JPH0647679U - Compressor shaft support structure - Google Patents

Abstract

(57) [Summary] [Purpose] The drive shaft support bearing on the front side is not required, and the total length of the drive shaft and front housing is shortened.
It is possible to reduce the size and weight, reduce the cost and weight, and since the support interval of the shaft becomes longer, the shaft support structure of the compressor that can improve the durability of the bearing and the shaft is provided. To provide. [Structure] Drive shaft 5 protruding from front housing 3
The bearing 16 around the protrusion 27 provided around the
The rotor 21 was attached via. In addition, the rotor 12 and the drive shaft 5 having the hub 24 are integrally connected,
This bearing 16 was used as the first bearing that supports this drive shaft.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a drive shaft support structure for a compressor for a car air conditioner.

[0002]

[Prior art]

 Conventionally, there are known compressors disclosed in JP-A-64-35095 (hereinafter referred to as Conventional Example 1) and JP-A-1-147171 (hereinafter referred to as Conventional Example 2).

The one shown in Conventional Example 1 is called a variable capacity vane compressor, and the one shown in Conventional Example 2 is called a variable capacity swash plate compressor. It is done by the main body.

In the above-mentioned conventional examples 1 and 2, the drive shaft of the compressor is supported at two places. One of the supporting parts is a bearing mounted on the front housing or the cylinder part, and the other supporting part is a bearing mounted on the rear cylinder part. A rotor is attached to the outer periphery of the protruding part that protrudes in through a bearing, and the rotor and drive shaft are connected via an electromagnetic clutch. The electromagnetic clutch is used as a safety mechanism to shut off the torque and stop the drive of the compressor when an abnormality occurs in the compressor.

[0005]

[Problems to be solved by the device]

 However, the use of an electromagnetic clutch is disadvantageous in terms of cost, weight, size, power, etc. Moreover, since the number of bearings used is large, it is disadvantageous in terms of cost, weight and size. There is.

Therefore, a first technical problem of the present invention is to provide a shaft support structure for a compressor that can shorten the overall lengths of the drive shaft and the front housing, and reduce the size and weight.

A second technical object of the present invention is to provide a shaft support structure for a compressor that can reduce costs.

A third technical object of the present invention is to provide a shaft support structure for a compressor that can improve the durability of bearings and shafts.

[0009]

[Means for Solving the Problems]

 According to the present invention, in a structure in which a drive shaft penetrating a front housing of a compressor is supported via first and second bearings, the projection protrudes outward from the front housing to surround the drive shaft. A shaft for a compressor, wherein an input rotor is attached to the periphery of a portion via a bearing, the input rotor and the drive shaft are integrally connected, and the bearing is the first bearing. A support structure is obtained.

Here, in the present invention, it is preferable to connect the drive shaft and the input rotor via a connecting member that breaks the connection at the time of overload.

[0011]

[Action]

 In the present invention, by integrally forming the drive shaft and the rotor, the bearing mounted between the protrusion of the front housing and the rotor can be used as the first bearing for supporting the drive shaft, It is no longer necessary to support the front housing or cylinder that was required in the past. Also, by integrally forming the drive shaft and rotor, an electromagnetic clutch is not required.

[0012]

【Example】

 An embodiment of the present invention will be described below.

First Embodiment A compressor shaft supporting structure according to a first embodiment of the present invention will be described in comparison with a conventional example.

FIG. 1 is a sectional view showing a capacity-variable swash plate compressor according to a conventional example. As shown in FIG. 1, the compressor is defined by a cylinder block 2 formed at one end of a housing 1, a front housing 3 formed at the other end of the housing 1, a front housing 3 and a cylinder block 2. Crank chamber 4, a drive shaft 5 ′ extending from the front housing 3 through the crank chamber 4 inside the housing 1 into the cylinder block 2, and provided in the crank chamber 4 together with the drive shaft 5 ′. The rotating rotor 6 is arranged around the drive shaft 5'and is connected to the rotor 6 via a pin 6a. As the rotor 6 rotates, the drive shaft 5'rotates at a predetermined angle. Swash plate 7, a swash plate 8 arranged around the drive shaft 5 and oscillating by the swash plate 7, and a piston reciprocating in the cylinder bore 2a according to the oscillating motion of the swash plate 8. And a 9.

Further, the cylinder bore 2a at one end of the housing 1 is provided with a valve mechanism including a valve plate 11 having a discharge valve to which a discharge valve retainer 11a is attached and a suction valve. A cylinder head 14 that defines the suction chamber 13 is arranged. Here, the drive shaft 5'includes a large-diameter portion 5a, a medium-diameter portion 5b, and small-diameter portions 5c and 5d, and the rotor 6, the swash plate 7, and the oscillating plate 8 are arranged in the large-diameter portion 5a. The middle diameter portion 5b is supported by the front housing 3 via the bearing 27. A seal spring mechanism 28 is arranged around the small diameter portion 5c of the drive shaft 5 '. A projecting portion 15 is formed so that one end of the front housing 3 projects along the periphery of the drive shaft 5 '.

On the other hand, an electromagnetic clutch 20 is arranged outside the front housing 3 at the other end of the housing 1. The electromagnetic clutch 20 is disposed in the rotor 21 ′, which is provided around the protruding portion 15 of the front housing 3 via a bearing 16, and is disposed in the rotor 21 ′, and is supported by the front end portion of the front housing 3. The electromagnet device 22, an armature 23 that moves in the axial direction by the suction action of the electromagnet device 22, a hub 24 ′ fixed to one end of the drive shaft 5 ′ inside the armature 23 by a nut 24 a, and a hub 24. ′ And a plate spring 25 ′ connecting the armature 23.

Around the rotor 21 ′ of the electromagnetic clutch, a groove 26 is provided along the outer peripheral surface for accommodating the V belt connected to the external drive source. Reference numeral 2b is an orifice, reference numeral 8a is a slider, and it is included in the variable capacity mechanism together with the guide rail 1a.

When the power of the electromagnet device 22 of the electromagnetic clutch 20 is turned on, the armature 23 is attracted to the axially right rotor 21 and rotates together with the rotor 21 ′ rotated by the external drive source. Since the armature 23 is connected to the hub 24 'provided at one end of the drive shaft 5'through the leaf spring 25', the rotation of the rotor 21 'is transmitted to the drive shaft 5'. With the rotation of the drive shaft 5 ', the rotor 6 rotates, thereby rotating the swash plate 7 that makes an angle with the drive shaft 5'connected via the pin 6a. The rotary motion of the swash plate 7 is converted into a rocking motion of the rocking plate 8 in the direction along the drive shaft 5 ', and is converted into a reciprocating motion of the piston 9 connected to the periphery of the rocking plate 8 in the cylinder 2a. Be touched. By the movement of the piston 9, the fluid in the suction chamber 13 is introduced into the cylinder 2a via the valve mechanism, compressed, and discharged into the discharge chamber 12 via the valve mechanism.

A part of the fluid in the discharge chamber 12 is introduced into the crank chamber 4 via the orifice 2b to adjust the pressure in the crank chamber. Here, when the pressure in the crank chamber 4 is relatively high, the swash plate 7 moves in a direction such that the inclination angle of the swash plate 7 becomes smaller due to the moment generated by the back pressure applied to the piston and the discharge pressure. , The amount of movement of the piston 9 is reduced, and the discharge capacity is reduced. On the other hand, when the pressure in the crank chamber 4 is relatively small, the same moment increases the inclination angle of the swash plate, which increases the movement amount of the piston 9 and increases the discharge capacity. Reference numeral 30 is a capacity adjusting mechanism that connects the crank chamber 4 and the discharge chamber 12 to each other when the pressure in the crank chamber 4 exceeds a predetermined pressure.

The present invention is applied to a conventional variable displacement compressor having such a structure as shown in FIG.

That is, in FIG. 2, the armature 23, the electromagnet device 22, the bearing 27 and the leaf spring 25 ′ shown in FIG. 1 are omitted, and the drive shaft 5 is omitted from the intermediate diameter portion 5 b in FIG. A rotor (input rotor) 21 installed via a bearing 16 around the front housing 3 and a hub 24 having a large plate body at one end are formed into a cylindrical shape with both ends inserted in respective grooves 24a, 21a. It is directly connected via the connecting member 25. The connecting member 25 is made of a material that is damaged by a shearing force of a predetermined value or more. When the connecting member 25 is overloaded, it breaks and blocks rotation from the rotor, stops rotation of the drive shaft, and protects the compressor from damage. be able to.

Further, in the swash plate type compressor according to the first embodiment of the present invention, this configuration allows the bearing 27 in FIG. 1 to be omitted and the drive shaft 5 to be shortened. In addition, it is possible to reduce the size by reducing the diameter of the rotor.

(Embodiment 2) A shaft support structure of a compressor according to Embodiment 2 of the present invention will be described in comparison with a conventional example.

FIG. 3 is a sectional view showing a variable displacement scroll compressor according to a conventional example. As shown in FIG. 3, the scroll compressor has a fixed scroll member 50 having a spiral body 52 on one surface of a plate body 51 and a spiral body 54 on one surface of a plate body 53, and the back surface of the scroll body 54. A movable scroll member 55 having a boss portion 56, a housing 57 provided so as to surround the movable scroll member 55, the other surface side of the plate of the movable scroll member 55, and the housing 57. And a discharge passage 58 for compressed fluid and a suction passage 59 for fluid.

The other end of the housing 57 is provided with a suction pressure detection device 60 for sensing the fluid pressure communicating with the suction passage 59, and a valve having a check valve in the suction passage 59 around the movable scroll member 55. A suction chamber 66 is provided which communicates with the mechanism 68a. Further, a discharge chamber 67 communicating with the discharge passage 58 is provided, and a bypass passage 68 is formed in the middle space of the fixed scroll member 50. The suction pressure detection device 60 is provided with an orifice 61 connected to the discharge chamber 67, a control valve 62 for detecting the suction pressure, a bellows 63, and a detection element 64 connected to the bellows 63. The control valve 62 is opened and closed based on the detected discharge pressure.

A front housing plate 70 is provided at one end of the housing 57.

The drive shaft 71 ′ includes a small diameter portion 71 a, a medium diameter portion 71 b, and a large diameter portion 71 c, and a movable scroll member via an eccentric pin 73 and an eccentric bush 74 provided on the large diameter portion 71 a. It is connected to the boss portion 56 at one end of 55. The small diameter portion 71a of the drive shaft 71 is supported by the protruding portion 76 'via the bearing 75, and the large diameter portion 71c is supported by the front housing 70 via the bearing 69. An electromagnetic clutch 80 is provided around the protruding portion 76 ′ of the housing plate 70 on one end side of the housing 57.

The electromagnetic clutch 80 includes a rotor 82 ′ provided around a protrusion 767 of the front housing plate 70 via a bearing 81, an electromagnet device 83 provided in the rotor 82 ′, and a drive shaft 71 ′. A hub 84 ′ provided at one outer end of the hub 84 ′, and an armature 86 ′ provided around the hub 84 ′ and connected to the hub 84 ′ via a leaf spring 85 ′.

In addition, a groove 87 for inserting a V-belt driven by an external drive source is provided around the rotor 82 '.

When the power of the electromagnet device 83 of the electromagnetic clutch 80 is turned on, the armature 86 ′ is attracted toward the rotor 82 ′ side and rotates with the rotation of the rotor 82 ′ that is rotated by an external power source. This rotation is connected to the hub 84 'via the leaf spring 85' to rotate the drive shaft 71 '. With the rotation of the drive shaft 71 ', the eccentric pin 73 makes a circular motion, causing the eccentric bush 74 to make a circular motion, and this motion causes the movable scroll member 55 to circle through the boss portion 56 having a bear ring on the inner peripheral surface. Exercise. Due to the circular motion of the movable scroll member, the respective spaces formed in the suction chamber move toward the center along the wall surfaces of the spiral bodies 52, 54, discharge into the discharge passage 58, and then into the discharge chamber 67. Moving.

Here, when the discharge pressure is high, the pressure detection device 60 detects the pressure and opens the control valve 62, whereby the bypass passage 68 having the reed valve 68a is formed, and the discharge pressure is increased. Is reduced.

On the other hand, when the discharge pressure is low, the pressure detecting device 60 detects the pressure and closes the control valve to close the bypass passage 68 and increase the discharge pressure.

FIG. 4 shows an example in which the present invention is applied to a conventional variable displacement scroll type compressor having such a configuration. As shown in FIG. 4, in the shaft supporting structure of the compressor according to the second embodiment of the present invention, the hub 84 ′ and the armature 86 ′ in FIG. The electromagnet device 83 of the rotor 82 ′, the small diameter portion 71 a of the drive shaft 71, and the bearing 75 supporting the same are omitted, and the rotor (input rotor) 82 is supported by the protruding portion 76 via the bearing 81. The hub 84 and the rotor 82 are connected via a cylindrical connecting portion 85 inserted in the grooves 84b and 82a provided in the hub 84 and the rotor 82, respectively. The connecting member 85 is made of a material that is damaged by a shearing force of a predetermined value or more. When the connecting member 85 is overloaded, the connecting member 85 breaks, the rotation of the drive shaft 71 is stopped, and the compressor can be protected from being broken.

As described above, according to the variable displacement scroll compressor according to the second embodiment of the present invention, the small diameter portion of the drive shaft 71 can be omitted by omitting the bearing 75 in FIG. The shaft 71 can be shortened and the diameter of the rotor can be reduced to reduce the size.

(Embodiment 3) A shaft support structure of a compressor according to Embodiment 3 of the present invention will be described in comparison with a conventional example.

FIG. 5 is a cross-sectional view showing an example of a conventional variable displacement type swash plate type compressor. As shown in FIG. 5, the double swash plate type compressor includes a swash plate chamber 101 provided in a housing 100, a plurality of cylinder bores 102 and 103 provided at both ends of the swash plate chamber 101, which form a pair in front and rear, It is provided at both ends of the housing 100, is connected to the ends of the cylinder bores 102, 103 via valve plate members 104, 105, and has a discharge chamber 106 and a suction chamber 107, and a discharge chamber 108 and a suction chamber 109, respectively. And cylinder heads 110 and 111, respectively. A double-headed piston 120 is reciprocally housed in each of the front and rear cylinder bores 102 and 103. A drive shaft 121 'is rotatably housed and supported in the housing 100, and the swash plate 122 is not rotatable relative to the drive shaft 121 and swings back and forth around its peripheral side. A swash plate guide portion 123 that supports the guide portion 123 and a rotor 124 that rotates the guide portion 123 are provided. The peripheral portion of the swash plate 122 is housed in the groove of the double-headed piston 120 via a pair of shoes 125, 125 on the front and back surfaces.

On the other hand, an electromagnetic clutch 130 is provided on the protrusion 112 side of the cylinder head 110. The electromagnetic clutch 130 includes a rotor 132 'provided on the protrusion 112 via a bearing 131, an electromagnet device 133 housed in the rotor 132', and a hub 134 'provided at one end of the drive shaft 121. It includes an armature 135 and an elastic member 136 'that connects the armature 135 and the hub 134'.

A recess 113 is formed in the center of the cylinder head 111, and a substantially tray-shaped actuator 114 is axially slidably arranged in the recess 113. With the actuator 114 as a boundary, the valve mechanism side of the recess 113 is the suction chamber 109, and the opposite side is the pressurizing chamber 115. A coil spring 116 is provided in the pressurizing chamber 115. The coil spring 116 urges the actuator 114 in the direction of separating the piston 120 from the valve mechanism 105. The fluid introduced from the discharge chamber 108 into the pressurizing chamber 115 can escape to the suction chamber 109 via the control valve 140. By controlling the communication between the pressurizing chamber 115 and the suction chamber 109 by the control valve 140, the pressure in the pressurizing chamber 115 is controlled, and as a result, the position of the actuator 114 is controlled.

A control piston 117 is axially slidably provided at the center of the rear of the cylinder block. A thrust needle bearing 119 is interposed between the control piston 117 and the slider 118. The thrust needle bearing 119 is arranged in the swash plate chamber 101 so as to be axially movable in the swash plate chamber 101 of the cylinder block. The fixed ring of the thrust needle bearing 119 is fixed to the slider 118. Therefore, the axial movement of the actuator 114 is transmitted to the slider 118 via the control piston 117 and the thrust needle bearing 119. As a result, by controlling the pressure in the pressurizing chamber 115 with the control valve, the inclination angle of the swash plate 122 can be controlled, and the displacement of the double-headed piston can be changed to change the discharge capacity. Reference numeral 120 is a bearing, and reference numeral 141 is a slider pin.

FIG. 6 shows a swash plate type compressor having such a structure to which the present invention is applied. As shown in FIG. 6, a drive shaft support structure for a compressor according to a third embodiment of the present invention includes a hub 134 having a plate member 134a fixed by a bolt 138 at one end of the drive shaft, and a drive shaft 121 surrounding. A rotor (input rotor) 132 supported around bearings 131 around the front housing protrusion 112 and a connecting member 136 for connecting the rotor 132 and the periphery of the hub 134. It differs from the example of FIG. 5 in that it does not have the armature 135, the electromagnet device 133, the elastic member 136 ′, and the bearing 137. The connecting member 136 breaks when the compressor is overloaded and stops driving the compressor to prevent the overload.

In the bi-swash plate type compressor according to the third embodiment of the present invention having such a configuration, the size of the drive shaft can be shortened, the diameter of the rotor can be reduced, and the size can be reduced. it can.

(Embodiment 4) A drive shaft structure of a compressor according to a fourth embodiment of the present invention will be described in comparison with a conventional example.

FIG. 7 is a sectional view showing an example of a conventional variable displacement vane compressor.

As shown in FIG. 7, the compressor includes a cylindrical cam ring 151, and a front plate 152 and a rear plate 153 that seal both ends of the cam ring 151.

A rotor 154 is rotatably accommodated in the cam ring 151. On the rotor 154, a plurality of vanes 155 are radially inserted into slits (not shown). A back pressure passage is formed at the bottom of this slit, and lubricating oil is supplied so as to apply a back pressure to the vane 155.

Both ends of the cam ring 151, the front plate 152, and the rear plate 153 are housed in the front housing 160 and the rear housing 161, respectively. A discharge chamber 162 is defined in the rear housing 161, and lubricating oil is stored at the bottom. A working chamber 156 is defined by the cam ring 151, the front plate 152, the rear plate 153, and the rotor 154, and the working chamber 156 and the discharge chamber 162 communicate with each other through a discharge hole (not shown). A suction chamber 163 is defined by the front housing 160 and the front plate 152, and the suction chamber 163 communicates with the working chamber 156 via a suction passage (not shown).

The drive shaft 170 includes a small diameter portion 170a, a medium diameter portion 170b, and a large diameter portion 170c, one end of which is connected to the rotor 154, and the other end of the small diameter portion 170a is provided with a hub 185 '. . The large diameter portion 70c is supported by the front housing 160 by a bearing 171, and the middle diameter portion 170b is supported by the front housing 160 via a seal spring mechanism 174.

A bypass port 158 formed on the front plate 152 and connecting the working chamber 151 and the suction chamber 163 is provided rotatably between the front plate 152 and the cam ring 155 to change the opening position of the bypass port 158. A movable plate 159 having a bypass opening is provided. Reference numeral 169 is a communication hole that connects the inside of the cam ring to the actuator.

The movable plate 159 operates the actuator 165 by the control mechanism 165 that detects the discharge gas pressure, and rotates the movable plate 159 to change the opening position of the bypass port 158 to the rotational direction of the rotor 154. Rotate in the direction along or in the opposite direction to change the discharge capacity of the compressor.

The front housing 160 has a protrusion 164 along the drive shaft 171. An electromagnetic clutch 180 is formed around the protruding portion 164.

The electromagnetic clutch 180 includes a rotor 183 ′ provided around the protrusion 164 of the front housing 160 via a bearing 182, an electromagnet 184 provided in the rotor 183, and an armature 187. Are connected around the hub 185 'via leaf springs 186'.

With the rotation of the rotor 154, the fluid sucked from the suction chamber 163 by the vanes 155 provided in the rotor 154 is compressed due to the shape change of the elliptical cam ring inner wall, and is discharged to the discharge chamber 162. To be done.

FIG. 8 shows an example in which the present invention is applied to a variable capacity vane compressor having such a configuration.

As shown in FIG. 8, the rotor (via the bearing 182 is provided around the protrusion 181 of the front housing 160 provided along the periphery of the drive shaft 170 in the direction in which the rotor (via An input rotor) 183 is provided, and on the other hand, a hub 185 having a plate 185a is provided at one end of the drive shaft 170. The rotor 183 and the hub 185 are cylindrical connecting members provided in respective grooves. It is connected via 186.

Therefore, in a type in which the speed is controlled by changing the rotation speed of a motor as an external drive source, when the compressor is overloaded, this protrusion breaks and the drive of the compressor stops, The destruction due to the overload of the compressor is prevented.

As described above, the variable capacity vane compressor according to the fourth embodiment of the present invention is downsized because the length of the drive shaft is shortened and the diameter of the rotor is reduced. be able to.

[0057]

[Effect of device]

 As described above, according to the present invention, the drive shaft support bearing on the front side is unnecessary, and the total length of the drive shaft and the front housing can be shortened.

Further, according to the present invention, cost and weight can be reduced by eliminating the abolished bearing of the clutch.

Further, according to the present invention, since the support interval of the drive shaft becomes long, the durability of the bearing and the drive shaft is improved.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing an example of a conventional displacement type swash plate compressor.

FIG. 2 is a sectional view showing an example in which the present invention is applied to the compressor of FIG.

FIG. 3 is a sectional view showing an example of a conventional variable displacement scroll type compressor.

4 is a diagram showing an example in which the present invention is applied to the compressor of FIG.

FIG. 5 is a cross-sectional view showing an example of a conventional variable displacement swash plate type compressor.

6 is a diagram showing an example in which the present invention is applied to the compressor of FIG.

FIG. 7 is a cross-sectional view showing an example of a conventional variable capacity vane compressor.

8 is a diagram showing an example in which the present invention is applied to the compressor of FIG.

[Explanation of symbols]

3,160 front housing 5,5 ', 71, 71', 121, 121 ', 170,
170 'Drive shaft 5b Medium diameter part 16,27,75,81,131,137,182
Bearing 20, 80, 130, 180 Electromagnetic clutch 21, 21 ', 82, 82', 132, 132 ', 18
3,183 'rotor 21a, 24a groove 23, 86', 135, 187 armature 24, 24 ', 84, 84', 134, 134 ', 18
5,185 'Hub 25,85,136,186 Connecting member 25' Leaf spring 71a Small diameter part 76 Projection part 82a, 84b Groove 84a Plate body 112,164 Front housing projection part 136 'Elastic member

Claims (1)

[Scope of utility model registration request] 1. A structure for supporting a drive shaft penetrating a front housing of a compressor via first and second bearings, wherein a projecting portion protruding outward from the front housing to surround the drive shaft is provided. A shaft support structure for a compressor, wherein an input rotor is attached to the periphery through a bearing, the input rotor and the drive shaft are integrally connected, and the bearing is the first bearing.