JPH05240160A - Variable capacity swash plate type compressor - Google Patents

Abstract

PURPOSE:To directly detect the displacement of a member displacing in conformation to piston stroke or the inclined rolling angle of a swash plate. CONSTITUTION:A piston support 21 for driving a piston 31, a support sleeve 25 for supporting a swash plate 12 for oscillating the piston support 21 at various oscillating angles, and a swash plate sleeve 15 for supporting the swash plate 12 with various inclined rolling angles to a main shaft 13 are provided. The displacement quantity of a member displaced in conformation to the stroke of the piston or the inclined rolling angle of the swash plate is detected, and a compressor or a driving source for driving the compressor is controlled on the basis of the signal detected by a stroke detecting means. Thus, the piston stroke can be precisely and reliably measured with a simple structure, and excellent capacity controlling property can be provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity swash plate compressor used for compressing refrigerant gas in an automobile air conditioner, and more particularly to a variable capacity swash plate type compressor which is suitable for detecting a stroke of a piston. Regarding compressors.

[0002]

2. Description of the Related Art A conventional piston stroke detecting means in a variable displacement swash plate compressor is, for example, an actual flat head 2-24081.
As described in the publication, a structure in which the displacement of the control piston is detected by a differential transformer type stroke sensor via a link mechanism is disclosed.

[0003]

In the conventional variable displacement swash plate type compressor, the displacement of the sleeve rotating with the main shaft is changed to the displacement of the control piston which is a non-rotating member via the control plate and the angular ball bearing. Converted,
Furthermore, since a differential transformer type stroke sensor that detects this displacement using a link mechanism and detects the displacement is provided in the outer portion of the compressor, the method and structure for detecting the piston stroke become complicated, and the compressor The outer diameter of is larger. In addition, depending on the position of the support shaft of the interlocking member, the displacement of the other end of the interlocking member detected by the position detector becomes smaller with respect to the axial displacement of the control piston, which causes a problem that the detection accuracy decreases. There is.

The object of the present invention is to solve the problems of the prior art, to improve the detection accuracy of the piston stroke, and to provide a piston stroke with a simple and compact structure and high reliability. It is an object of the present invention to provide a variable capacity swash plate compressor that can be detected, can improve the capacity controllability of the compressor, and can reduce power consumption.

[0005]

To achieve the above object, a variable displacement swash plate compressor according to the present invention is provided with a piston, a piston support for driving the piston, and a tilt angle with respect to the main shaft that is rotated by the main shaft. The tilt angle of the swash plate includes a swash plate that swings the piston support by changing the swash plate, a swash plate sleeve that supports the swash plate and is slidable, and a support sleeve that is connected to the piston support via the swash plate sleeve. In the variable capacity swash plate compressor that changes the capacity to control the capacity,
A means for detecting the amount of displacement of a member that is displaced according to the stroke of the piston or the tilt angle of the swash plate is provided.

The displacing member may be formed of a support sleeve, and the detecting means may detect the amount of displacement of the support sleeve.

The displacing member may be formed of a swash plate sleeve, and the detecting means may detect the displacement amount of the swash plate sleeve.

The member which is further displaced may be formed by a piston support, and the detecting means may be one which detects the amount of displacement of the piston support.

A piston, a piston support for driving the piston, a swash plate which is rotated by the main shaft and swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate sleeve which supports the swash plate and is slidable. In a variable displacement swash plate type compressor that includes a support sleeve that is connected to a piston support via a swash plate sleeve, and performs displacement control by changing the tilt angle of the swash plate, a detection rod is provided on the support sleeve It is also possible to adopt a configuration in which a means for detecting the displacement amount of is provided.

Further, a piston, a piston support for driving the piston, and a swash plate which is rotated by the main shaft and swings the piston support by changing a tilt angle with respect to the main shaft,
A variable capacity swash plate compressor that includes a slidable plate sleeve that supports the swash plate and is slidable, and a support sleeve that is connected to the piston support via the swash plate sleeve, and that performs displacement control by changing the tilt angle of the swash plate. In the above, the detection rod provided in conjunction with the support sleeve may be taken out to the outside, and a means for detecting the displacement amount of the detection rod may be provided outside.

Further, a piston, a piston support for driving the piston, a swash plate that is rotated by the main shaft and swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate sleeve that supports the swash plate and is slidable. And a support sleeve connected to the piston support through a swash plate sleeve, and a variable capacity swash plate compressor that performs displacement control by changing the tilt angle of the swash plate, the detection provided in conjunction with the swash plate sleeve The rod may be taken out to the outside via the main shaft, and a means for detecting the displacement amount of the detection rod may be provided to the outside.

A piston, a piston support for driving the piston, a swash plate which is rotated by the main shaft and swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate sleeve which supports the swash plate and is slidable. In a variable displacement swash plate type compressor that includes a support sleeve that is connected to a piston support via a swash plate sleeve, and performs displacement control by changing the tilt angle of the swash plate, a detection rod is provided on the support sleeve The means for detecting the displacement of
It may be a displacement gauge provided on a slide pin inserted into a support sleeve to prevent rotation of the piston support.

Further, a piston, a piston support for driving the piston, and a swash plate which is rotated by the main shaft and swings the piston support by changing a tilt angle with respect to the main shaft,
A variable capacity swash plate compressor that includes a slidable plate sleeve that supports the swash plate and is slidable, and a support sleeve that is connected to the piston support via the swash plate sleeve, and that performs displacement control by changing the tilt angle of the swash plate. In the above, the detection rod may be provided on the support sleeve, and the means for detecting the displacement amount of the detection rod may be a displacement meter provided on a slide pin inserted into the support sleeve to prevent rotation of the piston support.

Further, a piston, a piston support for driving the piston, a swash plate which is rotated by the main shaft and swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate sleeve which supports the swash plate and is slidable. And a support sleeve connected to the piston support via a swash plate sleeve, in a variable displacement swash plate compressor that performs displacement control by changing the tilt angle of the swash plate, the support sleeve is provided with a detection target, A configuration may also be adopted in which a displacement gauge that detects the amount of displacement of the detection body is disposed so as to face the detection body.

A means for detecting the amount of displacement of the member which is displaced in accordance with the stroke of the piston or the tilt angle of the swash plate, means for amplifying the detection signal, and rotation of the drive source by inputting the amplified signal. A configuration including a drive source control circuit that performs speed control may be used.

A control valve for changing the tilt angle of the swash plate, a means for detecting a displacement amount of a member which is displaced in accordance with a stroke of the piston or a tilt angle of the swash plate, and means for amplifying the detection signal. , And means for controlling the control valve by inputting the amplified signal.

Further, the means for detecting the displacement amount of the member which is displaced according to the stroke of the piston or the tilt angle of the swash plate may be a displacement gauge or a slip ring.

And in the case of an automobile, it is preferable that the invention is as follows.
In a vehicle equipped with the variable capacity swash plate compressor according to any one of paragraphs (1) to (4) above, the rotational speed signal of at least one of the engine and the variable capacity swash plate compressor is input, and the rotational speed of either one is predetermined. The control means is provided to reduce the capacity of the variable capacity swash plate compressor when the rotational speed is exceeded.

[0019]

According to the present invention, a member that is displaced according to the stroke of the piston or the tilt angle of the swash plate, for example, the displacement of a support sleeve that swings and supports the piston support, slides on the main shaft, and rotates the swash plate. Displacement of swash plate sleeve to support,
Since the displacement of the oscillating piston support or the like is directly detected, the piston stroke can be measured reliably and easily.

Further, in the structure for detecting the displacement of the support sleeve, the support sleeve slides on the swash plate sleeve in the main shaft direction but does not rotate around the main shaft in accordance with the change of the compressor capacity. Reliability is improved.

Further, since the compressor or the drive source for driving the compressor is controlled based on the signal detected by the stroke detecting means of the piston, a wide range of integrated control can be performed and the capacity controllability of the compressor is improved. An air conditioning system that reduces power consumption can be constructed.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS. 1 and 2 show the entire structure of the variable displacement swash plate compressor of the present embodiment, and FIG. 1 shows a state in which the piston stroke is maximum, that is, the swash plate tilt angle is maximum. 2 shows a state in which the tilt angle of the swash plate is minimum. FIG. 3 shows A- of FIG.
It is an A line sectional view. 4 and 5 are sectional views showing the support sleeve assembly, FIG. 4 is a sectional view taken along the line BB in FIG. 2, and FIG. 5 is a sectional view taken along the line CC in FIG.

The housing comprises a front housing 1 and a cylinder block 2. That is, the bowl-shaped front housing 1 is installed and fixed to one end of the cylindrical cylinder block 2. A main shaft 13 is rotatably supported by radial needle roller bearings 18 and 19 provided at both ends in a central portion of these cross sections, and a swash plate chamber 10 for accommodating a swash plate 12 is formed in the front housing 1. Has been done. Inside the cylinder block 2, a plurality of cylinders 33 (six cylinders in this embodiment) are arranged in the circumferential direction centering on the main shaft 13 and parallel to the main shaft.

A drive plate 14 is fixed to the main shaft 13 by press fitting, pins or plastic coupling. An ear portion 141 is formed on the drive plate 14, and a spherical seat 142 is provided on the ear portion 141.
The hemispherical shoe 16 is slidably attached to the spherical seat 142. In addition, the ears 14 of the drive plate 14
The side surfaces of the swash plate 1 and the ears (not shown) of the swash plate 12 are in contact with each other and are not separated. As a result, the drive plate 14 is rotated by the rotation of the main shaft 13.
Rotational force is applied to the swash plate ears from the ears 141 of the swash plate 1.
2 rotates.

A swash plate sleeve 15 is attached to the spindle 13.
3 is slidably incorporated in the axial direction, and the swash plate sleeve 15 and the swash plate 12 are connected by a swash plate sleeve pin 17.

An outer ring 22 is provided inside the piston support 21.
The inner ring 23 is arranged inside the outer ring 22, and these members are connected by a support sleeve pin 24. Support sleeve pin 2
4 has a cylindrical cross section at a portion in contact with the inner ring 23 and the outer ring 22, but a contact portion with the piston support 21 has a width across flats parallel to the axial direction of the main shaft 13, and The support sleeve pin 24 is prevented from rotating around the axis with the outer ring 22. On the other hand, inner ring 2
3 and the support sleeve 25 are the support sleeve pin 2
It is concluded by 6. Therefore, the support sleeve pin 24 and the support sleeve pin 26 form a universal joint. The displacing member is formed of a support sleeve, a swash plate sleeve, or a piston support.

The piston support 21 and the swash plate 12 configured as described above are connected to the support sleeve 25 via the swash plate sleeve 15. That is, the swash plate sleeve 15 is mechanically connected to the support sleeve 25 via the elastic body 27 and the spring support bearing 28, and
Rolling bearings 29 provide rolling treatment between the two. The elastic body 27 is for applying a preload to the swash plate 12, the swash plate sleeve 15, and the swash plate 12 and the piston support 21. The swash plate 12 and the swash plate sleeve 15 are made of elastic material 2
The elastic force of 7 pushes the swash plate sleeve 15 to the right in FIG. 1 and pushes the swash plate 12 to the right via the swash plate sleeve pin 17, and as a result, the swash plate 12 and the swash plate 12 are pushed. Without separating from the sleeve 15
Moreover, the swash plate 12 tilts about the swash plate sleeve pin 17. On the other hand, the swash plate 12 and the piston support 21
The elastic body 27 generates a force that pushes the support sleeve 25 leftward. The elastic force acts in the order of support sleeve 25 → support sleeve pin 26 → inner ring 23 → support sleeve pin 24 → outer ring 22 → piston support 21. As a result, the piston support 21 is pressed leftward, that is, toward the swash plate 12 side. Therefore, the piston support 21 is prevented from separating from the swash plate 12. A thrust bearing 30 is provided between the swash plate 12 and the piston support 21 to facilitate the rotation of the swash plate 12.

A ∪ part 251 is formed on the outer peripheral surface of the support sleeve 25 in the axial direction, and the ∪ part 251 is slidable in the axial direction on the slide pin 60 fixed to the bearing housing 201 of the cylinder block 2. It has become. Thereby, the movement around the shaft is restricted so that the piston support 21 does not rotate around the main shaft 13. The piston support 21 includes balls 32 on both ends of the rod 323.
One end of the plurality of connecting rods 32 having 1, 322 is
The piston 3 is rotatably mounted around the center of the ball 321 and is rotatably mounted around the center of the ball 322 on the other end.
1 is attached.

The plurality of pistons 31 are incorporated in a plurality of cylinders 33 provided in the cylinder block 2. Piston rings 34 and 35 are attached to the piston 31. The cylinder block 2 includes an intake valve plate 5, a cylinder head 4, a discharge valve plate 6, a packing 7,
The rear cover 3 is arranged, and is integrally fixed to the rear cover 3 with a bolt (not shown) or the like together with the front housing 1 arranged so as to surround the drive plate 14, the swash plate 12, the piston support 21, and the like. The airtightness between the front housing 1 and the cylinder block 2 is an O-ring 38.
Therefore, the airtightness between the rear cover 3 and the cylinder block 2 is O.
It is held by a ring 39.

The rear cover 3 is provided with a suction port (not shown) and a discharge port (not shown). The suction port (not shown) is connected to the suction passage 302, and is connected to the suction chamber 8 via the control valve 400. The suction chamber 8 and the discharge chamber 9
Respectively communicate with the suction port 401 and the discharge port 402 via the suction valve plate 5 and the discharge valve plate 6, respectively. The intake port 401 and the discharge port 402 are respectively connected to the cylinder 3
3 is provided on the cylinder head 4.

The upstream side of the control valve 400 and the swash plate chamber 10 in the front housing 1 communicate with each other through a gap such as the rear cover 3, the stop pin 75, and the radial needle roller bearing 18 at the rear end of the main shaft 13, and the same. It is under pressure. Also,
The downstream side of the control valve 400 communicates with the suction chamber 8.

Next, the structure of the control valve 400 will be described.

The piston-shaped main valve 410 is arranged in the middle of the flow path connecting the suction passage 302 and the suction chamber 8, and is inserted into the main valve case 411 together with the main valve 410 and the main valve spring 412. The main valve case 411 includes O-rings 414 and 415 and a lid 43.
It is airtight and fixed to the rear cover 3 by 5 and forms a flow path 413 on the downstream side of the control valve together with the main valve 410. The main valve spring 412 is urged to increase the opening degree of the main valve 410. A bellows chamber 421 that houses the bellows 420 is formed on the opposite side of the main valve spring 412, and the bellows chamber 421 and the suction passage 302 communicate with each other through a pressure equalizing hole 422. A pressure equalizing hole 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.

The pilot valve 430 is biased toward the bellows 420 by a pilot valve spring 431.
A bellows spring 425 is attached to the bellows 420.
It is installed so as to bias 20 in the direction of contracting. Head spring 4 via pilot valve spring 431
A plunger 450 having 51 is installed, and an electromagnetic coil 452 is formed around the plunger 450.

The pilot valve chamber 432, in which the pilot valve 430 is provided, communicates with the discharge chamber 9 through the communication holes 433, 434 and 304, and the head of the main valve 410 is communicated through the communication passage 440 through the pilot valve 430. Communicating with the department.

As shown in FIG. 2, the minimum capacity of the compressor is regulated by the end portion 2 of the support sleeve 25 on the cylinder head 4 side.
52 is brought into contact with the swash plate chamber 10 side end portion 202 of the bearing housing 201 of the cylinder block 2. In addition, for the regulation of the maximum capacity, the tilt regulating seat (not shown) provided on the drive plate 14 and the tilt regulating seat (not shown) of the swash plate 12 come into contact with each other. At this time, since a proper gap is provided other than the members in contact with each other, it is possible to prevent the members from contacting each other.

The thrust force (axial force) acting on the main shaft 13 when the gas is compressed is the drive plate 14 described above.
And is supported by a thrust bearing 42 installed between the front bearing 1 and the front housing 1. The thrust trace on the front housing 1 side of the thrust bearing 42 has a spherical shape. Radial force acting on the main shaft 13 (radial force)
Are supported by two radial needle roller bearings 19 and 18 provided in the bearing housing 201 of the front housing 1 and the cylinder block 2.

With the above structure, when the main shaft 13 of the compressor is driven by the engine (not shown),
The drive plate 14 and the swash plate 12 rotate, and the piston support 21 makes an oscillating motion with respect to the rotating shaft of the main shaft 13.
As a result, the piston 31 reciprocates in the cylinder 33, whereby the refrigerant returned from the refrigeration cycle (not shown) flows into the suction port (not shown), and the control valve 40
At 0, the pressure is controlled (decompressed) to an appropriate pressure, and is introduced into the suction chamber 8 formed in the rear cover 3 with an appropriate control differential pressure between the pressure upstream of the control valve 400, that is, the pressure in the swash plate chamber 10. .. Then, it flows into the cylinder 33 through the suction port 401 of the cylinder head 4 and the suction valve plate 5, and the suction stroke is completed. The refrigerant compressed by the piston 31 passes through the discharge port 402 of the cylinder head 4 and the discharge valve plate 6 and is discharged to the discharge chamber 9 formed in the rear cover 3, and is discharged from a discharge port (not shown) in a refrigeration cycle (Fig. (Not shown).

Next, the capacity control mechanism will be described. When the heat load of the evaporator (not shown) decreases, the suction pressure of the compressor, that is, the pressure in the suction passage 302 decreases, so that the bellows 420 expands. As a result, the pilot valve 430 opens and the pilot valve chamber 43
The discharge pressure in 2 is transmitted through the communication passage 440 to the main valve 4
It acts on the head of 10 and pushes down the main valve 410. Therefore, since the flow path 413 on the downstream side of the control valve is throttled,
The pressure in the suction chamber 8, that is, the pressure immediately before the suction port 401 is reduced. As a result, the pressure difference between the left and right of the piston 31 increases, so that the swash plate is pulled toward the suction chamber, the tilt angle of the swash plate decreases, and the piston stroke decreases.

On the other hand, when the heat load on the evaporator (not shown) is increased, the above operation is reversed. That is, the heat load increases, the suction pressure increases, the bellows 420 contracts, and the pilot valve 430 closes. As a result, the head pressure of the main valve 410 decreases, and the flow path 413 on the downstream side of the control valve opens, so that the pressure difference between the left and right sides of the piston 31 decreases, the tilt angle of the swash plate increases, and the stroke of the piston 31 increases. Will grow.

Next, capacity control by external control will be described. The current applied to the electromagnetic coil 452 is changed by an external signal (for example, temperature, pressure, etc.) to control the suction pressure of the compressor. For example, when cooling power is required during cool down, the electromagnetic coil 4
When the applied current to 52 is reduced, the attraction force of the plunger 450 is reduced and the pressing force of the head spring 451 is increased, so that the pilot valve 430 is closed. As a result, since the main valve 410 is fully opened, the compressor is operated at the maximum stroke, that is, the maximum capacity.

In this way, the capacity of the compressor is controlled by the control valve 4
00 to adjust the pressure difference between the suction chamber 8 and the swash plate chamber 10, that is, the pressure difference between both sides of the piston 31, and the piston support 21 from each piston 31 via the connecting rod 32.
The tilting moment of the swash plate 12 is controlled by changing the position and magnitude of the resultant force of the forces acting on.

Next, the piston stroke detecting means will be described. As described above, the ∪ part 251 is formed on the outer peripheral surface of the support sleeve 25 in the axial direction, and the ∪ part 251 is formed in the bearing housing 2 of the cylinder block 2.
A slide pin 60 fixed to 01 is slidable in the axial direction. As a result, the movement about the axis is restricted so that the piston support 21 connected to the support sleeve 25 by the support sleeve pins 24 and 26 does not rotate around the main shaft 13. The slide pins 60 fixed to the bearing housing 201 of the cylinder block 2 are provided at two locations in axial symmetry with respect to the main shaft 13, and one of them also serves as a displacement detector (displacement meter) 600. That is, the displacement detector 600 is a differential transformer, and has a cylindrical housing 601, a coil 602, and a core 603.
And a lead 604. The core 603 has
An L-shaped detection rod 605 is connected, and the end of the detection rod 605 on the swash plate 12 side is a support sleeve 25.
It is fixed to. Therefore, the core 603 is displaced within the coil 602 in response to the displacement of the support sleeve 25.

With the above construction, the swash plate 12 rotates counterclockwise in FIG. 1 in the process of decreasing the piston stroke, that is, the compressor capacity from the maximum capacity (FIGS. 1 and 2), Along with that, the swash plate sleeve 15 slides on the main shaft 13 in the right direction. As the swash plate sleeve 15 moves, the support sleeve 25 moves rightward on the slide pin 60 and the housing 601 of the displacement detector 600. At this time, since the support sleeve 25 is supported by the rolling bearing 29 and the swash plate sleeve 15, the support sleeve 25 does not rotate around the axis of the main shaft 13,
Performs movement only in the axial direction. Therefore, the detection rod 605 and the core 6 fixed to the support sleeve 25 are
03 moves to the right in the coil 602. That is,
Displacement detector 600 according to displacement of piston stroke
The core 603 is displaced in the coil 602 only in the main axis direction, and the displacement amount of the core 603 is detected. The description of the operation principle of the differential transformer is omitted.

According to the present embodiment, by directly detecting the displacement amount of the support sleeve which is displaced in accordance with the piston stroke or the tilt angle of the swash plate, the structure of the detecting means can be simplified and the piston can be reliably operated. Strokes can be detected. Furthermore, there is an effect that the detection accuracy and reliability can be improved.

FIG. 6 is an enlarged sectional view showing a support sleeve assembly showing another embodiment of the present invention. This embodiment is also a means for detecting the amount of displacement of the support sleeve, similarly to the above. Compared with the embodiment shown in FIG. 5, the same parts are designated by the same reference numerals, and the description of the structure will be omitted.

Cylinder head 4 of support sleeve 25
The detected body 610 is installed on the side outer peripheral end 252, and the displacement gauge 611 is arranged in the bearing housing 201 of the cylinder block 2 at a position corresponding to the detected body 610. For the displacement meter 611, for example, an eddy current type or capacitance type displacement meter is a good opponent.

With the above construction, the support sleeve 25 is displaced in response to a change in piston stroke, and the relative position between the object to be detected 610 and the displacement gauge 611 is changed, so that the maximum piston stroke or the minimum piston stroke is preset. By determining the electric output of the displacement meter 611 at the position, the displacement amount of the support sleeve 25, that is, an arbitrary piston stroke can be uniquely detected.

According to this embodiment, the same effect as that of the above embodiment can be exhibited, and the detecting means can be further simplified.

Next, another embodiment of the present invention will be described. Figure 7
8 and FIG. 8 show the entire structure of the variable capacity swash plate type compressor of this embodiment, FIG. 7 shows the maximum capacity state of the compressor, and FIG. 8 shows the minimum capacity state. is there.
Here, as compared with the embodiment shown in FIG. 1 and FIG. 2, the same reference numerals are given to the same parts, and therefore the description of the structure of those parts will be omitted.

The support sleeve 25 is provided with a detection rod 620 in the axial direction, and the detection rod 620 is
Cylinder block 2, intake valve plate 5, cylinder head 4,
It is taken out of the compressor through the respective through holes formed in the discharge valve plate 6, the packing 7, and the rear cover 3. The detection rod 620 is installed in the bearing housing 202 near the main shaft 13. Cylinder block 2, intake valve plate 5, cylinder head 4, discharge valve plate 6
Further, there is an appropriate gap between each through hole provided in the packing 7 and the detection rod 620, so that the detection rod 620 can move smoothly. A chamber 80 for accommodating the lock pin 75 is formed in the center of the rear cover 3, and the chamber 80 is formed by a gap such as the radial needle roller bearing 18 at the rear end of the main shaft 13 and the swash plate chamber 10.
Since it is in communication with the swash plate chamber pressure, that is, the suction pressure. Therefore, it is not necessary for the detection rod 620 and each of the above-mentioned members to keep gas tight.

On the opposite side of the rear cover 3 from the chamber 80, a ∪ part 62 is provided.
1 is formed, and the displacement detector 600 is installed in the ∪ portion 621. The displacement detector 600 is a differential transformer, and includes a cylindrical housing 601 and a detection rod 620.
And a coil 602 and a lead 604, and the housing 601 is fixed to the ∪ portion 621. Gas sealing between the detection rod 620 and the rear cover 3 is performed by the shaft sealing device 622 provided in the ∪ portion 621. Since the pressure of the chamber 80 is low and the detection rod 620 does not make a rotational motion but reciprocates only and the reciprocating motion only occurs when the capacity changes, the gas tightness can be relatively easily achieved. ..

With the above structure, the support sleeve 25 moves in the axial direction with the change of the compressor capacity, and the detection rod 620 moves the coil 60 of the displacement detector 600.
Since the inside of 2 is displaced in the axial direction, the amount of displacement can be uniquely measured.

According to this embodiment, since the displacement detector can be installed outside the rear cover 3, the displacement detector 60
There is an effect that the maintenance of 0 can be performed without opening the rear cover 3 and the detecting means can be made very compact.

Next, another embodiment of the present invention will be shown. Figure 9
10 and 10 show the entire structure of the variable capacity swash plate type compressor of the present embodiment. FIG. 9 shows the compressor capacity in the maximum capacity state, and FIG. 10 shows the minimum capacity state. is there. Here, as compared with the embodiment shown in FIGS. 1 and 2, the same parts are denoted by the same reference numerals, and therefore the description of the structure and operation of those parts will be omitted.

An L-shaped detection rod 151 is fixed to a swash plate sleeve 15 that slides on the main shaft 13, and a cutout portion 138 having an axial width slightly larger than the displacement amount of the detection rod 151 is described below. The main shaft 13 is provided so as to open to the communication passage 131. The detection rod 151 is passed through a communication passage 131 that is bored in the center of the main shaft 13 with a diameter slightly larger than the outer diameter of the detection rod 151 so as to be longer than the displacement amount of the swash plate sleeve 15. Have been taken out. The tip of the detection rod 151 has a spindle 1
The gas-tightness is maintained by the screw member 139 screwed to the tip of the shaft 3 and the shaft sealing means 152. In the present embodiment, the detection rod 151 is shown as an integral type, but this is not a limitation. For example, in consideration of the assemblability, a portion fixed to the swash plate sleeve 15 and a portion through which the main shaft 13 passes through the communication passage 131. The configuration may be such that and are separate members. The specific means for detecting the displacement amount of the detection rod 151 will be described later.

With the above structure, the piston 3
When the stroke of No. 1 is the maximum, that is, when the capacity decreases from the maximum capacity state (in the process of changing from FIG. 9 to FIG. 10), the swash plate sleeve 1 is reduced as the tilt angle of the swash plate decreases.
5 moves to the right in FIG. Therefore, the detection rod 151 fixed to the swash plate sleeve 15 is similarly displaced rightward, and finally the state shown in FIG. 10 is obtained. That is, the displacement amount of the swash plate sleeve 15 that is displaced according to the piston stroke or the swash plate tilt angle is detected.

According to the present embodiment, by detecting the displacement amount of the swash plate sleeve which is displaced in accordance with the piston stroke or the swash plate tilt angle, the detecting means can be simply constructed and the piston stroke can be reliably determined. Since it can be detected and the displacement amount can be measured outside the compressor, there is an effect that maintenance or the like can be performed without opening the front housing 1.

11 and 12 show a swash plate sleeve 15
FIG. 6 is a partial cross-sectional view disclosing specific means for detecting the amount of displacement of the detection rod 151 fixed to FIG. Compared to FIG. 9 or FIG. 10, it is the same as the front housing 1 except that an electromagnetic clutch 136 for transmitting rotational power of the engine to the compressor is attached to the left end portion of the front housing 1.

First, in the detecting means shown in FIG. 11, the screw member 139 fixed to the tip end of the main shaft 13 surrounds the detecting rod 151 in which the differential transformer type displacement gauge 150 is fixed to the swash plate sleeve 15. It is installed. The differential voltage displacement type displacement meter 150 includes a bottomed cylindrical housing 156, a detection rod 151 and a coil 153, and one end of the housing 156 has a threaded portion. Also, the displacement meter 1
50 or the screw member 139 has a slip ring 154.
Are electrically connected to the displacement meter 150. The slip ring 154 is composed of a rotor (not shown) and a stator (not shown), and is connected to the displacement meter 150 with the rotor. Therefore, the electric signal 155 of the displacement gauge to the outside is taken out from the stator of the slip ring 154. Therefore, the members that rotate together with the main shaft 13 are the detection rod 151, the shaft sealing means 152, the coil 153, the housing 156, the screw member 139, and the rotor (not shown) of the slip ring 154.

With the above structure, the detection rod 151 which is displaced in accordance with the tilt angle of the piston or the swash plate.
It is possible to take out the displacement amount of as an electric signal to the outside of the compressor. Although FIG. 11 shows an embodiment in which the displacement gauge 150 is attached to the outside of the compressor, the present invention is not limited to this, and there is also a method of attaching the displacement gauge 150 to the main shaft 13, for example.

FIG. 12 shows a case where the displacement gauge 150 is attached to a device other than the compressor. That is, the member 100 other than the compressor,
For example, the detection rod 1 fixed to the swash plate sleeve 151 by fixing the housing 156 of the displacement detector 150 to a bracket or the like for attaching the compressor to an engine or the like.
This is a configuration for measuring the movement amount of 51. Therefore, the spindle 13
The members that rotate together are the detection rod 151, the shaft sealing means 152, and the screw member 139, which obtain the electric signal 155 from the stationary housing 156.

In this embodiment, since the displacement gauge can be fixed and used, the types of displacement gauges used can be expanded and the measuring means can be simplified.

FIG. 13 shows another embodiment of the present invention. On the outer peripheral wall of the front housing 1, a plurality of displacement gauges 101,
102 and 103 are airtightly held and fixed. The displacement gauges 101, 102 and 103 include a piston support 2
The swash plate 12 is arranged so as to detect the displacement of the detection object 210 provided at the outer peripheral end of the swash plate 1. On the other hand, the armature plate 137 of the electromagnetic clutch 136 fixed to the tip of the main shaft 13 is provided with a protrusion 108, and the rotation detector 10 corresponds to the protrusion 108.
9 are installed.

Next, the operation of this embodiment will be described. The rotation detector 109 detects or outputs one pulse each time the main shaft 13 makes one rotation, that is, one pulse / one rotation pulse. When the compressor is operated at the maximum capacity, that is, at the maximum swash plate tilt angle (FIG. 13 shows that state), the piston support 21 swings with the maximum swing width, so that the detected object 210 also tilts. It reciprocates in the plate chamber 10 with the maximum width. The detected body 210 reciprocates once in the swash plate chamber 10 each time the main shaft 13 makes one revolution. The displacement meter 101 is arranged so as to contact the detection body 210 when the detection body 210 is located at the leftmost end in the axial direction in the drawing.
Similarly, the displacement meter 102 is installed at a position corresponding to the detected object 210 and the displacement meter 103 is installed at the minimum capacity position when the compressor is operated at an intermediate capacity between the maximum capacity and the minimum capacity. ..

Therefore, when the main shaft 13 makes one revolution at the maximum capacity, the object 210 to be detected and the displacement detector 101,
The number of pulses generated in 102 and 103 is six. At the intermediate capacity, since there is no pulse from the displacement meter 101, there are four pulse trains per one rotation. At the minimum capacity, only the displacement gauge 103 generates a pulse, so that the number of pulses per revolution of the main shaft 13 is two. here,
The units 104, 105 and 106 shown in the figure are
An input / output device and an amplifier for the displacement meters 101, 102 and 103. Therefore, based on the pulse signal per one rotation of the main shaft 13 obtained by the rotation detector 109,
The capacity of the compressor can be measured by measuring the number of pulses generated by the displacement gauges 101, 102 and 103. Further, the device 107 for automatically measuring includes a rotation detector 109 and units 104, 105 and 106.
It is composed of a device for inputting the pulse signal output from the device, an amplifier, a pulse calculator, a calculator for calculating the compressor capacity, and a device for outputting the result.

In this embodiment, three displacement gauges are used, but the present invention is not limited to this.
For example, the capacity state of the compressor can be measured more finely by increasing the number of displacement gauges.

As described above, according to this embodiment, the displacement of the swinging member, for example, the piston support can be measured, so that the capacity state of the compressor can be accurately measured.

Next, FIGS. 14 to 16 show an embodiment of the control means based on the signal of the piston stroke or the displacement control state of the compressor obtained by the above-mentioned means or the like.

FIG. 14 shows means for detecting the amount of displacement of a member which is displaced according to the piston stroke or the swash plate tilt angle (hereinafter referred to as the stroke sensor 510), and an amplifier for amplifying the electric signal of the stroke sensor 510. 52
0, and a control circuit 530 for controlling the drive source of the compressor, for example, the engine, by the output signal from the amplifier 520, that is, the piston stroke signal.
The control is performed so that fluctuations in the rotational speed of the engine due to fluctuations in the heat load of the compressor are reduced.

FIG. 15 shows a control means which uses a signal obtained from the stroke sensor 510 and the amplifier 520 as a control signal for the control valve 400 of the compressor. That is, when it is desired to operate the compressor at the maximum capacity such as when rapid cooling is required, the electromagnetic coil of the control valve 400 of the compressor is applied so that the compressor always operates at the maximum capacity by the signal of the stroke sensor 510. Use as a control signal to lower the current. In addition, when the rotation speed of the compressor increases and the required cold power decreases, the control signal increases the current applied to the electromagnetic coil of the control valve 400. Further, by recognizing the rotational speed signal of at least one of the engine and the compressor, and if the rotational speed of one of them becomes higher than a predetermined rotational speed, the control means may forcefully reduce the capacity of the compressor. You can

FIG. 16 discloses an integrated control means including a compressor and a drive source for driving the compressor. The piston stroke signal of the compressor obtained from the stroke sensor 510 and the amplifier 520 is input to a control circuit 530 such as a drive source that drives the compressor, such as an engine, and is also input to the control valve 400 of the compressor. .. That is, it controls both the drive source and the compressor using the piston stroke signal. For example, the case of being installed in an automobile engine will be described. When climbing uphill while driving the compressor, the compressor power is a considerable burden from the engine side. Therefore, in such a case, the load of the engine power is reduced by reducing the capacity of the compressor. Also,
The capacity of the compressor is controlled in order to eliminate variations in the engine speed that accompany the driving of the compressor when the engine is operating at idle speed. In all of these controls, the power load of the engine is prioritized over the heat load on the refrigeration cycle side, and thus the drivability of the vehicle can be improved. On the other hand, when the rapid cooling at midsummer is required, operate the compressor at maximum capacity,
Moreover, the cooling speed is increased by increasing the rotation speed of the engine. In FIG. 16, the control flow by the signal of the stroke sensor is unidirectional, that is, in series, but the present invention is not limited to this. For example, the signal of the stroke sensor is transmitted to the control valve 400 of the compressor and the compression valve. It may be a means for inputting in parallel to a control circuit of a drive source for driving the machine and controlling.

As described above, by controlling the compressor or the drive source for driving the compressor based on the signal from the stroke sensor, the capacity controllability of the compressor can be improved and the power consumption can be minimized. There is an effect that such an air conditioning system can be configured.

In all of the above description of the embodiments, the pressure in the swash plate chamber is kept constant, and the pressure in the cylinder suction port is made lower than the pressure in the swash plate chamber by the control valve to change the tilt angle of the swash plate. Although the swash plate type compressor has been disclosed, for example, as disclosed in Japanese Patent Publication No. 58-4195, the pressure in the swash plate chamber is increased by using blow-by gas or discharge gas while keeping the cylinder inlet pressure constant. The same effect can be obtained with a variable capacity swash plate compressor of the type that controls the tilt angle of the swash plate.

[0075]

According to the present invention, the amount of displacement of a member that is displaced according to the piston stroke or the tilt angle of the swash plate can be directly detected, so that the piston stroke can be reliably measured, and The stroke detecting means and structure can be simplified and the size can be reduced.

Further, since the displacement amount of the member which does not rotate around the main axis can be detected, the detection accuracy can be improved and the reliability can be improved.

Furthermore, since the compressor or the drive source for driving the compressor can be controlled based on the signal detected by the stroke detecting means, a wide range of integrated control can be performed and the capacity controllability of the compressor can be improved, and the consumption can be improved. An air conditioning system with reduced power can be provided.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a maximum capacity state of an embodiment of the present invention.

FIG. 2 is a vertical cross-sectional view showing a minimum capacity state of an embodiment of the present invention.

3 is a cross-sectional view taken along the line AA of FIG.

FIG. 4 is a sectional view taken along the line BB of FIG. 2 showing a support sleeve assembly of the present invention.

5 is a cross-sectional view taken along the line CC of FIG.

FIG. 6 is an enlarged sectional view showing a support sleeve assembly according to another embodiment of the present invention.

FIG. 7 is a vertical sectional view showing a maximum capacity state of another embodiment of the present invention.

FIG. 8 is a vertical sectional view showing a minimum capacity state of another embodiment of the present invention.

FIG. 9 is a longitudinal sectional view showing a maximum capacity state of another embodiment of the present invention.

FIG. 10 is a vertical sectional view showing a minimum capacity state of another embodiment of the present invention.

FIG. 11 is a partial cross-sectional view of means for detecting a displacement amount of a detection rod fixed to a swash plate sleeve according to the present invention.

FIG. 12 is a partial cross-sectional view of means for detecting a displacement amount of a detection rod fixed to a swash plate sleeve according to the present invention.

FIG. 13 is a diagram for measuring a displacement amount of a piston support according to another embodiment of the present invention.

FIG. 14 is a diagram showing a control means based on a signal of a piston stroke or a displacement control state of the present invention.

FIG. 15 is a diagram showing a control means based on a piston stroke or displacement control state signal of the present invention.

FIG. 16 is a diagram showing a control means based on a piston stroke or displacement control state signal of the present invention.

[Explanation of symbols]

 12 Swash plate 13 Spindle 14 Drive plate 15 Swash plate sleeve 21 Piston support 25 Support sleeve 31 Piston 33 Cylinder 600 Displacement detector

Claims (13)

[Claims] 1. A piston, a piston support that drives the piston, a swash plate that is rotated by a main shaft and that swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate that supports and slides the swash plate. A variable capacity swash plate compressor that includes a movable swash plate sleeve and a support sleeve that is connected to the piston support via the swash plate sleeve, and performs displacement control by changing the tilt angle of the swash plate, wherein the piston A variable capacity swash plate type compressor provided with means for detecting the amount of displacement of a member that displaces in accordance with the stroke or the tilt angle of the swash plate. 2. The variable capacity swash plate compressor according to claim 1, wherein the displacing member is formed of a support sleeve, and the detecting means detects a displacement amount of the support sleeve. 3. The variable capacity swash plate type compression device according to claim 1, wherein the displacing member is formed of a swash plate sleeve, and the detecting means detects a displacement amount of the swash plate sleeve. Machine. 4. The variable capacity swash plate compressor according to claim 1, wherein the displacing member is formed of a piston support, and the detecting means detects a displacement amount of the piston support. 5. A piston, a piston support that drives the piston, a swash plate that is rotated by a main shaft and that swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate that supports and slides. A variable displacement swash plate type compressor that includes a swash plate sleeve that can be moved, and a support sleeve that is connected to the piston support through the swash plate sleeve, and that performs displacement control by changing a tilt angle of the swash plate. A variable capacity swash plate compressor, characterized in that a detection rod is provided on a sleeve, and means for detecting a displacement amount of the detection rod is provided. 6. A piston, a piston support for driving the piston, a swash plate which is rotated by a main shaft and swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate supporting and sliding. A variable displacement swash plate type compressor that includes a swash plate sleeve that can be moved, and a support sleeve that is connected to the piston support through the swash plate sleeve, and that performs displacement control by changing a tilt angle of the swash plate. A variable capacity swash plate type compressor, characterized in that a detection rod provided in conjunction with a sleeve is taken out to the outside, and means for detecting the displacement amount of the detection rod is provided to the outside. 7. A piston, a piston support for driving the piston, a swash plate rotated by a main shaft and swinging the piston support by changing a tilt angle with respect to the main shaft, and a slide supporting and supporting the swash plate. A variable displacement swash plate type compressor that includes a swash plate sleeve that can be moved and a support sleeve that is connected to the piston support via the swash plate sleeve, and that performs displacement control by changing a tilt angle of the swash plate. A variable capacity swash plate compressor characterized in that a detection rod provided in conjunction with a plate sleeve is taken out to the outside via the main shaft, and means for detecting the displacement amount of the detection rod is provided to the outside. 8. A piston, a piston support for driving the piston, a swash plate rotated by a main shaft and swinging the piston support by changing a tilt angle with respect to the main shaft, and a slide supporting and supporting the swash plate. A variable displacement swash plate type compressor that includes a swash plate sleeve that can be moved, and a support sleeve that is connected to the piston support through the swash plate sleeve, and that performs displacement control by changing a tilt angle of the swash plate. A detection rod is provided on the sleeve, and the means for detecting the amount of displacement of the detection rod is a displacement gauge provided on a slide pin inserted into the support sleeve to prevent rotation of the piston support. Capacity swash plate type compressor. 9. A piston, a piston support for driving the piston, a swash plate which is rotated by a main shaft and swings the piston support by changing a tilt angle with respect to the main shaft, and a swash plate supporting and sliding. A variable displacement swash plate type compressor that includes a swash plate sleeve that can be moved, and a support sleeve that is connected to the piston support through the swash plate sleeve, and that performs displacement control by changing a tilt angle of the swash plate. A variable capacity swash plate compressor, wherein a detected body is provided on a sleeve, and a displacement gauge for detecting a displacement amount of the detected body is arranged so as to face the detected body. 10. A means for detecting a displacement amount of a member which is displaced according to a stroke of a piston or a tilt angle of a swash plate, a means for amplifying a detection signal thereof, and a drive source which receives the amplified signal. The variable capacity swash plate compressor according to claim 1, further comprising a control circuit of the drive source that controls a rotation speed. 11. A control valve for changing a tilt angle of a swash plate, a means for detecting a displacement amount of a member which is displaced in accordance with a stroke of a piston or a tilt angle of the swash plate, and an amplification of a detection signal thereof. The variable capacity swash plate compressor according to claim 1, further comprising means and means for inputting the amplified signal and controlling the control valve. 12. The means for detecting the amount of displacement of a member that is displaced according to the stroke of the piston or the tilt angle of the swash plate is a displacement gauge or a slip ring. A variable capacity swash plate compressor according to item 1. 13. A vehicle equipped with the variable capacity swash plate compressor according to claim 1, wherein a rotational speed signal of at least one of an engine and the variable capacity swash plate compressor is input. A vehicle having control means for reducing the capacity of the variable displacement swash plate compressor when either one of the rotational speeds exceeds a predetermined rotational speed.