JPS5968587A - Compressor - Google Patents

Abstract

PURPOSE:To make the selection between compressive operation and non-compressive operation possible under the state that driving force is inputted to a rotor by a method wherein the selective change of the driving center of the rotor between two positions or between a position eccentric to the center of the rotor and a position concentric to the center of the rotor is made possible. CONSTITUTION:The rotation of a front shaft 64, which is a driving shaft, is transmitted through the engagement between a projection 74 and an engaging groove 76 to an inner rotor 52 in order to apply free-running torque through a rear projection 58 to a rear shaft 54. During engine running, because a stopper device 86 is in the released state, the rear shaft 54 can rotate freely, resulting in bringing the rotor 48 into idle running and performing no compression work. However, when a manual switch for the device is turned ON, a solenoid 96 is deenergized and consequently the stopper device 86 is put into actuation, resulting in checking the rotation of the rear shaft 54 in the state that the axis center O3 of the rear projection 58 is incoincidence with the center line O2 of a rotor chamber 4 so as to cause the rotor 48 to eccentrically pivot in order to compress refrigerant. In such a manner as described above, the compressive and the non-compressive drives are made possible under the state that the driving force is inputted to the rotor.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a rotor that is formed in a main body and rotates eccentrically along the inner circumferential surface of the rotor in a rotor chamber, and a rotor that is provided on the main body side so as to be in constant contact with the outer circumferential surface of the rotor. The present invention relates to a rotary compressor that is equipped with a vane and compresses gas (for example, refrigerant gas) between the vane, the inner peripheral surface of the rotor, and the outer peripheral surface of the rotor.

Conventionally, in this type of compressor, a friction clutch containing an electromagnetic coil, etc. is often installed in the compressor at the moment of switching between a state in which compression work is performed and a state in which no compression work is performed. When the clutch is in the connected state, external rotational driving force is transmitted to the drive shaft and drives the rotor, while when the clutch is in the disconnected state, no driving force is input to the shaft and the rotor is at rest. In conventional compressors, the compressor operating state and the non-compressing operating state are selected depending on whether the latch is engaged or not, and it is necessary to transmit a considerably large rotational torque. One disadvantage is that the friction surface and electromagnetic coil are quite large, resulting in a larger compressor and heavier electrical equipment.

With this background in mind, the present invention provides a compression system that allows driving force to be input to the rotor and selectively perform compression operation and non-compression operation while the rotor remains in this state without using a latch device as in the past. It was created for the purpose of providing an opportunity.

As a result, the characteristics of the compressor according to the present invention are as follows: Very roughly speaking, the drive center of the rotor is moved away from the rotor center in the state where compression work is performed and the state where it is not performed. It is configured such that it can be selectively changed between two positions: an eccentric eccentric position and a concentric position concentric with the eccentric position, and more specifically, it includes each of the following components (1) to 00. It is located in the place where it is composed of.

(1) A rotor chamber with a circular cross-section formed inside and equipped with at least one suction port and one discharge valve. (2) Between the suction port and the discharge valve that are adjacent to each other. is provided, is held movably in the radial direction of the rotor chamber by the main body, and is located on the center side of the rotor chamber.
\A biased vane (3) A shaft (4) installed in the rotor chamber of the rear shaft, which is provided parallel to the center line of the rotor chamber and eccentrically a certain distance from the center line, and is rotatably supported by the main body. A rear protrusion with a circular cross section is provided on the facing end surface with an offset of 1 t from the axis of the rear shaft, which is equal to the eccentricity between the axis and the center line of the rotor chamber indicated by L. A rotor (6) is housed and is in sliding contact with the tips of the vanes on its outer peripheral surface.The rotor (6) is provided on the end surface of the rotor on the rear shaft side, eccentrically by the eccentric amount t from the center line of the rotor, and the rear protrusion or one rear hole is provided. A rear hole or rear protrusion (7) rotatably fitted into the main body is provided on the opposite side of the rear shaft with the rotor in between, and parallel to the center line of the rotor, and rotates at the front end of the main body. A front protrusion (9) that draws a rotation locus that includes the center line of the front shaft rotor chamber and the axis of the rear shaft inside, which is connected to the front shaft rotor chamber center line and the axis of the rear shaft. an engagement groove 00 that is formed and engages with the front protrusion to transmit rotation of the front shaft to the rotor; a rotation inhibiting device that prevents rotation of the rear shaft when the rear protrusion is aligned with the center line of the rotor chamber; In this compressor, the rotation of the rear shaft is prevented, and in this state, the rotor moves around the stationary rear protrusion, that is, in the rotor chamber. The rear shaft performs compression work by eccentrically rotating along the inner peripheral surface of the rotor chamber around an axis that is concentric with the center line of the rotor and is eccentric by approximately the above eccentric amount j from the rotor center line. In the allowed T state, the rotor rotates idly about the axis of the rear shaft, which is concentric with the rotor's center line, and is maintained in a state where no compression work is performed. Then, the above-mentioned compression operation in which compression work is performed and idle operation in which compression work is not performed are switched by the blocking +L operation of the rotation prevention device that prevents rotation of the rear shaft and the release operation to release the inhibition, and the operation pattern is changed. Since it is sufficient for the rotation prevention device to perform the function of a stopper, it is necessary to select a rotation prevention device that is equipped with a fairly large friction clutch that transmits and interrupts the internal driving force, as in the past. The compressor is smaller compared to
It can be easily destroyed.

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a compressor for compressing refrigerant installed in an automobile as a vehicle interior near-conditioning device will be described below with reference to the drawings.

In FIG. 1, 2 is a cylindrical cylinder, and the inner space of the cylinder 2 is a rotor chamber 4 having a circular cross section.

A front sight plate 1-6 is arranged and fixed on one opening end surface of the cylinder 2, and a front sight plate 1-6 is arranged and fixed on the other opening end surface (respectively), and furthermore, a front sight plate 1-6 is arranged and fixed on the other opening end surface. Freon I/Housing 1
0 is provided, while the rear sight plates 1 and 8 and the cylinder 2 are housed inside - the crusher housing 12 is airtightly integrated with the front housing 10, and in this embodiment, these members including the cylinder 2 are A main body 14 of the compressor is constructed from the above.

The front housing 10 is provided with a suction port 16, and refrigerant gas (for example, Freon scum, etc.) returned from the external cooling circuit is introduced into a suction chamber 18 formed inside the housing 10 through the suction port 16. The refrigerant introduced there passes through the front side plate 6 and passes through suction ports 20 and 22 that open on the inner peripheral surface of the cylinder 2 at positions symmetrical to each other, sandwiching the center of the rotor chamber 4, as shown in FIG. It is guided into the rotor chamber 4. Matoko,
Close to the suction ports 20 and 22, the cylinder 2 has a discharge chamber 24 formed inside the rear housing 12.
Discharge ports 26 and 28 are formed at symmetrical positions with respect to the center of the rotor chamber 4 to communicate the rotor chamber 4 with the rotor chamber 4 . Discharge valves 80 and 82 are provided in the discharge ports 26 and 28, respectively, and when the refrigerant pressure on the rotor chamber 4 side reaches a level that overcomes that on the discharge chamber 24 side, the valves 84 and 86 open. While the compressed refrigerant is discharged into the discharge chamber 24,
When this size is not reached, the valves 84 and 86 are closed to prevent the refrigerant from flowing back. The refrigerant discharged into the discharge chamber 24 through the discharge valves 80 and 82 is sent out again to the external cooling circuit via a discharge port 88 provided in the rear housing 12, as shown in FIG.

As is clear from FIG. 2, the suction ports 20 adjacent to each other
A vane groove 40.42 is formed between the rotor chamber 4 and the discharge valve 30, and between the suction port 22 and the discharge valve 32, and extends through the wall of the cylinder 2 along a central plane that includes the centerline of the rotor chamber 4. Two vanes 44 and 46 are held in these vane grooves 40 and 42 so as to be slidable in the radial direction of the rotor chamber 4, respectively, independently of each other. The vanes 44 and 46 have a length slightly smaller than the wall thickness of the cylinder 2, and are moved toward the center of the rotor chamber 4 by the refrigerant pressure 'B' of the discharge chamber 24 acting on each rear end and by a spring (not shown). The tips are rounded in an arc shape in the thickness direction.

A rotor 48 having a smaller diameter than the inner diameter of the rotor chamber 4 is housed in the rotor chamber 4 . The rotor 48 has a generally cylindrical shape as a whole, including a cylindrical outer rotor 50 and a solid inner rotor 52 rotatably fitted inside the outer rotor 50 . As shown in FIG. 1, the outer rotor 50 is made longer in the axial direction than the inner rotor 52, and both end surfaces of the outer rotor 50 are in sliding contact with the front sight plate 1. -6 and the rear sight plays 1 and 8, movement in the axial direction within the rotor chamber 4 is restricted.

A flyer shaft 54 is provided on the rear end side of the rotor 48 . The rear shirt I.54 is arranged so that its axis O -Sight play 1-
．． It is rotatably supported by 8.

At the end of the rear shaft 54 facing the rotor chamber 4, a third
(As shown in this figure, a rear protrusion 58 with a circular cross-sectional shape is integrally formed. As is clear from Fig. 1, the axis 03 of the rear protrusion 58 is aligned with the center line 02 of the rotor chamber 4 It is offset from the axis 01 of the rear shirt 1-54 by the same distance ef as the eccentricity te with respect to the axis 01 of the shaft 54. Therefore, when the rear shaft 54 is rotated, the axis of the rear protrusion 58 O3 is the center line O of the rotor chamber 4
Draw a rotation trajectory passing through 2.

The rear protrusion 58 is rotatably fitted through a bearing 62 into a rear hole 60 having a circular cross section formed at the end of the inner rotor 52, which is a component of the rotor 48, on the rear shaft 54 side. The rotor 48 has a radius R of the rotor chamber 4.
The rear hole 60 has a radius r that is substantially equal to the two values r minus the eccentricity e between the rear projection 58 and the rear shaft 54, and the rear hole 60 is located from the center line 04 of the rotor 48 to It is provided eccentrically by the same j distance as e.

On the other hand, a front shaft 64 is provided on the opposite side of the rear shaft 1-54 with the rotor 48 in between. The wire core O6 of the front shaft 64 is 1~
Parallel to the axis 01 of 54 (in this embodiment, the axis 01
1, and this front shaft 64 is
The end on the rotor 48 side is rotatably supported by the front sight play 1-6 via a brane bearing 66, and the opposite end is rotatably supported by the front housing 10 via a roller bearing 68. between the bearings 66 and 68 (bearings), the housing 1 is connected to the fron 1 to the shaft 64 and the fron 1.
A shaft seal 7° is provided to maintain airtightness between the compressor body 14 and the compressor body 14 to prevent refrigerant from leaking from the suction chamber 18 to the outside of the compressor body 14. The front end of the front shaft 64 is slightly protruded outward from the front end of the front housing 10, and a belt pulley 72 is fixed thereto with a key 73. Rotational drive part of vehicle engine and Freon 1~
The rotary shaft 64 is connected, and the rotational driving force is transmitted to the front 1-
The signal is transmitted to the shaft 64.

Of the end surfaces of the front shaft 64 and the rotor 48 that face each other, a front protrusion 74 having a circular cross section is integrally formed on the end surface of the front shaft 64. The axis 06 of the front projection 74 is offset by a distance e'' from the axis 05 of the front shaft 64, and this eccentricity t el
is made larger than the eccentricity e between the rear projection 58 and the carrier shaft 54, so that when the front shaft 64 rotates, the axis 6 of the front projection 74 is aligned with the center line 02 of the rotor chamber 4 as shown in FIG. Axis center of rear shaft 54 0□
0
The relative position of the front I/protrusion 74 with respect to □ is selected. In other words, the axis 06 of the Freon l-protrusion 74 is
A rotation that can be rotated around the center line ( ) 2 of the rotor chamber 4 and at the same time can be rotated around the axis 0□ of the rear shirts 1 to 54, and that satisfies both of these two conditions. ``Draw a trajectory.''

As shown in FIG. 3, the front protrusion 74 is slidable into an engagement groove 76 in a knee hole formed in the radial direction of the end surface of the inner rotor 52 on the front shaft 64 side via a slider 78. The sliter 78 is a substantially rectangular flocked body having a thickness corresponding to the length of the front projection 74, and the sliter 78 is a flocked body having a substantially rectangular shape and has a thickness corresponding to the length of the front projection 74. The slider 78 can be considered to be a part of the front projection 74, and the front projection 74 can also be viewed as a projection with a slider.
Both side surfaces formed parallel to each other are engaged in a state in which they are almost in contact with the groove wall surface of the retaining groove 76, and are sandwiched between the groove bottom surface and the end surface of the front shaft 64, as is clear from FIG. It is slidably fitted into the groove 76. Holding groove 7
6 is a tree nut T @ In the example, a slider 78 is installed along the diameter direction of the inner rotor 52 including the center line (03) of the rear hole 60 into which the rear protrusion 58 is fitted, over the entire length of the diameter.
The inner circumferential surface of the outer rotor 50 is formed on the opposite side to the side where the center line (03) of the rear hole 60 is offset. The end surface of the slider 78 facing the outer rotor 50 is formed into a cylindrical surface shape with a curvature corresponding to the inner circumferential surface of the outer rotor 50, as shown in FIG.

In this way, since the front protrusion 74 is engaged with the engagement groove 76 of the rotor 48 via the slider 78 (in other words, it has the slider 78), the rotation of the front shaft 64 is transmitted to the rotor 48. be done. At this time, as shown in FIG. 2, the rotation locus drawn by the axis 06 of the front projection 74 should include both the center line 02 of the rotor chamber 4 and the axis 0□ of the rear shaft 54 inside. Therefore, the rotor 48 can be rotated eccentrically around the center line 02 of the rotor chamber 4 in the same direction by the circumferential movement (rotation) of the front I/protrusion 74 in one direction. It is also possible to simply rotate it around the axis 01 of . When the rotation of the front shaft 64 is transmitted to the rotor 48, the rotational force is transmitted to the rear shaft 54 through the f-collision protrusion 58 which is fitted into the rear hole 60 of the rotor 48 as shown in FIG.

The rear shaft 54 is slightly protruded rearward from the bearing portions of the rear sight plays I to 8, and a circular plate member is attached to the protruding portion by a key 82 to align the axis 01 of the rear shaft 54 with the axis 01 of the rear shaft 54. A flange-shaped disk portion 84 is formed which is fixed to the rear shaft 54 and is rotatable integrally with the main body portion of the rear shaft 54 . This disc part 84 constitutes a part of the rear shirt 1-54 as a stopper retaining part, and the rear shirt 1-54 is provided at the rear end of the rear housing 12 close to the outer periphery of the disc part 84. An electromagnetic stopper device 86 is provided which functions as a rotation prevention device to prevent rotation of the rotation of the rotor 54 .

This stopper device @86 consists of a thick-walled cylindrical holding flock 88 made of non-magnetic material fixed to the inner surface of the rear housing 12.
A movable iron core 92 having a stopper protrusion 90 at the tip thereof is provided inside.
is held movably in a direction parallel to the axis 01 of the rear shaft 54, and is constantly held by a spring 94.
The movable iron core 9
A solenoid 96 is disposed on the holding flock 88 at the rear end (+l+1) of 2, and when the solenoid 96 is energized, the movable iron core 92 resists the biasing force of the spring 94 and closes the holding flock 88. While the solenoid 96 is pulled in and maintained in the single state, when the solenoid 96 is demagnetized, the movable iron core 92 is caused to protrude toward the outer periphery of the disk portion 84 based on the biasing force of the spring 94. Disc part 8
4, the axis 03 of the rear protrusion 58 is aligned with the rotor chamber 4.
An engagement notch 98 is formed at an angular position that coincides with the center line 02 of the movable iron core 92 and faces the stopper protrusion 90 of the movable iron core 92.

When the stopper protrusion protruding toward the disk portion 84 engages (fits in) with the engagement notch 98, the rotation of the rear shirt 1-54 is caused to align with the axis 03 of the rear protrusion 58 and the center of the rotor chamber 4. On the other hand, when the movable iron core 92 is pulled by the solenoid 96 and the stopper protrusion 90 is disengaged from the engagement notch 98, the rotation of the rear shaft 54 is prevented. or permissible. The solenoid 96 is energized when the key switch of the automobile is turned on, and its energization and demagnetization are controlled by a manual switch for the air conditioning system and a temperature sensor installed in the vehicle interior. 'The stopper device 86 is then actuated or deactivated.

Note that in the stopper device 86, the solenoid 96
By reversing the roles played by the springs 94 and 94, the movable iron core 92 is held in the holding block 8 with a biasing force that can overcome the frictional force when the stopper protrusion 90 and the engagement notch 98 engage.
By providing a spring that urges the movable iron core 92 inward, and providing a solenoid that projects the movable iron core 92 against the spring force of the spring in the energized state, the stopper device is activated when the solenoid is demagnetized. It can also be configured so that it is in an inactive state. In addition, the engagement notch 98
Instead, it is also possible to prevent the rotation of the rear shaft 54 in the same manner as described above by providing an engaging protrusion on the outer circumference of the disc portion 84 and engaging the engagement protrusion with the stopper protrusion 90. From a further perspective, such a rotation prevention device can be considered to include the disc portion 84 having the engagement notch 98 and the like, and the stopper device 86 as described above.

An oil pump 100 for lubrication is provided at the rearmost end of the rear shaft 54 further behind the portion where the disk portion 84 is provided, and is used as a storage chamber for separating lubricating oil when the rear shaft 54 rotates. Oil is sucked up from the discharge chamber 24 and passes through an oil passage (not shown) to the front and rear shaft bearings 66.56, the outer peripheral surface of the inner rotor 52, and both the front and rear protrusions 74.58.
Also, parts such as the shaft seal 70 are supplied with oil, thereby reversing the lack of lubrication that tends to occur during idle rotation. Note that during compression operation when the rear shaft 54 is prevented from rotating, the oil pot 100 does not operate. Because of the communication state, even if the oil pump 100 is stopped, the riko oil accumulated in the lower part of the discharge chamber 24 can be supplied by the discharge pressure of the refrigerant.

Next, the overall operation of the compressor configured as above will be explained.

In FIG. 1, when the front shaft 71-64 is rotated by the rotational driving force of the engine drive unit via the belt pulley 72, etc., the front shaft rotates 640 times due to the engagement of the front shaft 1 to the protrusion 74 and the engagement groove 76. is the inner rotor 5
As the inner rotor 52 rotates, rotational torque acts on the rear shaft 1 via the rear protrusion 58 as the inner rotor 52 rotates.

While the engine is rotating, the key switch is naturally turned on, the solenoid 96 is energized, and the stopper device 8
6 is in the released state, the lift shaft 54 is rotatable, and the rotor 48 only rotates at idle and does not perform compression work.

However, when the manual switch for the air conditioning device is turned on, the solenoid 96 is demagnetized and the stopper protrusion 90 is fitted into the engagement notch 98 of the disc portion 84.
The axis 03 of the rear protrusion 58 coincides with the center line 02 of the rotor chamber 4, and the rear shaft 540 is prevented from rotating in this state.

Therefore, as the front shaft I.64, which is the drive shaft, rotates, the rotor 48 receives the driving force from the front protrusion 74 that draws a rotation locus shown in FIG. 2, and is stopped on the center line 02 of the rotor chamber 4. 1. It is eccentrically rotated around the Collier protrusion 58. In other words, the rotor 48 is eccentric from its own center line by the eccentric amount ef, and the outer peripheral surface of the outer rotor 50 or the vane 44.
46 and the inner circumferential surface of the rotor chamber 4, as shown by the arrows in FIG.
direction toward the adjacent suction port 20.22. After the refrigerant passes through the suction port 20 of the seal portion of the compression work 50 between the inner peripheral surfaces, the refrigerant confined in the area A is compressed and discharged into the discharge chamber 24 through the discharge valve 32, and this compression In parallel with the progress of the refrigerant, the refrigerant is sucked into the compartment space following the area A from the suction port 20.
In the subsequent second half of the rotation process, as shown in FIG. 4, the compression of the refrigerant confined in area B and the suction of the refrigerant from the suction port 22 are performed in parallel. Such a process is repeated.

When the rotor 48 eccentrically rotates to perform compression work, the second
As is clear from the figure and FIG. 4, the front projection 74
The slider 78 reciprocates within the engagement groove 76 of the inner rotor 52. Therefore, the length of the engagement groove 76 must be set equal to or longer than this sliding distance.

Further, as is clear from FIG. 2, the centers of rotation of the rotor 48 in which the engagement groove 76 is formed and the front protrusion 74 that engages with the groove 76 together with the slider 78 are shifted, so that the rotor 48 (this slider 78 slides in the retaining groove 76 as described above, and the front protrusion 74 rotates relative to the slider 78 to some extent).

When the temperature inside the passenger compartment drops below the set value due to the operation of the aforementioned Mauna compressor, the temperature sensor issues a signal, and based on this signal, the solenoid 9 of the stopper device 86 shown in FIG.
6 is excited, the movable iron core 92 is drawn into the holding block 88, and the engagement between the stopper protrusion 90 and the engagement notch 98 is released.

This release is possible by overcoming the frictional force between the stopper protrusion 90 and the engagement notch 98 and the urging force of the spring 94, so the solenoid 96, which has a considerably smaller capacity than the solenoid that operates the electromagnetic clutch, can be used. The engagement between the two can be released.

When the rear shaft 54 is allowed to rotate based on this release of engagement, the rear protrusion 58, which had been stationary on the center line 0□ of the rotor chamber 4 and was the center of eccentric rotation of the rotor 48,
Or, the rotor 48 is mounted around the axis 01 of the rear shaft 54.
The rotor 48 moves to a position concentric with the rear shaft 54 as shown in FIG. C1 inner rotor 5 substantially in contact with the inner circumferential surface
2 is aligned with the axis 0.2 of the rear shaft 54 by the front protrusion 74. It will be rotated around n. At this time,
The front protrusion 74 is located at the groove end without moving relative to the engagement groove 76, and the outer rotor 50 has a tangential direction acting between the inner peripheral surface of the rotor chamber 4 and the tips of the vanes 44, 46. Either it remains stationary due to the frictional force between the inner rotor 52 and the inner rotor 52, or it rotates slightly due to the frictional force between the inner rotor 52 and the viscosity of the lubricating oil. In any case, in this state, the inner rotor 52 simply rotates around the same axis (01) concentrically and integrally with the rear shaft 54 and the front shaft 64, as is clear from FIG. At this time, the rotor 48 is completely stopped and does not rotate eccentrically, so the refrigerant is not compressed or sucked into the rotor chamber 4, and the compressor is in an idling state in which it does no compression work.

Next, another embodiment of the present invention will be described based on FIG.

In this example, in addition to the above example,
A balance weight is provided to ensure dynamic balance during compressor operation. When the rotor 48 eccentrically rotates around the stationary rear protrusion 58, a load WR based on centrifugal force acts on the rotor 48. front shaft 6
A balance weight 104 that generates a load W1 in the opposite direction to the load WR is fixed to the front shaft 6 in the suction chamber 18, and on the outer periphery of the front end surface of the belt pulley 72, A balance weight 106 that generates a load W2 in the same direction as the load WR is fixed. The magnitude of these loads is set to be W2 + WR==W□, and is based on the center of gravity position P (line of action of load W2) of the balance way l-106 in the axial direction of the front shaft 64. load W1.

If the distances to each line of action of WR are el and h, the relative position of the balance weight 104 is determined so as to satisfy the relationship e□・Wl−eR・～■R, and thereby the rotor 48 The dynamic imbalance caused when the compressor rotates eccentrically and performs compression work is corrected.

On the other hand, if the rotor 48 is allowed to rotate, the shaft 5
At idle, when the rotor 48 simply rotates about the axis 01 of the rotor 48, the load does not act on the rotor 48. However, on the outer periphery of the disk portion 84, there are
A balance way l-108 which generates a load W3 in the same direction as the load WR in place of the load WR based on the rotation of the load WR is provided integrally, and there is a distance of 6M1i between the line of action between the load W3 and the load W2. e3 tosleba, el・Wl-4
Balance weight 1 to satisfy the relationship 3.W3
The size and location of 08 are selected. Therefore, the dynamic balance of the entire compressor is maintained even during idle operation.
This is what happens.

In this way, if the dynamic balance is maintained both during compression, when the rotor 48 rotates eccentrically, and during idling, when it simply rotates, vibration and noise will be reduced to a lower level, and both the front and rear shafts 64.54 bearing 68,6
6.56 durability is improved. Since the other points are the same as those in the previous embodiment, the same reference numerals are given to the main members.

Yet another embodiment will be described based on FIG. 6.

In this embodiment, a front protrusion 110 with a circular cross section is eccentrically provided on the front end surface of the inner rotor 52, and a roller 1
12 is rotatably fitted to form a protrusion with a roller, while the front shaft 64 has a thick disc-shaped flange 114 on the side facing the roller chamber 4, and has a t-shape. An engagement groove 116 that engages with the front projection 110 is formed in the flange 114, and the rotation of the front shaft 64 is transmitted to the inner rotor 52 by engagement between the two. The roller 112 of the front protrusion 110 fits into the engagement groove 116 with a slight gap between the groove walls, and is pressed against one of the groove walls by the rotational torque.
The engagement groove 116 is designed to be able to rotate inside the rotor 4.
It has a length that allows the relative movement of the front protrusion 110 during eccentric rotation of the flange 114, and is formed without penetrating to the outer circumferential surfaces on both sides of the flange 114, and the end surface of the flange 114 plays the role of sealing off the rotor chamber 4. Other parts are the same as those in the previous embodiment.Secondly, the same reference numerals are given to the main members and their explanations are omitted, but even with this structure, the embodiment shown in Fig. 1 etc. Substantially the same actions and effects can be obtained.

In FIG. 6, the relationship between the rear protrusion 58 and the rear hole 60 can also be reversed, that is, the inner rotor 52 may be provided with a rear protrusion, and the rear shirt 1-54 may be provided with a rear hole that fits therein. Since there is ample space inside the inner rotor 52, the rear hole 60 of the inner rotor 52 is formed long toward the flange 114 of the rear shaft 64, and the rear protrusion 58
By doing the same, the inner rotor 5 of the fitting length of both
If the ratio of 2 to the axial length is made large, there is an advantage that the rotor 48 can be supported more stably.

Furthermore, in the above embodiment, the front shaft 1 to the shaft were arranged at the same level as the rear shaft, but if they were in relative positions where the rotational force could be transmitted to the rotor through engagement between the front protrusion and the engagement groove, They do not necessarily have to be arranged concentrically; for example, if the front shaft is arranged concentrically with the rotor chamber, the eccentric rotation of the rotor during compression can be made into uniform rotation. In addition, the front protrusion may be of a simple pin type, as in the above-mentioned embodiment, including a sliver or roller, or may be formed integrally with the front shaft or rotor. Even if it is not there, the role can be fulfilled as long as the relative position remains unchanged.

Regarding the rotor, is it desirable to have a structure in which the outer rotor is fitted around the inner rotor so as to be able to rotate relative to each other as explained earlier, or is it necessarily limited to this structure? Instead, they can be made into an integrated structure. In the above explanation, the main compressor that forms the rotor chamber inside is equipped with two inlets and two discharge valves, but if there is at least one of each, compression work can be performed. Therefore, it also covers structures with one vane or three or more vanes.

Further, in order to control the compression work to a state where it is performed or not performed, the rotation prevention device that prevents rotation to the rear shaft 1 is limited to the electromagnetic stopper device exemplified above. It is also possible to use a known blocking means as long as it can block the rotation of the shaft at the rotational phase.

It goes without saying that the present invention may be implemented in various other forms without departing from the scope of the claims.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing a compressor that is an embodiment of the present invention, and is also a sectional view taken along line II in FIG. 2, and FIG. 2 is a nt+ sectional view in FIG. Figure 3 is an exploded perspective view showing a part of the compressor, and Figure 4 is a cross-sectional view illustrating the operation of the compressor during compression operation, corresponding to Figure 2. This is a diagram showing the results. 5(9) and 6 are longitudinal sectional views (partially non-sectional in FIG. 6) of a compressor that is another embodiment of the present invention, and correspond to FIG. 1, respectively. (The symbols are the main ones, and the ones necessary for explanation are shown here). 2: Printer 4: Rotor chamber 6: Front sight play I/8: Rear side plate] 0: Front housing 12: Rear housing (including 2 to 12 above) 14; Main salary of compressor 20.2
2: Suction port 80, 82: Discharge force 44.46: Vane 48: Rotor 50: Outer rotor 52
:Inner rotor 54:Rear shaft 58:Rear protrusion 6
0: Rear hole 64: Front shaft 74.1
10: Front protrusion

Claims (1)

[Scope of Claims] A main body having a rotor chamber with a circular cross section formed inside and having at least one suction port and one discharge valve; a vane provided between the main body, movably held in the radial direction of the rotor chamber by the main body, and biased toward the center of the rotor chamber;
The shaft is provided eccentrically by a certain distance from the center line and is rotatably supported by the main body, and the shaft center of the D'J shaft and the shaft center of the rear shirt 1 are located on the end face facing the rotor chamber of the rear shirt 1. A rear protrusion with a circular cross section, which is provided eccentrically by the amount of eccentricity with respect to the center line of the rotor chamber, has a rear hole and a circle having a radius approximately equal to the value obtained by subtracting the amount of eccentricity from the radius of the rotor chamber. A rotor which is a columnar member and is housed in the rotor chamber and comes into sliding contact with the tip of the vane on its outer peripheral surface, and the eccentric amount t from the center line of the rotor is provided on the end surface of the rotor on the lift shaft side.
a rear hole which is provided eccentrically and rotatably fits into the rear hole, and a rear hole and a rear projection which are provided on the opposite side from the rear projection 1 with the rotor interposed therebetween; and a front shirt l~ provided parallel to the center line of the skeleton rotor, rotatably supported by the front end of the main body, and connected to a driving device 1; radially formed on the other end face facing each other and the front protrusion whose center line during operation draws a rotation locus that includes the rotor chamber center line and the rear shaft axis inside. is,
an engagement groove that engages with the front protrusion to transmit rotation of the front shaft to the rotor; and a rotation prevention device that prevents rotation of the rear shaft when the rear protrusion is aligned with the rotor chamber centerline. When the rear shaft is prevented from rotating, the rotor performs compression work by eccentrically moving around the stationary rear protrusion, and when the rear shaft is allowed to rotate, the rotor performs compression work. Compression is characterized in that the rear shaft simply rotates around the axis and does not perform compression work. Iso.