JPH0248710Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a variable displacement wobble plate compressor used for compressing refrigerant gas in a vehicle air conditioner.

(Prior art and its problems) Conventionally, the discharge capacity is changed by changing the inclination angle of the rocking plate, and in order to regulate the minimum tilt angle position and the maximum tilt angle position of the rocking plate, mutual impact is required. As a variable capacity rocking plate compressor having mating surfaces, for example, Japanese Patent Application Laid-Open No. 129907
No. 54-94107 are well known.

In all of these conventional devices, the abutting surfaces are metal parts that directly abut each other, so when the inclination angle of the rocking plate is rapidly changed from the minimum to the maximum or vice versa, the metal parts The direct collision generates a loud collision sound that can be felt by people inside the vehicle, and the impact at the time of the collision is large, causing problems such as having an adverse effect on the members of the collision part.

(Purpose of the invention) The present invention has been developed in view of the above circumstances, and is designed to prevent collision noise from occurring, reduce the impact during collision, and prevent any adverse effects on the members of the collision part. The purpose of the present invention is to provide a variable capacity wobbling plate compressor.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention is configured to prevent the occurrence of collision noise by providing a buffer means on the collision surfaces.

(Example) Hereinafter, each example of the present invention will be described based on the drawings. First, regarding the first embodiment, FIGS.
This will be explained with reference to the figures. 1 in FIGS. 1 and 4 is a housing, which includes a cylindrical case 2 and the case 2.
a cylinder head 4 liquid-tightly attached to one end surface (left end surface in the figure) via a valve plate 3;
A head member 5 is attached to the other end surface (right end surface in the figure) of the case 2 in a liquid-tight manner. A cylinder block 6 is integrally formed inside the case 2, and a crank chamber 7 is defined by the end surface of the cylinder block 6 on the side of the head member 5, the inner peripheral wall of the case 2, and the inner surface of the head member 5. ing. An oil reservoir 8 is formed inside the lower part of the case 2, and the oil reservoir 8 communicates with the crank chamber 7. The cylinder block 6 has a plurality of cylinders arranged at predetermined intervals in the circumferential direction, centered on the drive shaft 9 disposed substantially along the central axis of the housing 1, and with the axis parallel to that of the drive shaft 9. A cylinder 10 is arranged, each of these cylinders 1
A piston 11 is slidably fitted in each of the pistons 0. The drive shaft 9 has its end on the cylinder head 4 side aligned with the center hole 6a of the cylinder block 6.
The head member 5 side end portion is rotatably supported on the inner circumferential surface of the head member 5 via an arm member 13 and a large-diameter ball bearing 14 in this order. .
A shaft end of the drive shaft 9 on the head member 5 side passes through the center hole 5a of the head member 5 and extends outward, and a pulley 15 is fitted to the extended end. There is. A mechanical seal 16 is interposed between the boss portion 13a of the arm member 13 and the center hole 5a of the head member 5, and the space between the boss portion 13a and the center hole 5a of the head member 5 is maintained airtight. ing. The pulley 15 is a drive belt (not shown) attached to a pulley on the output shaft side of an on-vehicle engine (not shown).
The rotation of the engine is transmitted to the drive shaft 9. A sleeve-shaped slider 1 is provided on the outer periphery of the approximately intermediate portion of the drive shaft 9 in the axial direction so as to be slidable on the drive shaft 9 in the axial direction but not rotatable in the circumferential direction.
7 is fitted, so that the slider 17 rotates together with the drive shaft 9.
A center hole 18a of a disc-shaped swing plate 18 is loosely fitted into the outer periphery of the slider 17 at an approximately intermediate portion in the axial direction, and both sides thereof are rotatably connected to the slider 17 via trunnion pins 19. ing. A cam surface at the tip of the arm portion 13b of the arm member 13 is located between the parallel guide portions 20 which are provided at predetermined positions on the surface of the rocking plate 18 on the side of the head member 5 and protrude in the radial direction thereof. 13c is engaged. Pins 21 protruding from both sides of the arm portion 13b of the arm member 13
Coil springs 23 are tensioned between the pins 22 and the pins 22 protruding from the parallel guide portions 20 of the swing plate 18, respectively. The tips of piston rods 24 projecting from the piston 11 are connected to the surface of the swing plate 18 on the cylinder block 6 side through ball joints 25, respectively. Therefore, as the swing plate 18 rotates, the piston 1
1 slides. Further, the tilt angle of the swing plate 18 with respect to the vertical plane changes depending on the pressure inside the crank chamber 7, and the change in the tilt angle causes the piston 1
1 stroke increases or decreases.

As shown in FIGS. 2 and 3, the maximum inclination angle position of the swing plate 18 is the position where one end surface (the right end surface in the figure) 17a of the slider 17 is provided on the inner end surface of the boss portion 13a of the arm member 13. Inner end surface 26 of annular groove 26
It is regulated by matching a. Further, the minimum inclination angle position of the swing plate 18 is determined by an annular abutment member whose other end surface (left end surface in the figure) 17b of the slider 17 is adjacent to the bearing 12 and fitted onto the outer periphery of the drive shaft 9. Inner end surface 28 of annular groove 28 of 27
It is regulated by matching a.

One end surface (abutting surface) 17a of the slider 17 and the inner end surface (abutting surface) of the annular groove 26 of the arm member 13
26a, when these are rapidly fitted together, refrigerant gas is trapped in the internal space of the annular groove 26, and a damper effect is produced by the refrigerant gas, which causes one part of the slider 17 to A buffer means 29 is provided to prevent the end surface 17a and the inner end surface 26a of the annular groove 26 from suddenly coming into contact with each other.

Further, the other end surface (abutting surface) 1 of the slider 17
7b and the inner end surface (abutting surface) 28a of the annular groove 28 of the abutment member 27, when these are in a state of rapid fitting, refrigerant gas is trapped in the internal space of the annular groove 28. state, a damper effect is produced by the refrigerant gas, and as a result, the other end surface 17b of the slider 17 and the inner end surface 2 of the annular groove 28
Buffer means 3 for preventing sudden collision with 8a
0 is configured.

The pressure inside the crank chamber 7 is adjusted by a pressure regulating valve 3.
1 will be held. The pressure regulating valve 31 is a normally open electromagnetic valve, and is attached to the cylinder head 4 as shown in FIG. That is, the pressure regulating valve 31 is a high pressure chamber (discharge chamber) 3 defined between the cylinder head 4 and the valve plate 3.
2 and the crank chamber 7 are interposed in a communication passage. Inflow port 31a of the pressure regulating valve 31
communicates with the high pressure chamber 32, and the outlet 31b communicates with the crank chamber 7 via a communication hole 3a of the valve plate 3 and a conduit (not shown) provided in the cylinder block 6. 33 is a low pressure chamber (suction chamber) defined between the cylinder head 4 and the valve plate 3, and the low pressure chamber 33 and the crank chamber 7 are communicated through an orifice (not shown). ing.

The pressure regulating valve 31 is electrically connected to an output section of an electronic control device (not shown), and an output section of a potentiometer 34 is electrically connected to an input section of the electronic control device. The potentiometer 3
4 electrically detects the inclination angle of the swing plate 18, and is disposed inside the cylinder head 4, and its slider 34a is pressed toward the drive shaft 9 by a coil spring 35. The large diameter shaft hole 41 of the drive shaft 9 is inserted through the rod 42 which is loosely fitted into the small diameter shaft hole 41a of the drive shaft 9 and is slidable in the axial direction.
It comes into contact with an internal slider 43 fitted inside b, and is adapted to follow the displacement of the internal slider 43 in the axial direction. Further, the slider 17 is connected to the cylinder head 4 by a coil spring 36.
Pressed to the side. 37 is an oil pump, one end of which communicates with the suction port 37a, and the other end of an oil passage 38 provided in the cylinder block 6 opens to the crank chamber 7, and an oil guide pipe 3 is connected to the open end.
The base end of the oil guide tube 39 is connected, and the tip of the oil guide tube 39 is immersed in the oil in the oil reservoir 8 and opened. Further, the discharge port 37b of the oil pump 37 is connected to an oil guide path 40 inside the cylinder block 6, so that lubricating oil is supplied to each sliding portion.

(Function) Next, the function of the variable capacity oscillating plate compressor of the present invention having the above configuration will be explained.

First, when the electronic control device is not supplying power, the pressure regulating valve 31 is in an open state, and the crank chamber 7
is in communication with the high pressure chamber 32. Moreover, if the compressor is stopped, the slider 17 is pressed by the coil spring 36 and biased to the left in FIG.
The swing plate 18 is held at the minimum tilt angle position. When rotation is transmitted from the vehicle engine (not shown) to the drive shaft 9 via the belt and pulley 15, the drive shaft 9 rotates together with the arm member 13 integrated therewith, and the arm member 13 rotates with its arm portion 13b. The swing plate 18 engaged with the tip of the swing plate 18 is rotated. Since the rocking plate 18 gives the piston 11 a minute stroke movement of several percent of its maximum stroke when it is at the minimum inclination angle position, the stroke movement of the piston 11 reduces the pressure in the low pressure side space and reduces the pressure in the high pressure side. raise. Crank chamber 7 into low pressure chamber 33
The fluid (refrigerant gas) inside the high pressure chamber 32 is guided.
The high-pressure fluid (refrigerant gas) in the crank chamber 7 is introduced into the crank chamber 7 through the inlet 31a of the pressure regulating valve 31, the outlet 31b, the communication hole 3a of the valve plate 3, and a conduction path (not shown) in this order. room 7
The internal pressure does not decrease, and the rocking plate 18 maintains the minimum inclination angle position by the biasing force of the coil spring 36.
The compressor is rotated at idle.

Next, when the electronic control device is supplying power, the pressure regulating valve 31 is closed and the crank chamber 7 and high pressure chamber 3 are closed.
2 is cut off, fluid (refrigerant gas) in the crank chamber 7 flows out into the low pressure chamber 33 due to the stroke of the piston 11, and the pressure in the crank chamber 7 begins to decrease, and the pressure in the high pressure chamber 32 flows out. The pressure increases and the rocker plate 18 therefore increases its angle of inclination, increasing the stroke movement of the piston 11 and increasing the displacement of the compressor. This change in the inclination angle of the rocking plate 18 is electrically detected by the potentiometer 34, and when the discharge capacity of the compressor corresponding to this inclination angle becomes equal to the discharge capacity required of the compressor,
The electronic control device opens the pressure regulating valve 31. Therefore, the pressure in the crank chamber 7 stops decreasing and the inclination angle of the rocking plate 18 stops increasing. When the pressure in the crank chamber 7 increases due to the introduction of high pressure and the inclination angle of the rocking plate 18 decreases, the pressure regulating valve 31
is closed, and the rocking plate 18 is operated in the direction of increasing the tilt angle.

In this way, if the discharge capacity of the compressor decreases below or exceeds the discharge capacity required for the heat load of the air conditioner, or if the heat load of the air conditioner increases or decreases, the discharge capacity of the compressor decreases to meet the heat load. If the discharge capacity falls below or exceeds the required discharge capacity, the above operation is repeated each time to automatically control the discharge capacity to an optimum state.

In the discharge volume control operation described above, when the swing plate 18 reaches the maximum inclination angle position, the slider 1
One end surface 17a of the arm member 13 abuts against the inner end surface 26a of the annular groove 26 of the arm member 13. In this case, when the swing plate 18 rapidly reaches the maximum inclination angle position, the slider moves as shown in FIG. At the time when the outer peripheral surface of one end surface 17a of the arm member 13 fits into the inner peripheral surface of the open end of the annular groove 26 of the arm member 13, the refrigerant gas within the annular groove 26 is trapped, and the refrigerant gas produces an air damper effect. One end surface 17a of the slider 17 has an annular groove 26
It gradually collides with the inner end surface 26a of , so no collision noise is generated.

Further, even when the rocking plate 18 rapidly reaches the minimum inclination angle position, the outer circumferential surface of the other end surface 17b of the slider 17 fits into the inner circumferential surface of the open end of the annular groove 28 of the abutting member 27, as shown in FIG. At the point when the refrigerant gas in the annular groove 28 is trapped, an air damper effect is produced by the refrigerant gas, so that the other end surface 17b of the slider 17 gradually abuts against the inner end surface 28a of the annular groove 28, and the refrigerant gas in the annular groove 28 is trapped. No collision noise occurs.

(Second Embodiment) Next, a second embodiment of the present invention will be described with reference to FIG. In this embodiment, the same parts as in the first embodiment are designated by the same reference numerals in the drawings.
In this embodiment, an elongated hole 44 with a predetermined axial length is bored along the axial direction at a predetermined position on the outer peripheral surface of the drive shaft 9 (the part where the large diameter shaft hole 41b is formed), and the elongated hole 44 is inserted into the slider 17.
The slider 17 can be opened and closed at
A small diameter hole 45 is bored in the outer circumferential surface of the approximately intermediate portion in the axial direction,
Furthermore, an abutment member 46 is provided in the large diameter shaft hole 41b of the drive shaft 9.
This is a configuration with a When the rocking plate rapidly reaches the maximum inclination angle position, one end surface 43a of the internal slider 43 is positioned corresponding to one end 44a of the elongated hole 44, as shown in FIG.
3a and one end surface 46a of the abutment member 46 with which it abuts, refrigerant gas is trapped, thereby forming a buffer means 29a in which an air damper effect is produced by the refrigerant gas. Further, when the rocking plate rapidly reaches the minimum inclination angle position, the other end surface 43b of the internal slider 43 is positioned corresponding to the other end 44b of the elongated hole 44, and this abuts against the other end surface 43b of the slider 43. Refrigerant gas is trapped between the boundary step 47 between the small diameter shaft hole 41a and the large diameter shaft hole 41b, and the buffer means 30a is configured in which an air damper effect is produced by the refrigerant gas.

(Third Embodiment) FIG. 6 shows a third embodiment of the present invention, in which buffer means 29b and 30b made of elastic members 48 and 49 are attached to both end surfaces of the slider 17, respectively.
Slider 1 when the rocking plate reaches the maximum tilt angle position
One end surface of the slider 17 abuts against the inner end surface 13b of the boss portion of the arm member 13 via the elastic member 48, and the other end surface of the slider 17 abuts against the inner end surface 13b of the boss portion of the arm member 13 via the elastic member 49 when the rocking plate is at the minimum inclination angle position. Abutting surface 27 of mating member 27
It collides with a.

(Fourth Embodiment) Furthermore, FIG. 7 shows a fourth embodiment of the present invention, in which an arm member with which the outer peripheral side end surface of the swing plate 18 abuts when the swing plate 18 is at the maximum inclination angle position. A buffering means 29c made of an elastic member 50 is provided on the abutting surface 13d of the slider 13, and an abutting member 27 with which the other end surface of the slider 17 abuts when the rocking plate 18 is at the minimum inclination angle position.
A buffer means 30c made of an elastic member 51 is provided on the abutment surface 27a.

In the third and fourth embodiments, the same parts as in the first embodiment are designated by the same reference numerals in the drawings.

(Effects of the Invention) As explained above, the variable displacement wobble plate compressor of the present invention provides buffers to the abutting surfaces that abut each other in order to regulate the minimum and maximum inclination angle positions of the wobble plate. Since the means is provided, it is possible to reduce the impact at the time of collision, so that collision noise is not generated, and furthermore, it is possible to achieve effects such as no impact force acting on the members of the collision portion.

[Brief explanation of the drawing]

1 to 4 show a first embodiment of the present invention, FIG. 1 is a partially cutaway side view of the variable displacement wobble plate compressor of the present invention, and FIG. 2 is a slider at the maximum inclination angle position. 3 is an enlarged sectional view of the slider section at the minimum inclination angle position, FIG. 4 is a cross-sectional view of the same compressor, and FIG. 5 is an enlarged sectional view of the slider section showing a second embodiment of the present invention. FIG. 6 is an enlarged sectional view of a slider portion showing a third embodiment of the present invention, and FIG. 7 is an enlarged sectional view of a slider showing a fourth embodiment of the present invention. 13b...Boss inner end surface (abutment surface), 13d...
...Abutting surfaces of arm members, 17a, 17b... End faces (abutting surfaces) of sliders, 18... Rocking plates, 26a, 2
8a...Inner end surface (abutting surface) of annular groove, 29, 29
a, 29b, 29c, 30, 30a, 30b, 3
0c...Buffer means.

Claims (1)

[Scope of utility model registration request] A variable capacity type in which the discharge capacity changes by changing the inclination angle of the oscillating plate, and has abutment surfaces that abut each other to regulate the minimum and maximum inclination angle positions of the oscillating plate. 1. A variable displacement wobble plate compressor, characterized in that the abutment surface portion is provided with a buffer means to prevent the occurrence of collision noise.