrations and noise inside and outside the car and by auditory sense. This is a value determined through implementation. The above centrifugal force value ±0.
5 kgf is a value when the vibration of the engine itself is small, and therefore, this value changes depending on the engine in which the compressor is installed.

In FIG. 23, similar to FIG. 22, the compressor rotation speed Nc=9
At 0 Orpm, the centrifugal force F with respect to the swash plate tilt angle α
The relationship between F (the combined centrifugal force of each rotating member) is compared between the embodiment of the present invention and conventional examples I and II. In conventional example ■, Fy≦-0.5kg at αmtn”O
f, but Fa>0.5kg in α, &8
f, so that α such that Fy=O is αmean(=
α,,,/2) is smaller than that. Therefore, since the centrifugal force becomes large at α, a8, that is, the maximum capacity side of the compressor, the vibration and noise inside and outside the vehicle cabin become large due to the unbalance of the primary rotation due to this centrifugal force. On the other hand, in conventional example ■, F is less than 0.5 kgf at αwax, but since Fy > 0.5 kgf at α=O, Fy
=O, which is larger than αmean. Therefore, when the compressor is driven at the minimum capacity side, an unbalance in the first order of rotation occurs due to centrifugal force as described above, and vibrations and noise increase.

Conventional example 1. In II, Fy = in αmean
Even if we take measures such as adding an additional mass to the armature of the electromagnetic clutch so that O, for example, the centrifugal force needle of the added mass in Fig. 23 moves upward and downward in parallel, the centrifugal force This does not reduce vibration and noise due to unbalance of the primary rotation.

FIG. 24 shows the case where the centrifugal force at α20 is set to O due to the mass distribution of the drive plate and the swash plate body. The capacity of the compressor is controlled during high-speed rotation, and it is often operated in a region where the swash plate tilt angle is small, so it is particularly effective in reducing vibration and noise during high-speed rotation.

FIG. 25 shows the overall structure of a variable stroke swash plate compressor showing another embodiment of the present invention, and differs from that shown in FIG. 1 described above in the following structure.

In other words, the structure does not have the balance mass part 146 provided below the center of the main shaft 13 of the drive plate 14, and the additional mass part 125 of the space swash plate main body 12 of the balance mass part 146 is increased. be. By increasing this additional mass portion 125, the counterclockwise tilting moment of the swash plate around the sleeve pin 17 (acts as a counterclockwise moment that attempts to raise the swash plate variant 12) can be increased. . As a result, the centrifugal force in the y-axis direction of the drive plate 14 alone becomes unbalanced. That is, the centrifugal force of the drive plate 14 becomes a centrifugal force Fyd only in the positive direction of the y-axis. Therefore, this Fy
An external mass 138 is provided on the armature portion 137 of the electromagnetic clutch 136 so as to balance the ++.

This embodiment will be explained from the relationship between the swash plate tilting angle α and the centrifugal force Fy in FIG. 22. In FIG.
(equivalent to -Fya mentioned above). In other words, even if the centrifugal force is not completely balanced by the drive plate 14 alone, the object of the present invention can be achieved by adding external mass to the electromagnetic clutch. Another advantage of this embodiment is that it is possible to adjust the unbalance of centrifugal force outside the compressor, and even minute adjustments are possible. In addition to reducing vibration and noise due to the primary rotation caused by centrifugal force, there is also an effect of reducing the control differential pressure at the control valve 400.

The above embodiments have been made for a variable capacity swash plate compressor in which the pressure in the swash plate chamber is kept constant and the swash plate tilting angle is changed by lowering the pressure at the cylinder suction port below the pressure in the swash plate chamber using a control valve. However, there is another method, as disclosed in Japanese Patent Publication No. 58-4195, in which the cylinder inlet pressure is kept constant and blow-by gas or discharge gas is introduced to increase the pressure in the swash plate chamber. Similar effects can be obtained with a variable stroke swash plate compressor that controls the tilt angle.

FIG. 26 and FIG. 27 are diagrams showing other embodiments in which the centrifugal force of the drive plate 14 is made almost zero.
The figure is a front view of the drive plate 14, and FIG. 27 is a front view of the drive plate 14.
It is a sectional view taken along the line IV-IV in the figure.

The drive plate 14 is provided with an ear portion 141 in which a cam groove 142 is formed, and the balance mass portion 146 and the tilt restriction portion 14
4 is provided. Here, the balance mass section 146
is the swash plate body (not shown) relative to the center of the main shaft 13.
When the swash plate tilts to its maximum, the eccentric mass part (
The wing structure has a space in the center so as not to interfere with the wing (not shown). That is, since the balance mass part is formed so as to surround the eccentric mass part of the swash plate main body, the eccentric mass part of the swash plate main body is
(The tilting moment that acts to reduce the tilting angle of the swash plate body becomes large).

Therefore, this embodiment has the effect that the object of the present invention can be achieved without increasing the dimension of the compressor in the main axis direction.

〔Effect of the invention〕

As described above, according to the present invention, firstly, it is possible to reduce the unbalance of the primary rotation due to the rocking motion of rocking members such as piston supports, thereby reducing the vibration and noise of the vehicle body in the entire capacity range of the compressor. can be reduced.

Secondly, since the amount of unbalance due to the rotation mechanism can be reduced, vibration and noise of the vehicle body can be reduced in the entire capacity range of the compressor.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing the structure of a variable capacity swash plate compressor showing one embodiment of the present invention, and FIG. 2 shows the structure of a variable capacity swash plate compressor showing another embodiment of the invention. A vertical sectional view, FIGS. 3 and 4 show the drive plate shown in FIG. 1, FIG. 3 is a front view, and FIG. 4 is a view in the direction of arrow A in FIG.
6 and 6 show the swash plate main body shown in FIG. 1, FIG. 5 is a front view of the swash plate main body, and FIG. 6 is a sectional view taken along line I-1 in FIG. 5. 7 is a front view of the piston support, FIG. 8 is a sectional view taken along the line 1-1 in FIG. 7, FIG. 9 is a front view of the piston support showing another embodiment of the invention, and FIG. 9 is a sectional view taken along line 1-1 in FIG. 9, FIG. 11 is a front view of a piston support showing another embodiment of the present invention, FIG. 12 is a sectional view taken along line I-I in FIG. 14 and 15 are longitudinal sectional views showing the relationship between α and β, and FIG. 16 is a drive plate showing another embodiment of the present invention. 17 is a front view showing the structure of the swash plate body, FIG. 18 is a front view showing the structure of the swash plate body showing an embodiment of the present invention, FIG. 19 is a cross sectional view thereof, and FIG. 21 is a cross-sectional view thereof, FIG. 22 is a diagram showing the relationship between the swash plate tilt angle and centrifugal force in an embodiment of the present invention, and FIG. 23 is a front view showing the structure of a balance ring according to the present invention. The figure shows the relationship between the swash plate tilt angle and centrifugal force of the present invention and a conventional example.
FIG. 24 is a diagram showing the relationship between the swash plate tilt angle and centrifugal force in another embodiment of the present invention, and FIG. 25 is a diagram showing the structure of a variable stroke swash plate compressor showing another embodiment of the present invention. FIG. 26 is a front view showing the structure of a drive plate according to another embodiment of the present invention, and FIG. 27 is a cross-sectional view thereof. 12... Swash plate body, 13... Main shaft, 14... Drive plate, 15... Sleeve, 17... Sleeve pin, 21... Piston support, 31... Piston, 33...・Cylinder, 216°217...Additional mass, 218°219...Recessed portion, 220.221...Member. .

Claims (1)

[Scope of Claims] 1. A main shaft rotatably driven by a drive source, a drive plate fixed to the main shaft, and an engaging portion that engages the drive plate so as to be tiltable in a tilted state with respect to the main shaft. a swash plate body that rotates together with the piston support that is rotatably supported by the rotating swash plate body and that swings;
In a variable displacement swash plate type compressor, which is composed of a piston that is hooked to this piston support and reciprocates within the cylinder, and which performs capacity control by changing the tilt angle of the swash plate body, a predetermined amount within a tilt angle range is used. A variable capacity variable capacity characterized in that at least the position of the center of gravity of the swash plate body is approximately aligned with the axis of the main shaft by providing a portion that balances the amount of unbalance of the engaging portion of the swash plate body at a tilt angle. Swash plate compressor. 2. The variable swash plate according to claim 1, wherein the balancing portion is provided on the engaging portion side with respect to the main shaft, and is a recess portion formed in a disk portion of the swash plate main body. Capacity swash plate compressor. 3. The balancing part is provided on the opposite side of the main shaft from the engaging part, and is a half-ring-shaped additional mass part along the outer periphery of the swash plate main body. The variable capacity swash plate compressor according to item 1. 4. A main shaft rotatably driven by a drive source, a drive plate fixed to the main shaft, and an inclined plane that is rotatably engaged with the drive plate through an engaging portion so as to be tiltable with respect to the main shaft. a plate body; a piston support that is rotatably supported by the rotating swash plate body and swings;
In a variable displacement swash plate compressor, which is configured with a piston that is hooked to the piston support and reciprocates within the cylinder, and which performs capacity control by changing the tilt angle of the swash plate body, the engagement of the swash plate body The variable displacement tilting device is characterized in that the center of gravity of the piston support is aligned with the center of gravity of the swash plate body, and the center of gravity of the piston support is aligned with the center of tilt of the swash plate body. Plate compressor. 5. A main shaft rotatably driven by a drive source, a drive plate fixed to the main shaft, and a tilting plate that is rotatably engaged with the drive plate and an engaging portion so as to be tiltable with respect to the main shaft. a plate body; a piston support that is rotatably supported by the rotating swash plate body and swings;
In a variable displacement swash plate compressor, which is configured with a piston that is hooked to the piston support and reciprocates within the cylinder, and which performs capacity control by changing the tilt angle of the swash plate body, the engagement of the swash plate body A variable capacity swash plate compressor, characterized in that the unbalance of the parts is balanced, the center of gravity is aligned approximately with the main shaft axis, and the center of tilt of the swash plate body is aligned with the center of gravity of the piston support. . 6. An additional mass is provided on the side opposite to the main shaft from the engaging portion of the drive plate, and the tilting angle at which the centrifugal force acting on the main shaft becomes zero is adjusted by the size of the additional mass. The variable capacity swash plate compressor according to claim 1. 7. The variable capacity swash plate compressor according to claim 6, wherein the additional mass is set such that a tilting angle at which the centrifugal force acting on the main shaft becomes zero is closer to a maximum tilting angle. 8. A main shaft rotatably driven by a drive source, a drive plate fixed to the main shaft, and a tilting plate that is rotatably engaged with the drive plate and an engaging portion so as to be tiltable with respect to the main shaft. a plate body; a piston support that is rotatably supported by the rotating swash plate body and swings;
In a variable capacity swash plate type compressor, which is configured with a piston that is hooked to the piston support and reciprocates within the cylinder, and which performs capacity control by changing the tilt angle of the swash plate body, at least the swash plate body is A variable capacity swash plate type compressor, characterized in that the mass distribution of the swash plate body is configured such that the centrifugal force generated has a small inclination with respect to the swash plate tilt angle. 9. The variable displacement swash plate compressor according to claim 1, wherein the main shaft is provided with an electromagnetic clutch, and the rotational balance of the drive plate is maintained by providing the armature of the electromagnetic clutch. 10. The variable displacement swash plate compressor according to claim 6, wherein the centrifugal force acting on the main shaft is larger when the swash plate tilt angle is small than when the swash plate tilt angle is large. 11. The variable displacement swash plate compressor according to claim 6, wherein an unbalance of centrifugal force caused by rotation of the drive plate is corrected by an additional mass provided on the main shaft. 12. The variable capacity swash plate compressor according to claim 1, wherein a balance ring having an additional mass portion on the engagement portion side of the swash plate body is provided in the nose portion of the swash plate body. 13. The piston support is provided with a rotation prevention mechanism having a support pin, and the tilting center of the swash plate body and a connecting rod for hanging the piston support and the piston are located approximately on the axial center line of the support pin. 5. The variable displacement swash plate compressor according to claim 4, wherein the center of the ball portion is held by the piston support. 14. The piston support is provided with a rotation prevention mechanism having a support pin, and the recess of the piston support that holds the connecting rod for hooking the piston support and the piston is located relative to the axial center of the support pin. 5. The variable displacement swash plate compressor according to claim 4, wherein the piston support is symmetrically formed and the center of gravity of the piston support is adjusted by adding additional mass between the recesses. 15. The variable displacement swash plate compressor according to claim 14, wherein the additional mass is comprised of a member having a large specific gravity. 16. The variable variable rate according to claim 14, wherein the inertia of the detent mechanism of the piston support is balanced by providing an additional mass in the piston support at a position opposite to the detent mechanism with respect to the main shaft. Capacity swash plate compressor. 17. The variable displacement swash plate compressor according to claim 14, wherein an additional mass is provided on the piston side. 18. The tilting angle of the swash plate body (angle from a plane perpendicular to the main axis) is α, and the line connecting the connecting rod spherical center of the piston support and the tilting center forms a plane perpendicular to the main axis. When the angle is β, if α≦β, an additional mass is provided to the piston support on the piston side from a plane passing through the center of tilt and having the swash plate tilt angle, and if α>β, the above The variable capacity swash plate compressor according to claim 5, wherein the additional mass is provided closer to the drive plate than in the plane. 19. The variable displacement swash plate compressor according to claim 14, wherein a recess is formed in the piston support on the side of the swash plate body from the center of tilt. 20. When the tilting angle of the swash plate body is α, and the angle between the line connecting the connecting rod sphere center of the piston support and the tilting center and the plane perpendicular to the main axis is β, α≦β. If α>β, a recessed portion is provided in the piston support closer to the drive plate than in the plane having α, and if α>β, a recessed portion is provided closer to the piston than the plane having α. The variable capacity swash plate compressor described in . 21. The variable capacity swash plate compressor according to claim 6, wherein the drive plate has a tilting restriction section, and the tilting restriction section is provided with an additional mass.